Air conditioner

Abstract

An air conditioner comprises an indoor unit. The indoor unit comprises a shell and a fan assembly. The shell comprises a first mounting cavity. The fan assembly is arranged in the first mounting cavity and comprises a volute and a fan. The volute comprises a second mounting cavity. The fan is arranged in the second mounting cavity and comprises a motor, a plurality of blades and an impeller. The impeller is connected with the motor and comprises a first connecting part. The first connecting part is connected with the motor, the multiple blades are arranged at intervals in the circumferential direction of the first connecting part, and the first connecting part comprises a first connecting part body and at least one first air guide part. And the at least one first air guide part is arranged along the side wall of the first connecting part body. Wherein the air inlet end of the fan is defined as a first end; one end opposite to the first end along the axial direction of the fan is defined as a second end; the first air guide part inclines relative to the axis of the first connecting part in the direction from the first end to the second end; the contour line of the first air guide part comprises multiple sections of arc lines, and the radiuses of the multiple sections of arc lines are different.

Description

air conditioner

[0001] This application claims priority to patent application No. 202420376646.9 filed on February 28, 2024, and priority to patent application No. 202420376667.0 filed on February 28, 2024; this application claims priority to Chinese patent application No. 202410242081.X filed on March 4, 2024; Chinese patent application No. 202420408583.0 filed on March 4, 2024, and priority to Chinese patent application No. 2024204081.X filed on March 4, 2024 46.9, claims the priority of the Chinese patent application with application number 202311207596.8 filed on September 19, 2023; the priority of the Chinese patent application with application number 202322239118.7 filed on August 21, 2023; the priority of the Chinese patent application with application number 202323308191.1 filed on December 05, 2023; and the priority of the Chinese patent application with application number 202323078399.9 filed on November 15, 2023, all of which are incorporated by reference into this application. Technical Field

[0002] The present disclosure relates to the technical field of air conditioning, and in particular to an air conditioner. Background Art

[0003] Air conditioners are widely used to regulate indoor temperature and consist of an indoor unit and an outdoor unit. The indoor unit is located indoors and is used to heat the indoor air. The indoor unit includes a fan assembly, which drives the indoor air through the air inlet and into the indoor heat exchanger. After the air has been heat exchanged, it flows back into the room.

[0004] Summary of the Invention

[0005] An air conditioner includes an outdoor unit and an indoor unit. The indoor unit is connected to the outdoor unit and includes a housing and a fan assembly. The housing includes a first mounting cavity. The fan assembly is mounted in the first mounting cavity and includes a volute and a fan. The volute includes a second mounting cavity. The fan is mounted in the second mounting cavity and includes a motor, multiple blades, and an impeller. The impeller is connected to the motor and includes a first connecting portion. The first connecting portion is connected to the motor, the multiple blades are spaced apart along the circumference of the first connecting portion, and the first connecting portion includes a first connecting portion body and at least one first air guide portion. The at least one first air guide portion is disposed along a sidewall of the first connecting portion body. The air inlet end of the fan is defined as the first end; the end of the fan opposite the first end along the axial direction of the fan is defined as the second end; the first air guide portion is inclined relative to the axis of the first connecting portion along the direction from the first end to the second end; and the contour of the first air guide portion includes multiple arc segments, each having different radii. BRIEF DESCRIPTION OF THE DRAWINGS

[0006] FIG1 is a structural diagram of an air conditioner according to some embodiments;

[0007] FIG2 is another structural diagram of an air conditioner according to some embodiments;

[0008] FIG3 is a structural diagram of an indoor unit according to some embodiments;

[0009] FIG4 is a velocity cloud diagram when the distance between the air inlet grille and the fan is 70 mm according to some embodiments;

[0010] FIG5 is a velocity cloud diagram when the distance between the air inlet grille and the fan is 30 mm according to some embodiments;

[0011] FIG6 is a structural diagram of a wind turbine according to some embodiments;

[0012] FIG7 is a structural diagram of a volute according to some embodiments;

[0013] FIG8 is a structural diagram of a volute body according to some embodiments;

[0014] FIG9 is a structural diagram of a second air guide portion according to some embodiments;

[0015] FIG10 is a structural diagram of an impeller according to some embodiments;

[0016] FIG11 is another structural diagram of an impeller according to some embodiments;

[0017] FIG12 is a cross-sectional view of a wind turbine according to some embodiments;

[0018] FIG13 is a velocity contour diagram at a first end of a wind turbine according to some embodiments;

[0019] FIG14 is a side view of a plurality of blades according to some embodiments;

[0020] FIG15 is a pressure contour diagram of an impeller according to some embodiments;

[0021] FIG16 is another structural diagram of an impeller according to some embodiments;

[0022] FIG17 is another structural diagram of an impeller according to some embodiments;

[0023] FIG18 is a cross-sectional view along line AA in FIG17;

[0024] FIG19 is a structural diagram of a first air guide portion according to some embodiments;

[0025] FIG20 is another structural diagram of the first air guide portion according to some embodiments;

[0026] FIG21 is another structural diagram of the first air guide portion according to some embodiments;

[0027] FIG22 is a cross-sectional view of another impeller according to some embodiments;

[0028] FIG23 is a noise contour diagram of an impeller according to some embodiments;

[0029] FIG24 is a velocity contour diagram of an impeller according to some embodiments;

[0030] FIG25 is another structural diagram of an indoor unit according to some embodiments;

[0031] FIG26 is another structural diagram of an indoor unit according to some embodiments;

[0032] FIG27 is another structural diagram of an indoor unit according to some embodiments;

[0033] FIG28 is a structural diagram of a first fan assembly according to some embodiments;

[0034] FIG29 is a structural diagram of a volute according to some embodiments;

[0035] FIG30 is a structural diagram of a volute according to some embodiments from another perspective;

[0036] FIG31 is a structural diagram of a second side plate according to some embodiments;

[0037] FIG32 is another structural diagram of a second side panel according to some embodiments;

[0038] FIG33 is a partial enlarged view of the circle A in FIG32;

[0039] FIG34 is another structural diagram of the second side plate according to some embodiments;

[0040] FIG35 is a partial enlarged view of the area circled B in FIG34;

[0041] FIG36 is a structural diagram of a volute tongue according to some embodiments;

[0042] FIG37 is another structural diagram of a volute tongue according to some embodiments;

[0043] FIG38 is a simulation diagram of static pressure distribution of the second side plate in the related art;

[0044] FIG39 is a simulation diagram of static pressure distribution of a second side plate according to some embodiments;

[0045] FIG40 is a simulation diagram of the dipole noise source distribution of the snail tongue in the related art;

[0046] FIG41 is a simulation diagram of the dipole noise source distribution of a snail tongue according to some embodiments;

[0047] FIG42 is a structural diagram of another second side plate according to some embodiments;

[0048] FIG43 is a partial enlarged view of the area circled C in FIG42;

[0049] FIG44 is another structural diagram of another second side plate according to some embodiments;

[0050] FIG45 is a partial enlarged view of the area circled D in FIG44 ;

[0051] FIG46 is another structural diagram of a volute tongue according to some embodiments;

[0052] FIG47 is another structural diagram of a volute tongue according to some embodiments;

[0053] FIG48 is a structural diagram of another indoor unit according to some embodiments;

[0054] FIG49 is a structural diagram of a third air guide portion according to some embodiments;

[0055] FIG50 is a schematic diagram of a path of air flowing through a third air guide portion according to some embodiments;

[0056] FIG51 is a simulation diagram of air flowing through a third air guide portion according to some embodiments;

[0057] FIG52 is a schematic diagram illustrating another path of air flowing through the third air guide portion according to some embodiments;

[0058] FIG53 is a partial enlarged view of FIG52;

[0059] FIG54 is another structural diagram of a third air guide portion according to some embodiments;

[0060] FIG55 is a partial enlarged view of circle E in FIG54;

[0061] FIG56 is a schematic diagram illustrating an arrangement of multiple components according to some embodiments;

[0062] FIG57 is another schematic diagram of an arrangement of multiple components according to some embodiments;

[0063] FIG58 is another schematic diagram illustrating an arrangement of multiple components according to some embodiments;

[0064] FIG59 is another structural diagram of another indoor unit according to some embodiments;

[0065] FIG60 is another structural diagram of another indoor unit according to some embodiments;

[0066] FIG61 is another structural diagram of another indoor unit according to some embodiments;

[0067] FIG62 is an exploded view of a first blower assembly according to some embodiments;

[0068] FIG63 is another structural diagram of the first fan assembly according to some embodiments;

[0069] FIG64 is another structural diagram of the first fan assembly according to some embodiments;

[0070] FIG65 is a cross-sectional view taken along line FF in FIG64;

[0071] FIG66 is a partial enlarged view of the area circled G in FIG65 ;

[0072] FIG67 is a structural diagram of a sealing ring according to some embodiments;

[0073] FIG68 is a partial enlarged view of the area circled H in FIG67;

[0074] FIG69 is another structural diagram of a sealing ring according to some embodiments;

[0075] FIG70 is a partial enlarged view of the area circled in FIG69;

[0076] FIG71 is another structural diagram of a sealing ring according to some embodiments;

[0077] FIG72 is a structural diagram of a second air duct according to some embodiments;

[0078] FIG73 is another structural diagram of a second air duct according to some embodiments;

[0079] FIG74 is a schematic diagram of a first profile line on a coordinate axis according to some embodiments;

[0080] FIG75 is a schematic diagram of a first profile according to some embodiments;

[0081] FIG76 is another schematic diagram of a first profile according to some embodiments;

[0082] FIG77 is a schematic diagram of a second air duct and a fan according to some embodiments;

[0083] FIG78 is another schematic diagram of a second air duct and a fan according to some embodiments;

[0084] FIG79 is another schematic diagram of a second air duct and a fan according to some embodiments;

[0085] FIG80 is a schematic diagram of the vortex flow direction of the second air duct according to some embodiments;

[0086] FIG81 is a block diagram of a fan according to some embodiments;

[0087] FIG82 is another block diagram of a fan according to some embodiments;

[0088] FIG83 is another structural diagram of a fan according to some embodiments;

[0089] FIG84 is a schematic diagram of a velocity triangle according to some embodiments;

[0090] FIG85 is a schematic diagram of an inlet installation angle and an outlet installation angle according to some embodiments;

[0091] FIG86 is another schematic diagram of inlet and outlet mounting angles according to some embodiments;

[0092] FIG87 is a schematic diagram of blade outlet angle adjustment according to some embodiments;

[0093] FIG88 is a structural diagram of yet another indoor unit according to some embodiments;

[0094] FIG89 is another structural diagram of yet another indoor unit according to some embodiments;

[0095] FIG90 is another structural diagram of yet another indoor unit according to some embodiments;

[0096] FIG91 is a structural diagram of a first spoiler according to some embodiments;

[0097] FIG92 is a partial structural diagram of a first spoiler according to some embodiments;

[0098] FIG93 is another structural diagram of a first spoiler according to some embodiments;

[0099] FIG94 is another partial structural diagram of a first spoiler according to some embodiments;

[0100] FIG95 is another structural diagram of a first spoiler according to some embodiments;

[0101] FIG96 is another partial structural diagram of the first gear according to some embodiments;

[0102] FIG97 is a schematic diagram of a first gear and a second gear according to some embodiments;

[0103] FIG98 is another schematic diagram of a first gear and a second gear according to some embodiments;

[0104] FIG99 is an exploded view of a first spoiler according to some embodiments;

[0105] FIG100 is a partial view of a first spoiler without a first gear according to some embodiments;

[0106] FIG101 is another schematic diagram of a first gear and a second gear according to some embodiments;

[0107] FIG102 is another partial structural diagram of the first spoiler without the first gear according to some embodiments;

[0108] FIG103 is another exploded view of a first spoiler according to some embodiments;

[0109] 104 is another exploded view of the first gear and the second gear according to some embodiments. DETAILED DESCRIPTION

[0110] The following will be combined with the accompanying drawings to clearly and completely describe some embodiments of the present disclosure. Obviously, the embodiments described are only some embodiments of the present disclosure, not all embodiments. Based on the embodiments provided by the present disclosure, all other embodiments obtained by ordinary technicians in this field are within the scope of protection of the present disclosure.

[0111] The use of "adapted to" or "configured to" herein is intended to be open and inclusive language that does not exclude devices adapted or configured to perform additional tasks or steps.

[0112] In the description of this application, it should be understood that the terms "center", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on this application.

[0113] In the following, for the convenience of description, unless otherwise specified, the directions of up, down, left, right, front and back in this disclosure are all expressed with reference to the state when the indoor unit is in operation.

[0114] In some embodiments, the air handling device may be an air conditioner, an air purifier, a fresh air blower, or a total heat exchanger. The air handling device includes a fan configured to drive air flow. The fan is, for example, a centrifugal fan.

[0115] In some embodiments, the air handling device is, for example, an air conditioner. As a common household appliance, the air conditioner is widely used in daily life.

[0116] In some embodiments, the air conditioner includes an indoor unit, the indoor unit includes an indoor heat exchanger, and the indoor heat exchanger performs heat exchange between indoor air and the refrigerant transmitted in the indoor heat exchanger to liquefy or vaporize the refrigerant.

[0117] In some embodiments, the air conditioner further includes an outdoor unit. The outdoor unit includes a compressor configured to compress a low-temperature, low-pressure gas-phase refrigerant into a high-temperature, high-pressure gas-phase refrigerant to assist the air conditioner in performing refrigerant circulation.

[0118] The outdoor unit further includes an outdoor heat exchanger configured to liquefy or vaporize the refrigerant by exchanging heat between outdoor air and the refrigerant transferred through the outdoor heat exchanger.

[0119] In some embodiments, the air conditioner further includes an expansion valve configured to regulate the flow of refrigerant within the piping of the air conditioner 100. The refrigerant cycle of the air conditioner is implemented by a compressor, a condenser (either an indoor or outdoor heat exchanger), an expansion valve, and an evaporator (either an outdoor or indoor heat exchanger). The refrigerant cycle includes a series of processes involving compression, condensation, expansion, and evaporation, and circulates the refrigerant to the regulated side.

[0120] After being compressed by the compressor, the low-temperature, low-pressure gas-phase refrigerant becomes a high-temperature, high-pressure gas-phase refrigerant, which then flows into the condenser. The condenser condenses the high-temperature, high-pressure gas-phase refrigerant into a high-pressure liquid-phase refrigerant, releasing heat into the surrounding environment during the condensation process. The expansion valve throttles and reduces the pressure of the high-pressure liquid-phase refrigerant, turning it into a low-pressure gas-liquid two-phase refrigerant. The evaporator absorbs heat from the surrounding environment and evaporates the low-pressure gas-liquid two-phase refrigerant to form a low-temperature, low-pressure gas-phase refrigerant. The low-temperature, low-pressure gas-phase refrigerant returns to the compressor, forming a refrigerant cycle. It should be noted that the indoor and outdoor units of the air conditioner can be integrated into the same housing or installed independently and separately.

[0121] In some embodiments, the indoor unit of the air conditioner is, for example, a floor-standing cabinet unit.

[0122] In some embodiments, as shown in FIG1 , the air conditioner 1000 includes an indoor unit 1100 , which is a unit of the air conditioner 1000 located indoors.

[0123] In some embodiments, the air conditioner further includes an outdoor unit 1200, which is a unit located outdoors of the air conditioner 1000. The indoor unit 1100 and the outdoor unit 1200 are connected by a pipeline to transmit refrigerant.

[0124] It should be noted that FIG1 illustrates an example in which the air conditioner 1000 is a wall-mounted air conditioner, with the indoor unit 1100 mounted on a wall. Of course, the air conditioner 1000 in some embodiments of the present disclosure may also be a floor-standing air conditioner. Furthermore, because the indoor unit 1100 in FIG1 is located indoors, while the outdoor unit 1200 is located outdoors, the outdoor unit 1200 is represented by a dotted line in FIG1 .

[0125] 2 , the outdoor unit 1200 includes a compressor 201. The compressor 201 is configured to compress the refrigerant so that the low-pressure refrigerant is compressed to form a high-pressure refrigerant.

[0126] As shown in Figure 2, the outdoor unit 1200 also includes an outdoor heat exchanger 202. The outdoor heat exchanger 202 is configured to exchange heat between outdoor air and the refrigerant transmitted through the outdoor heat exchanger 202. For example, when the air conditioner 1000 is in cooling mode, the outdoor heat exchanger 202 operates as a condenser, causing the refrigerant compressed by the compressor 201 to condense by dissipating heat to the outdoor air through the outdoor heat exchanger 202. When the air conditioner 1000 is in heating mode, the outdoor heat exchanger 202 operates as an evaporator, causing the decompressed refrigerant to absorb heat from the outdoor air through the outdoor heat exchanger 202 and evaporate. The outdoor heat exchanger 202 is provided with a coil connected to the refrigerant circuit. The refrigerant flows through the coil of the outdoor heat exchanger 202 to exchange heat with the outdoor air.

[0127] As shown in Figure 2, the outdoor unit 1200 also includes an expansion valve 204. The expansion valve 204 is connected between the outdoor heat exchanger 202 and the indoor heat exchanger 20. The opening of the expansion valve 204 regulates the pressure of the refrigerant flowing through the outdoor heat exchanger 202 and the indoor unit 1100, thereby adjusting the refrigerant flow between the outdoor heat exchanger 202 and the indoor heat exchanger 20. The flow and pressure of the refrigerant flowing between the outdoor heat exchanger 202 and the indoor heat exchanger 20 will affect the heat exchange performance of the outdoor heat exchanger 202 and the indoor unit 1100. The opening of the expansion valve 204 is adjustable to control the flow and pressure of the refrigerant flowing through the expansion valve 204. For example, the expansion valve 204 expands the liquid refrigerant condensed in the condenser into a low-pressure liquid refrigerant. It should be noted that some embodiments of the present disclosure are described using the expansion valve 204 as an example. Of course, in some embodiments, the expansion valve 204 may also be provided in the indoor unit 1100 .

[0128] As shown in Figure 2, the outdoor unit 1200 further includes a four-way valve 205. The four-way valve 205 is connected to the refrigerant circuit and is configured to switch the flow direction of the refrigerant in the refrigerant circuit so that the air conditioner 1000 performs cooling mode or heating mode.

[0129] In some embodiments, as shown in Figures 3, 25, and 26, the indoor unit includes a housing 100 (i.e., a casing), which defines a first installation cavity 14. The housing 100 has a top and a bottom at its ends in the height direction. The housing 100 has a left side and a right side at its ends in the length direction. The housing 100 has a front side and a rear side at its ends in the width direction.

[0130] 3 , 25 , and 26 , the housing 100 includes a first air inlet 101 , which is located at the front of the housing 100 and near the bottom of the housing 100 . Indoor air is input into the first installation cavity 14 through the first air inlet 101 .

[0131] In some embodiments, as shown in FIG27 , the first installation cavity includes a first air duct 111, and the first air duct 111 extends along the height direction of the housing 100. Indoor air is heat-exchanged in the first air duct 111 to form conditioned air. It should be noted that the conditioned air can be cold air, hot air, or air at room temperature.

[0132] In some embodiments, the first air outlet 102 is connected to the first air duct 111 , and the air entering the first air duct 111 through the first air inlet 101 is output to the room through the first air outlet 102 .

[0133] In some embodiments, the first air inlet 101 is connected to the first air duct 111 , so that indoor air can enter the first air duct 111 through the first air inlet 101 .

[0134] In some embodiments, while a first air inlet 101 is provided on the front side of the shell 100, a first air inlet 101 may also be provided on at least one of the left or right sides of the shell 100, thereby increasing the air intake volume of the indoor unit 10.

[0135] In some embodiments, as shown in Figures 3 and 25 to 27, the housing 100 further includes a first air outlet 102, which is disposed on the front side of the housing 100 and is closer to the top of the housing 100 than the first air inlet 101. The heat-exchanged air is output to the indoor environment through the first air outlet 102.

[0136] The first air inlet 101 can be respectively arranged on the left and right sides of the housing 100. This not only increases the air intake volume of the indoor unit 10, but also helps to improve the uniformity of the air intake.

[0137] In some embodiments, the housing 100 further includes an air inlet grille 13 , which is disposed at the first air inlet 101 and configured to filter indoor air entering the housing 100 to prevent dust particles from entering the first installation cavity 14 .

[0138] In some embodiments, as shown in FIG3 , the indoor unit further includes a first fan assembly 500 . The first fan assembly 500 is disposed in the first mounting cavity 14 and in the direction of air flow from the first air inlet 101 to the first air outlet 102 . The first fan assembly 500 is configured to drive air from the indoor space into the housing 100 through the first air inlet 101 and, after heat exchange, out through the first air outlet 102 . The first fan assembly 500 includes a fan, which may be, for example, a centrifugal fan, an axial flow fan, or a crossflow fan.

[0139] The following description mainly takes the example that the first fan assembly 500 includes a centrifugal fan.

[0140] 3 , the outdoor unit 1200 further includes an indoor heat exchanger 20. In the airflow direction, the indoor heat exchanger 20 is disposed on the air outlet side of the first fan assembly 500, that is, above the first fan assembly 500.

[0141] In some embodiments, the air inlet side of the first fan assembly 500 is arranged toward the first air inlet 101 , and the air outlet side of the first fan assembly 500 is arranged toward the indoor heat exchanger 20 .

[0142] In some embodiments, the indoor unit further includes a water receiving pan, which is disposed on one side of the indoor heat exchanger 20 along the X direction. For example, the water receiving pan is disposed below the indoor heat exchanger 20 to collect condensed water generated on the surface of the indoor heat exchanger 20 .

[0143] In some embodiments, the indoor unit further includes a drain pipe connecting the water receiving tray with a space outside the housing 100 and configured to drain condensed water in the water receiving tray to the outside of the housing 100 .

[0144] In some embodiments, as indicated by the arrows in Figure 3, when the indoor unit is operating, the first fan assembly 500 operates, allowing indoor air to enter the indoor unit through the air inlet grille 13. The air then flows through the first fan assembly 500 to the indoor heat exchanger 20. After heat exchange with the indoor heat exchanger 20, the air is discharged into the room through the first air outlet 102. The fan assembly includes a centrifugal fan, such as a single-inlet centrifugal fan. During operation, single-inlet centrifugal fans must balance motor heat dissipation, air flow guidance through the wheel, and motor avoidance. The centrifugal fan includes a hub, and the airflow passing through the hub accounts for 45% to 55% of the total inlet airflow. The hub's resistance to airflow reduces the fan's work. The hub includes at least one through-hole, which is configured to assist the fan in dissipating heat. In related art, the through-hole is typically fan-shaped or trapezoidal. While this achieves heat dissipation and reduces resistance, it also leads to problems with airflow guidance by the hub and the generation of intake noise.

[0145] When the first fan assembly 500 is in operation, intake noise may be generated on its air intake side.

[0146] In some embodiments, Figure 4 shows a wind speed (Velocity) cloud diagram on the y-axis (y-component) at a position 70 mm away from the air inlet grille on the air inlet side of the indoor unit's internal fan, and Figure 5 shows a wind speed cloud diagram at a position 30 mm away from the air inlet grille on the air inlet side of the indoor unit. According to Figures 4 and 5, the change in the distance between the air inlet grille 13 and the first fan assembly 500 will cause uneven air intake state of the indoor unit, and thus cause the problem of air intake noise.

[0147] To solve the above problems, some embodiments of the present disclosure provide a first fan assembly 500, which may include a centrifugal fan. For example, the first fan assembly 500 may be a centrifugal fan structure with single-sided air intake, or a centrifugal fan structure with double-sided air intake.

[0148] As shown in FIG. 6 and FIG. 7 , in some embodiments, the first fan assembly 500 includes a volute 400 , and the volute 400 defines a second installation cavity 430 (ie, the installation cavity).

[0149] In some embodiments, as shown in FIG27 to FIG30 , the first fan assembly 500 further includes a fan body 411 . The volute 400 includes a second installation cavity 403 , and the fan body 411 is disposed inside the second installation cavity 403 .

[0150] In some embodiments, as shown in Figures 6, 7, 31, and 32, the volute 400 includes a volute body 450, which may be, for example, a curved structure, and defines the aforementioned second mounting cavity 403 within the volute body 450. The first fan assembly 500 is disposed within the second mounting cavity 403. The second air inlet 401 is disposed in the volute body 450 and communicates with the accommodating cavity 403.

[0151] In some embodiments, the volute body 450 may include a first side plate 410 .

[0152] In some embodiments, the volute body 450 further includes a second side plate 420, and the first side plate 410 is disposed opposite to the second side plate 420. In some embodiments, the inner wall of the volute body 450 is adapted to the airflow path to facilitate airflow.

[0153] In some embodiments, as shown in Figures 6 and 7, the volute 400 further includes a second air guide portion 113 (air guide ring), which is disposed on the second side plate 420. The second air guide portion 113 defines a second air inlet 401, through which air flows into the second installation cavity 430.

[0154] In some embodiments, as shown in FIG7 , the volute 400 further includes a fourth air guide portion 114 , which is defined by a first side plate 410 and a second side plate 420 and is disposed near the indoor heat exchanger 20 . The fourth air guide portion 114 defines a second air outlet 402 , through which air flows out of the second installation cavity 430 .

[0155] For example, the opening direction of the second air inlet 401 is substantially toward the front side of the housing 100 .

[0156] As shown in Figures 25 and 26, the housing 100 further includes a third side panel 1001, which may be referred to as the front panel of the indoor unit 10. The housing 100 further includes a fourth side panel. The third side panel 1001 and the fourth side panel are arranged along the width of the housing 100. The fourth side panel may be referred to as the rear panel of the indoor unit 10.

[0157] In some embodiments, as shown in FIG. 6 , components in the second installation cavity 430 can be installed or repaired through the fourth air guide portion 114 .

[0158] In some embodiments, as shown in Figures 6, 7, and 9, the volute 400 further includes a third air guide portion 600 (exhaust portion), which is disposed at the second air guide portion 113 and is configured to guide airflow to the second mounting cavity 430. For example, the third air guide portion 600 may be a circular ring structure.

[0159] In some embodiments, as shown in FIG9 , the third air guide 600 includes a fixing portion 131 extending along an edge of the body of the third air guide 600. The third air guide 600 is connected to the volute body 450 via the fixing portion 131. For example, the fixing portion 131 may be a circular ring structure.

[0160] In some embodiments, the third air guide portion 600 further includes one or more first clipping portions 133 (snaps), and the first clipping portions 133 are disposed on a side of the fixing portion 131 that faces the volute 400. For example, when the third air guide portion 600 includes multiple first clipping portions 133, the multiple first clipping portions 133 are spaced apart in the circumferential direction of the fixing portion 131.

[0161] In some embodiments, as shown in FIG8 , the volute 400 further includes a second clamping portion 115 (convex portion), which is disposed on a side of the volute 400 near the second mounting cavity 430. The first clamping portion 133 and the second clamping portion 115 are engaged to connect the fixing portion 131 to the volute body 450.

[0162] For example, the volute 400 may include a plurality of second clamping portions 115 . In this case, the first clamping portion 133 and the second clamping portion 115 are provided correspondingly, thereby ensuring the connection stability and reliability between the third air guide portion 600 and the volute 400 .

[0163] In some embodiments, the volute 400 further includes a mounting portion (eg, a through hole), and the first clamping portion 133 extends into the second mounting cavity 430 of the volute 400 through the corresponding mounting portion and is clamped with the corresponding second clamping portion 115 .

[0164] For example, in the assembled state, the fixing portion 131 abuts against the volute 400 .

[0165] In some embodiments, as shown in FIG9 , the third air guide 600 further includes a guide portion 132 . The guide portion 132 extends from a side of the fixing portion 131 near its center, along the first side plate 410 toward the second side plate 420 . That is, the guide portion 132 extends from a side of the fixing portion 131 near its center toward the second mounting cavity 430 . The guide portion 132 is configured to guide the flow of air. For example, the guide portion 132 may be an arc-shaped structure.

[0166] 6 , the first fan assembly 500 further includes a fan 120, which is disposed in the second installation cavity 430 and corresponds to the third air guide portion 600. For example, the fan 120 may be a centrifugal fan.

[0167] In some embodiments, the fan 120 and the third air guide portion 600 are coaxially arranged.

[0168] In some embodiments, when the first fan assembly 500 is a centrifugal fan with a single-side air intake, the fan 120 is a centrifugal fan with a single-side air intake. As shown in Figures 6 and 10, the fan 120 includes an impeller 121 and a plurality of blades 1212. The plurality of blades 1212 are spaced apart along the circumference of the impeller 121.

[0169] 10 and 11 , the impeller 121 further includes a first connection portion 1211 (hub), and a plurality of blades 1212 may be spaced apart along the circumference of the first connection portion 1211. For example, the first connection portion 1211 may be cylindrical with one end closed and the other end open.

[0170] In some embodiments, as shown in FIG10 , the impeller 121 further includes a second connection portion 1213 (first ring), one end of each of the plurality of blades 1212 being connected to the second connection portion 1213 and spaced apart along the circumference of the second connection portion 1213. Thus, the plurality of blades 1212 can be fixed by the second connection portion 1213.

[0171] For example, the first connection portion 1211 is disposed in a space enclosed by the plurality of blades 1212 and the second connection portion 1213 , and is connected to a side of the second connection portion 1213 away from the plurality of blades 1212 .

[0172] In some embodiments, as shown in Figures 10 and 11, the impeller 121 further includes a third connecting portion 1214 (second ring), and the other ends of the plurality of blades 1212 are connected to the third connecting portion 1214. In this way, the second connecting portion 1213 and the third connecting portion 1214 can ensure the reliability of the fixing of the plurality of blades 1212.

[0173] In some embodiments, the first connection portion 1211 , the second connection portion 1213 , the third connection portion 1214 , and the plurality of blades 1212 may be an integral piece.

[0174] In some embodiments, as shown in FIG. 12 , the fan 120 further includes a motor 122 . The motor 122 is connected to the impeller 121 and is configured to drive the fan 120 to operate.

[0175] In some embodiments, the motor 122 includes an output shaft 1221. The motor 122 is disposed in the space enclosed by the first connecting portion 1211. The first connecting portion 1211 is connected to the motor 122. For example, the first connecting portion 1211 is covered by the motor 122, and the motor 122 is connected to the first connecting portion 1211 via the output shaft 1221. When the motor 122 is in operation, the motor 122 drives the impeller 121 to rotate via the output shaft 1221.

[0176] In some embodiments, the motor 122 is connected to the first side plate 410 via fasteners (eg, screws) to achieve connection between the fan 120 and the volute 400 .

[0177] In the assembled state, the second connection portion 1213 of the impeller 121 is close to the first side plate 410 , and the third connection portion 1214 of the impeller 121 forms the air inlet side of the fan 120 .

[0178] In other embodiments, when the first fan assembly 500 is a centrifugal fan structure with double-sided air intake, the fan 120 is a centrifugal fan with double-sided air intake.

[0179] In this case, the volute 400 includes at least one second air guide portion 113. When the at least one second air guide portion 113 includes two second air guide portions 113, one of the two second air guide portions 113 is disposed on the second side plate 420 and defines a second air inlet 401; the other of the two second air guide portions 113 is disposed on the first side plate 410 and defines a third air inlet.

[0180] In other embodiments, the fan 120 includes at least one third air guide portion 600 , and the at least one third air guide portion 600 is respectively connected to the at least one second air guide portion 113 .

[0181] At this time, when the fan 120 is running, the air flow enters from the second air guide portion 113 provided on the first side plate 410 and the second air guide portion 113 provided on the second side plate 420 , merges in the volute 400 , and then flows out from the fourth air guide portion 114 .

[0182] In some embodiments, when the inner circle of the third air guide 600 does not intersect with the first connection portion 1211, a plane perpendicular to the axis of the fan 120 is used as a reference plane. On this reference plane, the side of the third air guide 600 close to the plurality of blades 1212 intersects with the plurality of blades 1212. In this way, under the guidance of the third air guide 600, the efficiency of airflow to the impeller 121 can be ensured.

[0183] It should be noted that, in some embodiments, the positive projection of the multiple blades 1212 on the reference plane is located outside the range defined by the side of the third air guide portion 600 close to the multiple blades 1212. At this time, the air flow can flow to the impeller 121, but the air volume at the impeller 121 is less than the preset air volume and cannot meet the indoor unit's demand for air volume.

[0184] In other embodiments, the positive projections of the multiple blades 1212 on the reference plane are located within the range defined by the side of the third air guide portion 600 close to the multiple blades 1212. At this time, part of the airflow will be dispersed outside the impeller 121, reducing the amount of air flowing to the impeller 121.

[0185] In some embodiments, as shown in FIG. 12 , the maximum outer diameter of the plurality of blades 1212 is defined as a first dimension D0 ; and the inner diameter of the third air guide portion 600 is defined as a second dimension D1 .

[0186] When the ratio D1 / D0 is less than the first preset threshold, the air intake of the first fan assembly 500 will be reduced, thereby reducing the operating efficiency of the air conditioner. For example, the first preset threshold may be 0.83.

[0187] In some embodiments, D1 and D0 satisfy: D1 ≥ 0.83D0, that is, D1 / D0 ≥ 0.83. In this way, the air intake volume of the first fan assembly 500 can be guaranteed, and the working efficiency of the air conditioner can be guaranteed.

[0188] When the D1 / D0 ratio is greater than a second preset threshold, part of the airflow passing through the third air guide 600 may flow outside the range defined by the maximum outer diameter of the plurality of blades 1212. This airflow may generate airflow impact when entering the impeller 121, resulting in increased airflow noise. For example, the second preset threshold may be 0.91.

[0189] In some embodiments, D1 and D0 further satisfy: D1≤0.91D0, that is, D1 / D0≤0.91. In this way, the air intake noise of the air conditioner can be reduced.

[0190] In some embodiments, the first dimension D0 and the second dimension D1 satisfy a first relationship, wherein the first relationship is: 0.83≤D1 / D0≤0.91.

[0191] In some embodiments, the dimension of the impeller 121 along its axial direction (eg, the M direction in FIG. 12 ) is defined as H1.

[0192] In some embodiments, the relationship between H1 and the first size D0 satisfies formula (1).

[0193] Wherein, Q is the volume flow rate in the working range of the fan 120; ω is the angular velocity of the fan 120, and ω can be any value in [41, 63]; n is a constant, and n can be any value in [0.4, 1.2].

[0194] In some embodiments, the first size D0 is any value in [300 mm, 400 mm], for example, D0 is 300 mm, 310 mm, 350 mm, 380 mm or 400 mm. In this case, Q is [1000 mm 3 / h, 2400m 3 / h], for example, Q is 1000m 3 / h、1200m 3 / h、1400m3 / h、1800m 3 / h、2000m 3 / h or 2400m 3 / h, etc.

[0195] In this way, when the first dimension D0 is determined, the size range of the impeller 121 along its axial direction can be determined according to formula (1).

[0196] When H1 and D0 satisfy formula (1), the speed and airflow rate of the fan 120 meet the requirements, which is conducive to ensuring the working performance of the fan 120.

[0197] In some embodiments, in the axial direction of the fan 120 , the distance between the fan 120 and the side of the third air guide 600 close to each other is defined as X1 , and the relationship between X1 and H1 satisfies formula (2).

[0198] Wherein, Q is the volume flow rate of the fan 120 in the working range, and φ is the pressure coefficient.

[0199] It should be noted that if the axial distance between the third air guide 600 and the fan 120 is less than the first preset distance, vibration and impact may cause the third air guide 600 and the fan 120 to collide. If the axial distance between the third air guide 600 and the fan 120 is greater than the second preset distance, airflow leakage may occur. Therefore, when X1 is set according to formula (2), the airflow guiding effect of the axial distance between the third air guide 600 and the fan 120 can be guaranteed.

[0200] In some embodiments, as shown in FIG12 , the distance between the side of the fan 120 closer to the second air guide 113 and the side of the second air guide 113 farther from the fan 120 in the axial direction of the fan 120 is defined as X2. Then, X1 and X2 satisfy the following equation: X2 = X1 + D. Where D is a constant, for example, any value in the range [5 mm, 12 mm], such as 5 mm, 6 mm, 8 mm, 10 mm, or 12 mm.

[0201] In some embodiments, as shown in FIG12 , the inner diameter of the second air guide 113 is defined as a third dimension D2. The ratio D2 / D1 of the third dimension D2 to the second dimension D1 is any value in the range [0.90, 1.50]. For example, D2 / D1 is any value in the range [1.06, 1.29]. D2 / D1 can be 1.06, 1.10, 1.20, or 1.29.

[0202] In some embodiments, the third dimension D2 and the second dimension D1 further satisfy the following: D2 = D1 + 2D, where D is consistent with D in the above relationship between X1 and X2.

[0203] In some embodiments, the radius of the guide portion 132 of the third air guide portion 600 is defined as R1, and R1 is any value between [16 mm, 30 mm]. For example, R1 is 16 mm, 20 mm, 26 mm, or 30 mm.

[0204] FIG13 shows the flow state of the airflow after the parameters of the first fan assembly 500 are improved. Table 1 is a relationship table of the air volume and noise of the fan assembly in the related art and the first fan assembly 500 provided in some embodiments of the present disclosure.

[0205] Table 1 Relationship between air volume and noise of fan components

[0206] As can be seen from FIG13 and Table 1, at the same speed, the first fan assembly 500 in the embodiment of the present disclosure has a flow rate increased by 10 to 20 m / s compared to the fan in the related art. 3 / h, while reducing intake noise. Here, CMH is the abbreviation of Cube Meter Hour, which means cubic meters per hour (m3 / h).

[0207] In some embodiments, along the axial direction of the fan 120, the end of the fan 120 away from the first side plate 410 is defined as the first end, and the end closer to the first side plate 410 is defined as the second end. Along the axial direction of the fan 120, the first end is, for example, the air inlet end of the fan 120, and the second end is, for example, the end opposite to the air inlet end along the axial direction of the fan 120.

[0208] In some embodiments, as shown in Figures 14 and 15 , two adjacent blades 1212 among the plurality of blades 1212 are defined as a first sub-blade and a second sub-blade. The radius of the rounded corner of the end surface of the first sub-blade near the first end of the fan 120 is defined as R2, and the radius of the rounded corner of the end surface of the second sub-blade near the first end of the fan 120 is defined as R3, where R2 is not equal to R3. This reduces the impact of airflow on the plurality of blades 1212, ensuring smooth and uniform airflow and reducing intake noise of the first fan assembly 500.

[0209] In some embodiments, as shown in FIG16 , the first connecting portion 1211 includes a first connecting portion body. The first connecting portion body includes a first wall 12111 and a second wall 12112. If the first connecting portion 1211 is cylindrical with one end closed and the other end open, the first wall 12111 and the second wall 12112 are connected. The second wall 12112 is a side wall of the first connecting portion 1211.

[0210] In some embodiments, as shown in FIG17 , the first connecting portion 1211 further includes one or more first air guides 200 (e.g., through holes), with the plurality of first air guides 200 spaced apart along the second wall 12112. The first air guides 200 can be spaced apart along the sidewalls of the first connecting portion 1211 and inclined relative to the axis of the first connecting portion 1211 from the first end to the second end. For example, the first air guides 200 can extend in a direction consistent with the direction of rotation of the fan 120. This helps improve the air flow guiding efficiency of the first air guides 200.

[0211] In some embodiments, as shown in Figures 17 and 18 , the contour of the first air guide 200 includes one or more arc segments, each having different radii. This allows the first air guide 200 to have an irregular shape, thereby suppressing intake noise while ensuring low wind resistance at the first connecting portion 1211.

[0212] It should be noted that, by making the contour line of the first air guide portion 200 include an arc line, the air guide efficiency of the first air guide portion 200 can be improved.

[0213] In some embodiments, as shown in FIG19 , a reference line of the first air guide 200 is defined as LP0. Along the center line LP0, the width of the first air guide 200 increases and then decreases from the first end to the second end. A plane perpendicular to the axis of the fan is used as a projection reference plane. In the orthographic projection of the projection reference plane, the reference line of the first air guide 200 is the line that bisects its area.

[0214] In some embodiments, the contour line of the first air guide portion 200 includes a first arc line 210 disposed near the first end.

[0215] In some embodiments, the contour of the first air guide 200 further includes a second arc 220 disposed near the second end, and the radius of the second arc 220 is greater than the radius of the first arc 210. In this way, the shape of the first air guide 200 can be made irregular, which is conducive to suppressing noise.

[0216] In some embodiments, the outline of the first air guide portion 200 further includes a first connecting line 230. The first connecting line 230 is located on one side of the center line LP0 of the first air guide portion 200 and is connected between the first arc line 210 and the second arc line 220. The first connecting line 230 can be a single arc line or can include multiple arc lines.

[0217] In some embodiments, the outline of the first air guide portion 200 further includes a second connecting line 240, which is located on the other side of the center line LP0 of the first air guide portion 200 opposite to the one side, and the second connecting line 240 is connected between the first arc line 210 and the second arc line 220. The second connecting line 240 can be a single arc line, or can include multiple arc lines connected in sequence.

[0218] In some embodiments, the first connection line 240 and the second connection line 240 protrude along one side away from each other.

[0219] In some embodiments, the first connecting line 230 is a segment of an arc line, and the second connecting line 240 includes multiple segments of an arc line.

[0220] In some embodiments, as shown in Figure 20, the line connecting the center of the first arc line 210 and the center of the second arc line 220 is defined as LP1, and the first connecting line 230 and the second connecting line 240 are asymmetric relative to the line LP1. In this way, the irregularity of the first air guide portion 200 can be increased, thereby suppressing the generation of noise.

[0221] For example, the line symmetrical to the line LP1 of the first connecting line 230 is defined as LP1', and the second connecting line 240 can be obtained by stretching the line LP1' in a direction away from the first connecting line 230. In this way, while achieving an irregular design of the first air guide portion 200, the area of ​​the first air guide portion 200 is increased, thereby improving the airflow guiding effect and heat dissipation effect of the first connecting portion 1211.

[0222] It can be understood that the line LP1 ′ is located on a side of the second connection line 240 close to the first connection line 230 , that is, the line LP1 ′ is located inside the first air guide portion 200 .

[0223] In some embodiments, referring to FIG. 19 , the second connection line 240 includes a third arc line 241 , and the third arc line 241 is located on a side of the second connection line 240 close to the first end.

[0224] In some embodiments, the second connecting line 240 further includes a fourth arc line 242 located on a side of the second connecting line 240 close to the second end, that is, the fourth arc line 242 is closer to the second end than the third arc line 241 .

[0225] In some embodiments, the second connecting line 240 further includes a fifth arc line 243 . In this case, the fifth arc line 243 is located between the third arc line 241 and the fourth arc line 242 , and is connected to the third arc line 241 and the fourth arc line 242 , respectively.

[0226] If the ratio of H2 to H1 is greater than a first predetermined ratio, the first air guide 200 may be closer to the first end of the first connecting portion 1211, thereby affecting the air flow and heat dissipation at the second end of the first connecting portion 1211. In some embodiments, the first predetermined ratio is, for example, 0.39. If the ratio of H2 to H1 is less than a second predetermined ratio, the second arc line 220 may extend to the second connecting portion 1213, thereby damaging the integrity of the plurality of blades 1212. In some embodiments, the second predetermined ratio is, for example, 0.21.

[0227] In some embodiments, as shown in FIG18 , the distance between the center of the second arc line 220 and the first side plate 410 along the axial direction of the fan 120 is defined as H2. That is, the distance between the center of the second arc line 220 and the end surface of the impeller 121 near the second end is H2. Then, H1 and H2 satisfy the following relationship: H2 = (0.21-0.39) H1. This determines the position of the first air guide 200 on the first connecting portion 1211.

[0228] In some embodiments, as shown in Figures 18, 19 and 21, along the axial direction of the fan 120, the distance between the center of the first arc line 210 and the center of the fourth arc line 242 is defined as d1; the distance between the center of the first arc line 210 and the center of the second arc line 220 is defined as d3.

[0229] Along the radial direction of the fan 120 (direction N in FIG. 18 ), the distance between the center of the fourth arc line 242 and the center of the second arc line 220 is defined as d2; the distance between the center of the first arc line 210 and the center of the second arc line 220 is defined as d4. Then, d1 and d2 satisfy: d2 = (0.91-1.14) d1; d1 and d3 satisfy: d1 = (0.68-1.04) d3; d3 and d4 satisfy:

[0230] When the ratio of H1 to the first dimension D0 is greater than a third predetermined ratio, the air intake volume can be increased, but due to the larger axial dimensions of the multiple blades, the generated intake noise increases. In some embodiments, the third predetermined ratio is, for example, 0.67. When the ratio of H1 to the first dimension D0 is less than a fourth predetermined ratio, the intake noise is reduced, but due to the smaller axial dimensions of the multiple blades, the air intake volume decreases. In some embodiments, the fourth predetermined ratio is, for example, 0.41.

[0231] In some embodiments, the first dimensions D0 and H1 further satisfy: H1 = (0.41-0.67) D0. In this way, the air intake volume can be increased and the intake noise can be reduced.

[0232] In some embodiments, the radius of the first arc line 210 is defined as r1, and r1 satisfies: r1 = (0.9-2.2)e (1.4～3) mm.

[0233] In some embodiments, the radius of the fourth arc line 242 is defined as r2, and r2 satisfies: r2 = (0.9-2.2)e (1.4～3) mm.

[0234] In some embodiments, the radius of the second arc line 220 is defined as r3, and r3 is any value between 18 and 36 mm, for example, 18 mm, 20 mm, 25 mm, 30 mm, 35 mm, or 36 mm.

[0235] If the ratio of the radius r4 of the first connecting line 230 to the first dimension D0 is greater than a fifth predetermined ratio, the structural strength of the first air guide 200 is weak and prone to deformation. The fifth predetermined ratio is, for example, 0.75. If the ratio of the radius r4 of the first connecting line 230 to the first dimension D0 is less than a sixth predetermined ratio, the area of ​​the first air guide 200 is small, hindering airflow and resulting in high noise. The sixth predetermined ratio is, for example, 0.3.

[0236] In some embodiments, the radius of the first connecting line 230 is defined as r4, and r4 and the first dimension D0 satisfy: r4=(0.3-0.75)D0.

[0237] In some embodiments, the radius of the third arc line 241 is defined as r5, and the radius of the fifth arc line 243 is defined as r6, then r5 and r6 satisfy: And r6 and r4 satisfy: r6 = (0.3 ~ 0.75) r4.

[0238] In some embodiments, the first connecting portion 1211 includes an odd number of first air guides 200, such as 3, 5, or 7, and the number of the first air guides 200 is coprime with the number of the blades 1212. In this way, the noise generated by the blades 1212 can be reduced.

[0239] In some embodiments, as shown in FIG22 , the size of the second connection portion 1213 increases from the first end to the second end. For example, the second connection portion 1213 is in the shape of an increasing arc from the first end to the second end of the fan 120. This improves the airflow guidance effect at the second end of the fan 120, facilitates airflow, and reduces noise.

[0240] In some embodiments, the second connection portion 1213 is connected to a side of the first connection portion 1211 close to the second end. For example, the second connection portion 1213 is disposed on an extension line of the side of the first connection portion 1211 close to the second end.

[0241] In some embodiments, the left side of Figure 23 shows an impeller in some embodiments of the present disclosure, and the right side shows an impeller in the related art. In some embodiments of the present disclosure, the noise generated by the improved impeller 121 is reduced compared to the noise generated by the impeller in the related art.

[0242] In some embodiments, the left side of Figure 24 is an impeller shown in some embodiments of the present disclosure, and the right side is an impeller shown in the related art. In some embodiments of the present disclosure, after improving the impeller 121, the airflow near the first connection part is more orderly than the airflow near the first connection part in the related art, which is beneficial to improving the diversion effect.

[0243] In some embodiments, the fan 120 in some embodiments of the present disclosure is actually tested in an air conditioner. The air volume is increased by 8% compared with the related art at the same speed.

[0244] Table 2 Relationship between fan diameter and noise

[0245] As shown in Table 2, the fan 120 of the present disclosure increases air volume while reducing the centrifugal fan diameter by 2.5%. While maintaining the same target air volume, the noise level can be reduced by 2dB(A). This facilitates the integration of the fan 120 into the overall machine and reduces weight by 12%.

[0246] In some embodiments, as shown in FIG25 , the housing 100 further includes an air deflector 200 (wind shield). The air deflector 200 is disposed at the first air outlet 102 and can be opened and closed to open or close the first air outlet 102, thereby adjusting the air volume of the air conditioner 1000. For example, the housing 100 may include one or more air deflectors 200.

[0247] In some embodiments, as shown in FIG2 , the indoor unit 10 includes an indoor heat exchanger (HE) 300 . The indoor heat exchanger 300 is configured to exchange heat between indoor air and the refrigerant transmitted through the indoor heat exchanger 300 . For example, in the cooling mode of the air conditioner 1000 , the indoor heat exchanger 300 operates as an evaporator, causing the refrigerant, after dissipating heat through the outdoor heat exchanger 202 , to absorb heat from the indoor air through the indoor heat exchanger 300 and evaporate. In the heating mode of the air conditioner 1000 , the indoor heat exchanger 300 operates as a condenser, causing the refrigerant, after absorbing heat through the outdoor heat exchanger 202 , to dissipate heat to the indoor air through the indoor heat exchanger 300 and condense. The indoor heat exchanger 300 is provided with a coil connected to the refrigerant circuit. The refrigerant flows through the coil of the indoor heat exchanger 300 to exchange heat with the indoor air.

[0248] As shown in Figure 27, the indoor heat exchanger 300 is disposed within the housing 100 and within the first passage 111. The indoor heat exchanger 300 is located near the top of the housing 100 and near the first air outlet 102. The air within the first passage 111 exchanges heat with the indoor heat exchanger 300 to form conditioned air, meeting cooling or heating needs.

[0249] In some embodiments, as shown in Figures 2 and 27, the indoor unit 10 further includes a fan assembly 500. The fan assembly 500 is disposed within the housing 100 and near the bottom of the housing 100. The fan assembly 500 is positioned near the first air inlet 101. The fan assembly 500 draws indoor air from the first air inlet 101 into the first passage 111. The indoor air is then heat-exchanged in the indoor heat exchanger 300 to form conditioned air, which then flows into the room through the first air outlet 102.

[0250] For example, the fan assembly 500 includes a centrifugal fan, an axial flow fan, or a cross flow fan. The following mainly describes the fan assembly 500 as including a centrifugal fan as an example.

[0251] In some embodiments, as shown in FIG27 to FIG30 , the fan assembly 500 includes a volute 400 . The volute 400 is located in the first accommodating cavity 112 and is disposed near the bottom of the housing 100 .

[0252] In some embodiments, as shown in FIG27 to FIG30 , the fan assembly 500 further includes a fan body 411 , and the volute 400 includes a second accommodating chamber 403 (accommodating chamber). The fan body 411 is disposed inside the second accommodating chamber 403 .

[0253] In some embodiments, as shown in FIG29 , the volute 400 includes a second air inlet 401 (volute air inlet). The second air inlet 401 is connected to the second accommodating chamber 403 , and the second air inlet 401 is connected to the first air inlet 101 and is correspondingly arranged so that indoor air enters the interior of the volute 400 from the first air inlet 101 through the second air inlet 401.

[0254] For example, the opening direction of the second air inlet 401 is substantially toward the front side of the housing 100 .

[0255] In some embodiments, as shown in Figures 28 to 30, the volute 400 further includes a second air outlet 402 (volute air outlet). The second air outlet 402 is close to the indoor heat exchanger 300, and the air inside the volute 400 is output from the second air outlet 402 and exchanges heat with the indoor heat exchanger 300 to form the conditioned air.

[0256] For example, the opening direction of the second air outlet 402 is substantially toward the top of the housing 100 .

[0257] In some embodiments, as shown in Figures 31 and 32, the volute 400 further includes a volute body (body) 450, and the volute body 450 (spiral section) defines a second accommodating chamber 403. The fan assembly 500 is disposed in the second accommodating chamber 403. The second air inlet 401 is disposed in the volute body 450 and communicates with the accommodating chamber 403.

[0258] In some embodiments, the inner wall of the volute body 450 is adapted to the airflow path to facilitate airflow.

[0259] It should be noted that after the fan assembly 500 drives the air into the second accommodating chamber 403 , the air flow path is roughly spiral, and when the air flows in the second accommodating chamber 403 , the air easily contacts the inner wall of the volute body 450 .

[0260] In some embodiments, as shown in FIG29 and FIG30 , the volute 400 further includes a first side plate 410 (front plate). The second air inlet 401 is provided on the first side plate 410 , and the first side plate 410 is close to the third side plate 1001 .

[0261] In some embodiments, as shown in Figures 29 to 31 , the volute 400 further includes a second side plate 420 (enclosing plate). The second side plate 420 is connected to the first side plate 410 and is located on a side of the first side plate 410 away from the third side plate 1001. For example, a first end of the second side plate 420 is connected to the first side plate 410, and a second end of the second side plate 420 extends away from the first side plate 410.

[0262] In some embodiments, as shown in Figures 31 and 32, the second side plate 420 includes an air outlet section 440, and the volute 400 also includes a second channel (air outlet duct) 404. The air outlet section 440 is connected to the volute body 450, and the second channel 404 is formed in the air outlet section 440. The first end of the second channel 404 is connected to the second accommodating chamber 403, and the second end of the second channel 404 is connected to the first channel 111, so that air in the second accommodating chamber 403 passes through the second channel 404 and enters the first channel 111 for heat exchange. The second air outlet 402 is formed in the air outlet section 440, so that the second air outlet 402 is connected to the second channel 404.

[0263] In some embodiments of the present disclosure, the side of the second side panel 420 away from the first side panel 410 is connected to the fourth side panel of the shell 100, so that the second side panel 420 and the fourth side panel of the shell 100 can enclose a second accommodating cavity 403 and a second channel 404 to limit the flow path of the airflow and improve the stability and reliability of the airflow.

[0264] The fan assembly 500 drives the indoor air from the first air inlet 101 through the second air inlet 401 into the second accommodating chamber 403 , and then flows out through the second channel 404 to exchange heat with the indoor heat exchanger 300 .

[0265] It should be noted that the second side plate 420 and the first side plate 410 enclose a second accommodating cavity 403 and a second channel 404 , and the second side plate 420 and the fourth side plate of the housing 100 further enclose a second air outlet 402 .

[0266] In some embodiments, as shown in FIG. 31 and FIG. 32 , the air outlet section 440 includes a first section 441 (an extension section), and the first section 441 is connected to the first end of the volute body 450 .

[0267] In some embodiments, as shown in Figures 31 and 32, the outlet section 440 further includes a second section 442 (expansion section). The second section 442 is connected to the second end of the volute body 450 and is disposed correspondingly to the first section 441 to form a second passage 404 with the first section 441. The second section 442 extends away from the volute body 450 and the first section 441.

[0268] In some embodiments, at least one of the first section 441 and the second section 442 is planar, and the second section 442 forms an angle with the first section 441. As shown in Figures 31 and 32, the distance H1 between the first section 441 and the second section 442 increases along the direction of the second passage 404 away from the second accommodating chamber 403, thereby improving the efficiency of airflow out of the volute 400.

[0269] In some embodiments, as shown in Figures 30 and 31 , the volute 400 further includes a volute tongue 430. The volute tongue 430 is provided on the inner wall of the volute 400 and is configured to guide the air in the second accommodating chamber 403 to flow toward the second channel 404.

[0270] In some embodiments, the volute tongue 430 is provided on the second side plate 420 and is located at the connection between the second section 442 and the volute body 450. In this way, the volute tongue 430 is convenient for guiding the flow of air.

[0271] In some embodiments, the volute tongue 430 extends from the first end of the second side plate 420 to the second end of the second side plate 420. As shown in FIG31 , the position of the volute tongue 430 closest to the first section 441 is the top of the volute tongue 430, and the top of the volute tongue 430 is the position where the distance between the second section 442 and the first section 441 is the smallest.

[0272] In some embodiments, a predetermined distance is provided between the volute tongue 430 and the fan assembly 500 to improve the reliability of the fan assembly 500. Furthermore, the gap between the volute tongue 430 and the fan assembly 500 (e.g., centrifugal fan 501) can be referred to as a volute tongue gap. FIG31 illustrates the minimum value b of the volute tongue gap.

[0273] It should be noted that during the operation of the fan assembly 500, periodic pressure pulsations are generated near the blades within the fan assembly 500, resulting in blade passing frequency (BPF) noise. When air flows, BPF noise may be caused by uneven flow fields and irregular flow paths. Here, uneven and irregular flow fields can refer to uneven air flow rates, large pressure gradient variations, and turbulent air flow.

[0274] When air flows through the volute tongue 430, a portion of the airflow is cut off by the volute tongue 430, converting static pressure into dynamic pressure, which then passes through the second channel 404 and exits the second accommodating chamber 403 through the second air outlet 402. The remaining portion of the airflow returns through the volute tongue 430 to the second accommodating chamber 403 to participate in the next power cycle. During this process, if the volute tongue gap is too small, the volute tongue 430 will be subjected to a greater impact of the airflow, resulting in more severe pressure pulsation and a higher blade vibration frequency, thus producing a sharp whistling sound, i.e., blade pass frequency noise. Although increasing the volute tongue gap can reduce blade pass frequency noise, increasing the volute tongue gap will also weaken the channel's power performance.

[0275] In some embodiments, as shown in Figures 33 to 36 , the volute 400 further includes at least one flow guide 460, and at least one flow guide 460 is disposed on the windward side of the volute tongue 430. The at least one flow guide 460 protrudes or is recessed from the windward surface of the volute tongue 430. The provision of the flow guide 460 can change the shape of the windward surface of the volute tongue 430, and airflow is refracted or scattered when passing through the windward surface of the volute tongue 430, or sound waves are refracted when passing through the windward surface of the volute tongue 430, thereby making the airflow process more complex, reducing sound energy, and achieving a noise reduction effect.

[0276] In some embodiments, the guide portion 460 extends from the first end of the second side plate 420 to the second end of the second side plate 420 so that the guide portion 460 has a larger contact area with the airflow, thereby improving the noise reduction effect.

[0277] In some embodiments, the guide portion 460 is disposed near the top of the volute tongue 430 , so that the guide portion 460 can contact the airflow entering the second channel 404 from the second accommodating cavity 403 .

[0278] In some embodiments, the at least one flow guide 460 includes a plurality of flow guides 460. The plurality of flow guides 460 are distributed in an array from the end where the volute tongue 430 is connected to the volute body 450 to the end where the volute tongue 430 is connected to the second section 442. In this way, the effect of the flow guide 460 on the airflow can be increased.

[0279] In some embodiments, as shown in Figures 31 and 37 , the volute tongue 430 includes a transition surface 439 (transition windward surface). This transition surface 439 is located on the windward side of the volute tongue 430 and is an arc-shaped surface. The transition surface 439 includes a first arc line 431 (a first volute tongue arc line), which is the intersection line between the transition surface 439 and the fourth side panel of the housing 100. For example, along the width direction of the housing 100, the orthographic projection of the end of the transition surface 439 away from the first side panel 410 onto a reference plane is the first arc line 431, and the arc length of the first arc line 431 is the first arc length R. The reference plane is a plane parallel to the third side panel 1001.

[0280] In some embodiments, as shown in Figures 32 to 35, the guide portion 460 includes a first guide portion 481. The first guide portion 481 protrudes from the windward surface of the volute tongue 430. For example, the windward surface of the volute tongue 430 can be stepped.

[0281] In some embodiments, the first air guide portion 481 is located at the midpoint of the first arc line 431 to increase the effect of the air guide portion 460 on the airflow.

[0282] In some embodiments, as shown in FIG33 , the windward surface of the volute tongue 430 includes a first curved surface 432. The first curved surface 432 includes a third arc line 436, which is the intersection line between the first curved surface 432 and the fourth side panel of the housing 100. For example, in the width direction of the housing 100, the orthographic projection of the end of the first curved surface 432 away from the first side panel 410 on the reference plane is the third arc line 436.

[0283] It should be noted that, as shown in Figure 37, when the volute tongue 430 is provided with a first guide portion 481, the shape of the windward surface becomes complicated, and the windward surface of the volute tongue 430 can still intersect with the fourth side panel of the shell 100 to form a first arc line 431. However, the first arc line 431 in the volute tongue 430 is a theoretical curve and not an actual curve.

[0284] As shown in Figure 37, the third arc line 436 does not overlap with the first arc line 431. In this way, when the volute tongue 430 is provided with the first guide portion 481, the distance between the windward surface of the volute tongue 430 and the first section 441 is greater than or equal to the distance between the windward surface of the volute tongue 430 and the first section 441.

[0285] In some embodiments, as shown in FIG. 37 , the distance that the first air guide portion 481 protrudes from the windward surface of the volute tongue 430 is a first distance, and the first distance is the thickness t of the first air guide portion 481 .

[0286] If the thickness t of the first guide portion 481 is less than 0.11 times the minimum gap b of the volute tongue 430 (t<0.11b), the thickness t of the first guide portion 481 will be too small. In this way, fewer sound waves will be refracted when passing through the windward surface of the volute tongue 430, reducing the noise reduction effect of the first guide portion 481.

[0287] In some embodiments, the thickness t of the first air guide portion 481 is greater than or equal to 0.11 times the minimum gap b of the volute tongue 430 (t ≥ 0.11b). In this way, the thickness t of the first air guide portion 481 can be increased, making the airflow movement process more complex and improving the noise reduction effect of the first air guide portion 481.

[0288] If the thickness t of the first air guide portion 481 is greater than 0.18 times the minimum gap b of the volute tongue 430 (t is greater than 0.18b), the thickness b of the first air guide portion 481 will be too large, which will also reduce the noise reduction effect of the first air guide portion 481.

[0289] In some embodiments, the thickness t of the first air guide portion 481 is less than or equal to 0.18 times the minimum gap b of the volute tongue 430 (t≤0.18b). In this way, when the airflow passes through the first air guide portion 481, the airflow is facilitated.

[0290] It should be noted that the minimum gap b of the volute tongue 430 may also be referred to as a first gap.

[0291] In some embodiments, by drafting the first guide portion 481, the distance between the side of the first guide portion 481 close to the volute body 450 and the side of the first guide portion 481 away from the volute body 450 is increased along the direction from the first side panel 410 to the fourth side panel of the shell 100 (such as the front-to-back direction).

[0292] In some embodiments, as shown in FIG36 , the volute tongue 430 further includes a first sub-volute tongue 421 and a second sub-volute tongue 422. The first end of the first sub-volute tongue 421 is connected to the volute body 450, and the second end of the first sub-volute tongue 421 is connected to the first end of the first flow guide portion 481. The first end of the second sub-volute tongue 422 is connected to the second section 442, and the second end of the second sub-volute tongue 422 is connected to the second end of the first flow guide portion 481.

[0293] The side of the first air guide portion 481 near the volute body 450 intersects with the first sub-volute tongue 421 to form a first angle α1. For example, the first tangent line and the second tangent line intersect to form the first angle α1. The first tangent line is a tangent line that passes through any point on the intersection line between the first sub-volute tongue 421 and the first air guide portion 481 and is tangent to the first sub-volute tongue 421. The second tangent line is a tangent line that passes through any point on the intersection line between the first sub-volute tongue 421 and the first air guide portion 481 and is tangent to the first air guide portion 481.

[0294] It should be noted that the first angle α1 can be determined according to different shapes of the volute tongue 430 .

[0295] If the first angle α1 is less than 30° (α1<30°), the portion of the first guide portion 481 close to the volute body 450 protruding from the windward surface of the volute tongue 430 will be too small, thereby reducing the noise reduction effect of the first guide portion 481.

[0296] In some embodiments, the first angle α1 is greater than or equal to 30° (α1 ≥ 30°). This allows the portion of the first air guide 481 protruding from the windward surface of the volute tongue 430 near the volute body 450 to be increased, thereby facilitating refraction or scattering of airflow as it passes through the windward surface of the volute tongue 430, thereby enhancing the noise reduction effect of the first air guide 481.

[0297] If the first angle α1 is greater than 45° (α1>45°), the portion of the first guide portion 481 close to the volute body 450 will protrude too much from the windward surface of the volute tongue 430, thereby reducing the noise reduction effect of the first guide portion 481.

[0298] In some embodiments, the first angle α1 is less than or equal to 45° (α1≤45°), which facilitates airflow passing through the first air guide portion 481 and improves the noise reduction effect of the first air guide portion 481 .

[0299] In some embodiments, as shown in Figure 36, the side surface of the first air guide portion 481 near the second section 442 intersects with the second sub-snail tongue 422 to form a second angle α2. For example, the side surface of the first air guide portion 481 near the second section 442 intersects with the second sub-snail tongue 422 to form the second angle α2. For example, the second angle α2 is formed by the intersection of a third tangent line and a fourth tangent line. The third tangent line is a tangent line that passes through any point on the intersection line of the second sub-snail tongue 422 and the first air guide portion 481 and is tangent to the second sub-snail tongue 422. The fourth tangent line is a tangent line that passes through any point on the intersection line of the second sub-snail tongue 422 and the first air guide portion 481 and is tangent to the first air guide portion 481.

[0300] It should be noted that the second angle α2 can be determined according to different shapes of the volute tongue 430 .

[0301] If the second angle α2 is less than 30° (α2<30°), the portion of the first guide portion 481 close to the second section 442 protruding from the windward surface of the volute tongue 430 will be too small, thereby reducing the noise reduction effect of the first guide portion 481.

[0302] In some embodiments, the second angle α2 is greater than or equal to 30° (α2 ≥ 30°). This allows the portion of the first air guide 481 protruding from the windward surface of the volute tongue 430 near the second section 442 to be increased, thereby facilitating refraction or scattering of airflow as it passes through the windward surface of the volute tongue 430, thereby enhancing the noise reduction effect of the first air guide 481.

[0303] If the second angle α2 is greater than 45° (α2>45°), the portion of the first air guide 481 adjacent to the second section 442 will protrude excessively from the windward surface of the volute tongue 430, thereby reducing the noise reduction effect of the first air guide 481. In some embodiments, the second angle α2 is less than or equal to 45° (α2≤45°). This facilitates airflow through the first air guide 481 and improves the noise reduction effect of the first air guide 481.

[0304] In some embodiments, the first angle α1 is different from the second angle α2 (α1≠α2).

[0305] In some embodiments, as shown in Figure 33, the first air guide portion 481 includes a first windward surface 461. The first windward surface 461 is disposed on the windward side of the first air guide portion 481. For example, the first windward surface 461 may be an arcuate surface.

[0306] In some embodiments, as shown in FIG35 , a second arc line 471 (a second spiral tongue arc line) is formed at one end of the first windward surface 461 near the first side panel 410. The arc length of the second arc line 471 is a second arc length r. The second arc line 471 is the intersection line between the first windward surface 461 and the first side panel 410. For example, in the width direction of the housing 100, the orthographic projection of the end of the first windward surface 461 near the first side panel 410 on the reference plane is the second arc line 471.

[0307] In some embodiments, the second arc length r of the second arc line 471 is greater than or equal to one fifth of the first arc length R of the first arc line 431 (r≧1 / 5R).

[0308] In some embodiments, the second arc length r of the second arc line 471 is less than or equal to one third of the first arc length R of the first arc line 431 (r≤1 / 3R).

[0309] In some embodiments, as shown in FIG35 , the first windward surface 461 further includes a fourth arc line 472. The fourth arc line 472 is the intersection line between the first windward surface 461 and the fourth side panel of the housing 100. For example, in the thickness direction of the housing 100, the orthographic projection of the end of the first windward surface 461 away from the first side panel 410 on the reference plane is the fourth arc line 472. The arc length of the fourth arc line 472 is the fourth arc length r1, and the second arc length r is less than or equal to the fourth arc length r1 (r≤r1).

[0310] In some embodiments of the present disclosure, simulation analysis is performed on the volute tongue 430 without the first guide portion 481 and the volute tongue 430 with the first guide portion 481 to verify the action mechanism of the volute tongue 430 on the airflow and the noise reduction effect.

[0311] As shown in FIG. 38 and FIG. 39 , the volute tongue 430 can change the concentrated distribution of pressure at the position of the volute tongue 430 to a certain extent, thereby improving the vibration frequency of the sound wave.

[0312] As shown in Figures 40 and 41 , the noise sources of fan assembly 500 are primarily concentrated at second air inlet 401, generating quadrupole noise and dipole noise due to boundary layer separation. Compared to a volute tongue 430 without first air guide 481, the distribution of this dipole noise on volute tongue 430 is more discrete. It should be noted that the quadrupole and dipole noise can be confirmed using Proudman acoustic power.

[0313] After testing, it was found that the volute tongue 430 can reduce the peak frequency of blade passing and reduce the average noise level within a predetermined range.

[0314] The above description mainly uses the example that the guide portion 460 protrudes from the windward surface of the volute tongue 430 . Of course, in some embodiments, the guide portion 460 may also be recessed in the windward surface of the volute tongue 430 .

[0315] For example, as shown in Figures 42 to 45 , the guide portion 460 includes a second guide portion 482. The second guide portion 482 is recessed in the windward surface of the volute tongue 430 to change the shape of the windward surface of the volute tongue 430. It should be noted that at least one guide portion 460 may include multiple first guide portions 481 or multiple second guide portions 482. Furthermore, at least a portion of the at least one guide portion 460 may be protruding or recessed in the windward surface of the volute tongue 430.

[0316] In some embodiments, the second air guide portion 482 is located at the midpoint of the first arc line 431 so that the second air guide portion 482 has a better effect on the airflow.

[0317] In some embodiments, as shown in FIG43 , the windward surface of the volute tongue 430 includes a second curved surface 437. The second curved surface 437 includes a seventh arc line 438. The seventh arc line 438 is the intersection line between the second curved surface 437 and the fourth side panel of the housing 100. For example, in the width direction of the housing 100, the orthographic projection of the end of the second curved surface 437 away from the first side panel 410 on the reference plane is the seventh arc line 438.

[0318] In some embodiments, as shown in FIG. 47 , the second air guide portion 482 is recessed from the windward surface of the volute tongue 430 by a second distance, and the second distance is a thickness t2 of the second air guide portion 482 .

[0319] In some embodiments, the thickness t2 of the second air guide portion 482 is greater than or equal to 0.11 times the minimum gap b of the volute tongue 430 (t≧0.11b).

[0320] In some embodiments, the thickness t2 of the second air guide portion 482 is less than or equal to 0.18 times the minimum gap b of the volute tongue 430 (t≤0.18b).

[0321] It should be noted that the minimum gap b of the volute tongue 430 may also be referred to as a second gap.

[0322] In some embodiments, by drafting the second guide portion 482, the distance from the side of the second guide portion 482 close to the volute body 450 to the side of the guide portion 460 close to the second section 442 is increased along the direction from the first side plate 410 to the fourth side plate of the shell 100.

[0323] In some embodiments, as shown in FIG46 , the volute tongue 430 includes a first sub-volute tongue 421 and a second sub-volute tongue 422. The first end of the first sub-volute tongue 421 is connected to the volute body 450, and the second end of the first sub-volute tongue 421 is connected to the first end of the first guide portion 481. The first end of the second sub-volute tongue 422 is connected to the second section 442, and the second end of the second sub-volute tongue 422 is connected to the second end of the first guide portion 481.

[0324] In some embodiments, as shown in FIG36 , the side surface of the second air guide portion 482 proximal to the volute body 450 intersects with the first sub-volute tongue 421 to form a first angle α1. For example, the fifth tangent line and the sixth tangent line intersect to form the first angle α1. The fifth tangent line is a tangent line passing through any point on the intersection line between the first sub-volute tongue 421 and the second air guide portion 482 and tangent to the first sub-volute tongue 421. The sixth tangent line is a tangent line passing through any point on the intersection line between the first sub-volute tongue 421 and the second air guide portion 482 and tangent to the second air guide portion 482.

[0325] It should be noted that the first angle α1 can be determined according to different shapes of the volute tongue 430 .

[0326] If the first angle α1 is less than 30° (α1<30°), the portion of the second guide portion 482 close to the volute body 450 that is recessed into the windward surface of the volute tongue 430 will be too small, thereby reducing the noise reduction effect of the second guide portion 482.

[0327] In some embodiments, the first angle α1 is greater than or equal to 30° (α1 ≥ 30°). This allows the portion of the second air guide 482 proximate to the volute body 450 to be recessed into the windward surface of the volute tongue 430 , thereby facilitating refraction or scattering of airflow as it passes through the windward surface of the volute tongue 430 , thereby enhancing the noise reduction effect of the second air guide 482 .

[0328] If the first angle α1 is greater than 45° (α1>45°), the portion of the second guide portion 482 close to the volute body 450 will be too much sunken into the windward surface of the volute tongue 430, thereby reducing the noise reduction effect of the second guide portion 482.

[0329] In some embodiments, the first angle α1 is less than or equal to 45° (α1≤45°), which facilitates airflow passing through the second air guide portion 482 and improves the noise reduction effect of the second air guide portion 482 .

[0330] In some embodiments, as shown in FIG36 , the side surface of the second air guide portion 482 near the second section 442 intersects with the second sub-snail tongue 422 to form a second angle α2. For example, the seventh tangent line intersects with the eighth tangent line to form the second angle α2. The seventh tangent line is a tangent line passing through any point on the intersection line between the second sub-snail tongue 422 and the second air guide portion 482 and tangent to the second sub-snail tongue 422. The eighth tangent line is a tangent line passing through any point on the intersection line between the second sub-snail tongue 422 and the second air guide portion 482 and tangent to the second air guide portion 482. It should be noted that the second angle α2 can be determined based on different shapes of the snail tongue 430.

[0331] If the first angle α2 is less than 30° (α2<30°), the portion of the second guide portion 482 close to the second section 442 that is recessed into the windward surface of the volute tongue 430 will be too small, thereby reducing the noise reduction effect of the second guide portion 482.

[0332] In some embodiments, the second angle α2 is greater than or equal to 30° (α2 ≥ 30°). This allows the portion of the second air guide 482 adjacent to the second section 442 to be recessed into the windward surface of the volute tongue 430 , thereby facilitating refraction or scattering of airflow as it passes through the windward surface of the volute tongue 430 , thereby enhancing the noise reduction effect of the second air guide 482 .

[0333] If the second angle α2 is greater than 45° (α2>45°), the portion of the second guide portion 482 close to the second section 442 will be too deeply sunken into the windward surface of the volute tongue 430 , thereby reducing the noise reduction effect of the second guide portion 482 .

[0334] In some embodiments, the second angle α2 is less than or equal to 45° (α2≤45°), which facilitates airflow passing through the second air guide portion 482 and improves the noise reduction effect of the second air guide portion 482 .

[0335] In some embodiments, the first angle α1 is different from the second angle α2 (α5≠α4).

[0336] In some embodiments, as shown in Figure 43, the second air guide portion 482 includes a second windward surface 462. The second windward surface 462 is disposed on the windward side of the second air guide portion 482. The second windward surface 462 may be an arcuate surface or a flat surface.

[0337] As shown in Figure 45, when the second windward surface 462 is an arc-shaped surface, the second windward surface 462 further includes a fifth arc line 491. The fifth arc line 491 is the intersection line between the second windward surface 462 and the first side panel 410. For example, in the width direction of the housing 100, the orthographic projection of the end of the second windward surface 462 closest to the first side panel 410 on the reference plane is the fifth arc line 491. The arc length of the fifth arc line 491 is the fifth arc length r2.

[0338] In some embodiments, the arc length r2 of the fifth arc line 491 is greater than or equal to one-fifth of the first arc length R of the first arc line 431 (r2 ≥ 1 / 5R).

[0339] In some embodiments, the arc length r2 of the fifth arc line 491 is less than or equal to one third of the first arc length R of the first arc line 431 (r2≤1 / 3R).

[0340] As shown in FIG45 , when the second windward surface 462 is an arc-shaped surface, the second windward surface 462 further includes a sixth arc line 492. The sixth arc line 492 is the intersection line between the second windward surface 462 and the fourth side panel of the housing 100. For example, in the width direction of the housing 100, the orthographic projection of the end of the second windward surface 462 away from the first side panel 410 on the reference plane is the sixth arc line 492. The arc length of the sixth arc line 492 is the sixth arc length r3, and the arc length r2 of the fifth arc line 491 is less than or equal to the arc length r3 of the sixth arc line 492 (r2 ≤ r3).

[0341] In some embodiments, as shown in FIG48 , the fan assembly 500 further includes a guide member 600 (guide ring). The guide member 600 is connected to the volute 400 and is disposed at the second air inlet 401 . The guide member 600 is configured to guide airflow into the second accommodating chamber 403 .

[0342] It should be noted that, by arranging the guide member 600 outside the second accommodating cavity 403 , the guide member 600 can guide the airflow from the second air inlet 401 into the interior of the volute 400 .

[0343] In some embodiments, as shown in FIG. 49 , the flow guide 600 encloses a first opening 601 .

[0344] In some embodiments, as shown in FIG49 , the air guide 600 includes a mounting portion 610. The mounting portion 610 is positioned corresponding to the edge of the second air inlet 401. When the air guide 600 is mounted on the second air inlet 401, the mounting portion 610 and the edge of the second air inlet 401 come into contact with each other. The mounting portion 610 forms a second opening, which is positioned corresponding to the second air inlet 401. Air passes through the second opening and enters the second accommodating chamber 403 from the second air inlet 401.

[0345] For example, the second opening may penetrate the mounting portion 610 along the axial direction of the mounting portion 610 .

[0346] In some embodiments, the outer diameter of the mounting portion 610 is larger than the inner diameter of the second air inlet 401 to prevent the mounting portion 610 from passing through the second air inlet 401 and entering the second accommodating cavity 403 , thereby improving assembly reliability.

[0347] In some embodiments, as shown in FIG49 , the flow guide 600 further includes a third flow guide portion 620 (flow guide portion). The third flow guide portion 620 is connected to the mounting portion 610 and is located inside the mounting portion 610. The third flow guide portion 620 extends along the circumference of the mounting portion 610, and the inner diameter of the third flow guide portion 620 decreases toward the center of the mounting portion 610. For example, the inner diameter of the third flow guide portion 620 toward the center of the mounting portion 610 is smaller than the inner diameter of the third flow guide portion 620 away from the center of the mounting portion 610.

[0348] The third guide portion 620 is disposed through the second air inlet 401 so as to guide airflow from the second air inlet 401 into the second accommodating chamber 403. The third guide portion 620 is located at the second opening and forms a third opening that is connected to the second opening.

[0349] In some embodiments, the windward surface of the third air guide portion 620 is a curved surface so as to guide the airflow into the second accommodating cavity 403 .

[0350] As shown in FIG51 , the streamline arrangement near the second air inlet 401 is obtained by simulating the flow of airflow. The closer to the outlet of the fan assembly 500 , the higher the flow rate of the airflow.

[0351] As shown in Figure 50, the windward surface of the third guide part 620 is usually a smooth curved surface. When the airflow flows through the windward surface of the third guide part 620, the airflow encounters less resistance. When the airflow leaves the third guide part 620, the vortex formed by the airflow is large, which in turn causes high noise.

[0352] In some embodiments, as shown in FIG49 , the third air guide portion 620 further includes at least one blocking portion 700 (blocking portion). The at least one blocking portion 700 is disposed on the windward surface of the third air guide portion 620 and is configured to interrupt or disperse the airflow passing through the at least one blocking portion 700, causing sound energy loss, thereby achieving a noise reduction effect.

[0353] It can be understood that after the blocking portion 700 is set on the windward surface of the third guide portion 620, the windward surface of the third guide portion 620 becomes complicated. When the gas flows through the windward surface of the third guide portion 620, the airflow or sound wave blocking portion 700 is deformed and refracted, and a small vortex is formed at the bottom.

[0354] In some embodiments, as shown in Figures 49, 52 and 53, at least one blocking portion 700 includes multiple blocking portions 700. This can improve the efficiency of interrupting or breaking up the airflow flowing through the multiple blocking portions 700, causing more sound energy loss and further improving the noise reduction effect.

[0355] In some embodiments, at least part of the blocking portion 700 is arranged along a line corresponding to a movement path of the airflow when flowing through the windward surface of the third air guide portion 620 , so that the blocking portion 700 can better interact with the airflow.

[0356] That is, at least part of the blocking portion 700 defines an arrangement line, which is located on the windward surface of the air guide 600 , and is arranged corresponding to the path of the airflow flowing through the windward surface of the air guide 600 .

[0357] Alternatively, the windward surface of the air guide 600 is formed with an arrangement line, which is arranged corresponding to the path of the airflow flowing through the windward surface of the air guide 600, and at least part of the blocking parts 700 are arranged along the arrangement line.

[0358] In some embodiments, as shown in Figures 55 to 58 , at least a portion of the plurality of guides 600 are configured as a first row of wiring 701. The first row of wiring 701 extends along the side of the third guide portion 620 connected to the mounting portion 610 toward the side of the third guide portion 620 extending into the second receiving cavity 403. For example, the first row of wiring 701 extends from point A to point B.

[0359] For ease of description, the end of the first row of wiring 701 close to the mounting portion 610 is defined as the first end (end A) of the first row of wiring 701, and the end of the first row of wiring 701 away from the mounting portion 610 is defined as the second end (end B) of the first row of wiring 701. Here, compared to the second end of the first row of wiring 701, the first end of the first row of wiring 701 is farther away from the interior of the volute 400.

[0360] As shown in FIG. 54 , the direction perpendicular to the first side plate 410 (refer to FIG. 48 ) is the direction of the thickness of the guide member 600 , and the thickness of the guide member 600 is defined as a first thickness H.

[0361] As shown in FIG. 55 and FIG. 57 , any blocking portion 700 located on the wiring has a normal line 704 , and the normal line 704 intersects with the first horizontal line 705 to form an offset angle β.

[0362] In some embodiments, the offset angle β is greater than or equal to 5° (β≥5°), which facilitates the manufacture of the flow guide 600 .

[0363] In some embodiments, the offset angle β is less than or equal to 8° (β≤8°), thereby facilitating airflow through the wiring.

[0364] It should be noted that if the offset angle β is less than 5° (β<5°), or the offset angle β is greater than 8° (β>8°), it is not conducive to achieving the direction along the first side plate 410 to the fourth side plate of the shell 100 (such as the front and rear direction) through demolding, and the distance between the side of the first guide portion 481 close to the volute body 450 and the side of the first guide portion 481 away from the volute body 450 increases.

[0365] It should be noted that, from the first end to the second end of the same row of wiring, the offset angle β formed by each blocking portion 700 on the same row of wiring increases successively. This makes it easier to direct the blocking portion 700 toward the airflow, thereby achieving a better interruption effect on the airflow, and also facilitates manufacturing.

[0366] As shown in FIG. 55 , along the thickness direction of the flow guide 600 , the distance from the first end of the wiring to the second end of the wiring is the height h of the wiring.

[0367] If the height h of the wiring is less than half the thickness H of the guide member 600 (h≥1 / 2H), the height h of the wiring will be reduced, making the distribution area of ​​the blocking portion 700 on the guide member 600 too small, thereby reducing the noise reduction effect.

[0368] In some embodiments, the height h of the wiring is greater than or equal to half the thickness H of the guide 600 (h ≥ 1 / 2H). In this way, the height h of the wiring can be increased, and the distribution area of ​​the blocking portion 700 on the guide 600 can be increased, thereby improving the noise reduction effect.

[0369] If the height h of the wiring is greater than two-thirds of the thickness H of the guide member 600 (h>2 / 3H), the distribution area of ​​the blocking portion 700 in the guide member 500 will be too large, making it difficult to further improve the noise reduction effect and increasing costs.

[0370] In some embodiments, the height h of the wiring is less than or equal to two-thirds of the thickness H of the guide member 600 (h≤2 / 3H). This can avoid excessive number or excessive shape of the blocking parts 700, thereby reducing costs while improving noise reduction effects.

[0371] As shown in Figure 55 , the projection of the first end of the wiring harness on the target plane and the projection of the second end of the wiring harness on the target plane define the width of the wiring harness. This target plane passes through the symmetry plane at the center of the third guide portion 620. Furthermore, the width b of the wiring harness is defined from the first end of the wiring harness to the second end of the wiring harness. The width of the wiring harness is perpendicular to the height of the wiring harness and lies in the same plane.

[0372] It should be noted that the midpoint of each blocking portion 700 arranged along the arrangement wiring is located on the arrangement wiring.

[0373] In some embodiments, the curvature radius of each blocking portion 700 located on the same row of wiring decreases sequentially from the first end of the row of wiring to the second end of the row of wiring.

[0374] In some embodiments, among two adjacent blocking portions 700 on the same row of wiring, the curvature radius of one blocking portion 700 near the first end of the row of wiring is twice the curvature radius of one blocking portion 700 near the second end of the row of wiring.

[0375] In some embodiments, the third air guide portion 620 includes a plurality of wirings arranged along a circumference on the windward surface of the third air guide portion 620 .

[0376] It should be noted that the path of the airflow when flowing through the windward surface of the third air guide portion 620 is a curve, and accordingly, the wiring is also a curve.

[0377] Since the airflow's inward rotation direction follows the blade's rotational direction, the shape of the wiring harness must align with this direction. This ensures that the airflow encounters as many obstructions as possible along its path as possible. Therefore, the wiring harness's inward rotational direction aligns with the fan assembly's 500 rotational direction and is opposite to the fan assembly's 500 blade curvature.

[0378] As shown in FIG58 , the wiring arrangement when the fan assembly 500 rotates clockwise and counterclockwise is different. The wiring arrangement when the fan assembly 500 rotates clockwise is defined as the first row of wiring 701 , and the wiring arrangement when the fan assembly 500 rotates counterclockwise is defined as the second row of wiring 706 .

[0379] As shown in FIG. 58 , the first end of the first row of wiring 701 overlaps with the second row of wiring 706 , and the second end of the first row of wiring 701 overlaps with the second row of wiring 706 .

[0380] Select point A at the first end of the first row of wiring 701 and point B at the second end of the first row of wiring 701, define the line connecting point A and point B as reference line 708, and the first row of wiring 701 and the second row of wiring 706 are symmetrically arranged about the reference line 708.

[0381] The width b1 of the first row of wirings 701 is the same as the width b2 of the second row of wirings 706 , and the height h1 of the first row of wirings 701 is the same as the height h2 of the second row of wirings 706 .

[0382] As shown in FIG55 , when the wiring row is the first wiring row 701 , the second end of the first wiring row 701 has a first tangent line 702 , and the first tangent line 702 and the second horizontal line 703 together define a third angle α.

[0383] The width b1 of the first row of wirings 701 and the height h1 of the first row of wirings 701 satisfy a first relationship: b1 = h1 / tanα.

[0384] If the third angle α is less than 65° (α<65°), the first tangent line 702 will be closer to the second horizontal line 703, thereby reducing the distribution area of ​​the blocking portion 700 on the guide member 600 and reducing the noise reduction effect.

[0385] In some embodiments, the third angle α is greater than or equal to 65° (α≥65°). In this way, the distribution area of ​​the blocking portion 700 on the guide member 600 can be increased, thereby improving the noise reduction effect.

[0386] If the third angle α is greater than 75° (α>75°), the first tangent line 702 will be further away from the second horizontal line 703, so that the distribution of the plurality of blocking portions 700 will be more scattered, thereby reducing the noise reduction effect.

[0387] In some embodiments, the third angle α is less than or equal to 75° (α≤75°). In this way, the number of the blocking portions 700 is prevented from being excessive or the shape of the blocking portions 700 being too large, and the airflow is facilitated.

[0388] As shown in FIG58 , when the row of wirings is the second row of wirings 706 , a second tangent line 707 is defined at the second end of the second row of wirings 706 . The second tangent line 707 and the second horizontal line 703 together define a third angle θ.

[0389] In some embodiments, the second angle θ is greater than or equal to 15° (θ≥15°).

[0390] In some embodiments, the second angle θ is less than or equal to 25° (θ≤25°).

[0391] It should be noted that the second angle θ and the third angle α are in a complementary relationship. Therefore, when the range corresponding to the third angle α is determined, the range corresponding to the second angle θ is also determined.

[0392] The width b2 of the second row of wirings 706 and the height h2 of the second row of wirings 706 satisfy a second relationship: b2 = h2 / tan(90°-θ).

[0393] It should be noted that the more blocking parts 700 there are on the same row of wiring, the better the effect of the blocking parts 700 on the airflow. However, in actual applications, the number of blocking parts 700 on the same row of wiring is also limited by the manufacturing process. Usually, the more blocking parts 700 there are on the same row of wiring, the stricter the requirements for the manufacturing process. Therefore, the number of blocking parts 700 on the same row of wiring still needs to balance the air guiding effect and the manufacturing process.

[0394] The following mainly describes the case where four blocking portions are provided on the same first row of wiring 701 as an example.

[0395] In some embodiments, as shown in FIG. 56 and FIG. 57 , a first blocking portion 710 is provided on the first row of wirings 701 , and the first blocking portion 710 is defined to have a first offset angle β1 .

[0396] In some embodiments, the first offset angle β1 is greater than or equal to 5° (β1 ≥ 5°).

[0397] In some embodiments, the first offset angle β1 is less than or equal to 8° (β1≤8°).

[0398] In some embodiments, a second blocking portion 720 is disposed on the first row of wirings 701 , and the second blocking portion 720 defines a second offset angle β2 .

[0399] In some embodiments, the second offset angle β2 is greater than or equal to 5° (β1 ≥ 5°).

[0400] In some embodiments, the second offset angle β2 is less than or equal to 8° (β2≤8°).

[0401] In some embodiments, a third blocking portion 730 is disposed on the first row of wirings 701 , and the third blocking portion 730 is defined to have a third offset angle β3 .

[0402] In some embodiments, the third offset angle β3 is greater than or equal to 5° (β3≧5°).

[0403] In some embodiments, the third offset angle β3 is less than or equal to 8° (β3≤8°).

[0404] In some embodiments, a fourth blocking portion 740 is disposed on the first row of wirings 701 , and the fourth blocking portion 740 defines a fourth offset angle β4 .

[0405] In some embodiments, the fourth offset angle β4 is greater than or equal to 5° (β4≧5°).

[0406] In some embodiments, the fourth offset angle β4 is less than or equal to 8° (β4≤8°).

[0407] It should be noted that the value ranges of the first offset angle β1, the second offset angle β2, the third offset angle β3 and the fourth offset angle β4 correspond to the value range of the offset angle β described above, and are not described again here.

[0408] The first barrier 710 , the second barrier 720 , the third barrier 730 and the fourth barrier 740 are arranged along the first row of wiring 701 in a direction from the first end to the second end of the first row of wiring 701 .

[0409] In some embodiments, the first offset angle β1 is smaller than the second offset angle β2 (β1<β2). For example, the first offset angle β1 is equal to twice the second offset angle β2 (β2=2β1).

[0410] In some embodiments, the first offset angle β1 is smaller than the third offset angle β3 (β1<β3). For example, the first offset angle β1 is equal to four times the third offset angle β3 (β3=4β1).

[0411] In some embodiments, the first offset angle β1 is smaller than the fourth offset angle β4 (β1<β4). For example, the first offset angle β1 is equal to 6 times the fourth offset angle β4 (β4=6β1).

[0412] In some embodiments, the second offset angle β2 is smaller than the third offset angle β3 (β2<β3). For example, the second offset angle β2 is equal to twice the third offset angle β3 (β3=2β2).

[0413] In some embodiments, the second offset angle β2 is smaller than the fourth offset angle β4 (β2<β4). For example, the second offset angle β2 is equal to four times the fourth offset angle β4 (β4=4β2).

[0414] In some embodiments, the third offset angle β3 is smaller than the fourth offset angle β4 (β3<β4). For example, the third offset angle β3 is equal to twice the fourth offset angle β4 (β4=2β3).

[0415] The curvature radius of the first blocking portion 710 is set to the first radius R1, the curvature radius of the second blocking portion 720 is set to the second radius R2, the curvature radius of the third blocking portion 730 is set to the third radius R3, and the curvature radius of the fourth blocking portion 740 is set to the fourth radius R4.

[0416] In some embodiments, the first radius R1 is greater than the second radius R2 (R1>R2). For example, the first radius R1 is equal to 1.5 times the second radius R2 (R1=1.5R2).

[0417] In some embodiments, the first radius R1 is greater than the third radius R3 (R1>R3). For example, the first radius R1 is equal to three times the third radius R3 (R1=3R3).

[0418] In some embodiments, the first radius R1 is greater than the fourth radius R4 (R1>R4). For example, the first radius R1 is equal to 4.5 times the fourth radius R4 (R1=4.5R4).

[0419] In some embodiments, the second radius R2 is greater than the third radius R3 (R2>R3). For example, the second radius R2 is equal to 1.5 times the third radius R3 (R2=1.5R3).

[0420] In some embodiments, the second radius R2 is greater than the fourth radius R4 (R2>R4). For example, the second radius R2 is equal to three times the fourth radius R4 (R2=3R4).

[0421] In some embodiments, the third radius R3 is greater than the fourth radius R4 (R3>R4). For example, the third radius R3 is equal to 1.5 times the fourth radius R4 (R3=1.5R4).

[0422] In some embodiments, the blocking portion 700 may be a concave point provided on the windward surface of the third guide portion 620 , and the blocking portion 700 may be recessed in the windward surface of the third guide portion 620 .

[0423] It should be noted that the principle of pit noise reduction is the same as that of sound-absorbing materials. During the propagation of sound waves, the surrounding fluid medium will produce friction and lose sound energy during the process of traveling, reflecting, and refracting on the surface of the object. The sound energy is converted into heat energy, thereby achieving noise reduction. On a smooth structural surface, the friction resistance is small, the propagation of sound waves in the fluid medium is relatively smooth, and the sound energy loss is small, so the noise is loud. On a rough and porous surface, the generation and propagation path of sound waves become complicated, the resistance becomes larger, and the sound energy loss becomes larger, so the noise is reduced. In addition, the rough and porous surface will break up the boundary layer detachment vortex generated after the fluid medium flows through, thereby reducing noise.

[0424] In some embodiments, the blocking portion 700 may be a convex point provided on the windward surface of the third air guide portion 620 , and the blocking portion 700 may be protruded from the windward surface of the third air guide portion 620 .

[0425] The indoor unit can reduce the noise generated when the airflow enters the housing without sacrificing the air intake volume.

[0426] The present disclosure further provides an air conditioner 1000. In some embodiments, as shown in FIG2 , the air conditioner 1000 includes an indoor unit 10.

[0427] The air conditioner 1000 further includes an outdoor unit 20. The indoor unit 10 and the outdoor unit 20 are connected by a pipeline to transmit refrigerant.

[0428] The cooling and heating cycle process includes: compression process, condensation process, expansion process and evaporation process.

[0429] In some embodiments, air conditioner 1000 includes a compressor 201. Low-temperature, low-pressure refrigerant enters compressor 201, which compresses it into high-temperature, high-pressure refrigerant gas and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into a condenser. The condenser condenses the compressed refrigerant into a liquid phase, releasing heat into the surrounding environment through the condensation process.

[0430] In some embodiments, the air conditioner 1000 further includes an expansion valve 204. The expansion valve 204 expands the high-temperature and high-pressure liquid refrigerant condensed in the condenser into a low-pressure liquid refrigerant. The expansion valve 204 can be located in the indoor unit 10 or the outdoor unit 20.

[0431] In some embodiments, the air conditioner 1000 further includes an evaporator. The evaporator evaporates the refrigerant expanded in the expansion valve 204 and returns the low-temperature, low-pressure refrigerant gas to the compressor 201. The evaporator achieves a cooling effect by utilizing the latent heat of evaporation of the refrigerant to exchange heat with the material to be cooled. Throughout this cycle, the compressor 201 regulates the temperature of the indoor space.

[0432] In some embodiments, the indoor unit 10 includes a first heat exchanger 300 (eg, an indoor heat exchanger).

[0433] The outdoor unit 20 includes a second heat exchanger 202 (eg, an outdoor heat exchanger). The first heat exchanger 300 and the second heat exchanger 202 are connected via a pipeline.

[0434] The first heat exchanger 300 and the second heat exchanger 202 function as a condenser or an evaporator.

[0435] For example, when the first heat exchanger 300 functions as a condenser, the compressor 201 functions as a heater in a heating mode.

[0436] For example, when the first heat exchanger 300 functions as an evaporator, the compressor 201 functions as a cooler in a cooling mode.

[0437] In some embodiments, the outdoor unit 20 further includes a four-way valve 205 located between the first heat exchanger 300 and the second heat exchanger 202 . The four-way valve 205 is configured to switch the first heat exchanger 300 and the second heat exchanger 202 as a condenser or an evaporator.

[0438] For example, the refrigeration working principle of the air conditioner 1000 is: the compressor 201 works to put the first heat exchanger 300 (in the indoor unit 10, it is the evaporator at this time) in an ultra-low pressure state, and the liquid refrigerant in the first heat exchanger 300 evaporates to absorb heat. The wind blown out by the first fan assembly 500 (such as the indoor fan) is cooled by the first heat exchanger coil and becomes cold air blown into the room. The evaporated refrigerant is pressurized by the compressor 201 and condensed into liquid under the high-pressure environment of the second heat exchanger 202 (in the outdoor unit 20, it is the condenser at this time), releasing heat. The heat is dissipated into the atmosphere through the second fan assembly 26 (such as the outdoor fan). Such a cycle can achieve cooling.

[0439] For example, the heating principle of air conditioner 1000 is as follows: the gaseous refrigerant is pressurized by compressor 201, becoming a high-temperature, high-pressure gas. It then enters the first heat exchanger 300 (this is the condenser), where it condenses and liquefies, releasing heat and becoming a liquid. This heats the indoor air, thereby raising the indoor temperature. The liquid refrigerant is then decompressed by the throttling device and enters the second heat exchanger 202 (this is the evaporator). It evaporates and absorbs heat, becoming a gas. This gas absorbs heat from the outdoor air (making the outdoor air even cooler), and then enters the compressor 201 again to begin the next cycle, thus achieving heating.

[0440] It should be noted that the indoor unit 10 in the present disclosure includes but is not limited to a wall-mounted air conditioner, a floor-standing air conditioner, a ducted air conditioner, a ceiling air conditioner, and the like.

[0441] In some embodiments, the indoor unit 10 is installed in an indoor space, and the indoor unit 10 provides processed cold air or warm air to the indoor space to adjust the temperature or humidity of the indoor space.

[0442] In some embodiments, as shown in Figures 59, 60, and 61, the indoor unit 10 includes a housing 100. The housing 100 includes a storage space 109, and the first heat exchanger 300 is disposed in the storage space 109. The housing 100 includes a first air inlet 101 (e.g., an indoor air inlet), and the storage space 109 is in communication with the first air inlet 101. The housing 100 also includes a first air outlet 112 (e.g., an indoor air outlet), and the storage space 109 is in communication with the first air outlet 112. The first air inlet 101 is in communication with the first air outlet 112.

[0443] In some embodiments, as shown in Figures 61 and 62, the indoor unit 10 further includes a first channel 111 (e.g., a heat exchange duct), which is in communication with the accommodating space 109. The first channel 111 is in communication with the first air inlet 101 and the first air outlet 112. The first heat exchanger 300 is located within the first channel 111, allowing the airflow within the accommodating space 109 to exchange heat with the first heat exchanger 300.

[0444] In some embodiments, as shown in Figures 61, 62, and 72, the indoor unit 10 includes a first fan assembly 500 (e.g., a fan assembly), which is located in the accommodating space 109. The first fan assembly 500 is disposed in the first passage 111. Thus, the first fan assembly 500 is configured to introduce airflow from outside the housing 100 into the accommodating space 109, providing power for the airflow in the accommodating space 109, so that the airflow enters the first passage 111 through the first air inlet 101, exchanges heat with the first heat exchanger 300, and then flows into the indoor space through the first air outlet 112.

[0445] The first fan assembly 500 includes a volute 21. It should be noted that the shape and size of the volute 21 can be designed according to the shape and size of the first fan assembly 500, so as to facilitate the installation and arrangement of the components in the accommodating space 109.

[0446] In some embodiments, as shown in Figures 62 and 72, the first fan assembly 500 further includes a second channel 404 (e.g., an air duct), and the second channel 404 (e.g., a volute air duct) is formed in the volute 21. A first end of the second channel 404 is connected to the first air inlet 101, and a second end of the second channel 404 is connected to the second air outlet 402.

[0447] In some embodiments, as shown in FIG61 , the indoor unit 10 includes a first heat exchanger 300 (e.g., a heat exchanger), which is located on a side of the first fan assembly 500 near the first air inlet 101. This allows the heat-exchanged airflow to quickly flow into the indoor space through the first air outlet 112, thereby improving the cooling or heating effect of the air conditioner 1000.

[0448] In some embodiments, as shown in FIG. 62 , the second channel 404 includes a second air outlet 402 communicating with the first air outlet 112 .

[0449] The second channel 404 further includes a second air inlet 401 in communication with the first air inlet 101. The second air inlet 401 is in communication with the second air outlet 402, so that the airflow in the second channel 404 can flow in through the second air inlet 401 and then flow out through the second air outlet 402, thereby changing the flow direction of the airflow in the second channel 404.

[0450] In some embodiments, as shown in Figures 62, 64 and 65, the first fan assembly 500 includes an air inlet portion 23 (such as an air inlet ring), and the air inlet portion 23 is located at one end of the volute 21 close to the second air inlet 401.

[0451] In some embodiments, the first blower assembly 500 includes an impeller 122 , and the impeller 122 is located within the second channel 404 .

[0452] In some embodiments, as shown in Figures 65 and 66, there is a predetermined assembly gap between the end of the air inlet 23 close to the impeller 122 and the impeller 122, so that the probability of collision between the rotating impeller 122 and the air inlet 23 can be reduced.

[0453] Due to the existence of the assembly gap, on the one hand, the airflow in the second channel 404 will flow back from the assembly gap to the second air inlet 401, affecting the air volume; on the other hand, the returning airflow collides with the incoming airflow, causing aerodynamic noise.

[0454] In the related art, in order to reduce the amount of air flowing out of the assembly gap between the impeller 122 and the air inlet 23, a curved, recessed annular structure is provided at one end of the impeller 122 near the air inlet 23. The air inlet 23 is configured as a protruding annular structure that cooperates with the recessed annular structure, thereby forming a curved channel between the impeller 122 and the air inlet 23. If the airflow wants to flow back to the second air inlet 401, it can only pass through the curved bend within the assembly gap. The curved bend increases the resistance to gas backflow, reduces the amount of gas backflow, and reduces air leakage. However, due to the difficulty in machining the recessed annular structure of the impeller 122 in this technical solution, and the complex steps during installation, the impeller 122 is prone to collision with the air inlet 23 during rotation.

[0455] In order to solve the above problems, some embodiments of the present disclosure provide an air conditioner 1000 .

[0456] In some embodiments, as shown in FIG59 , an air conditioner 1000 includes an indoor unit 10, which is a vertical indoor unit. The indoor unit 10 includes a top plate 1914, which is located at the top of the housing 100. The indoor unit 10 also includes a base 1915, which is located at the bottom of the housing 100. The direction from the top plate 1914 toward the base 1915 is generally consistent with the extension direction of the housing 100, which is the height direction of the vertical indoor unit.

[0457] In some embodiments, as shown in FIG. 59 , the first air inlet 101 is disposed at the front of the housing 100 . The first air inlet 101 may be located on the same side as the first air outlet 112 , thereby facilitating the flow of indoor air into the accommodating space 109 .

[0458] In some embodiments, the first air inlet 101 is located at the rear of the housing 100, and the first air outlet 112 is located at the front of the housing 100. This makes it easier for the airflow after heat exchange to blow toward the user, which is beneficial to improving the heat exchange effect of the air conditioner.

[0459] In some embodiments, as shown in Figures 60, 62 and 63, the first fan assembly 500 includes a fan 17 (such as a centrifugal fan), and the fan 17 is located in the second channel 404. The second channel 404 connects the second air outlet 402 and the second air inlet 401, and the second air inlet 401 is connected to the first air inlet 101. In this way, the fan 17 can change the flow direction of the airflow in the accommodating space 109.

[0460] In some embodiments, the second air inlet 401 corresponds to the end of the fan 17 (centrifugal fan) close to the first air inlet 101. The second air inlet 401 can be set to a circular or elliptical shape, etc., so that the airflow entering the fan 17 through the first air inlet 101 can be increased.

[0461] In some embodiments, the second air outlet 402 is connected to the first channel 111, and the fan 17 can make the air flow enter the fan 17 through the first air inlet 101 and flow to the second air duct 113 and the first channel 111. The fan 17 can make the air flow pass through the first air inlet 101 and flow to the first channel 111. The air flow exchanges heat with the first heat exchanger 300 in the first channel 111. After absorbing the cold or heat released by the first heat exchanger 300, the air flow is blown out to the indoor space through the first air outlet 112.

[0462] In some embodiments, as shown in FIG62 , the first fan assembly 500 includes an impeller 122 . Impeller 122 is located within the second passage 404 and is positioned opposite the second air inlet 401 . Impeller 122 is a generally cylindrical structure with a hole in the middle. Impeller 122 rotates to drive airflow from the first air inlet 101 into the accommodation space, then through the second air inlet 401 into the second passage 404 before being blown out of the first air outlet 112 into the indoor space.

[0463] It should be noted that the flow direction of the airflow in the second channel 404 is that the airflow flows into the impeller 122 from front to back along the axial direction of the impeller 122, and then the airflow is driven by the impeller 122 to flow along the radial direction of the impeller 122, and finally the airflow passes through the second air outlet 402 connected to the second channel 404 and flows into the first channel 111.

[0464] In some embodiments, as air flows through the second channel 404 within the volute 21, it is driven by the impeller 122 from the second air inlet 401 into the second channel 404. The air is then driven by the high-speed rotating impeller 122 into the first channel 111. A first zone is formed within the second channel 404 on the outer periphery of the impeller 122. At this point, the area between the air inlet 23 and the impeller 122 forms the second zone. Part of the air flows from the first zone to the second zone. The air pressure in the first zone is higher than that in the second zone. The air flows from the outer periphery of the impeller 122 to the assembly gap, ultimately exiting the second channel 404.

[0465] In some embodiments, as shown in Figures 62 and 66 , the first fan assembly 500 includes a sealing portion 3 (e.g., a sealing ring). The sealing portion 3 is an annular structure, or a flat annular structure. The sealing portion 3 is located within the second channel 404 and between the impeller 122 and the air inlet 23.

[0466] The sealing portion 3 is arranged in the assembly gap, and the extension direction of at least part of the sealing portion 3 is substantially consistent with the axial direction of the impeller 122. When the airflow flows from the outer peripheral side of the impeller 122 to the assembly gap, since the sealing portion 3 is arranged in the assembly gap, when the airflow outside the sealing portion 3 reaches the sealing portion 3, the airflow is blocked from continuing to flow toward the second air inlet 401, which can reduce the amount of airflow flowing back to the second air inlet 401.

[0467] It is understood that the sealing portion 3 can block part of the airflow and reduce the assembly gap, so that the airflow can only flow back to the second air inlet 401 through the gap between the sealing portion 3 and the impeller 122, and cannot flow smoothly through the assembly gap between the air inlet 23 and the impeller 122. In addition, a semi-enclosed flow channel is formed between the sealing portion 3, the impeller 122, and the air inlet 23. Compared with a completely open flow channel, the semi-enclosed flow channel can reduce the amount of airflow backflow.

[0468] In some embodiments, as shown in Figures 65 and 68 , at least two first protrusions 31 are provided on a surface of the sealing portion 3 on one side near the impeller 122. The at least two first protrusions 31 are spaced apart along the circumference of the sealing portion 3 and protrude toward the center of the sealing portion 3. In this way, the backflow of the airflow can be blocked.

[0469] In some embodiments, as shown in Figures 68 to 70, the first protrusion 31 includes a curved surface 311 (convex curved surface), and the curved surface 311 extends along the radial direction of the sealing portion 3 toward the center of the sealing portion 3. In this way, when the air flow flows from the second air inlet 401 to the sealing portion 3, the curved surface 311 can guide the air flow entering from the second air inlet 401 to flow along the direction guided by the curved surface 311 (that is, the direction from the second air inlet 401 to the second air outlet 402). It should be noted that the curved surface 311 can reduce the resistance to the incoming air compared to a convex plane with edges and corners.

[0470] In addition, the curved surface 311 can block the backflow airflow flowing along the axial direction of the impeller 122 from entering the assembly gap, reducing the airflow leaking from the gap between the side surface (inner ring side surface) of the sealing part 3 and the impeller 122, and the sealing effect is better.

[0471] In some embodiments, as shown in Figures 67 to 69, the first protrusion 31 is a cylinder, and the first protrusion 31 has two bottom surfaces 312. The bottom surface 312 of the cylinder is semi-elliptical. The first bottom surface 312 is provided on the side of the first protrusion 31 close to the second air inlet 401, and the second bottom surface 312 is provided on the side of the first protrusion 31 close to the impeller 122. The side surface of the cylinder is provided between the two bottom surfaces 312, and the side surface of the cylinder extends along the axial direction of the impeller 122.

[0472] As shown in Figures 69 and 70, in some embodiments, the bottom surface 312 of the cylinder and one side of the sealing portion 3 have two intersection points, namely A1 and B1. There is a point C1 on the longer arc formed by the two intersection points A1 and B1. Point C1 is the position point with the maximum curvature on the arc. The center of the sealing portion 3 is recorded as O1. The straight line where C1 and O1 are located is the first connecting line K1, and the straight line where A1 and B1 are located is the second connecting line K2.

[0473] The included angle between the first connecting line K1 and the second connecting line K2 is α. When α is 90°, the drainage effect of the curved side surface of the column is not obvious.

[0474] In some embodiments, α is not 90°, so that the column is tilted, which helps improve the drainage effect of the first protrusion 31. In some embodiments, when the impeller 122 rotates counterclockwise in FIG. 74 , when α is less than 90°, for example, α is 89°, 88°, or 87°, as the angle α decreases, the angle between the inclined curved side surface of the column and the inner sidewall of the sealing portion 3 decreases, thereby improving the drainage effect of the first protrusion 31 on the airflow within the assembly gap.

[0475] For another example, α is 83°, 84° or 85°. As the angle of α increases, the angle between the inclined curved side surface of the column and the inner wall of the sealing portion 3 becomes larger. In this way, the resistance of the first protrusion 31 to the airflow in the assembly gap is increased, and the amount of airflow flowing out of the second air inlet 401 through the assembly gap can be reduced.

[0476] In some embodiments, the impeller 122 rotates in a clockwise direction in FIG. 75 , and α is greater than 90°, for example, α is 97°, 96°, or 95°. As the angle of α decreases, the angle between the inclined curved side of the cylinder and the inner wall of the sealing portion 3 becomes smaller. In this way, the resistance of the first protrusion 31 to the airflow in the assembly gap is increased, and the amount of airflow flowing out of the second air inlet 401 through the assembly gap can be reduced.

[0477] For another example, α is 65°, 75° or 85°. As the angle of α decreases, the angle between the inclined curved side of the column and the inner wall of the sealing portion 3 becomes larger, thereby improving the drainage effect of the first protrusion 31 on the airflow in the assembly gap.

[0478] In some embodiments, multiple first protrusions 31 are arranged in a circular array in the inner ring of the sealing portion 3. For example, when the number of first protrusions 31 is less than 10, the distance between two adjacent first protrusions 31 will increase, resulting in the first protrusions 31 having an insignificant effect on the airflow guidance.

[0479] In some embodiments, the number of the first protrusions 31 is not less than 10, for example, the number of the first protrusions 31 is 12, 15 or 18, etc. As the number of the first protrusions 31 of α increases, the distance between two adjacent first protrusions 31 decreases, thereby improving the drainage effect of the first protrusions 31 on the airflow.

[0480] In some embodiments, the number of the first protrusions 31 is not less than 30, for example, the number of the first protrusions 31 is 32, 34 or 36, etc., thus improving the airflow guiding effect of the first protrusions 31.

[0481] In some embodiments, when the distance between two adjacent first protrusions 31 is greater than 12 mm, the first protrusions 31 have an insignificant effect on guiding the airflow.

[0482] In some embodiments, the distance between two adjacent first protrusions 31 is no more than 12 mm. For example, the distance between two adjacent first protrusions 31 is 8 mm, 10 mm or 12 mm, etc. In this way, the guiding effect on airflow and the blocking effect on backflow airflow can be enhanced.

[0483] In some embodiments, as shown in Figures 61 and 62, the volute 21 includes a first side panel 410 (e.g., a front side panel), which is located on a side of the volute 21 near the air inlet 23. The volute 21 also includes a second side panel 420. The second side panel 420 is connected to the first side panel 410. The first side panel 410, the second side panel 420, and the housing 100 collectively define a second air outlet 402. The first side panel 410 of the volute 21 is provided with a second air inlet 401 that is in communication with the first air inlet 101, and the air inlet 23 is connected to the second air inlet 401.

[0484] In some embodiments, as shown in Figure 66, the side of the sealing portion 3 away from the air inlet portion 23 is the first side. In the axial direction of the impeller 122, the distance L1 between the first side of the sealing portion 3 and the first side plate 410 is greater than the distance L2 between the side of the impeller 122 away from the center of the impeller 122 and the first side plate 410, that is, L1≥L2.

[0485] In this way, the sealing portion 3 and the impeller 122 overlap in the axial direction of the impeller 122, so that the airflow outside the sealing portion 3 and flowing radially along the impeller 122 cannot flow into the assembly gap. When the airflow is driven to the outside of the impeller 122 by the impeller 122, because the end of the impeller 122 close to the second air inlet 401 is located inside the sealing portion 3, the airflow cannot flow in from the outside of the sealing portion 3. The sealing portion 3 effectively blocks the gap between the impeller 122 and the sealing portion 3 extending in the axial direction of the impeller 122. The airflow can only flow in from the gap between the inner side surface of the sealing portion 3 and the outer side of the impeller 122, reducing the airflow out of the assembly gap and making the installation and manufacturing of the sealing portion 3 simpler.

[0486] In some embodiments, as shown in Figures 62 and 66 , the air inlet portion 23 is connected to the first side plate 410. The air inlet portion 23 includes a first fixing portion 222 (an outer peripheral fixing ring) connected to the first side plate 410.

[0487] In some embodiments, the air inlet portion 23 further includes an inner peripheral drainage portion (peripheral drainage ring), which is configured to guide airflow.

[0488] In some embodiments, as shown in FIG. 62 , the first fixing portion 222 is connected to the first side panel 410 via a snap-fit ​​structure, ie, a split structure. This facilitates installation and maintenance of the first fixing portion 222 .

[0489] In some embodiments, as shown in FIG. 62 , the first fixing portion 222 and the inner peripheral drainage portion may be integrally formed, thereby facilitating the processing and production of the first fixing portion 222 and the first side plate 410 .

[0490] In some embodiments, the first side plate 410 further includes a second fixing portion, and the first fixing portion 222 includes an extending hook portion, which is connected to the second fixing portion to fix the air inlet portion 23 and the first side plate 410 .

[0491] It should be noted that the first fixing portion 222 includes one or more extension portions (extension hook portions), and the second fixing portion is arranged corresponding to the extension portion. When the first fixing portion 222 includes multiple extension portions, the first side panel 410 includes multiple second fixing portions, and the multiple extension portions are arranged in a circular array. The multiple second fixing portions are arranged in a circular array so that each extension portion is connected to the corresponding second fixing portion.

[0492] The first fixing portion 222 is connected to the first side plate 410 via at least one clamping structure. When the at least one clamping structure includes a plurality of clamping structures, the plurality of clamping structures are arranged in a circular array on the first fixing portion 222 .

[0493] In some embodiments, as shown in FIG71 , the sealing portion 3 includes mounting portions 33. The number of mounting portions 33 corresponds to the number of the snap-fit ​​structures. It should be noted that the mounting portions 33 on the sealing portion 3 extend in the axial direction of the sealing portion 3 for no more than half of the axial extension of the sealing portion 3. This facilitates the securement of the air inlet portion 23 and the first side plate 410.

[0494] In some embodiments, as shown in FIG62 , the inner peripheral guide portion (inner peripheral guide ring) has a curved surface structure. The curved surface on the outer side of the inner peripheral guide portion is a guide curved surface. At least a portion of the guide curved surface is a curved surface extending from front to back in a direction away from the second air inlet 401, so that the airflow flows into the second channel 404 along the axial direction of the impeller 122. When the second channel 404 is under negative pressure, the airflow enters from the second air inlet 401. When the airflow flows near the air inlet 23, the guide curved surface guides the airflow flowing along the outer surface of the air inlet 23 into the second channel 404. The surface of the guide curved surface is smooth to reduce the loss of air volume caused by collision between the airflow and the guide curved surface.

[0495] In some embodiments, the inner diameter of the air inlet 23 is smaller than the inner diameter of the second air inlet 401 , so that the inner peripheral guide portion of the air inlet 23 is located inside the second channel 404 to guide the air flow along the air inlet 23 into the second channel 404 .

[0496] In some embodiments, impeller 122 includes a mounting bracket.

[0497] In some embodiments, the impeller 122 includes a rotating wheel, a mounting frame is connected to the rotating wheel, and the mounting frame is disposed on an inner side wall of the rotating wheel.

[0498] In some embodiments, as shown in FIG. 62 , the rotating wheel includes a plurality of blades 221 .

[0499] In some embodiments, as shown in Figures 62, 64, and 66, the rotating wheel further includes a first fixing portion 222. The first fixing portion 222 is fixed to an end of the impeller 122 near the air inlet 23, so that the plurality of blades 221 can extend in a direction away from the air inlet 23 along the axial direction of the impeller 122. The first fixing portion 222 can fix and support the plurality of blades 221.

[0500] In some embodiments, the rotating wheel includes at least one first fixing portion 222. At least one first fixing portion 222 is located inside the blade 221, and at least one first fixing portion 222 is located outside the impeller 122, so that the stability of the rotating wheel can be improved.

[0501] In some embodiments, the outer diameter of at least one first fixing portion 222 located outside the impeller 122 is substantially the same as the outer diameter of the end of the impeller 122 adjacent to the second air inlet 401. The first fixing portion 222 secures and supports the plurality of blades 221, thereby improving the stability of the impeller 122 and extending its service life.

[0502] In some embodiments, when the first fan assembly 500 rotates, a third zone (low pressure area) is formed in the second channel 404, and one end of the impeller 122 is arranged opposite to the second air inlet 401, so that the airflow enters the interior of the impeller 122 from the second air inlet 401, thereby shortening the flow path of the airflow entering the impeller 122.

[0503] In some embodiments, a second air outlet 402 extending radially along the impeller 122 is formed in the volute 21, and the second air outlet 402 is connected to the first channel 111 so that the airflow flowing radially along the impeller 122 flows from the second air outlet 402 into the first channel 111 without changing the flow direction 2 of the airflow again, thereby improving the efficiency of airflow transportation.

[0504] In some embodiments, the air flow in the gap between the volute 21 and the fan 17 flows along the rotation direction in the second channel 404 (such as counterclockwise rotation) toward the second air outlet 402. The gap tends to shrink along the flow direction, and the gap tends to expand at the position connected to the second air outlet 402, which will cause air leakage at the volute tongue, and then cause poor backflow at the volute tongue, resulting in prominent blade passing frequency (BPF) noise; the volute tongue has a large chamfer transition, which will also cause poor outflow at this location and thus louder noise; the part of the volute 21 adjacent to the volute tongue suddenly changes to a flat shape, causing the pressure to be converted into dynamic pressure in advance, resulting in a large air volume loss and an increase in the octave average (OA) of the noise.

[0505] In some embodiments, as shown in Figures 72 and 73, the volute 21 includes a first volute portion 12, which is a concave surface. In order to adapt to the fan 17 and facilitate the assembly of the fan 17, a second channel 404 that matches the eccentric vortex line inside the fan 17 can be formed between the first volute portion 12 and the fan 17. The second channel 404 can make the airflow transition of the fan 17 more natural and smooth, thereby differentiating and reducing the impact of the airflow.

[0506] The volute 21 includes a tongue 11, which is connected to the first volute portion 12 and located at the second air outlet 402. The first volute portion 12 can adapt to the changes in the airflow driven by the fan 17 as it returns from the tongue 11 to the inside of the second channel 404, ensuring a smooth return of the airflow to the interior of the second channel 404, reducing disturbances to the operation of the fan 17 and ensuring stable airflow from the fan 17. This maintains airflow stability, especially when resistance increases (such as when the filter or heat exchanger is clogged), and reduces abnormal noise caused by airflow fluctuations.

[0507] In some embodiments, as shown in FIG74 , the inner surface of the first volute portion 12 and the axis perpendicular to the fan 17 are used as reference planes, and the intersection line formed by the intersection of the reference plane and the inner surface of the first volute portion 12 is the first profile line 14 of the first volute portion 12. During operation, the fan 17 accelerates the local airflow through mechanical rotation to generate a negative pressure area. A third channel 1811 (as shown in FIG85 ) is formed between any two adjacent blades 221 among the plurality of blades 221. The third channel 1811 (e.g., a blade channel) is connected to the second channel 404. The third channel 1811 allows the surrounding airflow to flow into the third channel 1811. The first side surface of the blade 221 can realize the conversion of the external airflow from dynamic pressure to static pressure, and the second side surface of the blade 221 realizes the conversion of static pressure to dynamic pressure.

[0508] During this process, the matching of the third channel 1811 and the second channel 404 allows the airflow in the second channel 404 to flow into the third channel 1811, changing the airflow direction. Because the position of the first volute portion 12 and the volute tongue 11 is required to convert the dynamic pressure of the airflow drawn into the third channel 1811 into static pressure, the change in the first profile 14 should not be too large.

[0509] In some embodiments, the first profile 14 is fitted with a parabola according to a mathematical relationship. As shown in FIG74 , the X-axis and Y-axis are located on a reference plane along the axis of the fan 17, with the center of the fan 17 as the origin. The X-axis is parallel to the airflow direction of the volute 21, the positive direction of the X-axis points to the location of the second air outlet 402, and the Y-axis is perpendicular to the X-axis. The trajectory of the first profile satisfies the predetermined relationship.

[0510] The first type of line fits the trajectory of the parabola according to the mathematical relationship:

[0511] y=p1×x 6 +p2×x 5 +p3×x 4 +p4×x 3 +p5×x 2 +p6×x+p7, where p1, p2, p3, p4, p5, p6, and p7 are natural numbers, x is the value on the X axis, and y is the value on the Y axis. For example, the coordinates of point 1 (point-1) are (x1, y1), the coordinates of point 2 (point-2) are (x2, y2), and the coordinates of point j (point-j) are (x j ,y j ).

[0512] The values ​​of p1, p2, p3, p4, p5, p6, and p7 vary for fans 17 of different sizes. For example, a fan 17 with a radius of 200 mm is shown in Table 3. Table 3 provides three embodiments. The values ​​of p1, p2, p3, p4, p5, p6, and p7 in any of these three embodiments can roughly achieve a smooth transition of the first profile 14.

[0513] Table 3

[0514] In some embodiments, p1 = 43.23, p2 = -7.2, p3 = -76.67, p4 = 9.596, p5 = 107.7, p6 = -13.67, and p7 = -216.8.

[0515] In other embodiments, p1 = 28.94, p2 = -17.21, p3 = -118.3, p4 = 75.3, p5 = 75.3, p6 = -27.12, and p7 = -222.6.

[0516] In some other embodiments, p1 = 57.52, p2 = 2.812, p3 = -35.07, p4 = 33.91, p5 = 140.2, p6 = -0.2119, and p7 = -210.9.

[0517] According to Table 3, a first profile 14 with a relatively smooth transition can be fitted.

[0518] As shown in FIG. 75 , in some embodiments, the distance between the volute 21 and the center of the fan 17 is represented by M. i Indicates that, along the direction of the pointer arrow in Figure 75, M i There is a trend of first getting bigger and then getting smaller. Since the first profile 14 obtained in this way is not a smooth parabola, it is not conducive to the smooth transition of the airflow and thus causes the aerodynamic noise in the flow channel to become larger.

[0519] In some embodiments, the first profile 14 in the second channel 404 connected to the volute tongue 11 plays a role of diffusing pressure between the upper and lower parts. The first profile 14 should show a smooth increasing trend to avoid flattening mutation phenomenon.

[0520] As shown in Figures 72 to 74, in some embodiments, the first profile 14 is arranged counterclockwise in Figure 74, and the distance between the first profile 14 and the center of the fan 17 decreases smoothly, and the first profile 14 shows an increasing trend near the volute tongue 11, so that the airflow in the second channel 404 transitions smoothly when passing through the second air outlet 402, and is less likely to cause the problem of increased airflow noise in the second channel 404. The smooth first profile 14 can eliminate the sudden pressure change at the bottom, and the overall dynamic and static pressure conversion is more uniform and layered, which will be beneficial to noise reduction.

[0521] Therefore, starting from the connection position between the first profile 14 and the volute tongue 11, the distance between the first profile 14 and the fan 17 can be avoided from gradually shrinking. According to the mathematical relationship in the above embodiment, a smoothly transitioned first profile 14 is fitted, thereby eliminating the pressure mutation on the inner surface of the second channel 404 near the bottom of the first volute portion 12, and the overall dynamic and static pressure conversion is more uniform and layered, which is conducive to noise reduction.

[0522] In some embodiments, as shown in FIG74 and FIG76 , the first end of the first profile 14 is in close proximity to the volute tongue 11, and the distance between the first profile 14 and the fan 17 does not show a trend of gradually shrinking. The first profile 14 includes j points, with a point on the side of the first profile 14 close to the volute tongue 11 being the first point, and the j points are arranged in sequence along the clockwise direction of the arrow in FIG76 toward the direction away from the volute tongue 11. The length of the line connecting the i-th point and the center of the circle is N i , that is, N i is the distance between the j points on the first profile 14 and the center of the circle, N i Satisfy the relationship: N i+1 -Ni ≥0, i=1,…j.

[0523] The first profile 14 is formed on the basis of the parabola formed by the mathematical relationship by satisfying N i+1 -N i ≥0, i=1, ...j, to calibrate the j points of the first profile 14, so that the first profile 14 satisfies the mathematical relationship and the parabolic growth value presents a smooth increasing trend, the airflow transition will be smoother, and the noise of the airflow rotation in the flow channel will be reduced.

[0524] In some embodiments, as shown in Figure 77, the volute tongue 11 has a rounded corner structure. Assume that the diameter of the fan 17 is D and the radius of the volute tongue 11 is r.

[0525] When 0.105×D>r, the radius of the volute tongue becomes small, which may cause the problem of increased noise at the volute tongue.

[0526] In some embodiments, D and r satisfy the relationship: 0.105×D<r.

[0527] For example, D is 200 mm and r is 22 mm. This is conducive to airflow transition and reduces the noise of airflow rotation in the flow channel.

[0528] When r>0.165×D, the radius of the volute tongue becomes large, and the aerodynamic performance of the first fan assembly 500 is reduced.

[0529] In some embodiments, D and r satisfy the relationship: r<0.165×D.

[0530] For example, D is 200 mm and r is 32 mm, which is beneficial to improving the efficiency of airflow transition and the aerodynamic performance of the first fan assembly 500.

[0531] In some embodiments, D and r satisfy the relationship: 0.105×D<r<0.165×D.

[0532] For example, D is 200mm and r is 27mm. This is beneficial to improving the efficiency of airflow transition and reducing the noise of airflow rotation in the flow channel. The radius of the volute tongue 11 is proportional to the diameter of the fan 17, and r is between 0.105×D and 0.165×D. For example, the diameter of the fan 17 is D, and the radius of the volute tongue 11 can be 0.15D. The radius of the volute tongue 11 is too small and presents a pointed tongue shape, resulting in an unclear drainage effect at the second air outlet 402. The airflow at the second air outlet 402 suddenly changes greatly, resulting in a high frequency of airflow fluctuations at high flow rates, which can easily cause BPF pitch. If the radius of the volute tongue 11 is too large, it will hinder the air outlet and easily generate gas vortices at the volute tongue 11, increasing noise.

[0533] As shown in Figure 78, the end of the volute tongue 11 adjacent to the first profile 14 is set as point P, and the angle between the line OP connecting the center O of the fan 17 and point P and the X-axis is a. Assuming that the angle between the X-axis and the X-axis after rotating counterclockwise is positive, the angle a satisfies the relationship: -2°≤a≤5°.

[0534] When a<-2°, the air outlet area of ​​the second air outlet 402 surrounded by the volute 21 and the volute tongue 11 is large, resulting in unstable airflow output by the fan 17.

[0535] When the angle a is greater than 5°, the air outlet area of ​​the second air outlet 402 surrounded by the volute 21 and the volute tongue 11 is small, resulting in noise when the fan 17 outputs air.

[0536] In some embodiments, the range of a is -2° to 5°, for example, a is -1°, 1° or 3°, etc. This can reduce the disturbance to the operation of the fan 17, stabilize the airflow output by the fan 17, and help reduce the noise at the volute tongue 11.

[0537] In the related art, the gap between the first profile 14 near the volute tongue 11 and the fan tends to shrink, which can easily lead to flow collection at the volute tongue 11, resulting in a larger dynamic pressure at the volute tongue 11, faster airflow, and more prominent BPF sound.

[0538] As shown in Figures 77 and 80, in some embodiments, the first profile 14 includes j points, with a point on the side of the first profile 14 close to the tongue 11 being the first point. The j points are arranged sequentially away from the tongue 11. The distance between the i-th point and the outer contour of the fan 17 is bi, where bi satisfies the relationship: bi+1-bi≥0. That is, as shown in Figure 79, b2≥b1. This means that the distance between the first profile 14 and the outer circumference of the fan 17 remains constant or increases, avoiding a tapering situation. This prevents flow concentration at the tongue 11, which results in a higher dynamic pressure at the tongue 11, and also prevents accelerated flow at the tongue 11, which could lead to a prominent BPF sound.

[0539] In some embodiments, as shown in FIG77 , if the diameter of the fan 17 is D, and D and bi satisfy the relationship: 0.045×D≥bi, since the gap between the first profile 14 and the outer peripheral surface of the fan 17 is too small, the gas reflux at the volute tongue 11 is affected, which can easily cause the BPF pitch.

[0540] In some embodiments, D and bi satisfy the relationship: 0.045×D<bi. For example, D is 200 mm and bi is 10 mm, which is beneficial to reducing noise and extending the service life of the volute 21 and the fan 17.

[0541] In some embodiments, as shown in FIG77 , if the diameter of the fan 17 is D, and D and bi satisfy the relationship: bi ≥ 0.08×D, since the gap between the first profile 14 and the outer peripheral surface of the fan 17 is too large, the position of the volute tongue 11 is likely to hinder the air outlet, and the backflow at the volute tongue 11 is obvious, resulting in low efficiency and small air volume of the fan 17.

[0542] In some embodiments, D and bi satisfy the relationship: bi < 0.08 × D. For example, D is 200 mm and bi is 15 mm, which is beneficial to improving the airflow output efficiency.

[0543] In some embodiments, as shown in FIG77 , assuming that the diameter of the fan 17 is D, D and bi satisfy the relationship: 0.045×D<bi<0.08×D.

[0544] When the diameter of the fan 17 is D, bi can be 0.06D. For example, when D is 200 mm, bi is 12 mm. This can reduce noise and improve airflow output efficiency.

[0545] In some embodiments, as shown in Figures 72 and 73, the volute 21 further includes a second volute portion 13, which is connected to the first volute portion 12 and protrudes away from each other. The second volute portion 13 includes a first portion 1301, which is a concave surface. The second volute portion 13 also includes a second portion 1302, which is a flat surface. The concave surface of the first portion 1301 is configured to accommodate the installation of the fan 17. The second volute portion 13 cooperates with the first volute portion 12 to form a second channel 404 between the first volute portion 12, the second volute portion 13, and the fan 17, which matches the vortex lines of the airflow. The second channel 404 can make the airflow driven by the fan 17 transition more naturally and smoothly, thereby gradually differentiating and reducing the impact of the airflow.

[0546] In some embodiments, the fan 17 can drive the airflow from the side close to the volute 11 back to the second channel 404, so that the airflow can reduce the disturbance to the operation of the fan 17, making the airflow of the fan 17 stable, especially when the resistance increases (such as when the filter and heat exchanger are dirty and clogged), maintaining the stability of the airflow and avoiding abnormal noise caused by airflow fluctuations.

[0547] As shown in Figures 77 and 78 , the intersection line formed by the inner surface of the second volute portion 13 and the reference surface is the second profile line 15 of the second volute portion 13. One end of the second profile line 15 is connected to the first profile line 14. The second profile line 15 includes a connected curved segment and a straight segment. The first end of the curved segment of the second volute portion 13 is connected to the first volute portion 12, the second end of the curved segment is connected to the first end of the straight segment, and the second end of the straight segment and the volute tongue 11 form the second air outlet 402.

[0548] The portion of the second profile 15 corresponding to the first portion 1301 of the second volute portion 13 is a curved segment, and the portion of the second profile 15 corresponding to the second portion 1302 of the second volute portion 13 is a straight segment. The first end of the straight segment is joined to the second end of the curved segment, and the joining portion between the curved segment and the straight segment has a smooth transition. This is conducive to a smooth transition of the airflow from the surface of the curved segment to the surface of the straight segment, making the streamline of the airflow in the second channel 404 smooth, avoiding the occurrence and development of turbulence caused by sudden changes in curvature, and improving the noise level.

[0549] In some embodiments, the straight line segment is an inclined straight line segment, so that the second air outlet 402 defined by the second channel 404 and the volute tongue 11 tends to increase along the center of the fan 17 toward the second air outlet 402 .

[0550] On the other hand, by setting the straight line segment as an inclined straight line segment, the size of the second air outlet 402 defined by the second volute portion 13 and the volute tongue 11 gradually increases in the height direction in the flow direction of the airflow (clockwise direction indicated by the arrow as shown in Figure 75), which can reduce the pressure drop of the second air outlet 402, help the airflow to remain smooth, make the streamline of the airflow in the second channel 404 smooth, avoid the occurrence and development of turbulence caused by sudden changes in curvature, and improve the noise level.

[0551] In some embodiments, the volute tongue 11 is substantially parallel to the axial direction of the fan 17. The volute tongue 11 is spaced apart from the fan 17 and is parallel to the axial direction of the fan 17, so that the streamline of the airflow in the second channel 404 is smooth.

[0552] In some embodiments, the first fan assembly 500 includes two fans 17, which can be respectively arranged on both sides of the fan, and the fan drives the two fans 17 to rotate. In this way, the air outlet speed of the second air outlet 402 can be increased, and the first fan assembly 500 can run smoothly.

[0553] In some embodiments, a second air inlet 401 is provided on one axial side of the fan 17 and a second air outlet 402 is provided on one radial side. The fan 17 includes a plurality of blades 221 spaced apart along the circumference of the fan 17. Each of the plurality of blades 221 has one end facing the second air inlet 401 and the other end extending away from the second air inlet 401.

[0554] Fan 17 includes 41 blades 221. Compared to 43 blades in the related art, the reduced number of blades 221 can reduce the volume of fan 17, reduce the weight of the air conditioner, and reduce production costs, resulting in good economic benefits. However, if the number of blades 221 is too small, the distance between blades 221 will increase, the airflow velocity will decrease, and it will be easy to cause boundary layer separation of the airflow, thereby reducing efficiency.

[0555] In some embodiments, the blades 221 may be backward blades, forward blades, radial blades, etc.

[0556] In some embodiments, as shown in Figures 81 and 82 , fan 17 includes a first connecting portion 1020 disposed at one axial end of the plurality of blades 221 and connected to a portion of the circumferential outer side of the plurality of blades 221. Fan 17 also includes a second connecting portion 1021 disposed at the other axial end of the plurality of blades 221 and connected to the other axial ends of the plurality of blades 221. This can increase the strength of fan 17, reduce airflow dispersion within fan 17, and increase the air volume output by air conditioner 1000.

[0557] In some embodiments, the blade 221 and the first connection portion 1020 and the second connection portion 1021 may be connected by welding.

[0558] In some embodiments, the connection between the blade 221 and the first connection portion 1020 and the second connection portion 1021 is a detachable connection, which is convenient for maintenance and replacement.

[0559] In some embodiments, the blade 221 , the first connection portion 1020 , and the second connection portion 1021 are an integrally formed structure, which can reduce production costs.

[0560] In some embodiments, the thickness of each blade 221 of the fan 17 is equal. In this way, compared with the blades 221 with larger and unequal thickness in the related art, the volume and weight of the fan 17 will be reduced. Therefore, the volume and weight of the fan 17 can be reduced (the weight of the fan 17 is reduced by 20%), reducing production costs and having good economic benefits.

[0561] In some embodiments, as shown in Figures 83, 84 and 86, two adjacent blades 221 among the multiple blades 221 form a third air inlet 1812 (such as a blade air inlet) on the radial inner side, and form a third air outlet 1813 (such as a blade air outlet) on the radial outer side, the diameter of the circle where one end of any blade 221 among the multiple blades 221 faces the third air outlet 1813 is D1, and the thickness of the blade 221 is δ.

[0562] In some embodiments, if δ and D1 satisfy the relationship: 0.0065×D1>δ, the thickness δ of blades 221 is too small. Given a certain number of blades 221, the spacing between blades 221, i.e., third channel 1811, increases, reducing the area of ​​contact between airflow and blades 221. This reduces the airflow processing capability of fan 17 and airflow efficiency. This results in the first fan assembly 500 requiring more power to output the same air volume, increasing energy consumption. Furthermore, since the thickness δ of blades 221 is too small, the airflow has a larger flow space, potentially causing unstable airflow, generating vortices and turbulence, and thus increasing the noise of air conditioner 1000.

[0563] In some embodiments, δ and D1 satisfy the relationship: 0.0065×D1≤δ, for example, D1 is 200 mm and δ is 1.4 mm. This is beneficial to improving the stable flow of airflow, reducing phenomena such as eddies and turbulence, and reducing the noise of the air conditioner 1000.

[0564] In some embodiments, if δ and D1 satisfy the relationship: δ>0.011×D1, the thickness δ of the blade 221 is too large. When the number of blades 221 is constant, the spacing between the blades 221, that is, the third channel 1811, will become smaller. The thickness of the blade 221 occupies part of the flow space of the airflow, affecting the flow of the airflow. In addition, the excessive thickness of the blade 221 will increase the friction loss, and the energy transferred by the blade 221 to the airflow is reduced. The dynamic pressure at the third air outlet 1813 also decreases, thereby affecting the air output of the air conditioner 1000.

[0565] In some embodiments, δ and D1 satisfy the relationship: δ≤0.011×D1, for example, D1 is 200 mm, and δ is 2 mm. This is beneficial to reducing the wear of the blades 221 and increasing the air output of the air conditioner 1000.

[0566] In some embodiments, δ and D1 satisfy the relationship: 0.0065×D1≤δ≤0.011×D1. For example, D1 is 200 mm and δ is 1.7 mm. This is conducive to improving the stable flow of airflow, increasing the air output of the air conditioner 1000, and reducing the noise of the air conditioner 1000.

[0567] It will be appreciated that two adjacent blades 221 define a third channel 1811 in the radial direction of fan 17. Third channel 1811 (e.g., a blade path) communicates with third air inlet 1812 and third air outlet 1813. Airflow enters third channel 1811 from third air inlet 1812. During operation of fan 17, blades 221 perform work on the airflow, generating static and dynamic pressure, causing the airflow within third channel 1811 to be output from third air outlet 1813.

[0568] According to the velocity triangle, as shown in FIG84 , the airflow entering the third channel 1811 from the third air inlet 1812 has an absolute velocity c1, whose components are the relative velocity w1 and the circumferential velocity u1 along the direction of the blade 221. The airflow passes through the third channel 1811 and flows out from the third air outlet 1813 at an absolute velocity c2. Similarly, the velocity components are the relative velocity w2 and the circumferential velocity u2 along the direction of the blade 221. In this process, the greater the static pressure obtained by the third channel 1811, the smaller the dynamic pressure at the third air outlet 1813. If the volute 21 matched with it is constant, the smaller the pressure loss in the flow channel of the volute 21, the greater the dynamic pressure conversion at the air outlet, that is, the air flow rate increases. Among them, the relevant calculation formulas (3) and (4) satisfy: P T =P8+P9+P 10 Formula (3)

[0569] In formula (3), P8 represents the static pressure increase due to centrifugal force when the air flows through the fan 17, P9 represents the static pressure increase converted by the relative speed reduction of the air flow due to the change in the cross-sectional area of ​​the third channel 1811, and P 10 represents the kinetic energy gained by the airflow through third channel 1811. After leaving blades 221, the airflow still has a certain velocity as it enters volute 21. The velocity decreases in third channel 1811, converting some of the kinetic energy into static pressure. This pressure is then converted to dynamic pressure at third air outlet 1813 before the airflow leaves first fan assembly 500. ρ in formula (4) represents the airflow density.

[0570] Therefore, according to the formula, the absolute speed, relative speed and circumferential speed of the speed triangle are closely related to the design parameters of the fan 17.

[0571] In some embodiments, as shown in FIG. 84 and FIG. 85 , the diameter of the circle where the end of any blade 221 of the plurality of blades 221 facing the third air inlet 1812 is located is D2 , and the relationship between D1 and D2 satisfies the following equation: D2 < D1 .

[0572] In some embodiments, if the relationship between D1 and D2 satisfies 0.815>D2 / D1, that is, the ratio of D2 to D1 is less than 0.815, when the ratio of D2 to D1 is too small, the third channel 1811 will be longer and the cross-sectional area at the third air outlet 1813 will be small, the resistance of the airflow in the third channel 1811 will increase, the energy loss will increase, and the air volume at the third air outlet 1813 will become smaller.

[0573] In some embodiments, D1 and D2 satisfy the relationship 0.815≤D2 / D1. For example, D1 is 200 mm and D2 is 164 mm. This is conducive to the flow of air in the third channel 1811.

[0574] In some embodiments, if the relationship between D1 and D2 satisfies D2 / D1>0.855, that is, the cross-sectional area at the third air outlet 1813 is larger, the airflow in the third channel 1811 is unstable, and eddies and turbulence are easily generated, thereby increasing the noise of the air conditioner 1000.

[0575] In some embodiments, D1 and D2 satisfy the relationship D2 / D1≤0.855. For example, D1 is 200 mm and D2 is 170 mm. This helps reduce the noise of the air conditioner 1000.

[0576] In some embodiments, D1 and D2 satisfy the relationship 0.815≤D2 / D1≤0.855. For example, D1 is 200 mm and D2 is 167 mm. This is beneficial for the airflow to flow in the third channel 1811 and for reducing the noise of the air conditioner 1000.

[0577] In some embodiments, as shown in FIG87 , the distance between two adjacent blades 221 among the multiple blades 221 is Δ (Δ1 or Δ2 as shown in FIG87 ). If the relationship between Δ and D1 satisfies 0.03×D1>Δ, the distance Δ is too small. When the size of the fan 17 remains unchanged, the number of blades 221 must be increased. In this way, the weight of the fan 17 will also increase, and the production cost will increase. Moreover, a too small distance Δ will affect the flow of airflow. The increase in frictional resistance during the flow of airflow will further affect the air volume, and noise will also be generated due to the turbulent flow of airflow.

[0578] In some embodiments, Δ and D1 satisfy the relationship: 0.03×D1≤Δ. For example, D1 is 200 mm and Δ is 6 mm. This is beneficial to the flow of air and increases the outflow of air in the third channel 1811.

[0579] In some embodiments, as shown in Figure 87, if the relationship between Δ and D1 satisfies Δ>0.04×D1, the distance Δ is too large. If the distance Δ is too large, the flow space of the airflow in the third channel 1811 becomes larger, and some airflow is scattered or overflows from the third channel 1811, which reduces the air volume reaching the third air outlet 1813, affecting the use effect of the air conditioner 1000.

[0580] In some embodiments, the relationship between Δ and D1 satisfies Δ≤0.04×D1. For example, D1 is 200 mm and Δ is 8 mm. This can improve the stability of the airflow in the third channel 1811 and facilitate the outflow of air at the third air outlet 1813.

[0581] In some embodiments, as shown in FIG87 , Δ and D1 satisfy the relationship: 0.03×D1≤Δ≤0.04×D1. For example, D1 is 200 mm and Δ is 7 mm. This can improve the stability of the airflow in the third channel 1811 and facilitate the flow of airflow.

[0582] In some embodiments, when the distance Δ between two adjacent blades 221 is not less than 0.03D1 and not greater than 0.04D1, the fan 17 has a larger air output.

[0583] When Δ is 0.035D1, the length of the third channel 1811 is moderate, the cross-sectional area at the third air outlet 1813 is appropriate, the airflow can flow stably in the third channel 1811 without generating additional energy loss, so that the dynamic pressure at the third air outlet 1813 is larger and a larger air volume can be generated.

[0584] As shown in FIG85 to FIG87, the angle between the extension line of any blade 221 of the plurality of blades 221 on the side facing the third air inlet 1812 and the tangent line of the circle on which the end of any blade 221 of the plurality of blades 221 facing the third air inlet 1812 lies is β 1A In fact, the angle between the airflow and the tangent line of the circle where the end of any blade 221 of the plurality of blades 221 facing the third air inlet 1812 is located is β1, β 1A and β1 satisfy the relationship: β 1A <β1. β 1A is the inlet installation angle, β1 is the blade inlet angle, and the inlet installation angle β 1A is a fixed value, which is determined when the fan 17 is assembled. The blade inlet angle β1 is not a fixed value, and the inlet installation angle β 1A The difference between the blade inlet angle β1 is the angle of attack, and the inlet installation angle β 1A Less than the blade inlet angle β1, that is, the angle of attack i=(β 1A -β1)<0.

[0585] This effectively reduces airflow at third air inlet 1812, converting the dynamic pressure of the airflow into static pressure and reducing the generation of vortices. The higher the static pressure generated, the greater the dynamic pressure (i.e., air volume) converted from the airflow through third channel 1811 at third air outlet 1813, thus increasing the air volume of air conditioner 1000 by 5.3%. Furthermore, the angle of attack ensures that the airflow experiences significant boundary layer separation only at third air outlet 1813 and prevents it from spreading. This limits the generation of vortices to, or even eliminates, vortices at, third air outlet 1813, resulting in a superior noise reduction effect.

[0586] If the angle of attack i=(β 1A-β1)>0, the airflow will produce boundary layer separation at the third air inlet 1812 and gradually expand toward the third air outlet 1813, resulting in greater flow loss and reducing the air volume at the third air outlet 1813.

[0587] In some embodiments, if β 1A Satisfies the relationship: 80°>β 1A When rotating, eddy current will be generated, which will easily generate noise.

[0588] In some embodiments, β 1A Satisfy the relationship: 80°≤β 1A , for example, β 1A It is 80°, which can reduce the generation of eddy currents and help reduce noise.

[0589] In some embodiments, if β 1A Satisfies the relationship: β 1A When the angle is greater than 90°, the flow of the airflow at the third air inlet 1812 will be reduced, resulting in increased energy loss at the third air inlet 1812.

[0590] In some embodiments, β 1A Satisfies the relationship: β 1A ≤90°, for example, β 1A It is 90°, which is beneficial to reducing energy loss at the third air inlet 1812.

[0591] In some embodiments, β 1A Satisfy the relationship: 80°≤β 1A ≤90°, for example, β 1A It is 85°, so that the flow of air at the third air inlet 1812 can be reduced, the dynamic pressure of the air flow can be converted into static pressure as much as possible, the generation of vortexes can be reduced, the energy loss at the third air inlet 1812 is small, and the air volume at the third air inlet 1812 is increased.

[0592] In some embodiments, as shown in FIG85 to FIG87, the angle between the extension line and the tangent line of the circle where the end of any blade 221 of the plurality of blades 221 facing the third air inlet 1812 is located is β 2A .

[0593] In some embodiments, if β 2A Satisfying the relationship 150°>β 2A When the outlet installation angle β 2A If it is too small, the distance Δ will decrease, which will affect the flow of air. The increase in friction resistance during the flow of air will further affect the air volume and generate noise due to the turbulent flow of air.

[0594] In some embodiments, β 2ASatisfy the relationship: 150°≤β 2A For example, β 2A It is 150°, which helps to reduce the noise caused by turbulent air flow.

[0595] In some embodiments, if β 2A Satisfying the relationship 165°<β 2A When the outlet installation angle β 2A If the value is too large, the distance Δ increases, the flow space of the airflow in the third channel 1811 becomes larger, and some airflow is scattered or overflows from the third channel 1811, which reduces the air volume reaching the third air inlet 1812 and affects the use effect of the air conditioner.

[0596] In some embodiments, β 2A Satisfies the relationship: β 2A ≤165°. For example, β 2A It is 165°, so that the air volume entering the third channel 1811 can be increased.

[0597] In some embodiments, β 2A Satisfy the relationship: 150°≤β 2A ≤165°. For example, β 2A It is 160°, which can reduce the noise caused by air flow turbulence, increase the air volume in the third channel 1811, and improve the output air flow of the air conditioner 1000.

[0598] In some embodiments, due to the outlet installation angle β 2A If the value is too large or too small, the curved shape of the blade 221 will be affected, and the spacing Δ between two adjacent blades 221 will change. 2A When the value is not less than 150° and not greater than 165°, the fan 17 has a larger air output.

[0599] As shown in Figures 83 and 85 , each of the multiple blades 221 includes, in the radial direction, a first section 114 (e.g., a guide arc section), one end of which is disposed toward the third air inlet 1812. The blade 221 also includes, in the radial direction, a second section 115 (e.g., a pressurization arc section) connected to the first section 114. The portion of the blade 221 in the radial direction that faces the third air outlet 1813 is the second section 115. The second section 115 and the first section 114 are connected at one end proximal to each other.

[0600] In some embodiments, the first segment 114 and the second segment 115 have different arc radii, and the arc radius of the second segment 115 is larger than the arc radius of the first segment 114. For example, the blade 221 of the fan 17 is a double-arc blade 221. In the radial direction of the blade 221, the portion away from the center of the fan 17 is the second segment 115, and the portion close to the center of the fan 17 is the first segment 114. The arc radius of the second segment 115 is larger than the arc radius of the first segment 114.

[0601] In addition, the side of the first section 114 close to the center of the fan 17 is connected to the side of the second section 115 close to the center of the fan 17, and the side of the first section 114 away from the center of the fan 17 is also connected to the side of the second section 115 away from the center of the fan 17. When the fan 17 is running, the airflow enters from the third air inlet 1812, the airflow is first guided by the first section 114 and then pressurized by the second section 115, and then flows out from the third air outlet 1813. The pressurized airflow passing through the second section 115 can improve the air outlet efficiency at the third air outlet 1813 and reduce the noise of the fan 17.

[0602] In some embodiments, the double-arc blades 221 can be an integral piece, which facilitates production and reduces production costs.

[0603] In some embodiments, the first section 114 and the second section 115 of the double-arc blade 221 can be separated to facilitate maintenance and replacement.

[0604] As shown in Figures 81 to 83, multiple blades 221 surround to form a first cavity 30, and the second connecting portion 1021 protrudes toward the first cavity 30 to form a second cavity 131. One end of the second cavity 131 is an open end, and the other end of the second cavity 131 is a closed end, and the closed end of the second cavity 131 is located in the first cavity 30. At least a portion of the first fan assembly 500 cooperates with one side of the open end of the second cavity 131, and at least a portion of the first fan assembly 500 is disposed in the second cavity 131.

[0605] In some embodiments, as shown in Figures 88 to 91 , the indoor unit 10 includes a first driving member 130. The first driving member 130 is disposed at the first air outlet 112. The indoor unit 10 also includes a first spoiler 116 (e.g., a first spoiler bar). The first spoiler 116 is connected to the first driving member 130. The first driving member 130 is configured to drive the first spoiler 116 to rotate about the axis of the first driving member 130. The length of the first spoiler 116 is substantially parallel to the axis of the first driving member 130.

[0606] The indoor unit 10 further includes a second driving member 140. The second driving member 140 is disposed at the first air outlet 112. The indoor unit 10 further includes a second spoiler 117 (e.g., a second spoiler bar). The second spoiler 117 is disposed at the first air outlet 112; the second driving member 140 is configured to drive the second spoiler 117 to rotate about an axis of the second driving member 140. The length of the second spoiler 117 is substantially parallel to the axis of the second driving member 140.

[0607] It should be noted that the first driving member 130 and the second driving member 140 include but are not limited to motors.

[0608] Thus, the first driving member 130 drives the first spoiler 116, and the second driving member 140 drives the second spoiler 117 to move (such as rotate), so that the first spoiler 116 and the second spoiler 117 disrupt the airflow output from the first air outlet 112 to prevent the airflow from blowing directly into the user.

[0609] In some embodiments, the first spoiler 116 and the second spoiler 117 are arranged in parallel, and the length direction of the first spoiler 116 and the second spoiler 117 is the same as the length direction of the first air outlet 112. In this way, the first spoiler 116 and the second spoiler 117 can disrupt more airflow output from the first air outlet 112.

[0610] In some embodiments, the first spoiler 116 and the second spoiler 117 have the same length, and the ends of the first spoiler 116 and the second spoiler 117 are flush. In this way, the uniformity of the disturbance of the airflow output from the first air outlet 112 by the first spoiler 116 and the second spoiler 117 can be improved.

[0611] In some embodiments, the first spoiler 116 and the second spoiler 117 rotate in the same direction but at different frequencies, which can improve the disruptive effect of the first spoiler 116 and the second spoiler 117 on the airflow output from the first air outlet 112 .

[0612] In some embodiments, the first spoiler 116 and the second spoiler 117 rotate in different directions but at the same frequency, so that the disruptive effect of the first spoiler 116 and the second spoiler 117 on the airflow output from the first air outlet 112 can also be improved.

[0613] In some embodiments, as shown in Figures 91 and 92, the indoor unit 10 further includes a first connecting rod 540, which is connected to one end of the first driving member 130. The first connecting rod 540 is arranged parallel to and spaced apart from the first spoiler 116, and the first connecting rod 540 is connected to the output shaft of the first driving member 130. In this way, the first driving member 130 can drive the first spoiler 116 to rotate via the first connecting rod 540.

[0614] In some embodiments, as shown in Figures 91 and 92, the indoor unit 10 further includes a second connecting rod 550, which is located between the first spoiler 116 and the first connecting rod 540. A first end of the second connecting rod 550 is connected to the first spoiler 116, and a second end of the second connecting rod 550 is connected to the first connecting rod 540. In this way, the connection between the first spoiler 116 and the first connecting rod 540 can be achieved through the second connecting rod 550.

[0615] In some embodiments, the length direction of the second connecting rod 550 may be perpendicular to or at other angles to the length direction of the first spoiler 116 . The second connecting rod 550 may provide a transmission connection between the first spoiler 116 and the first connecting rod 540 .

[0616] In some embodiments, the first connecting rod 540 is coaxially arranged with the output shaft of the first driving member 130 , and the first spoiler 116 is parallel to and spaced apart from the output shaft of the first driving member 130 , so that the first spoiler 116 can rotate around the output shaft of the first driving member 130 .

[0617] In some embodiments, as shown in Figures 89 and 90, the indoor unit 10 further includes a first gear 110. The first gear 110 is sleeved on the outside of the output shaft of the first driving member 130 and is coaxially arranged with the output shaft. The first gear 110 is connected to the first gear 110 via the output shaft of the first driving member 130 to drive the first gear 110 to rotate, and the second spoiler 117 is connected to the first gear 110.

[0618] For example, the first driving member 130 is configured to drive the first gear 110 to rotate, and the rotation of the first gear 110 can drive the second spoiler 117 to rotate around the axis of the output shaft of the first driving member 130. Since the distances between the first spoiler 116 and the second spoiler 117 and the axis of the output shaft of the first driving member 130 are different, the first spoiler 116 and the second spoiler 117 rotate around the axis of the output shaft of the first driving member 130 at different rates, thereby improving the disruptive effect on the airflow.

[0619] As shown in Figure 91, in some embodiments, the indoor unit 10 further includes a second gear 120, which is drivingly connected to the output shaft of the second driving member 140. For example, the second gear 120 can be sleeved outside the output shaft of the second driving member 140 and arranged coaxially with the output shaft. The first gear 110 meshes with the second gear 120. The second driving member 140 drives the second gear 120 to rotate, and the second gear 120 drives the first gear 110, which in turn drives the second spoiler 117 to rotate. In this way, the rotation of the first spoiler 116 and the second spoiler 117 can enhance the disruptive effect on the airflow at the first air outlet 112.

[0620] In some embodiments, as shown in Figures 93 and 94, the diameter of the pitch circle of the second gear 120 is smaller than the diameter of the pitch circle of the first gear 110, thereby changing the transmission ratio between the first gear 110 and the second gear 120. Even if the output shaft speeds of the first driving member 130 and the second driving member 140 are the same, the rotation speeds of the first spoiler 116 and the second spoiler 117 are different. In this way, the output airflow passing through the first air outlet 112 can be made softer.

[0621] In some embodiments, as shown in Figures 95, 96, and 99, a first engaging portion 140A is provided at one end of the first connecting rod 540 near the first driving member 130, and a second engaging portion 150 (as shown in Figure 103) is provided at one end of the first driving member 130 near the first connecting rod 540. The first engaging portion 140A is inserted into the second engaging portion 150.

[0622] It is understandable that the first matching portion 140A can be removed from the second matching portion 150 , which facilitates replacement or maintenance of the first spoiler 116 .

[0623] In some embodiments, the first spoiler 116 , the second connecting rod 550 , the first connecting rod 540 and the first matching portion 140A may be an integrated structure, which helps to improve the strength of the structure.

[0624] In some embodiments, as shown in Figures 101 to 103, the first gear 110 includes a third mating portion 160, and a fourth mating portion 900 is provided at one end of the second spoiler 117 near the first driving member 130. The fourth mating portion 900 is inserted into the third mating portion 160 and can be removed from the third mating portion 160 to facilitate replacement or maintenance of the second spoiler 117.

[0625] In some embodiments, as shown in Figures 97, 102 and 104, a third connecting rod 800 is provided at the end of the second spoiler 117 close to the first gear 110, the length direction of the third connecting rod 800 is perpendicular to the length direction of the second spoiler 117, the first end of the third connecting rod 800 is connected to the second spoiler 117; the second end of the third connecting rod 800 is connected to the fourth matching portion 900.

[0626] In some embodiments, as shown in FIG. 100 , the second spoiler 117 , the third connecting rod 800 , and the fourth matching portion 900 may be an integrated structure, which is beneficial for improving the strength of the structure.

[0627] In some embodiments, as shown in FIG89 , the indoor unit 10 includes a mounting plate located at the first air outlet 112 , through which the first driving member 130 and the second driving member 140 pass to connect with the first spoiler 116 and the second spoiler 117 .

[0628] In some embodiments, the mounting plate is disposed at the first air outlet 112 , the first driving member 130 and the second driving member 140 are located on the side of the mounting plate away from the accommodating space 109 , and the first driving member 130 and the second driving member 140 are located on the side of the mounting plate close to the accommodating space 109 .

[0629] In some embodiments, an air guide plate is provided at the first air outlet 112 . When the air guide plate closes the first air outlet 112 , the first spoiler 116 and the second spoiler 117 are located inside the indoor unit 10 .

[0630] In some embodiments, as shown in FIG98 , the first gear 110 includes a first hole, which is a circular hole and is disposed along the thickness direction of the first gear 110. The axis of the first hole is collinear with the axis of the first gear 110. The output shaft of the first driving member 130 is located in the first hole and can rotate within the first hole.

[0631] For example, the diameter of the output shaft of the first driving member 130 is smaller than the diameter of the first hole, so as to improve the smoothness of the rotation of the first gear 110 relative to the output shaft of the first driving member 130 .

[0632] In some embodiments, a bearing is provided on the output shaft of the first driving member 130, which connects the output shaft of the first driving member 130 to the first gear 110. The bearing includes an inner ring and an outer ring. The inner ring is coaxially disposed within the outer ring and rotatably connected to the outer ring. The inner ring is sleeved around the output shaft of the first driving member 130, and the outer ring is disposed within the first hole. The bearing improves the smoothness of the rotation of the first gear 110 relative to the output shaft of the first driving member 130.

[0633] In some embodiments, as shown in Figures 97 and 104, the second gear 120 includes a second hole. The second hole is a circular hole and is arranged along the thickness direction of the second gear 120. The axis of the second hole is collinear with the axis of the second gear 120. The second gear 120 includes a keyway, and the second hole is connected to the keyway. The outer peripheral wall of the output shaft of the second driving member 140 is provided with a connecting key. The output shaft of the second driving member 140 is inserted into the second hole so that the connecting key matches the keyway, thereby enabling the second driving member 140 to drive the second gear 120 to rotate.

[0634] In some embodiments, the first heat exchanger 300 includes a first heat exchange section, a second heat exchange section, and a third heat exchange section connected in sequence. The first heat exchange section is located farther from the wall than the third heat exchange section, and the second heat exchange section is located above the first heat exchange section. Indoor air enters the indoor unit 10 through the first air inlet 101, passes through the first, second, and third heat exchange sections, and is then output through the first air outlet 112. The first, second, and third heat exchange sections isolate the fan 17 from the first air inlet 101. This improves the heat exchange efficiency of the first heat exchanger 300.

[0635] In some embodiments, the lengths of the first, second, and third heat exchange sections are aligned with the length of the indoor unit 10. The first heat exchange section is located within the accommodation space 109 on a side away from the wall. The width of the first heat exchange section is vertical, while the width of the second heat exchange section is inclined. The second heat exchange section tilts upward toward the wall, with the bottom of the second heat exchange section connected to the top of the first heat exchange section. The third heat exchange section tilts downward toward the wall, with the top of the third heat exchange section connected to the top of the second heat exchange section.

[0636] In some embodiments, the indoor unit further includes a grille, which is disposed at the first air inlet 101 . This prevents debris from entering the housing 100 through the first air inlet 101 and helps extend the service life of the air conditioner 1000 .

[0637] It should be noted that any one of the technical solutions disclosed in the present disclosure can solve one or more of the above-mentioned technical problems and achieve certain invention purposes to a certain extent; multiple technical disclosures can also be combined into an overall solution to solve one or more of the above-mentioned technical problems and achieve certain invention purposes; some of the technical disclosures can also be selected to combine into an overall solution, while adopting related technologies and deteriorated solutions, but the deterioration trend can be compensated by the means disclosed in this technology, and the above-mentioned one or more technical problems can be solved to a certain extent as a whole and certain invention purposes can be achieved; each technical disclosure combined into a complete technical solution constitutes an organic and inseparable overall solution, which solves technical problems as a whole and achieves certain invention purposes.

[0638] Any technical disclosure in this disclosure, as well as the recombination of multiple technical disclosures, can form a complete technical solution and can solve one or more of the above-mentioned technical problems and achieve the purpose of the invention. They all belong to the content of this disclosure and are the content that is directly and unambiguously determined based on the content of this disclosure.

[0639] In the description of the above embodiments, specific features, structures, materials or characteristics may be combined in an appropriate manner in any one or more embodiments or examples.

[0640] Those skilled in the art will understand that the scope of the present invention is not limited to the above specific embodiments, and that certain elements of the embodiments may be modified and replaced without departing from the spirit of the present application. The scope of the present application is limited by the appended claims.

Claims

1. An air conditioner, comprising: Outdoor unit; as well as The indoor unit is connected to the outdoor unit and comprises: A housing including a first mounting cavity; A fan assembly is disposed in the first installation cavity, and the fan assembly includes: a volute, comprising a second mounting cavity; and A fan is disposed in the second installation cavity, and the fan comprises: Motor; a plurality of blades; and An impeller is connected to the motor and comprises: A first connection part is connected to the motor, the plurality of blades are arranged at intervals along the circumference of the first connection part, and the first connection part includes: A first connecting portion body; At least one first air guide portion is arranged along the side wall of the first connecting portion body; Among them, the air inlet end of the fan is defined as the first end; the end along the axial direction of the fan and opposite to the first end is defined as the second end; along the direction from the first end to the second end, the first air guide portion is inclined relative to the axis of the first connecting portion; the contour line of the first air guide portion includes multiple arc lines, and the radii of the multiple arc lines are different.

2. The air conditioner according to claim 1, wherein: Along a reference line of the at least one first air guide portion, in a direction from the first end to the second end, a width of the first air guide portion first increases and then decreases.

3. The air conditioner according to claim 1 or 2, wherein: The multiple arc lines of the first air guide portion include: a first arc line, disposed close to the first end; a second arc line, disposed near the second end; A first connecting line is disposed on one side of the center line of the at least one first air guide portion and is connected between the first arc line and the second arc line; and A second connecting line is provided on the other side of the center line of the first air guide portion opposite to the one side, and is connected between the first arc line and the second arc line; The line connecting the center of the first arc line and the center of the second arc line is defined as LP1, the first connecting line and the second connecting line are located on both sides of LP1, and the first connecting line and the second connecting line are asymmetric relative to LP1.

4. The air conditioner according to claim 3, wherein: The dimension of the impeller along its axial direction is defined as H1, and the distance between the center of the second arc line and the end face of the impeller close to the second end is defined as H2, then H1 and H2 satisfy: H2 = (0.21-0.39) H1.

5. The air conditioner according to claim 3, wherein: A line symmetrical to LP1 of the first connecting line is defined as LP1′, and LP1′ is located on a side of the second connecting line close to the first connecting line.

6. The air conditioner according to any one of claims 3 to 5, wherein: The second connecting line comprises: a third arc line, located on a side of the second connecting line close to the first end; a fourth arc line, located on a side of the second connecting line close to the second end; and The fifth arc line is located between the third arc line and the fourth arc line, and is connected to the third arc line and the fourth arc line respectively.

7. The air conditioner according to claim 6, wherein: Along the axial direction of the fan, the distance between the center of the first arc line and the center of the fourth arc line is defined as d1; Along the radial direction of the fan, a distance between the center of the fourth arc line and the center of the second arc line is defined as d2; Along the axial direction of the fan, a distance between the center of the first arc line and the center of the second arc line is defined as d3; Then the d1 and the d2 satisfy: d2 = (0.91 ~ 1.14) d1; the d1 and the d3 satisfy: d1 = (0.68 ~ 1.04) d3.

8. The air conditioner according to claim 7, wherein: Along the axial direction of the fan, a distance between the center of the first arc line and the center of the second arc line is defined as d3; Along the radial direction of the fan, a distance between the center of the first arc line and the center of the second arc line is defined as d4; Define the distance between the center of the second arc line and the end surface of the impeller close to the second end as H2; Then d3, d4 and H2 satisfy:

9. The air conditioner according to any one of claims 1 to 8, wherein: The impeller further includes a second connection portion; one end of the plurality of blades is connected to the second connection portion and are arranged at intervals along the circumference of the second connection portion; The first connection portion is connected to a side of the second connection portion away from the plurality of blades.

10. The air conditioner according to any one of claims 1 to 9, wherein: The volute also includes: a second air guide portion, through which the airflow enters the second installation cavity; the fan is coaxially arranged with the second air guide portion; and The third air guide portion is connected to the second air guide portion; the air inlet side of the fan is arranged toward the third air guide portion.

11. The air conditioner according to claim 10, wherein: Define the maximum outer diameter of the plurality of blades as a first size D0; The inner diameter of the third air guide portion is defined as a second size D1; Then the first size D0 and the second size D1 satisfy a first relationship.

12. The air conditioner according to claim 11, wherein: The first relational expression is: 0.83≤D1 / D0≤0.

91.

13. The air conditioner according to claim 11 or 12, wherein: In the axial direction of the fan, a distance between the fan and one side of the third air guide portion close to each other is defined as X1; The dimension of the impeller along its axial direction is defined as H1; Then X1 and H1 satisfy: X1 = (2Q / 3600φ) × H1; Wherein, Q is the volume flow rate of the fan in the working range, and φ is the pressure coefficient.

14. The air conditioner according to claim 13, wherein: The H1 and the first dimension D0 satisfy: Wherein, ω is the angular velocity of the fan, and n is a constant.

15. The air conditioner according to any one of claims 11 to 14, wherein: An inner diameter of the second air guiding portion is defined as a third dimension D2; Then the ratio of the third size D2 to the second size D1 is any value in [1.06, 1.29].

16. The air conditioner according to claim 11 to 15, wherein: The third size D2 and the second size D1 also satisfy: D2 = D1 + 2D; Wherein, D is any value in [5mm, 12mm].

17. The air conditioner according to any one of claims 10 to 16, wherein: In the axial direction of the fan, a side of the fan close to the third air guide portion is defined, and a side of the fan close to the third air guide portion is defined. The distance between the two sides is X1; In the axial direction of the fan, a distance between a side of the fan close to the second air guide portion and a side of the second air guide portion away from the fan is defined as X2; Then X1 and X2 satisfy: X2=X1+D; wherein D is a constant.

18. The air conditioner according to any one of claims 10 to 17, wherein: The third air guide portion comprises: a fixing portion, the third air guide portion being connected to the volute through the fixing portion; and A guide portion, formed by extending from one side of the fixing portion close to the center thereof toward the installation cavity; The radius R1 of the guide portion is defined as any value in the range of [16 mm, 30 mm].

19. The air conditioner according to any one of claims 10 to 18, wherein: The end surfaces of the plurality of blades close to the first end have rounded corners; defining two adjacent leaves among the plurality of leaves as a first sub-leaf and a second sub-leaf; The radius of the fillet on the end surface of the first sub-blade close to the first end is defined as R2, and the radius of the fillet on the end surface of the second sub-blade close to the first end is defined as R3, then R2 is not equal to R3.

20. The air conditioner according to any one of claims 10 to 19, wherein: Taking a plane perpendicular to the axis of the fan as a reference plane, the orthographic projections of the plurality of blades on the reference plane are located within a range defined by a side of the third air guide portion close to the plurality of blades.

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