WO2024037083A1

WO2024037083A1 - Air conditioner, centrifugal fan, and air conditioner indoor unit

Info

Publication number: WO2024037083A1
Application number: PCT/CN2023/095355
Authority: WO
Inventors: 张震; 张荣海; 王鹏宇; 齐宝; 冯月文; 颜鲁华
Original assignee: 青岛海信日立空调系统有限公司
Priority date: 2022-08-18
Filing date: 2023-05-19
Publication date: 2024-02-22

Abstract

An air conditioner (100), a centrifugal fan (102A), and an air conditioner indoor unit (10). The air conditioner (100) comprises the air conditioner indoor unit (10). The air conditioner indoor unit (10) comprises a housing (101), and at least one fan assembly (102) and a fin heat exchanger (103) which are provided in the housing (101). Any one of the at least one fan assembly (102) comprises an air vent (24); the air vent (24) is arranged toward an air outlet (16) of the housing (101) and comprises a target edge (240); the target edge (240) is an edge of the air vent (24) in a first direction; the fin heat exchanger (103) is located between the air outlet (16) and the air vent (24) and is provided with a plurality of wind receiving areas (M2); each wind receiving area (M2) comprises a target fin (320); the target fin (320) is a fin, located at the edge, among partial fins (32) corresponding to the wind receiving area (M2); the target fin (320) corresponds to the target edge (240) of the air vent (24) corresponding to the wind receiving area (M2), and a target included angle (μ) between the line connecting the target fin (320) to the corresponding target edge (240) and the first direction is any angle within a first preset angle range.

Description

Air conditioners, centrifugal fans and air conditioning indoor units

This application claims the priority of the Chinese patent application with application number 202211001615.7 submitted on August 19, 2022, and the priority of the Chinese patent application with application number 202210992858.5 submitted on August 18, 2022, all of which The contents are incorporated into this application by reference.

Technical field

The present disclosure relates to the technical field of household appliances, and in particular to an air conditioner, a centrifugal fan and an air conditioning indoor unit.

Background technique

Air conditioners have become a common appliance in people's work and life. Among them, duct air conditioners have the characteristics of small size, beautiful appearance and easy maintenance.

Contents of the invention

On the one hand, an air conditioner is provided. The air conditioner includes an indoor unit. The indoor unit includes a housing, at least one fan assembly and a fin heat exchanger. The housing includes an air outlet. The at least one fan assembly is disposed in the housing, and any one of the at least one fan assembly includes an air outlet, the air outlet is disposed toward the air outlet, and includes a target edge, the target edge is the edge of the air outlet along the first direction. The fin heat exchanger is arranged in the housing and is located between the air outlet and the air outlet. The fin heat exchanger includes a plurality of fins; the plurality of fins are spaced apart along the first direction, and the first direction is perpendicular to the plurality of fins. The fin heat exchanger has a plurality of wind receiving areas, and the multiple wind receiving areas are located on a side of the plurality of fins close to the air outlet; any one of the multiple wind receiving areas is exposed to The wind area corresponds to a portion of the plurality of fins, and the portion of the fins is in contact with air flowing out of an air outlet of a fan assembly. The partial fins corresponding to any of the wind receiving areas include a target fin, and the target fin is a fin located at the edge of the partial fins. The target fin corresponds to the target edge of the air outlet corresponding to any wind receiving area, and a connection line between the target fin and the corresponding target edge and the first The target angle between the directions is any angle within the first preset angle range.

On the other hand, a centrifugal fan is provided. The centrifugal fan includes a volute, at least one current collector, an impeller and at least one reinforcing rib. The volute has an air outlet and an air inlet, and the volute includes an enclosure, at least one side of the enclosure is open to form an opening. The at least one current collector is connected to the enclosure. Any one of the at least one current collector corresponds to an opening and blocks the opening. The air inlet is provided on the current collector, and the air outlet is provided on the enclosure. The impeller is arranged in the volute. The at least one reinforcing rib connects at least one axial end of the impeller. Any one of the at least one reinforcing ribs extends along the circumferential direction of the impeller. The at least one reinforcing rib includes a first end surface and a second end surface. The first end surface is spaced apart from the second end surface by a predetermined distance, and the first end surface is closer to the impeller than the second end surface. The current collector includes a connecting portion and a bending portion. The connecting portion connects the bending portion and the enclosure respectively, and is located on a side of the first end surface away from the impeller; the bending portion The portion protrudes in a direction away from the impeller relative to the connecting portion and is arranged around the air inlet.

Description of drawings

Figure 1 is a structural diagram of an air conditioner according to some embodiments;

Figure 2 is a perspective view of an air conditioning indoor unit according to some embodiments;

Figure 3 is a perspective view of the internal unit of the air conditioner in Figure 2 from another perspective;

Figure 4 is an exploded view of a housing of an air conditioner according to some embodiments;

Figure 5 is a cross-sectional view of a housing of an air conditioner according to some embodiments;

Figure 6 is a perspective view of an air conditioning indoor unit with the casing removed according to some embodiments;

Figure 7 is a structural diagram of an air conditioning indoor unit according to some embodiments;

Figure 8 is a cross-sectional view of an air conditioning indoor unit according to some embodiments;

Figure 9 is another cross-sectional view of an air conditioning indoor unit according to some embodiments;

Figure 10 is another cross-sectional view of an air conditioning indoor unit according to some embodiments;

Figure 11 is a structural diagram of a centrifugal fan in related art;

Figure 12A is a structural diagram of an air conditioning indoor unit according to some embodiments;

Figure 12B is another structural diagram of an air conditioning indoor unit according to some embodiments;

Figure 13 is a structural diagram of a centrifugal fan according to some embodiments;

Figure 14 is another structural diagram of a centrifugal fan according to some embodiments;

Figure 15 is a partial enlarged view of circle A in Figure 14;

Figure 16 is a schematic diagram of the backflow phenomenon in a centrifugal fan according to some embodiments;

Figure 17 is a structural diagram of a current collector of a centrifugal fan according to some embodiments;

Figure 18 is a schematic diagram of another backflow phenomenon in a centrifugal fan according to some embodiments;

Figure 19 is a structural diagram of the connecting portion located between the first end surface and the second end surface according to some embodiments.

Detailed ways

Some embodiments of the present disclosure will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present disclosure. Based on the embodiments provided by this disclosure, all other embodiments obtained by those of ordinary skill in the art fall within the scope of protection of this disclosure.

Unless the context otherwise requires, throughout the specification and claims, the term "comprise" and its other forms such as the third person singular "comprises" and the present participle "comprising" are used. Interpreted as open and inclusive, it means "including, but not limited to." In the description of the specification, the terms "one embodiment", "some embodiments", "exemplary embodiments", "example", "specific "example" or "some examples" and the like are intended to indicate that a particular feature, structure, material or characteristic associated with the embodiment or example is included in at least one embodiment or example of the present disclosure. The schematic representations of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials or characteristics described may be included in any suitable manner in any one or more embodiments or examples.

Hereinafter, the terms “first” and “second” are used for descriptive purposes only and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of indicated technical features. Therefore, features defined as "first" and "second" may explicitly or implicitly include one or more of these features. In the description of the embodiments of the present disclosure, unless otherwise specified, "plurality" means two or more.

In describing some embodiments, the expression "connected" and its derivatives may be used. The term "connection" should be understood in a broad sense. For example, "connection" can be a fixed connection, a detachable connection, or an integrated connection; it can be a direct connection or an indirect connection through an intermediate medium. The embodiments disclosed herein are not necessarily limited by the content herein.

"A and/or B" includes the following three combinations: A only, B only, and a combination of A and B.

The use of "suitable for" or "configured to" in this document implies open and inclusive language that does not exclude devices that are suitable for or configured to perform additional tasks or steps.

As used herein, "about," "approximately," or "approximately" includes the stated value as well as an average within an acceptable range of deviations from the particular value, as determined by one of ordinary skill in the art. Determined taking into account the measurement in question and the errors associated with the measurement of the specific quantity (i.e., the limitations of the measurement system).

As used herein, "parallel," "perpendicular," and "equal" include the stated situation as well as situations that are approximate to the stated situation within an acceptable deviation range, where Such acceptable deviation ranges are as determined by one of ordinary skill in the art taking into account the measurement in question and the errors associated with the measurement of the particular quantity (ie, the limitations of the measurement system).

Usually, when the air conditioner is in working condition, the windward side of the fin heat exchanger in the air conditioner indoor unit will produce broadband noise (or called fin sound). The frequency of this broadband noise is in the range of 1000Hz to 3000Hz. Users are more sensitive to noise with frequencies in the range of 1000Hz to 3000Hz.

Figure 1 is a structural diagram of an air conditioner according to some embodiments.

As shown in Figure 1, some embodiments of the present disclosure provide an air conditioner 100.

The air conditioner 100 is a split air conditioner composed of an outdoor unit 20 and an indoor unit 10 . The outdoor unit 20 and the indoor unit 10 are connected through pipelines to transport refrigerant. The outdoor unit 20 includes a compressor 201, a four-way valve 202, an outdoor heat exchanger 203, and an expansion valve 204. The indoor unit 10 includes an indoor heat exchanger 103A (eg, fin heat exchanger 103). The compressor 201, outdoor heat exchanger 203, expansion valve 204 and indoor heat exchanger 103A connected in sequence form a refrigerant circuit. The refrigerant circulates in the refrigerant circuit and mixes with the air through the outdoor heat exchanger 203 and the indoor heat exchanger 103A respectively. Perform heat exchange to achieve air conditioner 100 cooling mode or heating mode.

The compressor 201 is configured to compress the refrigerant such that the low-pressure refrigerant is compressed to form a high-pressure refrigerant.

The outdoor heat exchanger 203 is configured to perform heat exchange between outdoor air and the refrigerant transported in the outdoor heat exchanger 203 . For example, the outdoor heat exchanger 203 works as a condenser in the cooling mode of the air conditioner 100, so that the refrigerant compressed by the compressor 201 dissipates heat to the outdoor air through the outdoor heat exchanger 203 and condenses; the outdoor heat exchanger 203 operates in the cooling mode of the air conditioner 100. In the heating mode, the air conditioner 100 operates as an evaporator, so that the decompressed refrigerant absorbs heat from the outdoor air through the outdoor heat exchanger 203 and evaporates.

The expansion valve 204 is connected between the outdoor heat exchanger 203 and the indoor heat exchanger 103A. The opening of the expansion valve 204 adjusts the pressure of the refrigerant flowing through the outdoor heat exchanger 203 and the indoor heat exchanger 103A to regulate the flow to the outdoors. The refrigerant flow rate between the heat exchanger 203 and the indoor heat exchanger 103A. The flow rate and pressure of the refrigerant flowing between the outdoor heat exchanger 203 and the indoor heat exchanger 103A will affect the heat exchange performance of the outdoor heat exchanger 203 and the indoor heat exchanger 103A. Expansion valve 204 may be an electronic valve. The opening of the expansion valve 204 is adjustable to control the flow rate and pressure of the refrigerant flowing through the expansion valve 204 .

The four-way valve 202 is connected in the refrigerant circuit, and the four-way valve 202 is configured to switch the flow direction of the refrigerant in the refrigerant circuit so that the air conditioner 100 executes the cooling mode or the heating mode.

Figure 2 is a perspective view of an air conditioner internal unit according to some embodiments. Figure 3 is a perspective view of the air conditioner indoor unit in Figure 2 from another perspective.

In some embodiments, as shown in FIGS. 2 and 3 , the indoor unit 10 further includes a housing 101 and a fan assembly 102 . The indoor heat exchanger 103A includes the fin heat exchanger 103. The fan assembly 102 and the fin heat exchanger 103 are installed in the housing 101 respectively.

The fin heat exchanger 103 is configured to perform heat exchange between indoor air and the refrigerant transported in the fin heat exchanger 103 . For example, when the air conditioner 100 is in the cooling mode, the fin heat exchanger 103 serves as an evaporator, and the refrigerant after being dissipated by the outdoor heat exchanger 203 absorbs the heat of the indoor air through the fin heat exchanger 103 and evaporates; when the air conditioner 100 In the heating mode, the fin heat exchanger 103 works as a condenser, and the refrigerant after absorbing heat through the outdoor heat exchanger 203 dissipates heat to the indoor air through the fin heat exchanger 103 to be condensed.

Compared with ordinary heat exchangers, the fin heat exchanger 103 includes fins. The fins can increase the heat transfer area and reduce the thermal resistance of convection heat transfer, thereby improving the heat transfer efficiency of the fin heat exchanger 103. The fins are described below.

The fan assembly 102 is configured to suck indoor air into the indoor unit 10 through the air inlet of the indoor unit 10 and send the indoor air after heat exchange with the fin heat exchanger 103 through the air outlet of the indoor unit 10 . The fan assembly 102 provides power for the flow of indoor air to increase the gas flow through the fin heat exchanger 103 per unit time, which is beneficial to improving the heat exchange efficiency of the fin heat exchanger 103 . The air inlet of the indoor unit 10 and the air outlet of the indoor unit 10 will be described below.

Figure 4 is an exploded view of a housing of an air conditioner according to some embodiments.

In some embodiments, as shown in FIG. 4 , the housing 101 includes a first side plate 11 , a second side plate 12 , a third side plate 13 and a fourth side plate 14 . The first side plate 11 and the second side plate 12 are spaced apart from each other along the second direction (eg, the up and down direction in FIG. 4 ). The third side plate 13 and the fourth side plate 14 are spaced apart along the first direction (eg, the left-right direction in FIG. 4 ). For example, the third side plate 13 and the fourth side plate 14 have substantially the same structure.

The first side plate 11 , the third side plate 13 , the second side plate 12 and the fourth side plate 14 are connected in sequence to form an accommodating cavity 19 .

Figure 5 is a cross-sectional view of a housing of an air conditioner according to some embodiments.

In some embodiments, as shown in FIG. 5 , the housing 101 includes an air outlet 16 and an air inlet 15 . The air outlet 16 and the air inlet 15 are arranged along the third direction (eg, the front and back direction in Figure 5). The air outlet 16 is connected with the accommodation cavity 19 and is located at one end (eg, front end) of the housing 101 . The air inlet 15 is connected with the accommodation cavity 19 and is located at the other end (eg, rear end) of the housing 101 . In other words, the air outlet 16 is located at one end (eg, front end) of the first side panel 11 or the second side panel 12 , and the air inlet 15 is located at the other end (eg, rear end) of the first side panel 11 or the second side panel 12 . ).

In some embodiments, as shown in FIGS. 4 and 5 , the housing 101 further includes a partition 17 . The partition 17 is installed in the accommodation cavity 19 , and is connected to at least one of the first side plate 11 , the second side plate 12 , the third side plate 13 and the fourth side plate 14 . In this way, the accommodating cavity 19 can be divided to facilitate the classified placement and installation of the structural components in the accommodating cavity 19 .

For example, as shown in FIG. 5 , the partition 17 divides the accommodation cavity 19 into a first sub-accommodation cavity 191 and a second sub-accommodation cavity. 192, and the first sub-accommodating cavity 191 and the second sub-accommodating cavity 192 are arranged in the front-rear direction. The second sub-accommodating cavity 192 is connected to the air outlet 16 , and the first sub-accommodating cavity 191 is connected to the air inlet 15 .

In some embodiments, as shown in FIGS. 4 and 5 , the partition 17 includes at least one first opening 171 . The first opening 171 is configured to communicate with the first sub-accommodating cavity 191 and the second sub-accommodating cavity 192 to form a passage from the air inlet 15 to the air outlet 16 within the housing 101 to facilitate air circulation. When the casing 101 satisfies air circulation, the plurality of side plates (such as the first side plate 11 , the second side plate 12 , the third side plate 13 and the fourth side plate 14 ) surrounding the accommodation cavity 19 One or more can be border structures. It is only necessary to provide air circulation ducts on the upper and lower sides or the front and rear sides of the fin heat exchanger 103 so that the shell 101 can satisfy the air circulation. This disclosure does not limit the structure of the multiple side plates surrounding the accommodation cavity 19 .

In some embodiments, the indoor unit 10 may be a duct air conditioner (duct unit). Alternatively, the indoor unit 10 may also be a wall-mounted indoor unit. The following description takes the indoor unit 10 as an air duct unit as an example.

In some embodiments, as shown in FIG. 4 , the indoor unit 10 further includes a plurality of connecting members 181 (eg, connecting ears). A plurality of connectors 181 are distributed at both ends of the housing 101 (such as the left end and the right end), and connect at least one of the first side plate 11 , the third side plate 13 or the fourth side plate 14 .

For example, a plurality of connectors 181 connect the left end and the right end of at least one of the first side plate 11 , the third side plate 13 or the fourth side plate 14 .

In some embodiments, the connector 181 includes a connector hole. The indoor unit 10 can be fixed below the ceiling by passing a fixing member (such as an expansion screw, etc.) through the connection hole and fixedly connecting it to the ceiling.

FIG. 6 is a perspective view of an air conditioning indoor unit with the casing removed according to some embodiments.

In some embodiments, the indoor unit 10 includes one fan assembly 102 or multiple fan assemblies 102 . The fan assembly 102 includes a centrifugal fan to facilitate circulation and heat exchange of indoor air. The centrifugal fan will be described below.

In the case where the indoor unit 10 includes a plurality of fan assemblies 102, the plurality of fan assemblies 102 are spaced apart along the left-right direction, and the axes of the plurality of fan assemblies 102 are approximately parallel to the left-right direction. For example, as shown in FIG. 6 , the indoor unit 10 includes two fan assemblies 102 . The fan assembly 102 includes a volute 21, an impeller 22, an air inlet 23 and an air outlet 24. The impeller 22 is installed in the volute 21 . At least one side of the volute 21 in the left-right direction (ie, the axial direction of the volute 21 ) is open to form an air inlet 23 . The volute 21 is open along one side close to the partition 17 to form an air outlet 24 , and the air outlet 24 faces the fin heat exchanger 103 . The air inlet 23 is connected with the air outlet 24.

In some embodiments, as shown in FIG. 6 , the fin heat exchanger 103 is located in the second sub-containing cavity 192 , and the plurality of air outlets 24 respectively correspond to the plurality of first openings 171 . The air outlet 24 is close to the first opening 171 corresponding to the air outlet 24, and one end (eg, front end) of the volute 21 close to the air outlet 24 is in contact with or connected to the edge of the first opening 171 corresponding to the air outlet 24 (eg, , fitting connection), or the end (such as the front end) of the volute 21 close to the air outlet 24 passes through the corresponding first opening 171 from back to front, so as to facilitate the installation of the air outlet 24 and facilitate the increase of the volute 21 The structural strength of the end close to the air outlet 24.

In this way, when the impeller 22 rotates, the air near the indoor unit 10 will be extracted by the fan assembly 102 and pass through the air inlet 23, the first sub-accommodating chamber 191 and the air inlet 15 in sequence. After that, the extracted air passes through the air outlet in sequence. 24. The first opening 171 is blown to the fin heat exchanger 103 located in the second sub-accommodating cavity 192, and then discharged from the indoor unit 10 through the air outlet 16.

In some embodiments, as shown in FIG. 6 , in the case where the indoor unit 10 includes two fan assemblies 102 , the partition 17 includes two first openings 171 . The two first openings 171 are spaced apart along the first direction. In this way, the air outlets 24 of the two fan assemblies 102 can be installed corresponding to and close to a first opening 171 respectively.

It should be noted that the previous description mainly takes the indoor unit 10 including two fan assemblies 102 as an example. Of course, the indoor unit 10 may also include one, three, four or more fan assemblies 102, which is not covered by this disclosure. is limited, and the number of fan assemblies 102 can be adjusted according to the index of air circulation volume per unit time.

In some embodiments, as shown in FIG. 6 , the blower assembly 102 also includes a motor 25 . The motor 25 is configured to drive the impeller 22 to rotate. The two volutes 21 are spaced apart along the left and right directions, and the motor 25 is installed between the two volutes 21 along the left and right directions, and the left and right ends of the motor 25 can be respectively connected to the two impellers 22 through the rotating shafts, so that the two impellers 22 They can rotate synchronously driven by the same motor 25.

In some embodiments, when the indoor unit 10 includes two fan assemblies 102, the two fan assemblies 102 are divided into Do not include a motor25. In this way, the two motors 25 can be installed in corresponding volutes 21, so that the two impellers 22 can rotate respectively driven by the two motors 25.

Some embodiments of the present disclosure mainly introduce the structure of the indoor unit 10 by taking the fan assembly 102 including a centrifugal fan as an example. Of course, the fan assembly 102 can also be an axial flow fan or a cross-flow fan, which is not limited in this disclosure.

It should be noted that when the fan assembly 102 includes an air inlet 23 and an air outlet 24, only the air inlet 23 is connected to the air inlet 15, and the air outlet 24 is connected to the air outlet 16, so that the air inlet 23 and the air outlet 16 are connected. Driven by the air circulates between the room and the indoor unit 10.

In some embodiments, as shown in FIG. 6 , the fin heat exchanger 103 includes a plurality of refrigerant tubes 31 and a plurality of fins 32 (as shown in FIG. 7 ). The plurality of refrigerant pipes 31 may be connected to the outdoor heat exchanger 203 and the outdoor unit 20 respectively, and the plurality of refrigerant pipes 31 are configured to circulate the refrigerant.

In the second sub-accommodating cavity 192, the plurality of refrigerant tubes 31 can be spaced apart in the up-down and front-to-back directions into multiple rows and columns, and any one of the multiple refrigerant tubes 31 can be arranged in the left-right direction (i.e., , the length direction of the refrigerant pipe 31) extends.

It should be noted that the plurality of fins 32 can be connected in contact with the plurality of refrigerant tubes 31 respectively, so as to increase the contact area between the refrigerant tube 31 and the air through the plurality of fins 32, thereby improving the heat exchange between the refrigerant and the air in the refrigerant tube 31. efficiency.

For example, any one of the plurality of fins 32 includes a plurality of through holes, and the plurality of through holes correspond to the plurality of refrigerant tubes 31 . The plurality of fins 32 are spaced apart along the left-right direction, so that the through holes corresponding to any one of the plurality of fins 32 are aligned along the left-right direction.

In this way, the plurality of refrigerant tubes 31 can be inserted into the corresponding through holes of the plurality of fins 32 from left to right (or from right to left), so that the plurality of refrigerant tubes 31 are in plug-in contact with the plurality of fins 32 . After that, connect the left end and the right end of the refrigerant pipe 31 (for example, the left end of one refrigerant pipe 31 is connected with the left end of another refrigerant pipe 31, and the right end of one refrigerant pipe 31 is connected with the right end of another refrigerant pipe 31). In this way, many The left and right ends of each refrigerant pipe 31 are connected respectively, or the plurality of refrigerant pipes 31 are divided into multiple groups, and the left and right ends of each group of refrigerant pipes 31 are connected to facilitate the circulation of the refrigerant.

It can be understood that by arranging a plurality of fins 32 spaced apart along the left and right directions, the heat dissipation area of the multiple refrigerant tubes 31 is increased, which is conducive to improving the heat exchange efficiency between the refrigerant and the air in the refrigerant tube 31, thereby quickly increasing or decreasing the heat exchange efficiency. The temperature of the air flowing through the fin heat exchanger 103.

In some embodiments, fin heat exchanger 103 has a block-like structure. For example, a plurality of sequentially connected refrigerant channels are opened in the middle of the fin heat exchanger 103, and the surface of the fin heat exchanger 103 is cut to form a fin structure. This fin structure can increase the heat exchange area of the fin heat exchanger 103.

It should be noted that the fins 32 may have a sheet-like structure, and the fins 32 may be approximately perpendicular to the left-right direction.

In some embodiments, as shown in FIG. 6 , the fin heat exchanger 103 further includes a first end 33 and a second end 34 . The first end 33 and the second end 34 are arranged opposite to each other.

When installing the fin heat exchanger 103, the first end 33 is close to the first side plate 11, the second end 34 is close to the second side plate 12 (as shown in Figure 4), and in the front and rear direction, the second end 34 is located between the first end 33 and the partition 17 or the fan assembly 102. In this way, the first end 33 and the air outlet 24 are spaced apart in the front and rear direction, and the fin heat exchanger 103 is located between the air outlet 16 and the air outlet 24 .

In this case, as shown in FIG. 6 , a first distance D1 between the second end 34 and the fan assembly 102 and a second distance D2 between the first end 33 and the fan assembly 102 are defined along the front-to-back direction. The first distance D1 and the second distance D2 are different from each other, and the first distance D1 is smaller than the second distance D2. In this way, the angle between the fin heat exchanger 103 and the first side plate 11 is an acute angle, and a first area M1 is formed between the first end 33 of the fin heat exchanger 103 and the first side plate 11 (as shown in Figure 6 Show).

In some embodiments, when installing the fan assembly 102, the axes of the plurality of fan assemblies 102 may be set to be approximately parallel to the left and right directions respectively. In this way, corresponding to the location of the first area M1, the air outlet 24 can be disposed close to the first area M1.

The above description mainly takes the shell 101 including the partition 17 as an example. Of course, in some embodiments, the partition 17 can also be omitted. In this case, it is only necessary to move the air outlet 24 closer to the fin heat exchanger 103 direction (for example, the side close to the first side plate 11 in the up and down direction), thereby increasing the contact area between the fin heat exchanger 103 and the air, and simplifying the structure of the casing 101 .

It should be noted that the previous description mainly takes the first distance D1 and the second distance D2 as different examples. certainly, In some embodiments, the first distance D1 and the second distance D2 may also be the same. In this case, the position of the fin heat exchanger 103 is directly opposite to the position of the air outlet 24 .

It should be noted that in some embodiments, when the indoor unit 10 includes multiple fan assemblies 102, any one of the multiple fan assemblies 102 may include a centrifugal fan, a cross-flow fan, or a cross-flow fan with approximately the same structure and shape. One of the fans or axial flow fans. The shape and size of the air outlet 24 of any one of the plurality of fan assemblies 102 may be the same. Furthermore, in the front-to-back direction, the distance between the air outlet 24 of any one of the plurality of fan assemblies 102 and the fin heat exchanger 103 is approximately the same.

Figure 7 is a structural diagram of an air conditioning indoor unit according to some embodiments.

In some embodiments, as shown in FIG. 7 , the indoor unit 10 includes a first fan assembly 1021 , a second fan assembly 1022 and a third fan assembly 1023 that are spaced apart in the left and right direction. When the first fan assembly 1021 , the second fan assembly 1022 and the third fan assembly 1023 respectively blow air from back to front toward the air outlet 16 , the angles between the rear sides of the plurality of fins 32 and the flow direction of the air are not exactly the same. .

Figure 8 is a cross-sectional view of an air conditioning indoor unit according to some embodiments.

In some embodiments, as shown in Figure 8, the fin heat exchanger 103 has a second area M2 (wind area). The second area M2 is located on a side (eg, the rear side) of the fin 32 close to the air outlet 24 , and at least a portion of the fin 32 is located within the second area M2 .

The fin heat exchanger 103 may have one or more second regions M2. When the indoor unit 10 includes multiple second areas M2 and multiple fan assemblies 102, the multiple fan assemblies 102 include multiple air outlets 24, and the multiple air outlets 24 respectively correspond to the multiple second areas M2.

Any one of the wind receiving areas M2 among the plurality of second areas M2 corresponds to a portion of the fins 32 of the plurality of fins 32 , and the portion of the fins 32 is in contact with the air flowing out of one air outlet 24 . When the air blown out by one of the plurality of air outlets 24 comes into contact with a corresponding part of the fins 32 in the second area M2, the angle between the flow direction of the air and the first direction is defined as the second target. Angle α (as shown in Figure 7).

For example, as shown in FIG. 8 , the indoor unit 10 includes a first sub-area M21 , a second sub-area M22 , a fourth fan assembly 1024 and a fifth fan assembly 1025 . The fourth fan assembly 1024 includes a first air outlet 241 , and the fifth fan assembly 1025 includes a second air outlet 242 . The first sub-region M21 corresponds to the first air outlet 241, and the second sub-region M22 corresponds to the second air outlet 242. In this case, when the air blown out by the first air outlet 241 contacts some of the fins 32 in the first sub-region M21, the angle between the air and the left and right directions is the second target corresponding to the first air outlet 241. Angle α. When the air blown out of the second air outlet 242 contacts some of the fins 32 in the second sub-region M22, the angle between the air and the left and right direction is the second target included angle α corresponding to the second air outlet 242.

It should be noted that, as shown in FIG. 7 , when the flow direction of the air P is parallel to the target plane, the second target included angle α is within the target plane or a plane parallel to the target plane. The target plane refers to the plane where the front-to-back direction and the left-right direction are located. Of course, in some embodiments, the flow direction of the air may not be parallel to the target plane.

In some embodiments, the fin heat exchanger 103 extends in the left-right direction, and the second target included angle α corresponding to the left and right ends of the fin heat exchanger 103 and the middle part of the fin heat exchanger 103 is smaller.

For example, the second target angle α corresponding to a part of the left end and the right end of the fin heat exchanger 103 (for example, the left end is close to the lower side and the right end is close to the lower side) is less than 30°, and in the fin heat exchanger 103 The second target angle α corresponding to the positions of the two second regions M2 that are close to each other is close to 30°.

It should be noted that when the fan assembly 102 is operating, broadband noise (ie, fin sound) with a frequency in the range of 1000 Hz to 3000 Hz will be generated at the target position of the fin heat exchanger 103 . The target position may be a position on the fin heat exchanger 103 corresponding to the second target included angle α between 10° and 30°.

Therefore, the structure and size of the fin heat exchanger 103, the fan assembly 102 and the housing 101 in the indoor unit 10 can be adjusted to set the second target angle corresponding to each point on the windward surface of the fin heat exchanger 103. α is adjusted to less than 10° or greater than 30° to avoid fin sound.

However, when the area of the air outlet 24 is small or the area of the second region M2 corresponding to the air outlet 24 is large, for example, the area of the second region M2 is larger than the area of the air outlet 24, then the air outlet will be smaller in the front-rear direction. The projection of 24 on the fin heat exchanger 103 will be located in the second area M2 corresponding to the air outlet 24 . In this way, when part of the air flowing out of the air outlet 24 is blown toward the fin heat exchanger 103 in the front-to-back direction, the angle between the flow direction of this part of the air and the left-right direction (the second The target angle α) will be close to or equal to 90°. The second target included angle α corresponding to the two ends (eg, left end and right end) of the fin heat exchanger 103 is smaller.

If the structure or size of the indoor unit 10 is adjusted so that the second target angle α corresponding to the two ends (for example, the left end and the right end) of the fin heat exchanger 103 is less than 10°, then due to the To the middle of the fin heat exchanger 103, the second target included angle α becomes larger and larger, then the second target included angle α will appear on the fin heat exchanger 103 at a position of 10° to 30°, thereby generating fin heat exchanger 103. Film sound.

Therefore, in some embodiments of the present disclosure, by adjusting the structure and size of the fin heat exchanger 103, the fan assembly 102 and the housing 101 in the indoor unit 10, multiple points corresponding to each point on the fin heat exchanger 103 can be adjusted. The minimum value of the second target included angle α is greater than 30° to avoid fin sound on the fin heat exchanger 103 .

In some embodiments, as shown in FIG. 6 , the air outlet 24 includes a target edge 240 . The target edge 240 is the edge of the air outlet 24 along the first direction.

In some embodiments, as shown in FIG. 7 , the partial fins 32 corresponding to the second area M2 include target fins 320 . The target fin 320 is a fin located at an edge (eg, the left edge or the right edge) of the partial fins 32 . The target fin 320 corresponds to the target edge 240 of the air outlet 24 corresponding to the second area M2.

In this case, the corresponding target included angle μ of any one of the plurality of air outlets 24 is the minimum value of the second target included angle α corresponding to the air outlet 24 . The angle between the connecting line between the target fin 320 and the corresponding target edge 240 and the first direction is set as the first target included angle μ (target included angle μ).

For example, as shown in FIG. 7 , the partial fins 32 corresponding to the second area M2 include the target fins 320 . When the target connection line K between the target edge 240 of the air outlet 24 of the third fan assembly 1023 and the target fins 320 is parallel to the target plane, the angle between the target connection line K and the left and right direction is the first target included angle. μ. Here, the target fin 320 refers to the fin 32 closest to the fourth side plate 14 among the partial fins 32 corresponding to the air outlet 24 of the third fan assembly 1023 . The target edge 240 of the air outlet 24 of the third fan assembly 1023 refers to the edge of the air outlet 24 of the third fan assembly 1023 close to the fourth side plate 14 in the left-right direction.

In some embodiments, there are multiple connecting lines between the target edge 240 and the target fin 320 , and the angle between the target connecting lines and the left and right direction is the target included angle μ. The target connection line refers to a connection line among the plurality of connection lines that is parallel to the target plane.

It should be noted that by adjusting the structure and size of the fin heat exchanger 103, the fan assembly 102 and the housing 101 in the indoor unit 10, any one of the plurality of fan assemblies 102 corresponds to the first The target included angle μ is any angle within the first preset angle range. The first preset angle range is 30° to 90°. In this way, the size of the second target angle α can be increased, which is beneficial to avoiding the generation of fin sound.

For example, the first target included angle μ corresponding to any one of the plurality of fan assemblies 102 is set to be greater than 35°, 40°, or 60°. In this way, the second target included angle α between 10° and 10° can be avoided. 30° area, which is beneficial to reducing the fin sound generated by the fin heat exchanger 103.

In some embodiments, when the area of the second region M2 is larger than the area of the air outlet 24 , the position where the fin sound is generated at one end of the second region M2 close to the third side plate 13 and the position of the second region M2 are The position where the fin sound is generated near the end of the fourth side plate 14 is concentrated toward the end near the first side plate 11 or the end near the second side plate 12 , or the end of the second area M2 near the first side plate 11 The position where the fin sound is generated, and the position where the fin sound is generated at the end of the second area M2 close to the second side plate 12, is concentrated toward the end close to the third side plate 13 or the end close to the fourth side plate 14, thereby reducing the fin sound. The area on the fin heat exchanger 103 where fin sound is generated is beneficial to reducing the intensity of the fin sound in the indoor unit 10 .

Figure 9 is another cross-sectional view of an indoor unit of an air conditioner according to some embodiments.

In some embodiments, as shown in Figure 9, the indoor unit 10 includes a sixth fan assembly 1026 and a seventh fan assembly 1027. The sixth fan assembly 1026 includes a third air outlet 243, and the seventh fan assembly 1027 includes a fourth air outlet. 244. In this case, the third air outlet 243 and the fourth air outlet 244 may have the same shape and size.

The width of any one of the plurality of air outlets 24 in the first direction is defined as a first spacing L1.

For example, as shown in FIG. 9 , the widths of the third air outlet 243 and the fourth air outlet 244 in the left-right direction are respectively the first distance L1.

In some embodiments, the shapes and sizes of the third air outlet 243 and the fourth air outlet 244 are not exactly the same. A distance L1 is the width corresponding to the air outlet 24 with a larger width in the left-right direction among the third air outlet 243 and the fourth air outlet 244.

It should be noted that the third distance D3 (as shown in FIG. 9 ) between two adjacent fins 32 in the left-right direction is between 1.4 mm and 1.8 mm. For example, the third distance D3 is 1.4mm, 1.6mm or 1.8mm. When the third distance D3 is greater than 1.8 mm, it is not conducive to the contact between the air flowing between two adjacent fins 32 and the fins 32 . When the third distance D3 is less than 1.4 mm, it is not conducive to the smooth circulation of air.

In some embodiments, as shown in FIG. 9 , the sixth fan assembly 1026 is located on a side (eg, the left side) of the seventh fan assembly 1027 close to the third side plate 13 , and the third air outlet 243 is located at the fourth air outlet. The side of 244 close to the third side plate 13 (eg, the left side). In the left-right direction, the end of the fin heat exchanger 103 close to the third side plate 13 (eg, the left end) is located at the side of the third air outlet 243 close to the third side plate 13 (eg, the left end). One end (eg, the right end) of the fin heat exchanger 103 close to the fourth side plate 14 is located on the side (eg, the right side) of the fourth air outlet 244 close to the fourth side plate 14 .

In this case, in the left-right direction, the right end of the fin heat exchanger 103 is closer to the fourth side plate 14 than the fourth air outlet 244, and the left end of the fin heat exchanger 103 is closer to the third outlet. The air port 243 is closer to the third side plate 13 .

In this way, it is advantageous to adjust the structure and size of the fin heat exchanger 103, the fan assembly 102 and the casing 101 in the indoor unit 10 so that both ends of the fin heat exchanger 103 (such as The second target included angle α corresponding to the end close to the third side plate 13 and the end close to the fourth side plate 14 is greater than 30°.

It is defined that along the first direction, the distance between the end of the fin heat exchanger 103 close to the third side plate 13 and the air outlet 24 of the plurality of air outlets 24 closest to the third side plate 13 is the second Spacing L2.

For example, as shown in FIG. 9 , the distance between the left end of the fin heat exchanger 103 and the third air outlet 243 is the second distance L2. The smaller the ratio (L2/L1) of the second distance L2 to the first distance L1, the smaller the interval value of the second target angle α.

Therefore, the width of the fin heat exchanger 103 in the left-right direction, the installation position of the fin heat exchanger 103, or the width of the leftmost air outlet 24 (eg, the fourth air outlet 244) can be adjusted. The ratio of the second distance L2 to the first distance L1 (L2/L1) is any value within the first preset ratio range, thereby adjusting the size of the second target angle α. For example, the first preset ratio range is 0.1 to 0.85. That is to say, the ratio of the second distance L2 to the first distance L1 is greater than 0.1 and less than or equal to 0.85 (0.1≤L2/L1≤0.85). For example, the ratio of the second distance L2 to the first distance L1 is 0.1, 0.3, or 0.85.

In this way, the fin heat exchanger 103 can have a larger heat dissipation area, and the size of the leftmost air outlet 24 (for example, the fourth air outlet 244) of the fin heat exchanger 103 can be reduced. To reduce a partial area on one end (eg, the left end) of the fin heat exchanger 103 . Since the second target angle α corresponding to this partial area is small, even between 10° and 30°, reducing this partial area is beneficial to reducing the fin sound generated at the left end of the fin heat exchanger 103 strength.

It is defined that along the first direction, the distance between the end of the fin heat exchanger 103 close to the fourth side plate 14 and the air outlet 24 closest to the fourth side plate 14 among the plurality of air outlets 24 is a third Spacing L3.

For example, as shown in FIG. 9 , the distance between the right end of the fin heat exchanger 103 and the fourth air outlet 244 is the third distance L3. The smaller the ratio (L3/L1) between the third distance L3 and the first distance L1, the smaller the interval value of the second target angle α.

Therefore, the width of the fin heat exchanger 103 in the left-right direction, the installation position of the fin heat exchanger 103, and the width of the fourth air outlet 244 can be adjusted to make the ratio of the third distance L3 to the first distance L1 ( L3/L1) is any value within the second preset ratio range, thereby adjusting the size of the second target angle α. For example, the second preset ratio range is 0.1 to 0.85. That is to say, the ratio of the third distance L3 to the first distance L1 is greater than 0.1 and less than or equal to 0.85 (0.1≤L3/L1≤0.85). For example, the ratio of the third distance L3 to the first distance L1 is 0.1, 0.3, or 0.85, etc. In this way, the fin heat exchanger 103 can have a larger heat dissipation area, and the size of the fin heat exchanger 103 protruding to the left from the fourth air outlet 244 can also be reduced to reduce the size of the fin heat exchanger 103. In the partial area at the other end (for example, the right end), since the second target angle α corresponding to this partial area is small, even between 10° and 30°, reducing this partial area is beneficial to reducing the fin replacement. The intensity of the fin sound generated at the right end of the heater 103.

It should be noted that by designing the structure and size of the indoor unit 10, the ratio of the second distance L2 to the first distance L1 can be less than or equal to 0.85, and the ratio of the third distance L3 to the first distance L1 can be less than or equal to 0.85. Alternatively, one of the ratio of the second pitch L2 to the first pitch L1 and the ratio of the third pitch L3 to the first pitch L1 may be made less than or equal to 0.85.

In some embodiments, in the front-to-back direction, the projections of the two air outlets 24 (eg, the fourth air outlet 244 and the third air outlet 243) located at the left end and the right end on the fin heat exchanger 103 can be located respectively at and In the two second areas M2 corresponding to the two air outlets 24 (such as the fourth air outlet 244 and the third air outlet 243), in this way, the air blown from the air outlet 24 can flow through the air outlet 24 more The corresponding fins 32 in the second area M2 thereby increase the heat exchange area of the fin heat exchanger 103.

In some embodiments, as shown in FIG. 6 , the indoor unit 10 further includes an electrical box assembly 104 . The electrical box assembly 104 is configured to mount and isolate circuit boards. The on or off state of the motor 25 can be adjusted through the circuit board, and the rotation speed of the motor 25 can also be adjusted. When the electrical box assembly 104 is installed, the electrical box assembly 104 can be installed at the left end or the right end of the first sub-accommodating cavity 191 .

In some embodiments, along the first direction, there is a target gap E1 between an end of the fin heat exchanger 103 close to the fourth side plate 14 and the fourth side plate 14 .

For example, as shown in FIG. 9 , the right end of the fin heat exchanger 103 is spaced apart from the fourth side plate 14 in the left-right direction to form a target between the right end of the fin heat exchanger 103 and the shell 101 Gap E. The target gap E1 is configured to facilitate installation of the refrigerant pipe 31 . By setting the target gap E1, the refrigerant pipe 31 can be connected to the outdoor heat exchanger 203 and the compressor 201, and it is also convenient to install the electrical box assembly 104, so that the air outlet 24 and the fin heat exchanger 103 are installed close to the third side plate respectively. 13 (for example, the left side) is beneficial to increasing the contact area between the flowing air and the fin heat exchanger 103 and using the internal space of the indoor unit 10 .

It is defined that along the first direction, the distance between the air outlet 24 of the plurality of air outlets 24 close to the target gap E1 and the fourth side plate 14 is a fifth distance L5. It is defined that along the first direction, the distance between the air outlet 24 of the plurality of air outlets 24 that is far away from the target gap E1 and the third side plate 13 is a ninth distance L9.

For example, as shown in FIG. 9 , the distance between the fourth air outlet 244 and the fourth side plate 14 is the fifth distance L5. The distance between the third air outlet 243 and the third side plate 13 is the ninth distance L9.

In some embodiments, as shown in FIG. 9 , a second target gap E2 is formed between the left end of the fin heat exchanger 103 and the third side plate 13 , and the difference between the ninth spacing L9 and the second spacing L2 (the first The difference Q1) is any value between 3mm and 30mm. In this way, the installation of the fin heat exchanger 103 is facilitated, and excessive air can be prevented from flowing out of the second target gap E2, thereby improving the production and installation efficiency of the fin heat exchanger 103.

In some embodiments, the ratio of the fifth distance L5 to the first distance L1 is any value in the third preset ratio range. For example, if the third preset ratio range is between 0.5 and 1.32, then the ratio of the fifth distance L5 to the first distance L1 is any value between 0.5 and 1.32. In this way, the left end of the fin heat exchanger 103 can have a larger contact area with the air, and the second target gap E2 can have sufficient space in the left and right directions, thereby facilitating the insertion of the refrigerant pipe 31 and connectivity.

In some embodiments, the difference between the fifth distance L5 and the third distance L3 (second difference Q2) is any value between 50 mm and 200 mm. In this way, it is beneficial to install the connecting refrigerant pipe 31 within the second target gap.

The foregoing description mainly takes as an example that the first target gap E1 is set between the right end of the fin heat exchanger 103 and the shell 101, and the second target gap E2 is formed between the left end of the fin heat exchanger 103 and the shell 101. Of course, in some embodiments, a first target gap E1 can also be formed between the left end of the fin heat exchanger 103 and the shell 101, and a second target gap E1 can be set between the right end of the fin heat exchanger 103 and the shell 101. Gap E2. In this way, the first target gap E1 and the electrical box assembly 104 can be located at the left end of the accommodating cavity 19 respectively, or the electrical box assembly 104 is located at the left end of the accommodating cavity 19 and the first target gap E1 is located at the right end of the accommodating cavity 19. It only needs to be adjusted accordingly. The present disclosure does not limit the corresponding proportional relationships among the second spacing L2, the ninth spacing L9, the third spacing L3, the fifth spacing L5, and the first spacing L1.

In some embodiments, in the case where the indoor unit 10 includes a fan assembly 102 and the fan assembly 102 includes an air outlet 24, the side (eg, rear side) of the fin heat exchanger 103 close to the air outlet 24 Located in a second area M2.

When the indoor unit 10 includes multiple fan assemblies 102, any one of the multiple fan assemblies 102 includes an air outlet 24, and the multiple air outlets 24 are spaced apart along the axial direction of the fan assembly 102 (i.e., the left and right directions). In the case of , the rear side of the fin heat exchanger 103 corresponds to a plurality of air outlets 24 , and any one of the air outlets 24 corresponds to a second area M2 .

It should be noted that an air flow barrier can be formed between two adjacent air outlets 24, and the air flow barrier is composed of The flowing air blown out by the two air outlets 24 is formed. The boundary lines of the two adjacent second areas M2 corresponding to the two air outlets 24 are part of the air flow barrier. In this case, the air blown from one air outlet 24 may only contact the fins 32 in the corresponding second area M2.

The position of the air flow barrier between the two air outlets 24 is related to the pressure of the air blown out by the two air outlets 24 . For example, in the left-right direction, the air flow barrier is closer to an air outlet 24 where the pressure of the blown air is smaller. Any one of the plurality of air outlets 24 has the same shape and size. The shape of any one of the plurality of air outlets 24 may be approximately rectangular or square. For example, as shown in FIG. 6 , since the impellers 22 in the two fan assemblies 102 are driven to rotate by a motor 25 , the pressure of the air blown out by the two air outlets 24 is approximately the same. In this case, an airflow barrier is formed in the middle position of the two air outlets 24 in the left-right direction.

The following description will take the example that the airflow barrier is located at the middle position of two adjacent air outlets 24 in the left and right direction.

It is defined that the distance between any two adjacent air outlets 24 in the plurality of air outlets 24 along the first direction is a fourth distance L4. For example, as shown in FIG. 9 , the distance between two adjacent air outlets 24 (eg, the third air outlet 243 and the fourth air outlet 244 ) is the fourth distance L4.

When the indoor unit 10 includes more than three air outlets 24 and the distances between two adjacent air outlets 24 are different, the fourth distance L4 is the maximum of the distances between the two adjacent air outlets 24 . value.

When the indoor unit 10 includes more than three air outlets 24 and the distance between two adjacent air outlets 24 is the same, the distance between the two adjacent air outlets 24 is the fourth distance L4 respectively.

By adjusting the distance between two adjacent air outlets 24 or the width of the air outlets 24, the fourth distance L4 is made smaller than or equal to the first distance L1 (L4≤L1). In this way, in the front-to-back direction, while the distance between the air outlet 24 and the fin heat exchanger 103 remains unchanged, it is beneficial to increase the tangent value of the second target included angle α, thereby increasing the second target included angle α. size, thereby weakening the fin sound between the two adjacent second areas M2.

It should be noted that usually the fourth distance L4 is greater than 0, so that two adjacent air outlets 24 are spaced apart in the left and right direction. Of course, in some embodiments, the fourth distance L4 may also be 0. In this case, the two air outlets 24 of the two adjacent fan assemblies 102 are merged into one larger air outlet 24. This disclosure will Not limited.

It should be noted that the tangent value of the second target included angle α is R/S, R is the side opposite the second target included angle α, and S is the side adjacent to the second target included angle α. As mentioned above, the length of the adjacent side S of the second target included angle α is mainly reduced to increase the tangent value of the second target included angle α, thereby increasing the second target included angle α, so as to achieve weakening of the fin heat exchanger 103 The effect of fin sound produced on the rear side. Of course, in some embodiments, the length of the opposite side R can also be increased to increase the tangent value of the included angle α, thereby increasing the second target included angle α to weaken the rear side of the fin heat exchanger 103 The effect of the fin sound generated is not limited by this disclosure.

Figure 10 is another cross-sectional view of an indoor unit of an air conditioner according to some embodiments.

The distance between the end of the fin heat exchanger 103 close to the first side plate 11 and the air outlet 24 is defined as an eighth distance L8.

For example, as shown in FIG. 10 , the distance in the front-rear direction between the first end 33 and the air outlet 24 is the eighth distance L8, and the angle between the fin heat exchanger 103 and the first side plate 11 is the second angle β. The first side plate 11 is perpendicular to the up and down direction. When the fin heat exchanger 103 is installed, the second included angle β is any angle within the third preset angle range. For example, the third preset angle range is between 30° and 60°, that is to say, the second included angle β is greater than or equal to 30° and less than or equal to 60°, that is, 30°≤β≤60°. For example, the second included angle β is 30°, 45° or 60°, etc.

In this way, the fin heat exchanger 103 remains tilted. When the height of the housing 101 is small, the fin heat exchanger 103 has a large contact area with the air flowing out of the air outlet 24 . If the second included angle β is less than 30° (β<30°), the air flowing between two adjacent fins 32 has a longer heat exchange path in the front-to-back direction, requiring greater wind pressure, which is not necessary. Helps increase air flow speed. If the second included angle β is greater than 60° and less than or equal to 90° (90°≥β>60°), the contact area between the fin heat exchanger 103 and the air will be reduced, thereby reducing the efficiency of the fin heat exchanger 103. Heat exchange efficiency.

In some embodiments, when the fin heat exchanger 103 is installed, the installation position of the fin heat exchanger 103 in the front-rear direction is adjusted so that the ratio of the eighth spacing L8 to the first spacing L1 is the fifth preset value. Any value in the ratio range, in this way, can increase the tangent value of the second target included angle α, thereby increasing the second target included angle α, thereby weakening the fin sound generated on the rear side of the fin heat exchanger 103. For example, the fifth preset ratio range is between 0.9 and 3. That is to say, the ratio of the eighth distance L8 to the first distance L1 is greater than or equal to 0.9 and less than or equal to 3 (0.9≤L8/L1≤3). For example, The ratio of the eighth distance L8 to the first distance L1 is 0.8, 1, or 3, etc.

In the case where the indoor unit 10 includes a plurality of air outlets 24 , the distances between the plurality of air outlets 24 and the first end 33 of the fin heat exchanger 103 in the front-rear direction may be the same. If the distances between the plurality of air outlets 24 and the first end 33 in the front-rear direction are inconsistent, the smallest distance is used as the eighth distance L8.

In some embodiments, as shown in FIG. 10 , the height of the housing 101 is defined as the sixth distance L6 along the second direction, and any one of the plurality of air outlets 24 is close to the second side plate 12 The distance between the edge of and the second side plate 12 is the seventh distance L7.

In the case where the indoor unit 10 includes a plurality of air outlets 24, if the lower edge of each air outlet 24 in the plurality of air outlets 24 is the same as the height of the second side plate 12 in the up and down direction, then the same height is defined. Seven pitch L7. If the lower edge of each air outlet 24 in the plurality of air outlets 24 and the height of the second side plate 12 in the up-down direction are different, then the minimum value among the plurality of heights is defined as the seventh distance L7.

In some embodiments, the ratio of the seventh distance L7 to the sixth distance L6 is any value within the fourth preset ratio range. For example, the fourth preset ratio range is between 0.56 and 0.8. That is to say, the ratio of the seventh distance L7 to the sixth distance L6 is greater than or equal to 0.56 and less than or equal to 0.8 (0.56≤L7/L6≤0.8). For example, the ratio of the seventh spacing L7 to the sixth spacing L6 is 0.56, 0.7 or 0.8, etc. In this way, the air outlet 24 can be positioned upward along the up-down direction.

In this case, the first end 33 is further away from the air outlet 24 in the front-rear direction than the second end 34 . Therefore, more air flowing out of the air outlet 24 flows toward the area near the upper end of the fin heat exchanger 103, which is beneficial to reducing the fin sound generated on the rear side of the fin heat exchanger 103.

In some embodiments, the ratio of the eighth spacing L8 to the sixth spacing L6 is any value in the sixth preset ratio range. For example, the sixth preset ratio range is between 0.86 and 2. That is to say, the ratio of the eighth spacing L8 to the sixth spacing L6 is greater than or equal to 0.86 and less than or equal to 2. For example, the ratio of the eighth spacing L8 to the sixth spacing L6 is 0.86, 1 or 2, etc. In this way, it is beneficial to increase the heat exchange area of the fin heat exchanger 103.

In some embodiments, as shown in FIG. 10 , the fan assembly 102 further includes a first connecting plate 26 and a second connecting plate 27 . The first connecting plate 26 is located at the upper end of the air outlet 24 , and the second connecting plate 27 is located at the lower end of the air outlet 24 . The first connecting plate 26 and the second connecting plate 27 are connected to the volute 21 respectively.

The first connecting plate 26 connects a portion of the volute 21 located at the upper end of the air outlet 24 . The second connecting plate 27 connects a portion of the volute 21 located at the lower end of the air outlet 24 . When the partition 17 is located between the second sub-accommodating cavity 192 and the first sub-accommodating cavity 191, the first connecting plate 26 and the second connecting plate 27 can respectively pass through the first opening 171 from back to front for installation. The first connecting plate 26 and the second connecting plate 27 .

In some embodiments, as shown in FIG. 10 , volute 21 includes volute sidewalls 211 . The volute side wall 211 is close to the air outlet 24 and close to the first side plate 11 . The front end of the volute side wall 211 is further away from the first side plate 11 than the rear end thereof, and the included angle between the volute side wall 211 and the first side plate 11 forms a third included angle Φ.

The front end of the first connecting plate 26 is closer to the first side plate 11 than the rear end thereof, and the included angle between the front end of the first connecting plate 26 and the first side plate 11 is the fourth included angle γ.

In this way, the volute 21 is close to the partition 17, and there is a gap between the volute 21 and the first side plate 11. The volute 21 can also be supported by the partition 17, so that the volute 21 is spaced apart from the first side plate 11. Thereby reducing the transmission of vibration.

For example, set the third included angle Φ to be greater than 0 and less than or equal to 10° (0<Φ≤10°), and the fourth included angle γ to be greater than 0 and less than or equal to 10° (0<γ≤10°). In this way, it can be avoided that the second angle Φ and the third angle γ are large, resulting in a large gap between the volute 21 and the first side plate 11 , thereby reducing the space utilization of the indoor unit 10 .

The front end of the second connecting plate 27 is further away from the first side plate 12 than the rear end thereof, and the included angle between the second connecting plate 27 and the target plane is the first included angle θ. The target plane is a plane parallel to the left-right direction and the up-down direction. The partition 17 may be approximately parallel to the target plane. When installing the first connecting plate 26 and the second connecting plate 27, since there is a large distance between the lower end of the air outlet 24 and the second side plate 12, the first included angle θ is set to the second preset angle. any angle within the range. For example, the second preset angle range is 54° to 90°, that is to say, the first included angle θ is greater than or equal to 54° and less than 90° (54°≤θ<90°). For example, the first included angle θ is 54°, 65°, or 85°, etc.

When the first included angle θ is less than 90° (θ<90°), the front end of the second connecting plate 27 can be bent downward relative to the target plane, so that part of the air blown out from the air outlet 24 can flow The area of the fin heat exchanger 103 close to the second side plate 12 is beneficial to increasing the contact area between the fin heat exchanger 103 and the air.

When the first included angle θ is greater than or equal to 54° (54°≤θ), the outflow air can be prevented from flowing directly through the lower end of the fin heat exchanger 103, which is beneficial to enlarging the rear side of the fin heat exchanger 103. The corresponding second target angle α can reduce the fin sound.

It should be noted that by adjusting the sixth distance L6, the seventh distance L7, the eighth distance L8 and the first included angle θ, and conducting multiple sets of simulation experiments, the following rules can be obtained.

When the ratio of the seventh distance L7 to the sixth distance L6 is not within the fourth preset ratio range, the first included angle θ is within the second preset angle range (for example, θ=54° or θ=60°), When the ratio of the eighth pitch L8 to the sixth pitch L6 is within the sixth preset ratio range, the fin sound of the indoor unit 10 is reduced compared to the indoor unit 10 before the parameters are adjusted, but the magnitude of the reduction in the fin sound is Not obvious.

When the ratio of the seventh distance L7 to the sixth distance L6 is within the fourth preset ratio range, the first included angle θ is within the second preset angle range, and the first included angle θ becomes larger (for example, θ=69° ), and the ratio of the eighth spacing L8 to the sixth spacing L6 is within the sixth preset ratio range, compared with the indoor unit 10 before the parameters are not adjusted, the fin sound of the indoor unit 10 is significantly reduced, but it still exists. Slight fin sound.

When the ratio of the seventh distance L7 to the sixth distance L6 is within the fourth preset ratio range, the first included angle θ is within the second preset angle range, and the first included angle θ continues to become larger (for example, θ=77 °), and the ratio of the eighth spacing L8 to the sixth spacing L6 is within the sixth preset ratio range, compared with the indoor unit 10 before the parameters are not adjusted, the indoor unit 10 will hardly produce fin sound, and the effect is most.

It should be noted that by adjusting the sizes of the first spacing L1, the second spacing L2, the third spacing L3, the fourth spacing L4, the fifth spacing L5, the eighth spacing L8 and the ninth spacing L9, the second spacing L2 is The ratio of the first spacing L1 is within the first preset ratio range, the ratio of the third spacing L3 to the first spacing L1 is within the second preset ratio range, and the ratio of the fifth spacing L5 to the first spacing L1 is within the third preset ratio range. Assuming that the ratio between the eighth distance L8 and the first distance L1 is within the fifth preset ratio range, and multiple sets of simulation experiments are performed, the following rules can be obtained.

When the ratio of the second distance L2 to the first distance L1 is close to or equal to the end point value of the first preset ratio range, and the ratio of the third distance L3 to the first distance L1 is close to or equal to the end point value of the second preset ratio range, the third When the ratio of the fifth spacing L5 to the first spacing L1 is close to or equal to the endpoint value of the third preset ratio range, the fin sound of the indoor unit 10 can be reduced compared to the indoor unit 10 before the parameters are not adjusted, but the fin sound The reduction is not obvious.

When the ratio of the second distance L2 to the first distance L1 becomes smaller, the ratio of the third distance L3 to the first distance L1 becomes smaller or slightly larger, and the ratio of the fifth distance L5 to the first distance L1 becomes smaller, the indoor unit 10 The fin sound is greatly reduced, but there is still a slight fin sound.

When the ratio of the second distance L2 to the first distance L1 continues to become smaller, the ratio of the third distance L3 to the first distance L1 continues to become smaller, and the ratio of the fifth distance L5 to the first distance L1 continues to become smaller, the indoor unit 10 is almost It will not produce fin sound and has the best effect.

It should be noted that the air supply system of centrifugal fans is widely used because of its advantages of high air supply efficiency, large air supply static pressure and low noise. However, due to the unreasonable structure of the centrifugal fan, the centrifugal fan is prone to air volume loss and backflow at the air inlet under high static pressure, which affects the efficiency, air volume and noise of the centrifugal fan's air supply system.

Figure 11 is a structural diagram of a centrifugal fan in the related art.

As shown in Figure 11, the centrifugal fan 102A' includes a volute 21', an impeller 22', a collector 220', an air inlet 23' and an air outlet 24'. The impeller 22' is located inside the volute 21'. The current collector 220' extends along the axial direction of the impeller 22' and is connected to the volute 21'. The air inlet 23' is opened on the current collector 220'.

The centrifugal fan 102A' works outward through the impeller 22'. When the impeller 22' rotates at high speed, the static pressure inside the volute 21' is much higher than the static pressure outside the volute 21', and the inner wall of the collector 220' is in contact with the impeller 22'. The distance between the outer end faces is relatively large, which is usually greater than 15mm, which is conducive to the formation of eddy currents.

In addition, the distance between the end of the current collector 220' close to the impeller 22' and the outer end surface of the impeller 22' is usually set to 3 mm to 6 mm to prevent the impeller 22' from being damaged after the volute 21' and the impeller 22' are assembled. Wear occurs between the volute and the volute 21'. In this case, when the centrifugal fan 102A' is working, the wind field inside the volute 21' is under the action of a relatively high static pressure, and the airflow passes through the vortex area and is connected to the impeller 22 from the end of the current collector 220' close to the impeller 22'. 'There is a loss between the outer end faces, and the greater the pressure inside the volute 21', the more obvious the backflow phenomenon will be, and the lower the air supply efficiency of the centrifugal fan 102A' will be.

Therefore, the structure of the current collector 220' affects the amount of backflow loss. The distance between the inner wall of the collector 220' and the outer end surface of the impeller 22' The distance between the end of the current collector 220' close to the impeller and the outer end surface of the impeller 22' has a greater influence on the size of the backflow loss.

It should be noted that the impeller diameter R' in the air duct simulation model satisfies: 130mm≤R≤200mm, and the impeller diameter R' in the air duct simulation model is set to 180mm (R=180mm).

Some embodiments of the present disclosure also provide a duct air supply type air conditioning indoor unit (hereinafter referred to as the air conditioning indoor unit).

Figure 12A is a structural diagram of an air conditioning indoor unit according to some embodiments.

In some embodiments, as shown in Figure 12A, the indoor unit 10 includes a housing 101 and a centrifugal fan 102A. The housing 101 includes an air outlet 16 and an air inlet 15 . The centrifugal fan 102A is located in the housing 101. The housing 101 includes an accommodation space in which the centrifugal fan 102A is installed. The air outlet 16 and the air inlet 15 are respectively connected with the accommodation space. In this way, when the centrifugal fan 102A works, the gas enters the accommodation space through the air inlet 15. The centrifugal fan 102A increases the gas pressure and sends the gas to the air outlet 16. The gas with the increased pressure is discharged from the air outlet 16 and passes through the air outlet 16. The air duct connected to the air outlet 16 flows to the user area to realize long-distance air supply.

Figure 12B is another structural diagram of an air conditioning indoor unit according to some embodiments. Figure 13 is a structural diagram of a centrifugal fan according to some embodiments.

As shown in FIGS. 12B and 13 , the indoor unit 10 further includes a motor 25 and an indoor heat exchanger 103A. The motor 25 is disposed in the accommodation space and connected to the centrifugal fan 102A. The indoor heat exchanger 103A is provided in the accommodation space and is located between the air outlet 24 and the air outlet 16 . In this way, the gas is discharged from the air outlet 24 of the centrifugal fan 102A and flows through the indoor heat exchanger 103A. The heat-exchanged gas then flows to the user area through 103A and the air duct connected with the air outlet 16, thereby realizing the function of adjusting the temperature in the user area. .

When the indoor unit 10 performs cooling, the temperature of the surface of the indoor heat exchanger 103A is usually low. When the gas is blown out from the centrifugal fan 102A and contacts the surface of the indoor heat exchanger 103A, the water vapor in the gas encounters cold on the surface of the indoor heat exchanger 103A and condenses into water droplets. Water droplets fall downward due to gravity.

Therefore, as shown in FIG. 12A , the indoor unit 10 also includes a water receiving tray 5 , which is located in the housing 101 and is provided below the indoor heat exchanger 103A. The water receiving tray 5 is used to collect condensed water dripping from the surface of the indoor heat exchanger 103A to prevent the condensed water from directly falling into the interior of the housing 101 and other components provided inside the housing 101, and to prevent the condensed water from affecting the indoor unit 10. normal work.

Figure 14 is another structural diagram of a centrifugal fan according to some embodiments. Figure 15 is a partial enlarged view of circle A in Figure 14.

Some embodiments of the present disclosure also provide a centrifugal fan 102A. As shown in FIGS. 13 to 15 , compared with the centrifugal fan 102A' in FIG. 11 , the centrifugal fan 102A further includes at least one current collector and a reinforcing rib. The structure of the at least one current collecting member is different from that of the current collecting member 220', and the at least one current collecting member and the reinforcing rib will be described below.

In some embodiments, as shown in FIGS. 13 to 15 , the centrifugal fan 102A includes a volute 21 , an impeller 22 and at least one collector 220 . The impeller 22 is located inside the volute 21 . The volute 21 includes an enclosure 210 , an air inlet 23 and an air outlet 24 . Along the axial direction of the impeller 22 , at least one side of the enclosure 210 is open to form a second opening (ie, opening) 213 . A second opening 213 corresponds to a current collector 220 . The current collector 220 is connected to the enclosure 210 and blocks the second opening 213 . The air inlet 23 is opened on the current collector 220 so that gas can enter the centrifugal fan 102A when the centrifugal fan 102A is working. The gas outlet 24 is opened on the enclosure 210 to discharge gas after the gas pressure increases.

When the centrifugal fan 102A is working, the gas enters the volute 21 from the air inlet 23, and the impeller 22 rotates at a high speed to drive the gas entering the volute 21 to rotate. When the gas flows through the impeller 22, it will change the flow direction and flow to the gas outlet. twenty four.

In some embodiments, as shown in FIG. 14 , the volute 21 further includes reinforcing ribs 214 . The reinforcing ribs 214 are configured to enhance the structural strength of the impeller 22 so that the impeller 22 remains stable when rotating at high speed.

The reinforcing rib 214 is connected to at least one end of the impeller 22 in the axial direction, and extends along the axial direction of the impeller 22 . As shown in FIG. 15 , the reinforcing rib 214 includes a reinforcing rib body 2140 , a first end surface 2141 and a second end surface 2142 . The first end surface 2141 and the second end surface 2142 are arranged opposite to each other. The first end surface 2141 and the second end surface 2142 respectively extend along the axial direction of the reinforcing rib body 2140 and are spaced apart on the outer peripheral surface of the reinforcing rib body 2140 . The second end surface 2142 is further away from the impeller 22 than the first end surface 2141 .

Figure 16 is a schematic diagram of the backflow phenomenon in a centrifugal fan according to some embodiments.

As shown in Figure 16, the dotted line represents the flow direction of the airflow. When the gas enters the volute 21 from the air inlet 23 of the volute 21 During the internal process, under high static pressure, a backflow phenomenon occurs at the air inlet 23, resulting in a loss of air volume and reducing the air supply efficiency.

Figure 17 is a structural diagram of a current collector of a centrifugal fan according to some embodiments.

In some embodiments, as shown in FIGS. 15 and 17 , the current collector 220 includes a connecting portion 2201 and a bending portion 2202 . The connecting portion 2201 is connected to the enclosure 210 , and the connecting portion 2201 is located on the side of the second end surface 2142 away from the impeller 22 .

As shown in FIG. 15 , the distance between the connecting portion 2201 and the first end surface 2141 is defined as the first distance A. It should be noted that the first end surface 2142 of the reinforcing rib 214 is equivalent to the outer end surface of the impeller 22'. The first distance A is equivalent to the distance between the inner wall of the collector 220' of the centrifugal fan 102A' and the outer end surface of the impeller 22', and the first distance A is greatly reduced.

Figure 18 is a schematic diagram of another backflow phenomenon in a centrifugal fan according to some embodiments.

In some embodiments, as shown in FIG. 18 , the connecting portion 2201 can block the return path of the airflow, thereby eliminating the vortex phenomenon inside the volute 21 and thereby reducing the air volume loss caused by the airflow return.

In some embodiments, the impact of the size of the first distance A on the airflow return loss is determined by testing the motor speed and the first distance A. For example, the wind duct simulation method and CFD simulation software are used to establish the wind duct simulation model. When the external static pressure is 200Pa and the impeller diameter R is 180mm, the following rules can be obtained.

For example, when the motor speed is 1200 rpm, when the first distance A is greater than 0 mm and less than or equal to 10 mm (0 mm < A ≤ 10 mm), the first distance A has a small impact on the air volume. When the first distance A is greater than 10 mm (A>10 mm), as the first distance A increases, the air volume decreases significantly, that is to say, the airflow return loss increases. When the motor speed is 1350rpm or 1500rpm, the air volume changes trend is the same as when the motor speed is 1200rpm. When the first distance A is greater than 10mm (A>10mm), as the first distance A increases, the air volume decreases significantly. The air supply efficiency of 102A decreases.

To sum up, when the first distance A is any value within the first preset distance range, the impact of the first distance A on the air volume is small. The first preset distance range is 0mm to 10mm. When the first distance A is greater than 10 mm (A>10 mm), the air supply volume of the centrifugal fan 102A decreases as the first distance A increases.

In some embodiments, when the first distance A is within the first preset distance range, as shown in FIG. 19 , in the axial direction of the impeller 22 , at least part of the connecting portion 2201 is located on the first end surface 2141 and the second end surface 2142, in this way, the connecting part 2201 is helpful to prevent the airflow from returning. For example, the first distance A is 6 mm to avoid wearing the volute 21 when the impeller 22 rotates.

As shown in FIG. 19 , the bent portion 2202 protrudes in a direction away from the impeller 22 and is further away from the impeller 22 than the connecting portion 2201 . The bent portion 2202 is provided around the air inlet 23 . In this way, the bent portion 2202 can guide the gas, and the inner wall of the bent portion 2202 has a U-shaped groove structure, which is beneficial to reducing the impact between the gas and the current collector 220 after the gas enters the volute 21 , thereby reducing the operating noise of the centrifugal fan 102A.

In some embodiments, as shown in FIG. 17 , the bending part 2202 includes a first sub-bending part 22021 and a second sub-bending part 22022. One axial end of the first sub-bending part 22021 is connected to the connecting part 2201, and the other axial end of the first sub-bending part 22021 extends in a direction away from the connecting part 2201. One axial end of the second sub-bent part 22022 is connected to the other axial end of the first sub-bent part 22021 , and the other axial end of the second sub-bent part 22022 extends toward the impeller 22 .

As shown in FIG. 15 , the distance between the other axial end of the second sub-bent portion 22022 (an end close to the second end surface 2142 ) and the second end surface 2142 is defined as the second distance B. That is, the distance between the end of the current collector 220 close to the impeller 22 and the reinforcing rib 214 is the second distance B. The second distance B is equivalent to the distance between the end of the current collector 220 ′ close to the impeller 22 ′ and the outer end surface of the impeller 22 ′. distance, and the second distance B is located on the path of the airflow return.

In some embodiments, the motor speed and the second distance B are tested to determine the impact of the second distance B on the airflow return loss. The following rules can be obtained through simulation experiments.

For example, when the rotation speed of the motor is 1200 rpm, when the second distance B is at any value within the second preset distance range, the second distance B has little impact on the air volume of the centrifugal fan 102A. The second preset distance range is 0mm to 5mm. When the second distance B is greater than 5 mm, the air volume of the centrifugal fan 102A is significantly reduced, that is, the return loss of the centrifugal fan 102A increases. And when the motor speed is 1350rpm or 1500rpm, the air volume is large The small change trend is basically the same as when the motor speed is 1200 rpm. When the second distance B is greater than 5 mm (B>5 mm), as the second distance B increases, the air volume of the centrifugal fan 102A decreases.

Therefore, when the second distance B is 3.5 mm, the air supply efficiency of the centrifugal fan 102A can be improved, and the end of the second sub-bent portion 22022 close to the impeller can be prevented from wearing the volute 21 .

As shown in FIG. 15 , the distance between the current collector 220 and the reinforcing rib 214 is defined as the third distance C. Because the third distance C is the minimum distance between the inner wall of the current collector 220 and the reinforcing rib 214 on the airflow return path. Therefore, when the third distance C is small, the loss resistance of the return air flow can be increased, thereby reducing the return loss of the air flow and improving the air supply efficiency of the centrifugal fan 102A.

In some embodiments, the motor speed and the third distance C are tested to determine the impact of the third distance C on the airflow return loss. The following rules can be obtained through simulation experiments.

For example, when the rotation speed of the motor is 13500 rpm, when the third distance C is any value within the third preset distance range, the third distance C increases and the air volume of the centrifugal fan 102A decreases. The third preset distance range is 0mm to 10mm.

Therefore, the third distance C can be 5 mm (C = 5 mm) to improve the air supply efficiency of the centrifugal fan 102A, and to avoid the minimum distance between the inner wall of the current collector 220 and the reinforcing rib 214 (the third distance C ) is too small, causing friction between the reinforcing ribs 214 and the volute 21 when the motor 25 drives the impeller 22 to rotate when the centrifugal fan 102A is working.

In some embodiments, the values of the first distance A, the second distance B, and the third distance C obtained through the air duct simulation method are used as examples to compare with the centrifugal fan 102A'. For example, in the centrifugal fan 102A provided by some embodiments of the present disclosure, the test was conducted when the first distance A was 6 mm, the second distance B was 3.5 mm, and the third distance C was 5 mm, and the centrifugal fan 102A and the centrifugal fan 102A were tested respectively. The speed and noise of centrifugal fan 102A'. After testing, the following rules can be obtained.

When the air volume is the same, the rotation speed of the centrifugal fan 102A is lower than the rotation speed of the centrifugal fan 102A'. For example, compared with the motor speed of the centrifugal fan 102A', when the external static pressure is 50pa, the motor speed of the centrifugal fan 102A is reduced by about 10rpm. When the external static pressure is 120pa, the motor speed is reduced by about 21rpm. When the static pressure is 200pa, the motor speed is reduced by about 30rpm.

When the air volume is the same, the noise of the centrifugal fan 102A is lower than the noise of the centrifugal fan 102A'. For example, when the air volume is the same, compared with the noise of centrifugal fan 102A', when the external static pressure is 50pa, the noise of centrifugal fan 102A is reduced by about 0.4dB. When the external static pressure is 120pa, the noise of centrifugal fan 102A is The noise is reduced by about 1.2dB. When the external static pressure is 200pa, the noise of the centrifugal fan 102A is reduced by about 1.9dB.

In summary, the centrifugal fan 102A provided by some embodiments of the present disclosure eliminates the vortex phenomenon inside the volute 21, and under the same air volume conditions, compared with the centrifugal fan 102A', the noise and motor speed of the centrifugal fan 102A are significantly reduced. .

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

Claims

An air conditioner, which includes an indoor unit, and the indoor unit includes:

Housing, including air outlet;

At least one fan assembly is provided in the housing; any one of the at least one fan assembly includes an air outlet; the air outlet is provided toward the air outlet and includes a target edge; the target edge is The edge of the air outlet along the first direction; and,

A fin heat exchanger is provided in the housing and is located between the air outlet and the air outlet; the fin heat exchanger includes a plurality of fins; the plurality of fins extend along the The first directions are spaced apart, and the first directions are perpendicular to the plurality of fins;

Wherein, the fin heat exchanger has a plurality of wind receiving areas, and the multiple wind receiving areas are located on a side of the plurality of fins close to the air outlet; any one of the multiple wind receiving areas A wind receiving area corresponds to a portion of the plurality of fins, and the portion of the fins is in contact with air flowing out of an air outlet of a fan assembly;

The partial fins corresponding to any of the wind receiving areas include a target fin, and the target fin is a fin located at the edge of the partial fins; the target fin is related to any of the wind receiving areas. The target edge of the air outlet corresponding to the wind area corresponds, and the target included angle between the connection line between the target fin and the corresponding target edge and the first direction is a first predetermined angle. Set any angle within the angle range.
The air conditioner according to claim 1, wherein the at least one fan assembly includes a plurality of fan assemblies, the plurality of fan assemblies are spaced apart along the first direction, and a plurality of the plurality of fan assemblies are The air outlets are spaced apart along the first direction;

The width of any one of the plurality of air outlets in the first direction is a first spacing;

The housing includes a first side plate and a second side plate, the first side plate and the second side plate are arranged oppositely along the second direction, and any one of the plurality of air outlets is along the The second direction is arranged close to the first side plate;

Along the third direction, one end of the fin heat exchanger close to the second side plate is closer to the fan assembly than an end of the fin heat exchanger close to the first side plate;

Wherein, the second direction is perpendicular to the first direction; the third direction is perpendicular to the first direction and perpendicular to the second direction.
The air conditioner according to claim 2, wherein the housing further includes a third side plate and a fourth side plate, the third side plate and the fourth side plate being oppositely arranged along the first direction;

Along the first direction, two ends of the fin heat exchanger are located on opposite sides of the plurality of air outlets;

Wherein, along the first direction, the distance between an end of the fin heat exchanger close to the third side plate and the air outlet closest to the third side plate among the plurality of air outlets. is the second spacing, and the ratio of the second spacing to the first spacing is any value within the first preset ratio range;

Along the first direction, the distance between an end of the fin heat exchanger close to the fourth side plate and the air outlet closest to the fourth side plate among the plurality of air outlets is a third There are three spacings, and the ratio of the third spacing to the first spacing is any value within the second preset ratio range.
The air conditioner according to claim 2 or 3, wherein along the first direction, a distance between any two adjacent air outlets in the plurality of air outlets is a fourth spacing, and the fourth The spacing is less than or equal to the first spacing.
The air conditioner according to claim 3 or 4, wherein the fin heat exchanger further includes a refrigerant tube; along the first direction, one end of the fin heat exchanger close to the fourth side plate There is a target gap between the fourth side plate and the fourth side plate, and the target gap is configured to install the refrigerant pipe;

Along the first direction, the distance between the air outlet close to the target gap among the plurality of air outlets and the fourth side plate is a fifth spacing; the distance between the fifth spacing and the first spacing is The ratio is any value within the third preset ratio range.
The air conditioner according to any one of claims 2 to 5, wherein along the second direction, the height of the housing is a sixth distance, and any one of the plurality of air outlets is close to the The distance between the edge of the second side panel and the second side panel is a seventh pitch; the ratio of the seventh pitch to the sixth pitch is any value within a fourth preset ratio range.
The air conditioner according to any one of claims 2 to 6, wherein any one of the at least one fan assembly further includes a connecting plate, the connecting plate is connected to the air outlet close to the second The edges of the side panels are connected;

The end of the connecting plate away from the air outlet is closer to the second side plate than the end of the connecting plate close to the air outlet; the first side between the connecting plate and the first plane The included angle is any angle within the second preset angle range;

Wherein, the first plane is parallel to the first direction and parallel to the second direction.
The air conditioner according to claim 6 or 7, wherein, along the third direction, a distance between an end of the fin heat exchanger close to the first side plate and the air outlet is 8 spacing;

Wherein, the ratio between the eighth spacing and the first spacing is any value within a fifth preset ratio range, and the ratio between the eighth spacing and the sixth spacing is a sixth preset ratio. Any value within the ratio range.
The air conditioner according to any one of claims 2 to 8, wherein the second included angle between the fin heat exchanger and the first side plate is any one within a third preset angle range. angle.
The air conditioner according to any one of claims 1 to 9, wherein the first preset angle range is 30° to 90°, the second preset angle range is 54° to 90°, and the The third preset angle range is 30° to 60°.
The air conditioner according to any one of claims 1 to 10, wherein the first preset ratio range is 0.1 to 0.85, the second preset ratio range is 0.1 to 0.85, and the third preset ratio range is 0.1 to 0.85. The ratio range is 0.5 to 1.32, the fourth preset ratio range is 0.56 to 0.8, the fifth preset ratio range is 0.9 to 3, and the sixth preset ratio range is 0.86 to 2.
A centrifugal fan including:

a volute, the volute has an air outlet and an air inlet, and the volute includes an enclosure, at least one side of the enclosure is open to form an opening;

At least one current collector is connected to the enclosure; any one of the at least one current collector corresponds to an opening and blocks the opening; the air inlet is provided on the collector On the flow piece, the air outlet is provided on the enclosure;

an impeller, arranged in the volute; and,

At least one reinforcing rib connects at least one end of the impeller in the axial direction; any one of the at least one reinforcing ribs extends along the axial direction of the impeller and includes:

first end face; and

a second end surface, the first end surface and the second end surface are separated by a predetermined distance, and the first end surface is closer to the impeller than the second end surface;

Wherein, the current collector includes a connecting part and a bending part, the connecting part connects the bending part and the enclosure respectively, and is located on a side of the first end surface away from the impeller; The bent portion protrudes in a direction away from the impeller relative to the connecting portion and is arranged around the air inlet.
The centrifugal fan according to claim 12, wherein the distance between the connecting part and the first end surface is any value within a first preset distance range.
According to the centrifugal fan of claim 13, the first preset distance range is 0mm to 10mm.
The centrifugal fan according to any one of claims 12 to 14, wherein,

The bending part includes a first sub-bending part and a second sub-bending part;

One axial end of the first sub-bending part is connected to the connecting part, and the other axial end of the first sub-bending part extends in a direction away from the connecting part;

One axial end of the second sub-bent part is connected to the other axial end of the first sub-bent part, and the other axial end of the second sub-bent part faces the impeller. extend.
The centrifugal fan according to claim 15, wherein the distance between the other end of the second sub-bent portion in the axial direction and the second end face is any value within a second preset distance range. .
The centrifugal fan according to claim 16, wherein the second preset distance range is 0mm to 5mm.
The centrifugal fan according to any one of claims 12 to 17, wherein the distance between the current collector and the reinforcing rib is any value within a third preset distance range.
The centrifugal fan according to claim 18, wherein the third preset distance range is 0 mm to 10 mm.
The centrifugal fan according to claim 12, wherein at least a part of the connecting portion is located between the first end surface and the second end surface along the axial direction of the impeller.
An air conditioner indoor unit, including:

The centrifugal fan according to any one of claims 12 to 20;

A casing, an accommodation space is defined in the casing; the casing also has an air inlet and an air outlet, and the air inlet and the air outlet are respectively connected with the accommodation space;

A motor, which is disposed in the accommodation space and connected to the impeller; and

Indoor heat exchanger, the indoor heat exchanger is arranged in the accommodation space and is located between the air outlet of the volute and the air outlet of the housing.