CN115342441A

CN115342441A - Air conditioner

Info

Publication number: CN115342441A
Application number: CN202211001615.7A
Authority: CN
Inventors: 张震; 张荣海; 王鹏宇; 齐宝
Original assignee: Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Current assignee: Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Priority date: 2022-08-19
Filing date: 2022-08-19
Publication date: 2022-11-15

Abstract

The invention discloses an air conditioner, relates to the technical field of household appliances, and aims to solve the problem of fin sound generated by a fin heat exchanger of an indoor unit. The air conditioner comprises an indoor unit, wherein a shell of the indoor unit is provided with a containing cavity, and an air inlet and an air outlet which are respectively communicated with the containing cavity. The fan assembly is installed in holding the intracavity and has the air inlet of intercommunication air intake and the gas outlet that sets up towards the air outlet. The fin heat exchanger is located and holds the intracavity to set up between air outlet and gas outlet. The fin heat exchanger comprises a plurality of fins distributed at intervals along a first linear direction. And one side of the fin heat exchanger facing the air outlet is provided with a wind receiving area, and the fins in each wind receiving area directly contact the air flowing out of the corresponding air outlet. The maximum included angle between a connecting line between the edge of each air outlet and the fin at the edge of the corresponding one of the wind receiving areas and the first direction is greater than 30 degrees. The air conditioner provided by the invention is used for reducing the running noise of the indoor unit.

Description

Air conditioner

Technical Field

The invention relates to the technical field of household appliances, in particular to an air conditioner.

Background

An air conditioning buried indoor unit (e.g., a duct unit) has been developed in response to the demand for market diversity and the change of the overall decoration space, and is increasingly used in general households due to its small installation and maintenance width. With the improvement of living standard, users not only pay attention to the adjusting capability of the air conditioner, but also have higher requirements on noise, and particularly, abnormal sounds are not allowed to appear in the indoor unit of a bedroom.

However, in the air conditioning indoor unit of the prior art, the windward side of the fin heat exchanger generates broadband noise with a frequency in the range of 1000 to 3000Hz, which is similar to the sound of a whistle, and is referred to as "fin sound" herein. The user is very sensitive to noise in the range of 1000-3000 Hz, so the fin tone reduces the comfort of the user.

Disclosure of Invention

The invention aims to provide an air conditioner, aiming at solving the problem of fin sound generated by a fin heat exchanger of an indoor unit.

In order to achieve the purpose, the invention adopts the following technical scheme:

some embodiments of the present invention provide an air conditioner, including an indoor unit, where the indoor unit includes a casing, a fan assembly, and a fin heat exchanger. The casing has holds the chamber and respectively with hold air intake and the air outlet that the chamber communicates. The fan subassembly is installed in holding the intracavity, and the fan subassembly has the air inlet of intercommunication air intake and the gas outlet that sets up towards the air outlet. The fin heat exchanger is located and holds the intracavity to set up between air outlet and gas outlet. The fin heat exchanger comprises a plurality of fins distributed at intervals along a first linear direction, and the first linear direction is perpendicular to the plurality of fins. One side of the fin heat exchanger facing the air outlet is provided with a wind receiving area, and the fins in each wind receiving area directly contact with the air flowing out of one corresponding air outlet. The maximum included angle between a connecting line between the edge of each air outlet and the fin at the edge of the corresponding wind receiving area and the direction vertical to the fins is larger than 30 degrees.

Therefore, in the indoor unit of the air conditioner, air can flow into the accommodating cavity from the air inlet through the driving of the fan assembly arranged in the accommodating cavity of the shell, and can be blown to the fin heat exchanger through the air inlet and the air outlet of the fan assembly, the air can exchange heat with the fins when flowing through gaps among the plurality of fins, and the air flowing through the fin heat exchanger is finally blown out from the air outlet of the shell, so that the refrigerating or heating effect of the preset space is realized. In the air flowing process, the structural size of each component of the indoor unit can be adjusted, so that the maximum included angle between the connecting line between the edge of each air outlet and the fin at the edge of the corresponding wind receiving area and the first direction perpendicular to the fin is larger than 30 degrees. Thus, on the windward side of each windward area facing the air outlet, by taking the included angle alpha between the flowing direction of the air contacted by each fin and the first direction as an example, through the arrangement, the included angle alpha between the windward side of each windward area and the first direction is favorably reduced or even eliminated, and the fin sound generated at the edge of the windward area of the fin heat exchanger is reduced or even eliminated.

In some embodiments, the fan assembly is a centrifugal fan and is provided in a plurality of numbers, the plurality of fan assemblies are distributed at intervals along the first straight line direction, and each fan assembly comprises an air outlet. The plurality of air outlets are distributed at intervals along the first straight line direction, and the maximum width dimension of each air outlet in the first straight line direction is L1.

In some embodiments, the housing includes a top side plate and a bottom side plate oppositely disposed along a second linear direction, the second linear direction is perpendicular to the first linear direction, and each air outlet is disposed adjacent to the top side plate along the second linear direction. Along the second linear direction, the end, close to the bottom side plate, of the finned heat exchanger is close to the fan assembly along the third linear direction, the end, close to the top side plate, of the finned heat exchanger is far away from the fan assembly along the third linear direction, and the finned heat exchanger is installed between the fan assembly and the air outlet along the third linear direction.

In some embodiments, along the first straight line direction, two ends of the finned heat exchanger along the first straight line direction are respectively located at two opposite sides of the plurality of air outlets. Along the first straight line direction, the minimum distance between one end face of the fin heat exchanger and the adjacent air outlet is L2, and L2/L1 is less than or equal to 0.85.

In some embodiments, the minimum distance between the other end face of the finned heat exchanger and the adjacent air outlet in the first straight line direction is L3, and L3/L1 is less than or equal to 0.85.

In some embodiments, each air outlet is identical in shape, the width dimension of each air outlet in the first linear direction is L1, the maximum distance between two adjacent air outlets in the first linear direction is L6, and L6 is less than or equal to L1.

In some embodiments, the number of the air outlets is two, and each of the air outlets has a rectangular cross-sectional shape in a direction parallel to the first straight line direction and the second straight line direction.

In some embodiments, along the first straight line direction, a mounting gap is formed between one end of the fin heat exchanger and the adjacent side wall of the shell, and is used for mounting and connecting a refrigerant pipe of the fin heat exchanger. Along the first straight line direction, the minimum distance between the edge of the air outlet close to the mounting gap and the shell is L5, and L5/L1 is less than or equal to 1.32.

In some embodiments, along the second linear direction, the height dimension of the housing is H1, the minimum distance between the edge of each air outlet far away from the top side plate and the bottom side plate is H2, and H2/H1 is greater than or equal to 0.44.

In some embodiments, an included angle θ between the edge of each air outlet away from the top side plate in the second linear direction and the vertical plane satisfies 54 ° ≦ θ < 90 °. Wherein the vertical plane is parallel to both the first linear direction and the second linear direction. And along the second linear direction, the edge of the air outlet far away from the top side plate is gradually close to the bottom side plate in the third linear direction.

In some embodiments, along the third linear direction, the minimum distance between one end of the finned heat exchanger close to the top side plate in the second linear direction and the air outlet is L7, L7/L1 is greater than or equal to 0.9, and L7/H1 is greater than or equal to 0.86.

In some embodiments, the top side plate is perpendicular to the second straight line direction, and the included angle beta between the finned heat exchanger and the top side plate is more than or equal to 30 degrees and less than or equal to 60 degrees.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings needed to be used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.

Fig. 1 is a schematic perspective view of an indoor unit included in an air conditioner according to an embodiment of the present disclosure;

fig. 2 is a perspective view of the indoor unit shown in fig. 1 at another angle;

FIG. 3 is a schematic illustration of an exploded view of the housing shown in FIG. 2;

FIG. 4 is a perspective cross-sectional view of the housing shown in FIG. 2;

fig. 5 is a schematic view of the internal structure of the indoor unit shown in fig. 1;

fig. 6 is a schematic structural diagram of an indoor unit provided in the embodiment of the present application, in which three fan assemblies are installed in the left-right direction;

fig. 7 is a cross-sectional view of an indoor unit 10 shown in fig. 1;

FIG. 8 is a wind field distribution diagram of the windward side (i.e., the rear side) of the finned heat exchanger shown in FIG. 7;

fig. 9 is a top view of the interior of an indoor unit provided in an embodiment of the present application;

fig. 10 is an interior side view of an indoor unit provided in an embodiment of the present application.

Reference numerals:

100-an air conditioner;

10-an indoor unit;

1-a shell; 11-top side plate; 12-a bottom side plate; 13-side plates; 14-a containment chamber; 141-fan cavity; 142-a heat exchange chamber; 15-air inlet; 16-air outlet; 17-a middle partition plate; 181-opening;

2-a fan assembly; 21-a volute; 22-a centrifugal impeller; 23-an air inlet; 24-an air outlet; 25-a drive motor; 26 a first guide plate; 27-a second guiding plate.

3-a finned heat exchanger; 31-refrigerant pipe; 32-fins; 33-a first end; 34-a second end;

4-electric appliance box component.

Detailed Description

The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only a part of the embodiments of the present application, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.

In the description of the present application, it is to be understood that the terms "upper", "lower", "left", "right", "front", "rear", "inner", "outer", and the like, indicate orientations or positional relationships based on the orientations or relative positional relationships shown in the drawings, are only for convenience in describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present application. The description of the above-described orientation can be flexibly set in the course of practical application in the case where the relative positional relationship shown in the drawings is satisfied, unless otherwise specified.

The terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or to implicitly indicate the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present application, "a plurality" means two or more unless otherwise specified.

It should be noted that in practical applications, due to the limitation of the precision of the device or the installation error, the absolute parallel or perpendicular effect is difficult to achieve. The vertical, parallel or same-directional descriptions in this application are not an absolute limiting condition, but indicate that the vertical or parallel structural arrangement can be realized within a preset error range (e.g., a deviation of 5 °), and a corresponding preset effect can be achieved, so that the technical effect of limiting the features can be realized maximally, the corresponding technical scheme is convenient to implement, and high feasibility is achieved.

In the description of the present application, unless expressly stated or limited otherwise, the terms "mounted," "connected," and "in communication with" are to be construed broadly and may include, for example, fixed connections, removable connections, integral connections, and rotatable connections. May be directly connected or indirectly connected through an intermediate. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as appropriate.

In the embodiments of the present application, the terms "include", "include" or any other variations are intended to cover non-exclusive inclusions, so that a process, an article, or an apparatus including a series of elements includes not only those elements but also other elements not explicitly listed or inherent to such a process, article, or apparatus. Without further limitation, an element defined by the phrase "comprising a … …" does not exclude the presence of another identical element in a process, article, or apparatus that comprises the element.

In the embodiments of the present application, words such as "exemplary" or "for example" are used to mean serving as an example, instance, or illustration. Any embodiment or design described herein as "exemplary" or "e.g.," is not necessarily to be construed as preferred or advantageous over other embodiments or designs. Rather, use of the word "exemplary" or "such as" is intended to present relevant concepts in a concrete fashion.

As shown in fig. 1, an embodiment of the present application provides an air conditioner 100, and the air conditioner 100 may include an indoor unit 10. Exemplarily, referring to fig. 1 and 2, the indoor unit 10 may include a case 1, and a fan assembly 2 and a fin heat exchanger 3 installed in the case 1. The finned heat exchanger 3 may form a refrigerant circulation loop with an outdoor unit (not shown) of the air conditioner 100, so that heat in the room may be transferred to the outside of the room by a compressor in the outdoor unit and the finned heat exchanger 3 in the indoor unit 10, thereby implementing a cooling operation of the air conditioner. And the fan assembly 2 can provide power for the air which circularly flows indoors so as to increase the gas flow passing through the fin heat exchanger 3 in unit time, and the heat exchange efficiency of the fin heat exchanger 3 is improved.

In some embodiments, referring to fig. 3, fig. 3 is a schematic diagram of an exploded structure of the housing 1 shown in fig. 2. Illustratively, the housing 1 may include a top side panel 11, a bottom side panel 12, and two side panels 13. Wherein, top side board 11 and bottom side board 12 can be followed upper and lower direction (be the second straight line direction) interval distribution, and two limit curb plates 13 can be followed left and right directions (be the first straight line direction) interval distribution, and the upper and lower both ends of every limit curb plate 13 can be connected with the corresponding edge of top side board 11 and bottom side board 12 respectively. For example, the left and right edges of the top side plate 11 may be connected to the upper edges of the two side plates 13, respectively, and the left and right edges of the corresponding bottom side plate 12 may be connected to the lower edges of the two side plates 13, respectively. In this way, the top side plate 11, the bottom side plate 12 and the two side plates 13 may enclose the receiving cavity 14. Referring to fig. 4, the front and rear ends of the housing 1 may respectively have an air outlet 16 and an air inlet 15 communicating with the accommodating chamber 14 along the front-rear direction (i.e., the third linear direction). The top side plate 11, the bottom side plate 12 and the two side plates 13 may also be regarded as enclosing an air outlet 16 and an air inlet 15 at the front end and the rear end, respectively. Alternatively, the air outlet 16 and the air inlet 15 may be provided at the front and rear ends of the top side plate 11 or the bottom side plate 12, respectively.

Illustratively, as shown in fig. 3 and 4, the housing 1 may further include a middle partition 17, the middle partition 17 may be installed in the accommodating cavity 14, and at least one of the two side plates 13, the top side plate 11, and the bottom side plate 12 may be connected to the middle partition 17 at four edges of the left, right, upper, and lower sides. In this way, the middle partition 17 may divide the accommodation chamber 14 into the heat exchange chamber 142 and the fan chamber 141 in the front-rear direction. The heat exchange cavity 142 may be communicated with the air outlet 16, and correspondingly, the fan cavity 141 may be communicated with the air inlet 15. In addition, the middle partition 17 may be provided with at least one opening 181 for connecting the fan cavity 141 and the heat exchange cavity 142, so that the front side and the rear side of the installation cavity 14 may be respectively communicated with the air outlet 16 and the air inlet 15, thereby implementing a flowing air circulation passage from the air inlet 15 to the air outlet 16 in the housing 1.

It should be noted that the indoor unit 10 of the air conditioner 100 provided in the embodiment of the present application may be a buried indoor unit, such as an air duct unit, or a wall-mounted indoor unit, and only the installation positions of the air inlet 15 and the air outlet 16 need to be adjusted correspondingly. Taking the indoor unit 10 as an air duct machine, as shown in fig. 3, the casing 1 may further include a plurality of ceiling engaging lugs 182, and the ceiling engaging lugs 182 may be uniformly distributed on left and right sides of the casing and connected to left and right ends of the top side plate 11 or the two side plates 13. Wherein, each ceiling engaging lug 182 is provided with a connecting hole, and the indoor unit 10 can be fixed below the ceiling through the ceiling engaging lug 182 by connecting methods such as an expansion suspender and the like. In this case, the top side plate 11 may be positioned above the bottom side plate 12, and may be perpendicular to the vertical direction (corresponding to the horizontal direction and the front-rear direction). A decorative layer such as a ceiling structure may then be installed under the ceiling to conceivably install the indoor unit 10 between the ceiling structure and the ceiling. In other embodiments, the indoor unit 10 of the present application may be directly installed on an indoor wall or a ceiling in a suspended manner, which is not limited to the above.

It should be noted that, for the casing 1, a middle partition 17 for separating the blower chamber 141 and the heat exchange chamber 142 may be provided in the installation chamber 14. So as to facilitate the classified arrangement and installation of the structural members in the installation cavity 14. In other embodiments, the installation cavity 14 does not need to be provided with a middle partition plate, and only the air outlet of the fan assembly 2 needs to be installed forwards towards the finned heat exchanger 3, so that the structure is simple. In addition, under the condition of satisfying the air circulation, the side walls which enclose the left and right sides and the upper and lower sides of the installation cavity 14 of the shell 1 can also be partially or completely arranged into a frame structure, and only flow pipelines of air are required to be arranged at the upper and lower sides or the front and rear sides of the fin heat exchanger 3 for drainage, so that the side walls are not limited.

As shown in fig. 5, in order to facilitate the circulation and heat exchange of the indoor air, the fan assembly 2 may be a centrifugal fan, and the number of the fan assemblies 2 may be one or more. If the number of the fan assemblies 2 is plural, a plurality of fan assemblies 2 may be spaced in the left-right direction, and the axis of the fan assembly 2 may be approximately parallel to the left-right direction.

For example, referring to fig. 5, each fan assembly 2 may include a volute 21 and a centrifugal impeller 22, the centrifugal impeller 22 being mounted within the volute 21. At least one side of the scroll casing 21 in the left-right direction (i.e., the axial direction of the scroll casing 21) is provided with an air inlet 23, and the scroll casing 21 is provided forward with an air outlet 24 communicating with the air inlet 23. The air outlet 24 may be disposed toward the fin heat exchanger 3 in the front. In the case that the center partition 17 is installed in the installation cavity 14 (as shown in fig. 3), the air outlet 24 may be disposed near one of the openings 181, and an edge of the scroll casing 21 near the air outlet 24 may be in contact with or fit with an edge of the one opening 181, and even a portion of the scroll casing near the air outlet 24 may pass through the corresponding opening 181 from back to front. In this way, under the rotation of the centrifugal impeller 22, air near the indoor unit 10 can be extracted through the air inlet 23, the fan chamber 141 and the air inlet 15 (shown in fig. 4), and the extracted air is blown forward to the corresponding part of the finned heat exchanger 3 in the heat exchange chamber 142 through the air outlet 24 and an opening 181, and finally blown out of the indoor unit 10 through the air outlet 16 communicated with the heat exchange chamber 142.

With continued reference to fig. 5, for example, in case that the number of the fan assemblies 2 is two, in the case that the middle partition 17 is installed between the heat exchange chamber 142 and the fan chamber 141, two openings 181 may be opened on the middle partition 17 along the left-right direction, so that each air outlet 24 may be installed corresponding to and close to one opening 181. In addition, the number of the fan assemblies 2 can be one, three, four or more, and can be adjusted according to the index of the air circulation amount in unit time.

In order to rotate the centrifugal impeller 22, the fan assembly 2 may further comprise a drive motor 25, as shown in fig. 5. Wherein, two volutes 21 can be followed left and right direction interval distribution, and driving motor 25 can be installed between two volutes 21 along left and right direction, and both ends can be connected with two centrifugal impeller 22 respectively through the pivot about driving motor 25 to make two centrifugal impeller 22 can rotate under same driving motor 25's drive step-by-step. In addition, a driving motor 25 may be installed in each volute 21, so that the two centrifugal impellers 22 can be driven by the two driving motors 25 to rotate respectively.

In other embodiments, the fan assembly 2 may also be an axial flow fan or a cross-flow fan, so that the air inlet 23 of the fan assembly 2 can be communicated with the air inlet 15, and the air outlet 24 of the fan assembly 2 can be communicated with the air outlet 16, so that the indoor air can circulate between the indoor space and the indoor unit 10 under the driving of the fan assembly 2. This is not a limitation of the present application. In the embodiment of the present application, a specific structure of the indoor unit 10 may be described by taking the fan assembly 2 as a centrifugal fan as an example.

As shown in fig. 5, the fin heat exchanger 3 installed in the heat exchange cavity 142 may include a plurality of refrigerant tubes 31 and a plurality of fins 32. For example, each refrigerant pipe 31 may communicate with the outdoor heat exchanger and the outdoor unit, respectively, for circulation of the refrigerant. In the heat exchange cavity 142, the plurality of refrigerant pipes 31 may be spaced apart in the up-down and front-back directions, and each refrigerant pipe 31 may extend in the left-right direction (i.e., the length direction of the refrigerant pipe 31). In order to increase the contact area between the refrigerant pipe 31 and the air and to improve the heat exchange efficiency between the refrigerant and the air in the refrigerant pipe 31, each fin 32 may be in contact connection with each refrigerant pipe 31 to increase the contact area between the refrigerant pipe 31 and the air through a plurality of fins 32. For example, each fin 32 may have a corresponding through hole corresponding to each refrigerant tube 31, and the plurality of fins 32 may be spaced apart from each other in the left-right direction, so that the corresponding through holes on each fin 32 may be aligned in sequence in the left-right direction, and then each refrigerant tube 31 may be inserted into the corresponding through hole of each air outlet 16 in sequence from left to right (or from right to left), so that each refrigerant tube 31 may be in plug contact with each fin 32. Then, the left and right ends of the refrigerant pipe 31 are correspondingly communicated, and if the left and right ends of the plurality of refrigerant pipes 31 are sequentially communicated, the plurality of refrigerant pipes 31 may be divided into a plurality of groups, and the left and right ends of each group of refrigerant pipes 31 may be sequentially communicated for the circulation flow of the refrigerant. Like this, through a plurality of fins 32 along left and right direction interval distribution, greatly increased the heat radiating area of a plurality of refrigerant pipes 31 to be favorable to improving the heat exchange efficiency of refrigerant and air in refrigerant pipe 31, with the temperature of the air of quick improvement or reduction flow through fin heat exchanger 3.

Furthermore, the finned heat exchanger 3 may also be a monolithic block structure. For example, a plurality of sequentially communicated refrigerant channels may be formed in the middle of the fin heat exchanger 3, and the surface of the fin heat exchanger 3 may be cut to form a fin structure that increases the heat exchange area.

It should be noted that, in the above-described embodiment, each fin may be regarded as a planar sheet-like structure, and each fin may be approximately perpendicular to the left-right direction.

With continued reference to FIG. 5, the finned heat exchanger 3 has two oppositely disposed ends, such as an upper end (i.e., first end 33) and a lower end (i.e., second end 34). For example, when the fin heat exchanger 3 is installed, the first end 33 of the fin heat exchanger 3 may be installed near the top side plate 11, and the second end 34 of the fin heat exchanger 3 may be installed near the bottom side plate 12 (as shown in fig. 3), and the second end 34 may be located between the first end 33 and the middle partition 17 (or the fan assembly 2), that is, the first end 33 may be spaced from the air outlet 24 and in the front-rear direction, and the fin heat exchanger 3 may be located between the air outlet and the air outlet 24 in the front-rear direction. So that the first end 33 of the fin heat exchanger 3 may form an acute angle area with the top side plate 11.

When the fan assembly 2 is a centrifugal fan, after the fan assembly 2 is mounted, the axis of each fan assembly 2 after mounting is approximately parallel to the left-right direction. So, corresponding above-mentioned fin heat exchanger 3's acute angle region, can lean on gas outlet 24 to set up along the left and right directions, if install median septum 17 in holding chamber 14, can set up opening 181 at the upside of median septum 17, be convenient for align the gas outlet 24 of installation fan subassembly 2, be favorable to strengthening the structural strength that volute 21 is close to gas outlet 24 department. If the middle partition 17 is not installed in the accommodating chamber 14, each air outlet 24 may be directly installed adjacent to the top side plate 11 in the up-down direction. This is advantageous in increasing the contact area of the fin heat exchanger 3 with air.

In addition, in other embodiments, the first end 33 and the second end 34 of the fin heat exchanger 3 may be kept consistent with the distance between the at least one fan assembly 2 in the front-rear direction, that is, the fin heat exchanger 3 is arranged opposite to the air outlet 24. It should be noted that, in the embodiment of the present application, if the number of the fan assemblies 2 is plural, if no particular description is provided, each fan assembly 2 may be regarded as one of a centrifugal fan, a cross-flow fan, or an axial-flow fan having approximately the same structural shape. Accordingly, the air outlet 24 of each fan assembly 2 may be the same size. Also, the distance of each air outlet 24 from the same position on the fin heat exchanger 3 in the front-rear direction may be made approximately the same.

However, the indoor unit 10 generates noise during use. Tests show that in the process that the fan component 2 operates to drive air to flow through the fin heat exchanger 3, the fin heat exchanger 3 can generate broadband noise with the frequency within the range of 1000-3000 Hz, and the broadband noise is similar to the sound of a whistle and is called as 'fin sound' in the text. The user is very sensitive to noise in the range of 1000-3000 Hz, so the fin tone reduces the comfort of the user.

Since the plurality of fins 32 may be distributed at intervals along the left-right direction, referring to fig. 6, fig. 6 is a schematic structural view of the indoor unit 10 provided by the embodiment of the present application, in which three fan assemblies 2 are installed along the left-right direction. When the plurality of fan assemblies 2 blow air toward the air outlet 16 from the rear to the front, the rear side edge of each fin 32 does not have the same angle with the flow direction of the air. Referring to fig. 7, fig. 7 is a cross-sectional view of the indoor unit 10 shown in fig. 1. In the case of the fin heat exchanger 3, the rear side (i.e., the side facing the air outlet 24) of the fin heat exchanger 3 has at least one wind receiving area 35, and the fins 32 in each wind receiving area 35 can directly contact the air flowing out of the corresponding one of the air outlets 24. That is, at least one wind receiving area 35 corresponding one-to-one to the air outlets 24 may be provided at the rear side of the fin heat exchanger 3. Based on this, when the blown air from each air outlet 24 contacts the corresponding fin 32 in one wind receiving area 35, an angle between the air flowing direction and the left-right direction is defined as α.

It should be noted that, in conjunction with fig. 6, when the flow direction of the air (as indicated by the arrows in the figure) is parallel to the horizontal plane (i.e. parallel to both the front-back direction and the left-right direction), the included angle α may be the included angle between the flow direction of the air and the left-right direction, and the included angle α is in the horizontal plane or the plane parallel to the horizontal plane. In other embodiments, the air flow direction may also have an included angle with the horizontal plane, and in this case, the projection angle of the included angle α parallel to the horizontal plane may be slightly larger than the included angle α.

Referring to fig. 8, fig. 8 is a wind field distribution diagram of the windward side (i.e., the rear side) of the fin heat exchanger 3 shown in fig. 7. The length of the fin heat exchanger 3 can extend along the left and right directions, and the included angle between the air outlet direction of the air and the included angle alpha of the left and right directions is smaller at the left and right ends of the fin heat exchanger 3 and the middle area of the fin heat exchanger 3. Based on this, in order to better analyze the distribution rule of the fin sound, the included angle α at the windward side of the fin heat exchanger 3 is sampled and analyzed, and the distribution rule of the included angle α at each point of the windward side of the fin heat exchanger 3 shown in table one can be obtained.

Watch 1

In table one, 0.00-1.07 refers to the coordinate position of the windward side (i.e., the rear side) of the finned heat exchanger 3 from left to right, and the unit is meter. 0.0-0.34 refers to the coordinate position of the windward side of the finned heat exchanger 3 from top to bottom, and the unit is also meter. The other data in the first table represent the size of the included angle α at the coordinate position corresponding to the windward side of the fin heat exchanger 3. As can be seen from fig. 8, in some embodiments, the left and right ends of the fin heat exchanger 3, especially the positions close to the lower side, both have an included angle α smaller than 30 °, and the included angle α of the two wind receiving areas 35 of the fin heat exchanger 3 is close to 30 °. Simulation experiments show that broadband noise (namely fin sound) with the frequency within the range of 1000-3000 Hz is generated at the positions of the left end and the right end of the fin heat exchanger 3, particularly at the position of the included angle alpha of 10-30 degrees.

In order to solve the above problem, in the embodiment of the present application, the structural dimensions of the finned heat exchanger 3, the fan assembly 2 and the casing 1 in the indoor unit 10 may be adjusted so that the included angle α is smaller than 10 ° or larger than 30 °.

However, in practical applications, since the wind receiving area 35 and the air outlet 24 have opposite areas in the front-rear direction, that is, in the case that the area of the wind receiving area 35 is larger than that of the air outlet 24, the vertical projection of the air outlet 24 on the fin heat exchanger 3 in the front-rear direction is located in a corresponding one of the wind receiving areas 35. That is, in the case where the air flowing out of the air outlet 24 is blown toward the fin heat exchanger 3 in the front-rear direction, the angle α between the flow direction of this part of the air and the left-right direction is close to or equal to 90 °. Because the included angle alpha of the finned heat exchanger 3 from the two ends to the middle part is gradually increased and approaches to 90 degrees. Therefore, if the structure or the size of the indoor unit 10 is adjusted so that the included angle α between the two ends of the finned heat exchanger 3 is smaller than 10 °. The wind receiving area 35 with the included angle alpha between 10 degrees and 30 degrees will inevitably appear on the fin heat exchanger 3, and the fin sound will be generated on the fin heat exchanger 3 as well.

Therefore, the problem that broadband noise with the frequency ranging from 1000 Hz to 3000Hz is generated on the finned heat exchanger 3 is solved. The structural dimensions of the finned heat exchanger 3, the fan assembly 2 and the casing 1 in the indoor unit can be adjusted, so that the maximum included angle mu between the connecting line between the edge of each air outlet 24 and the fin at the edge of the corresponding wind-receiving area and the left-right direction is larger than 30 degrees. For example, as shown in fig. 6, when a dotted line between a right edge of the air outlet 24 (shown in fig. 5) of the rightmost one of the fan assemblies 2 in fig. 6 and the rightmost fin 32 is parallel to the horizontal plane, an angle between the dotted line and the left-right direction may be regarded as a maximum angle μ between a line between a right edge of the right air outlet 24 and the rightmost fin 32 and the left-right direction. Of the lines between the left side edge of the right air outlet 24 and the fins 32 at the left side edge of the right wind receiving area 35 (shown in fig. 7), one of the lines parallel to the horizontal direction may be at the maximum angle μ to the left-right direction.

In this way, by adjusting the structural dimensions of the finned heat exchanger 3, the fan assembly 2 and the casing 1 in the indoor unit 10, the maximum included angle μ between the connecting line of each air outlet 24 and the rear end of the fin at the edge of the corresponding wind-receiving area and the left-right direction is greater than 30 °. The included angle α can increase the size of the corresponding included angle α at the rear end of each fin 32 in each wind receiving area 35, which is beneficial to reducing the generation range of fin tones in each wind receiving area 35. For example, if the maximum included angle μ can be continuously increased, for example, to be greater than 35 °, 40 ° or even 60 °, it is beneficial to eliminate a region where the corresponding included angle α of the rear end of each fin 32 in each wind receiving region 35 is 10 ° to 30 °, and even the corresponding included angle α of the rear end of each fin 32 in each wind receiving region 35 can be further made to be much greater than 30 °, which is beneficial to reducing or even eliminating fin noise generated at the edge of the wind receiving region 35 of the fin heat exchanger 3.

Alternatively, if the projection of the air outlet 24 on the fin heat exchanger 3 in the front-rear direction is only a part of the corresponding wind receiving area 35. In this way, the positions at which the fin tones are generated at the left and right edges of the wind receiving area 35 can be concentrated toward the upper end or the lower end, or the positions at which the fin tones are generated at the upper and lower edges of the wind receiving area 35 can be concentrated toward the left end or the right end. Therefore, the range of the area of the fin heat exchanger 3 where the fin sound is generated is reduced, and the strength of the fin sound in the indoor unit 10 is favorably reduced.

Illustratively, as shown in fig. 9, fig. 9 is a top view of the interior of an indoor unit 10 according to an embodiment of the present application. Here, the two air outlets 24 may have the same shape and size, that is, the width of each of the two air outlets 24 in the left-right direction may be L1. In addition, if the two air outlets 24 are not completely the same in shape and size, L1 may be the width of the one air outlet 24 having the largest width in the left-right direction. For the fin heat exchanger 3, the distance d between two adjacent fins 32 in the left-right direction may range from 1.4mm to 1.8mm. If the distance d between two adjacent fins 32 is greater than 1.8mm, the contact between the air flowing between two adjacent fins 32 and the fins 32 is not facilitated. If the distance d between two adjacent fins 32 is less than 1.4mm, smooth air circulation is not facilitated.

In addition, the included angle alpha between the two ends of the finned heat exchanger is larger than 30 degrees. Referring to fig. 9, in the left-right direction, the left end of the finned heat exchanger 3 may be located on the left side of the leftmost air outlet 24, and the right end of the finned heat exchanger 3 may be located on the right side of the rightmost air outlet 24. That is, in the left-right direction, the left end and the right end of the fin heat exchanger 3 are respectively located at the left side and the right side of the plurality of air outlets 24 (or the fan assembly 2), that is, the right end of the fin heat exchanger 3 may be located at the right side of the rightmost air outlet 24, and the left end of the fin heat exchanger 3 may be located at the left side of the leftmost air outlet. Based on this, the minimum distance between the left end of the finned heat exchanger 3 and the leftmost (near) one of the air outlets 24 is defined as L2. Therefore, the L2/L1 is less than or equal to 0.85 by adjusting the width of the finned heat exchanger 3 in the left-right direction or the installation position of the finned heat exchanger 3 and also by adjusting the width of the leftmost air outlet 24. Therefore, the size that the left end of the fin heat exchanger 3 protrudes out of the leftmost air outlet 24 can be reduced as much as possible while the fin heat exchanger 3 is ensured to have a sufficient heat dissipation area, so that the area range of the included angle alpha of the left end of the fin heat exchanger 3 between 10 degrees and 30 degrees is reduced or even eliminated, and the intensity of fin sound generated at the left end of the fin heat exchanger 3 is favorably reduced or even completely eliminated.

Accordingly, as shown in fig. 9, the minimum distance between the right end of the finned heat exchanger 3 and the rightmost (adjacent) one of the air outlets 24 may be defined as L3. Therefore, the L3/L1 is less than or equal to 0.85 by adjusting the width of the finned heat exchanger 3 in the left-right direction or the installation position of the finned heat exchanger 3 and also by adjusting the width of the rightmost air outlet 24. Therefore, the fin heat exchanger 3 is ensured to have a sufficient heat dissipation area, and meanwhile, the size that the right end of the fin heat exchanger 3 protrudes out of the rightmost air outlet 24 can be reduced as much as possible, so that the area range of the included angle alpha of the right end of the fin heat exchanger 3 between 10 degrees and 30 degrees is reduced or even eliminated, and the intensity of fin sound generated by the right end of the fin heat exchanger 3 is favorably reduced or even completely eliminated.

In terms of the structural size, L2/L1 ≦ 0.85 and L3/L1 ≦ 0.85 may be satisfied at the same time, or may be provided alternatively. In addition, in the front-rear direction, in order to increase the heat exchange area of the fin heat exchanger 3, the sizes of L2 and L3 may be made larger than 0. In this way, in the front-rear direction, the projections of the two air outlets 24 at the left and right ends on the fin heat exchanger 3 can be respectively located in the two wind receiving areas 35, so that the air flowing out of the air outlets 24 can flow through the fins 32 in the corresponding wind receiving areas 35 more, and the heat exchange area of the fin heat exchanger is increased.

Referring to fig. 5, since the indoor unit 10 may further include an electrical box assembly 4, the electrical box assembly 4 is used for installing and isolating a control circuit board (not shown), so that the on or off state of the driving motor 25 can be adjusted through the control circuit board, and the rotation speed of the driving motor 25 can also be adjusted. When the electrical box assembly 4 is installed, the electrical box assembly 4 may be installed at both left and right ends of the blower chamber 141, for example, between the side plate 13 (shown in fig. 4) on the right side and the scroll casing 21 on the rightmost side. In addition, in other embodiments, the electrical enclosure assembly 4 may also be located between the left side plate 13 and the leftmost volute casing 21, which is not limited thereto.

Accordingly, the fin heat exchanger 3 is convenient for the refrigerant pipe 31 to communicate with the outdoor heat exchanger and the compressor in the outdoor unit. As shown in fig. 9, the right end of the fin heat exchanger 3 may be spaced from the right side plate 13 in the left-right direction so that a mounting gap (not shown) is formed between the right end of the fin heat exchanger 3 and the housing 1. Thus, due to the installation gap, when the refrigerant pipe 31 (as shown in fig. 5) is connected and installed, the air outlet 24 and the fin heat exchanger 3 can be installed in a manner of being uniformly deviated to the left side by being matched with the electrical box assembly 4 installed at the right end of the fan cavity 141, which is beneficial to improving the contact area between the flowing air and the fin heat exchanger 3, and the planning of the inner space of the indoor unit 10 is more reasonable and effective.

Based on this, referring to fig. 9, in the left-right direction in the casing 1, the minimum distance between the left side plate 13 and the leftmost air outlet 24 may be defined as L4, and the minimum distance between the right side plate 13 and the rightmost air outlet may be defined as L5.

When the fin heat exchanger 3 is installed, due to assembly or production errors, in order to improve the production and installation efficiency of the fin heat exchanger 3, an assembly gap can be formed between the end face at the left end of the fin heat exchanger 3 and the side plate 13 at the left side, and L4-L2 is more than or equal to 3mm and less than or equal to 30mm, so that excessive air can be prevented from flowing out of the assembly gap when the fin heat exchanger 3 is installed. For example, if L4-L2 is less than 3mm, a production process with higher precision is required when the casing 1 and the fin heat exchanger 3 are produced, and in the process of assembling the fin heat exchanger 3, the installation alignment at the left end of the fin heat exchanger 3 has higher precision requirement, which is not beneficial to improving the production and installation efficiency of the indoor unit 10. If L4-L2 is greater than 30mm, a large assembly gap is formed between the left end face of the fin heat exchanger 3 and the left side plate 13, so that more air flows out of the fan cavity 141 through the assembly gap, and the heat exchange efficiency of the fin heat exchanger 3 is reduced.

Correspondingly, L5/L1 can be set to be less than or equal to 1.32 at the left end of the fin heat exchanger 3, so that the left end of the fin heat exchanger 3 can be ensured to have sufficient contact area with air, and meanwhile, the installation gap can be enabled to have sufficient space in the left and right directions, and therefore the insertion and communication of the refrigerant pipe 31 are facilitated. For example, L5-L3 is more than or equal to 0.33L1 or L5-L3 is more than or equal to 50mm and less than or equal to 200mm can be arranged between the side plate 13 on the left side and the fin heat exchanger 3, so that a connecting refrigerant pipeline can be installed in the installation gap.

In the above embodiment, in the fin heat exchanger installed in the heat exchange chamber 142, an installation gap configured to communicate the refrigerant pipe 31 may be provided between the left end of the fin heat exchanger 3 and the casing 1, and an assembly gap may be provided between the right end of the fin heat exchanger 3 and the casing 1. Can be so that installation clearance and electrical apparatus box subassembly 4 all are located the left end that holds chamber 14, also can be so that electrical apparatus box subassembly 4 and installation clearance are located the left and right sides both ends that hold chamber 14 respectively. Only the corresponding proportional relations among L2, L4, L3, L5 and L1 need to be adjusted correspondingly, which is not limited,

in some embodiments, taking the fan assemblies 2 as centrifugal fans as an example, if the number of the fan assemblies 2 is one and there is only one air outlet 24, the rear sides of the fin heat exchangers 3 may be located in the same wind receiving area 35.

If the number of the fan assemblies 2 is multiple, each fan assembly 2 may be provided with one air outlet 24, and the air outlets 24 may be distributed at intervals along the axial direction (i.e., the left and right direction) of the fan assembly 2, and a wind receiving area 35 may be provided at the rear side of the fin heat exchanger 3 corresponding to each air outlet 24. It should be noted that, between two adjacent air outlets 24, a virtual air wall may be formed between the flowing air blown out from each air outlet 24. Correspondingly, the boundary line of two adjacent wind receiving areas 35 on the rear side of the fin heat exchanger 3 can be regarded as a part of the virtual wind wall. That is, the air blown out of each air outlet 24 may contact only the fins 32 in the corresponding wind-receiving area 35.

Wherein the position of the virtual air wall between the two air outlets 24 is related to the pressure of the air blown out between each air outlet 24. For example, the virtual air wall is closer to one air outlet 24, which blows air with smaller pressure, in the left-right direction. In the embodiment of the present application, it can be considered that the shape and size of each air outlet 24 are the same in the plurality of fan assemblies 2, and the shape of each air outlet 24 may be approximately rectangular or square in a cross section perpendicular to the front-rear direction, unless otherwise specified. Accordingly, referring to fig. 5, since the centrifugal impellers 22 of the two fan assemblies 2 can be driven by the same driving motor 25, the pressure of the air blown out from each air outlet 24 can be regarded as being uniform. At this time, the above-mentioned virtual air wall may be formed at the middle position of the two air outlets 24 in the left-right direction.

Therefore, in the left-right direction, the virtual air wall may be located at the middle position of two adjacent air outlets 24. In conjunction with fig. 9, a maximum distance between two adjacent air outlets 24 may be defined as L6. It should be noted that if the number of the air outlets 24 is greater than or equal to three, and the distances between two adjacent air outlets 24 are different, L6 refers to the largest distance size. Alternatively, in the plurality of air outlets 24, the distances between two adjacent air outlets 24 may be equal in size and all may be L6. In the case where the shape and size of each air outlet 24 are the same, the interval between two adjacent air outlets 24 or the width of the air outlet 214 may be adjusted such that L6 ≦ L1. Therefore, under the condition that the distance between the air outlet 24 and the fin heat exchanger 3 in the front-rear direction is not changed, the L6 is set to be not more than L1, so that the tangent value of the included angle alpha is increased, namely the size of the included angle alpha is increased, and the fin sound generated between the two adjacent wind receiving areas 35 is weakened.

In the above embodiment, the size of L6 is generally larger than zero, that is, the adjacent two air outlets 24 are spaced in the left-right direction. If L6 is equal to zero, the two air outlets 24 of two adjacent fan assemblies 2 may be merged into a larger air outlet. This is not limitative.

It should be noted that, in the above embodiment, in the process of adjusting and increasing the included angle α, it can be regarded as increasing the tangent value of the included angle α by decreasing the side length (i.e., the denominator) of the adjacent edge, so as to achieve the purpose of increasing the included angle α to weaken the fin sound generated by the rear side surface of the fin heat exchanger 3. In addition, the tangent of the angle α can be increased by increasing the side length (i.e., the numerator) of the opposing sides.

Illustratively, as shown in fig. 10, fig. 10 is an internal side view of an indoor unit 10 provided in an embodiment of the present application. Since the upper end (i.e., the first end 33 is shown in fig. 5) of the finned heat exchanger 3 installed in the heat exchange cavity 142 is installed close to the top side plate 11, the lower end (i.e., the second end 34) of the finned heat exchanger 3 is installed close to the bottom side plate 12, and the second end 34 is located between the first end 33 and the fan assembly 2 in the front-rear direction. Therefore, the distance between the upper end of the finned heat exchanger 3 and the air outlet 24 in the front-rear direction can be defined as L7, the included angle between the finned heat exchanger 3 and the top side plate 11 is defined as β, and the top side plate 11 can be perpendicular to the up-down direction.

Therefore, when the fin heat exchanger 3 is installed, the included angle beta between the fin heat exchanger 3 and the top side plate can be between 30 degrees and 60 degrees. In this way, by inclining the finned heat exchanger 3 installed in the heat exchange cavity 142, the finned heat exchanger 3 can have a sufficient contact area with the air flowing out of the air outlet 24 under the condition that the height of the shell 1 is small. If the included angle β is less than 30 °, the air flowing between two adjacent fins 32 has a longer heat exchange path in the front-rear direction, and a larger air pressure is required, which is not favorable for increasing the flow speed of the air. If the included angle is smaller than or equal to 90 degrees and is larger than or equal to 60 degrees, the contact area between the fin heat exchanger 3 and air can be greatly reduced, and the heat exchange efficiency of the fin heat exchanger 3 can be reduced.

In some embodiments, when the finned heat exchanger 3 is installed, the installation position of the finned heat exchanger 3 in the front-rear direction in the heat exchange chamber 142 can also be adjusted. For example, L7/L1. Gtoreq.0.9 may be set. Therefore, the tangent value of the included angle alpha is increased, so that the included angle alpha is increased, and the fin sound generated by the rear side surface of the fin heat exchanger 3 is weakened. In the case where the number of the air outlets 24 is plural, the distances between the plural air outlets 24 and the first end of the fin heat exchanger 3 in the front-rear direction may be the same. If the plurality of air outlets 24 are not vertically spaced from the first end 33 of the fin heat exchanger 3 in the front-rear direction, the smallest one of the air outlets is L7.

In some embodiments, with continued reference to fig. 10, it may be defined that the height of the housing 1 in the up-down direction is H1, and the height of the lower side edge of each air outlet 24 and the bottom side plate 12 in the up-down direction is H2. In the case where the number of the air outlets 24 is plural, if the lower edge of each air outlet 24 is the same as the height of the bottom side plate 12 in the vertical direction, H2 is used. If the heights are not completely the same or different, the smallest one is H2. Based on this, H2/H1 is not less than 00.56, so that the air outlet 24 can be arranged as upward as possible in the vertical direction. With the fin heat exchanger 3, since the first end 33 (i.e., the upper end, refer to fig. 5) is farther away from the air outlet 24 in the front-rear direction than the second end 34 (i.e., the lower end). Therefore, the air flowing out of the air outlet 24 can flow to the area of the fin heat exchanger 3 close to the upper end more, which is equivalent to increase the size of the L7, and is beneficial to weakening the fin sound generated by the rear side surface of the fin heat exchanger 3. Therefore, the combination of the above embodiment can also make L7/H1 more than or equal to 0.86, which is beneficial to increasing the heat exchange area of the fin heat exchanger 3.

It should be noted that, as shown in fig. 10, at the air outlet 24 at the front end of each volute 21, the fan assembly 2 may further include a first guide plate 26 and a second guide plate 27 respectively connected to the volutes 21 at the upper and lower edges of the air outlet 24. The first guide plate 26 and the second guide plate 27 are part of the scroll casing 21 or the fan assembly 2, respectively, the first guide plate 26 may be connected with the scroll casing 21 at an upper side edge of the air outlet 24, and the second guide plate 27 may be connected with the scroll casing 21 at a lower side edge of the air outlet 24. If the middle partition 17 is disposed between the heat exchange cavity 142 and the fan cavity 141, the first guide plate 26 and the second guide plate 27 may be installed through the opening 181 from back to front (as shown in fig. 5), respectively. Wherein, the upper side wall of the upper side of the volute 21 close to the air outlet 24 can be bent downwards from back to front, and the bending angle is phi. The front end of the first guide plate 26 may be bent upward such that the first guide plate 26 may be at an angle γ to the plane. In this way, the upper side wall of the volute casing 21 close to the middle partition 17 can have a gap with the top side plate 11, and can be supported by connecting part of the middle partition 17, so that the upper side wall and the top side plate 11 can be arranged at an interval to avoid the transmission of vibration. Illustratively, 0 < Φ ≦ 10 ° and 0 < γ ≦ 10 ° may be provided. In this way, a large gap formed between the volute casing 21 and the top side plate 11 due to a large bending angle can be avoided, thereby reducing the utilization rate of the internal space of the indoor unit 10.

And the front end of the second guide plate 27 may be bent downward so that the second guide plate 27 may be angled with respect to a vertical plane, which may be a plane parallel to both the left-right direction and the up-down direction, and the middle partition plate 17 may also be approximately parallel to the vertical plane. When the first guide plate 26 and the second guide plate 27 are installed, since the lower side edge of the air outlet 24 has a large distance from the bottom side plate 12, θ can be made 54 ° ≦ θ ≦ 90 °. Thus, because θ is less than 90 °, that is, the front end of the second guide plate 27 can be bent downward relative to the horizontal plane, that is, part of the air blown out from the air outlet 24 can flow through the area of the fin heat exchanger 3 near the lower end, which is beneficial to improving the contact area between the fin heat exchanger 3 and the air. Meanwhile, when part of air can flow through the area of the lower end of the fin heat exchanger 3, because the angle theta is less than or equal to 54 degrees, the air flowing out can be prevented from directly flowing through the lower end of the fin heat exchanger 3, the included angle alpha of the rear side surface of the fin heat exchanger 3 can be increased, and therefore the generated fin sound can be weakened, and even can disappear.

In combination with the above embodiments, the above embodiments can be verified by the sets of simulation experiments in table two, table three and table four, respectively.

Watch two

Watch III

Watch four

As can be seen from the table two, the adjustment of the parameters in the schemes 1 to 6 was verified by the simulation experiment to determine whether the fin noise of the indoor unit 10 can be reduced by controlling the magnitudes of the parameters H1, H2, L7, and θ. As can be seen from the third and fourth tables, the simulation experiment verifies whether the parameter adjustment in the schemes 7 to 12 can reduce the fin noise of the indoor unit 10 by controlling the magnitudes of the parameters L1, L2, L3, L4, L5, L6, and L7.

In the simulation experiments of the

schemes

1 and 2, the fin noise of the indoor unit 10 can be reduced by adjusting the parameters of H1, H2, L7, and θ, compared with the indoor unit 10 before adjustment, but the reduction range is not obvious. In the simulation experiment of the scheme 3, the fin sound of the indoor unit 10 was greatly reduced, but there was still a slight fin sound generation. In the simulation experiments of the schemes 4 to 6, the indoor unit 10 hardly generates fin sound, and the effect is the best.

In table three, the parameter sizes of L1, L2, L3, L4, L5, L6, and L7 in the cases 7 to 12 are described, and in table four, the ratios of L2, L3, L4, L5, L6, and L7 to L1 in the cases 7 to 12 are described. In the simulation experiment of the embodiment 7, the fin noise of the indoor unit 10 can be reduced by adjusting the parameters of L1, L2, L3, L4, L5, L6, and L7, compared with the indoor unit 10 before adjustment, but the reduction range is not obvious. In the simulation experiments of the versions 8 and 9, the fin sound of the indoor unit 10 was greatly reduced, but there was still a slight fin sound generation. In the simulation experiments of the schemes 10 to 12, the indoor unit 10 hardly generates the fin sound, and the effect is the best.

In the description herein, particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples.

The above description is only for the specific embodiments of the present application, but the scope of the present application is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present application should be covered within the scope of the present application. Therefore, the protection scope of the present application shall be subject to the protection scope of the claims.

Claims

1. An air conditioner, characterized in that, includes indoor set, indoor set includes:

the shell is provided with an accommodating cavity, and an air inlet and an air outlet which are respectively communicated with the accommodating cavity;

the fan assembly is arranged in the accommodating cavity and is provided with an air inlet communicated with the air inlet and an air outlet arranged towards the air outlet; and the number of the first and second groups,

the finned heat exchanger is positioned in the accommodating cavity and is arranged between the air outlet and the air outlet; the fin heat exchanger comprises a plurality of fins distributed at intervals along a first linear direction, and the first linear direction is perpendicular to the plurality of fins;

one side of the fin heat exchanger facing the air outlet is provided with a wind receiving area, and the fins in each wind receiving area directly contact the air flowing out of the corresponding air outlet; the maximum included angle between a connecting line between the edge of each air outlet and the fin at the edge of the corresponding wind receiving area and the first direction is larger than 30 degrees.

2. The air conditioner according to claim 1, wherein said fan assembly is a centrifugal fan and is plural in number, said plural fan assemblies are spaced apart along said first linear direction, each of said fan assemblies includes one of said air outlets; the plurality of air outlets are distributed at intervals along the first straight line direction, and the maximum width dimension of each air outlet in the first straight line direction is L1;

the shell comprises a top side plate and a bottom side plate which are oppositely arranged along a second straight line direction, the second straight line direction is perpendicular to the first straight line direction, and each air outlet is arranged close to the top side plate along the second straight line direction;

along the second linear direction, one end, close to the bottom side plate, of the fin heat exchanger is close to the fan assembly in a third linear direction, one end, close to the top side plate, of the fin heat exchanger is far away from the fan assembly in the third linear direction, and the fin heat exchanger is installed between the fan assembly and the air outlet in the third linear direction.

3. The air conditioner according to claim 2, wherein both ends of the finned heat exchanger in the first linear direction are respectively located on opposite sides of the plurality of air outlets in the first linear direction;

along the first straight line direction, the minimum distance between one end face of the finned heat exchanger and the air outlet close to the end face is L2, and L2/L1 is less than or equal to 0.85; and/or the presence of a gas in the gas,

along the first straight line direction, the minimum distance between the other end face of the finned heat exchanger and the air outlet close to the other end face of the finned heat exchanger is L3, and L3/L1 is less than or equal to 0.85.

4. The air conditioner according to claim 2, wherein each of the air outlets has the same shape, and each of the air outlets has a width dimension L1 in the first linear direction, and a maximum distance between two adjacent air outlets in the first linear direction is L6, and L6 is equal to or less than L1.

5. The air conditioner according to claim 3, wherein the number of the air outlet ports is two, and a sectional shape of each of the air outlet ports in a direction parallel to the first straight line direction and the second straight line direction is a rectangle.

6. The air conditioner according to claim 2, wherein along the first straight line direction, a mounting gap is formed between one end of the fin heat exchanger and the side wall of the shell body close to the one end of the fin heat exchanger, and the mounting gap is used for mounting and connecting a refrigerant pipe of the fin heat exchanger;

and along the first straight line direction, the minimum distance between the edge of the air outlet close to the mounting gap and the shell is L5, and L5/L1 is less than or equal to 1.32.

7. The air conditioner according to claim 2, wherein along the second linear direction, the height dimension of the housing is H1, the minimum distance between the edge of each air outlet far away from the top side plate and the bottom side plate is H2, and H2/H1 is greater than or equal to 0.56.

8. The air conditioner according to claim 7, wherein an angle θ between an edge of each of said air outlets facing away from said top side plate in said second linear direction and a vertical plane satisfies 54 ° θ < 90 °;

wherein the vertical plane is parallel to both the first linear direction and the second linear direction; and along the second linear direction, the edge of the air outlet far away from the top side plate is gradually close to the bottom side plate in the third linear direction.

9. The air conditioner according to claim 7, wherein along the third linear direction, the minimum distance between one end of the finned heat exchanger in the second linear direction, which is close to the top side plate, and the air outlet is L7, and L7/L1 is greater than or equal to 0.9, and L7/H1 is greater than or equal to 0.86.

10. The air conditioner as claimed in claim 2, wherein said top side plate is perpendicular to said second linear direction, and an angle β between said finned heat exchanger and said top side plate satisfies 30 ° β 60 °.