CN218544615U

CN218544615U - Air conditioner

Info

Publication number: CN218544615U
Application number: CN202221665396.8U
Authority: CN
Inventors: 高文栋; 刘晓蕾; 李亚军; 孟建军
Original assignee: Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Current assignee: Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Priority date: 2022-06-30
Filing date: 2022-06-30
Publication date: 2023-02-28
Anticipated expiration: 2032-06-30

Abstract

The utility model discloses an air conditioner relates to domestic appliance technical field, aims at solving because the big problem of machine running noise in the air conditioning that the fin sound leads to. In the indoor unit of the air conditioner, the fan assembly is arranged in the accommodating cavity of the shell, and the fin heat exchanger is positioned in the accommodating cavity and arranged between the air outlet and the air outlet. The first end of the fin heat exchanger is located on one side, close to the top side plate, of the fin heat exchanger and is arranged at intervals with the top side plate, the first end and the gas outlet are distributed at intervals along a first linear direction, the second end of the fin heat exchanger is located on one side, far away from the top side plate, of the first end, and the second end of the fin heat exchanger is located on the fan assembly along the first linear direction. The porous medium layer is filled between the first end and the top side plate. Along the first straight line direction, the porous medium layer is used for passing through air, and the fluid resistance coefficient of the porous medium layer is larger than that of the fin heat exchanger. The utility model provides an air conditioner is used for reducing the noise in operation of indoor set.

Description

Air conditioner

Technical Field

The utility model relates to the technical field of household appliances, especially, relate to an air conditioner.

Background

An air-conditioning buried indoor unit (such as a ducted air conditioner) is developed according to market diversity requirements and overall decoration space changes, and is increasingly used in ordinary households due to 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 the air conditioner in a bedroom is not allowed to generate abnormal sound.

However, in the air-conditioning indoor unit in the prior art, because the finned heat exchanger and the upper cover plate form an acute included angle on the windward side, the wind blown out from the fan easily flows back in a small space at the included angle to form a vortex, and the vortex can make the edge of the fin vibrate continuously, so that fin sound is generated, the noise generated when the air-conditioning indoor unit operates is large, and inconvenience is brought to users.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide an air conditioner aims at solving because the big problem of air conditioning indoor set running noise that the fin sound leads to.

In order to achieve the above purpose, the utility model adopts the following technical scheme:

some embodiments of the utility model provide an air conditioner, including the indoor set, the indoor set includes casing, fan subassembly, fin heat exchanger and porous medium layer. The casing has holds the chamber and respectively with hold air intake and the air outlet that the chamber communicates, and the casing includes the top side board. 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 positioned in the accommodating cavity and is arranged between the air outlet and the air outlet. The fin heat exchanger is provided with a first end and a second end which are oppositely arranged, the first end is located on one side, close to the top side plate, of the fin heat exchanger and is arranged at intervals with the top side plate, the first end and the gas outlet are distributed at intervals along a first linear direction, the second end is located on one side, far away from the top side plate, of the first end, and the second end is located on the fan assembly along the first linear direction. The porous medium layer is filled between the first end and the top side plate. And along the first straight line direction, the porous medium layer is used for passing air, and the fluid resistance coefficient of the porous medium layer is larger than that of the fin heat exchanger.

So, in the casing of indoor set, under fan assembly's drive, the in-process of blowing to fin heat exchanger by the air that the gas outlet blew out, when air is being close to fin heat exchanger's a side edge towards fan assembly, even the air can form the vortex in the acute angle region of first end and roof side board, however, because the porous medium layer can pass through certain air, some air can flow to air outlet department through the porous medium layer, thereby can reduce the vortex intensity in the acute angle region, be favorable to weakening the intensity of this place fin sound, with the noise that reduces air conditioner operation. Meanwhile, as the fluid resistance coefficient of the porous medium layer is larger than that of the fin heat exchanger, most of air still flows through the fin heat exchanger to exchange heat, and the problem that the heat exchange efficiency of the air conditioner is greatly reduced is avoided.

In some embodiments, the housing further comprises a drainage member, and the drainage member is in contact connection with the top side plate. The drainage piece is provided with a drainage surface, and the drainage surface is arranged opposite to the end surface of the first end. Along the direction of perpendicular to top curb plate, the interval of drainage face and top curb plate is crescent by fan subassembly to air outlet. The porous medium layer is also filled between the drainage surface and the first end.

In some embodiments, the porous medium layer is in fit contact with the drainage surface, the end surface of the first end facing the drainage surface, and the edge of the top side plate close to the drainage member.

In some embodiments, the porous medium layer comprises sound absorbing cotton or open cell foam.

In some embodiments, the porous medium layer is made of a metallic material.

In some embodiments, the fluid resistance coefficient of the porous media layer comprises a porous inertial resistance coefficient and a porous viscous resistance coefficient, the porous inertial resistance coefficient is 240000-350000 kg/m ⁴ The coefficient of porous viscous resistance is 350000-500000 kg s/m ³ 。

In some embodiments, the fan assembly is a centrifugal fan. The casing still includes two support frames, and along fan assembly's axial, two support frames are close to the both ends setting of fin heat exchanger respectively to connect between first end and drainage piece. And the porous medium layer is filled between the two support frames along the axial direction of the fan assembly.

In some embodiments, the indoor unit further comprises an appliance box assembly. The air outlet comprises a first air outlet and a second air outlet, and the air inlet comprises a first air inlet and a second air inlet. The fan assembly includes a first centrifugal fan and a second centrifugal fan. The first centrifugal fan is arranged close to the electrical box assembly. The first centrifugal fan is provided with a first air inlet and a first air outlet, the first air inlet is communicated with the air inlet, and the first air outlet is arranged towards the fin heat exchanger and is communicated with the first air inlet. The second centrifugal fan is positioned at one end of the first centrifugal fan far away from the electric box assembly. The second centrifugal fan is provided with a second air inlet and a second air outlet, the second air inlet is communicated with the air inlet, and the second air outlet is arranged towards the fin heat exchanger and is communicated with the second air inlet. And the fluid resistance coefficient of the porous medium layer corresponding to the first air outlet is smaller than or equal to the fluid resistance coefficient of the porous medium layer corresponding to the second air outlet.

In some embodiments, the first centrifugal fan includes a first volute and a first centrifugal impeller, and the first centrifugal impeller is mounted within the first volute. The second centrifugal fan comprises a second volute and a second centrifugal impeller, and the second centrifugal impeller is installed in the second volute. The fan assembly further comprises a driving motor, and the driving motor is installed between the first volute and the second volute. Output shafts at two ends of the driving motor are respectively connected with the first centrifugal impeller and the second centrifugal impeller along the axial direction of the first centrifugal impeller; and the driving motor is electrically connected with the electric box component.

In some embodiments, the housing further comprises two side panels, a bottom side panel, and a middle partition. Two curb plates are along first centrifugal fan's axial, and two curb plates are connected with two relative edges of top curb plate respectively. The bottom side plate is provided with two oppositely arranged edges and is respectively connected with one end of each side plate, which is far away from the top side plate. The top side plate, the bottom side plate and the two side plates are enclosed to form an accommodating cavity. Along the first straight line direction, the fan assembly is arranged close to the air inlet, and the fin heat exchanger is arranged close to the air outlet. Along first linear direction, the median septum is installed between fan subassembly and finned heat exchanger to will hold the chamber and separate for the air inlet chamber that is close to the fan subassembly and the air-out chamber that is close to finned heat exchanger, and the median septum corresponds first gas outlet and second gas outlet and has seted up two openings respectively and be used for communicateing air inlet chamber and air-out chamber.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required to be used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the description below 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 air conditioner according to an embodiment of the present disclosure;

fig. 2 is a schematic perspective view of the indoor unit shown in fig. 1;

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. 2;

FIG. 6 is a schematic view of the air flow between the fan assembly and the fins shown in FIG. 5;

FIG. 7 is a schematic view of the finned heat exchanger shown in FIG. 5 showing the generation of a vortex flow between the heat exchanger and the air outlet;

FIG. 8 is a simulated flow field profile provided by an embodiment of the present application;

fig. 9 is a graph illustrating a noise spectrum of an indoor unit according to an embodiment of the present disclosure;

FIG. 10 is a side sectional view of the air conditioner of FIG. 5 mounted to a baffle;

FIG. 11 is a left side view of the air conditioner shown in FIG. 10;

FIG. 12 is a bottom view of the baffle shown in FIG. 10;

FIG. 13 is a perspective view of the baffle member shown in FIG. 12;

fig. 14 is a perspective cross-sectional view of another indoor unit provided in the embodiment of the present application;

FIG. 15 is an enlarged partial schematic view of the porous medium layer installed between the first end and the top side plate shown in FIG. 14;

FIG. 16 is an enlarged partial schematic view of the porous medium layer installed between the first end and the drainage member shown in FIG. 14;

fig. 17 is a schematic perspective view of an indoor unit provided with a support frame according to an embodiment of the present disclosure;

fig. 18 is a partially enlarged view of a portion a in fig. 17.

Reference numerals are as follows:

100-an air conditioner;

10-an indoor unit;

1-a shell; 11-top side plate; 12-bottom side plate; 13-side plates; 14-a containment chamber; 141-an air inlet cavity; 142-an air outlet cavity; 15-air inlet; 16-air outlet; 17-a middle separator; 181-opening; 182-ceiling attachment lugs; 183-drainage member; 184-a support frame;

2-a fan assembly; 21-a first centrifugal fan; 211-a first volute; 212-a first centrifugal impeller; 213-a first air inlet; 214-first outlet port; 22-a second centrifugal fan; 221-a second volute; 222-a second centrifugal impeller; 223-a second air inlet; 224-a second air outlet; 23-drive the motor.

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

4-a flow guide part; 41-a first wing plate; 411-first base; 412-first connecting edge; 413-a first leeward side; 42-a second wing panel; 421-second base; 422-a second connecting edge; 423-second leeward side; 43-a connecting plate;

5-an electrical box assembly;

6-porous medium layer.

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 obtained by a person of ordinary skill in the art based on the embodiments in the present application without making any creative effort belong to 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 the case may be.

In the embodiments of the present application, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one of 8230, and" comprising 8230does not exclude the presence of additional like elements in a process, article, or apparatus comprising the element.

In the embodiments of the present application, the words "exemplary" or "such as" are used herein to mean serving as an example, instance, or illustration. Any embodiment or design described herein as "exemplary" or "such as" 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, where 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 as to transfer indoor heat to the outdoor space through a compressor in the outdoor unit and the finned heat exchanger 3 in the indoor unit 10. 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 illustration 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 respectively along upper and lower direction interval distribution, and left and right direction interval distribution can be followed respectively to two limit curb plates 13, 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 have an air inlet 15 and an air outlet 16 respectively communicating with the accommodating chamber 14 along the front-rear direction (i.e., the first 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 inlet 15 and an air outlet 16 at the front end and the rear end, 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 left, right, upper, and lower edges of the middle partition 17. Thus, the middle partition 17 can divide the accommodating chamber 14 into the air outlet chamber 142 and the air inlet chamber 141 in the front-rear direction. The air outlet chamber 142 can be communicated with the air outlet 16, and correspondingly, the air inlet chamber 141 can be communicated with the air inlet 15. In addition, the middle partition 17 may be provided with at least one opening 181 for communicating the air inlet cavity 141 and the air outlet cavity 142, so that the installation cavity 14 may be respectively communicated with the air inlet 15 and the air outlet 16, so as to implement a ventilation channel 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 a duct unit. Or a wall-mounted indoor unit. Taking an air duct machine as an indoor unit as an example, 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 the left and right sides of the casing and respectively connected to the left and right ends of the two side plates 13 or the top side plate 11. Wherein, each ceiling engaging lug 182 is provided with an engaging hole, and the indoor unit 10 can be fixed under the ceiling by the ceiling engaging lug 182 through the connection manner of an expansion hanging rod 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 parallel to the horizontal direction and the front-rear direction). Decorative layers such as a ceiling structure may be subsequently 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 also be directly installed on an indoor wall or ceiling in a hanging manner, which is not limited to this.

It should be noted that, for the housing 1, a middle partition 17 for separating the air inlet chamber 141 and the air outlet chamber 142 may be disposed 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, no middle partition plate is required to be disposed in the installation cavity 14, and only the first air outlet 214 and/or the second air outlet 224 need to be respectively installed forward toward the finned heat exchanger 3, which is simple in structure. In addition, under the condition of satisfying the air circulation, the side walls which surround the left and right sides and the upper and lower sides of the installation cavity 14 of the shell 1 can be partially or completely arranged into a frame structure, and only flow pipelines of air are required to be respectively arranged at the upstream and downstream sides of the finned heat exchanger 3 for drainage, so that the side walls are not limited.

As shown in fig. 5, in order to facilitate the heat exchange of the indoor air, the fan assembly 2 may include a first centrifugal fan 21 and a second centrifugal fan 22, and the first centrifugal fan 21 and the second centrifugal fan 22 may be sequentially distributed in the left-right direction. Taking the example in which the first centrifugal fan 21 is located on the right side of the second centrifugal fan 22.

Exemplarily, referring to fig. 5, the first centrifugal fan 21 may include a first volute 211 and a first centrifugal impeller 212, the first centrifugal impeller 212 being installed in the first volute 211. At least one side of the first scroll casing 211 in the left-right direction (i.e., the axial direction of the first scroll casing 211) is provided with a first inlet port 213, and the first scroll casing 211 is forwardly provided with a first outlet port 214 communicating with the first inlet port 213. The first air outlet 214 may be disposed toward the fin heat exchanger 3 in the front. In the case where the center partition 17 is installed in the installation cavity 14 (as shown in fig. 3), the first air outlet 214 may be disposed near one opening 181 on the right side, and an edge of the first volute 211 near the first air outlet 214 may contact or even be in close contact with an edge of the opening 181 on the right side. In this way, under the rotation of the first centrifugal impeller 212, the first centrifugal fan 21 can draw the air in the air inlet chamber 141 through the first air inlet 213, and blow the drawn air forward to the right portion of the fin heat exchanger 3 in the air outlet chamber 142 through the first air outlet 214 and the opening 181 on the right side, and finally blow out the indoor unit 10 from the air outlet 16 communicating with the air outlet chamber 142.

With continued reference to fig. 5, the second centrifugal fan 22 may include a second volute 221 and a second centrifugal impeller 222, the second centrifugal impeller 222 being mounted within the second volute 221. At least one side of the second scroll casing 221 in the left-right direction (i.e., the axial direction of the second scroll casing 221) is provided with a second air inlet 223, and the second scroll casing 221 is provided forward with a second air outlet 224 communicating with the second air inlet 223. The second air outlet 224 may be disposed toward the fin heat exchanger 3 in the front. In the case where the center partition 17 is installed in the installation cavity 14 (as shown in fig. 3), the second air outlet 224 may be disposed near one opening 181 on the left side, and the edge of the second volute 221 near the second air outlet 224 may contact or even be in close contact with the edge of the opening 181 on the left side. In this way, under the rotation of the second centrifugal impeller 222, the second centrifugal fan 22 can draw the air in the air inlet chamber 141 through the second air inlet 223, and blow the drawn air forward to the left portion of the fin heat exchanger 3 in the air outlet chamber 142 through the second air outlet 224 and the left opening 181, and finally blow out the indoor unit 10 through the air outlet 16 communicated with the air outlet chamber 142.

In order to rotate the first centrifugal impeller 212 and the second centrifugal impeller 222, as shown in fig. 5, the fan assembly 2 may further include a driving motor 23. The first centrifugal fan 21 and the second centrifugal fan 22 may be spaced apart from each other in the left-right direction, and the driving motor 23 may be installed between the first centrifugal fan 21 and the second centrifugal fan 22 in the left-right direction. The axes of the driving motor 23, the first centrifugal impeller 212 and the second centrifugal impeller 222 can be collinear, so that the output shafts at the left and right ends of the driving motor 23 can be respectively connected to and synchronously drive the first centrifugal impeller 212 and the second centrifugal impeller 222 to rotate.

In addition, the driving motor 23 may be installed at the right side of the first centrifugal fan 21, so that the first centrifugal impeller 212 and the second centrifugal impeller 222 may be connected to the output shaft at the left side of the driving motor 23 through a transmission shaft, so that the driving motor 23 may synchronously drive the first centrifugal impeller 212 and the second centrifugal impeller 222 to rotate. Or, the driving motor 23 may be installed on the left side of the second centrifugal fan 22, so that the first centrifugal impeller 212 and the second centrifugal impeller 222 may be connected to the output shaft on the right side of the driving motor 23 through a transmission shaft, so that the driving motor 23 can synchronously drive the first centrifugal impeller 212 and the second centrifugal impeller 222 to rotate.

In some other embodiments, the first centrifugal fan 21 may also include a first driving motor, and the first driving motor may be installed in the first volute 211 and connected to the first centrifugal impeller 212 for driving the first centrifugal impeller 212 to rotate around the left-right direction. Correspondingly, the second centrifugal fan 22 may also include a second driving motor, and the second driving motor may be installed in the second volute 221 and connected to the second centrifugal impeller 222 for driving the second centrifugal impeller 222 to rotate around the left-right direction. Or the air can be driven to pass through the air inlet cavity 141, the air outlet cavity 142 and the finned heat exchanger 3 in sequence by the air inlet 15, and finally blown out of the indoor unit 10 by the air outlet 16.

It should be noted that the fan assembly 2 provided in the embodiment of the present application may be a centrifugal fan, and may also be an axial flow fan or an oblique flow fan, both of which may drive air to flow through the installation cavity 14. The number of the centrifugal fans of the fan assembly 2 can be one, three, four or more, and can be adjusted according to the index of the air circulation amount in unit time. This is not limitative. In the embodiment of the present application, the air inlet of the fan assembly 2 may include a first air inlet 213 and a second air inlet 223, and the air outlet of the fan assembly 2 may include a first air outlet 214 and a second air outlet 224.

In the outlet cavity 142, as shown in fig. 5, the fin heat exchanger 3 may include a plurality of refrigerant tubes 31 and a plurality of fins 32. For example, the plurality of refrigerant pipes 31 may respectively communicate with a compressor and an outdoor heat exchanger in an outdoor unit of the air conditioner 100 (shown in fig. 1) for circulation of a refrigerant. In the outlet chamber 142, the plurality of refrigerant pipes 31 may be spaced apart in the up-down and front-rear directions, and each refrigerant pipe 31 may extend in the left-right direction. 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 fins 32 may be distributed at intervals along the left-right direction, so that the corresponding through holes on each air outlet 16 may be aligned along the left-right direction, and then each refrigerant tube 31 may be sequentially inserted into the corresponding through hole of each air outlet 16 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 a plurality of refrigerant pipe 31's heat radiating area to refrigerant and air's heat exchange efficiency has been improved in refrigerant pipe 31, with improve fast or reduce indoor air temperature.

Furthermore, the finned heat exchanger 3 may also be of unitary construction. For example, a plurality of sequentially communicated coolant 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.

With continued reference to fig. 5, the finned heat exchanger 3 has two oppositely disposed ends, such as an upper end (i.e., the first end 33) and a lower end (i.e., the 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, that is, the first end 33 may be spaced from the first air outlet 214 and the second air outlet 224 in the front-rear direction. Since the plurality of fins 32 may be spaced apart from each other in the left-right direction, in conjunction with fig. 6, 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. With reference to fig. 7, the included angle between the finned heat exchanger 3 and the top side plate 11 is an acute angle towards the fan assembly 2. When the air (i.e., the main air flow shown in fig. 7) blown toward the fin heat exchanger 3 by the air outlets (i.e., the first air outlet 214 and/or the second air outlet 224) contacts the rear side edges of the fins 32, part of the main air flow will flow back upward and rearward after contacting the rear side edges of the fins 32. As such, a vortex is formed between the return air and the main air flow.

For the above reasons, the simulated flow field distribution diagram shown in fig. 8 can be obtained by simulating the flow field between the fin heat exchanger 3 and the fan assembly 2 of the indoor unit 10. It is obvious that the fin heat exchanger 3 generates a shedding vortex flow of different degrees in the rear side of the fin heat exchanger 3 in the vicinity of the first centrifugal fan 21 and the second centrifugal fan 22, respectively. The detached vortex flow reduces the heat exchange efficiency of the refrigerant in the refrigerant pipe 31. Also, since air in different directions flows are separated to different degrees at the rear side edges of the fins 32 when blown onto the fins 32, a negative pressure region is formed near the rear side edges of the fins 32. Based on this, the detached vortex generated by the flow separation will continue to flow forward under the driving of the main air flow, and forms feedback and generates sound wave when contacting the rear side edge of the fin 32, forming self-oscillation phenomenon, thereby generating abnormal sound.

The noise spectrum graph of the indoor unit shown in fig. 9 can be obtained by performing simulation analysis on the noises of different frequencies generated when the indoor unit 10 (the duct unit) operates. Obviously, significant noise (i.e., fin noise) occurs in the frequency band between 3K and 4K, which greatly increases the amount of noise generated during operation of the indoor unit 10.

In order to solve the problem of loud operation noise of the indoor unit 10 due to the fin sound. As shown in fig. 10, the indoor unit 10 may further include a flow guide 4. For example, the air guiding element 4 may be installed in the air outlet cavity 142 and connected to the top side plate 11, or may be connected to the adjacent side plate 13. Meanwhile, the flow guide 4 may be located between the fin heat exchanger 3 and the first air outlet 214 (as shown in fig. 5). In this way, when the air blown out from the first air outlet 214 is blown to the fin heat exchanger 3, the air guide 4 can guide the air flowing therethrough to change the flowing direction of the air. If the air flowing through the air guide member 4 is dispersed to the left and right sides, it may be dispersed as if it were to the upper and lower sides. Therefore, the air blown out from the first air outlet 214 is prevented from being concentrated in the partial area at the rear side of the fin heat exchanger 3, the self-oscillation intensity of the rear side edge of the fin heat exchanger 3 corresponding to the area of the first air outlet 214 is reduced, the fin sound intensity is weakened, and the purpose of reducing the noise volume when the indoor unit 10 operates is achieved.

In some embodiments, the fan assembly 2 may be a centrifugal fan having an air outlet mounted adjacent the top side panel 11. In this way, the air blown out of the air outlet will be concentrated in the area of the first end 33 of the fin heat exchanger 3. Therefore, the flow guide piece 4 can be directly contacted with the top side plate 11 or even attached to the top side plate. Therefore, the air flowing through the air guide member 4 can be dispersed to the left, the right or the lower part, and is prevented from being excessively concentrated on the rear area of the first end 33, which is beneficial to weakening the fin sound intensity, so as to achieve the purpose of reducing the noise volume when the indoor unit 10 operates.

And, because water conservancy diversion spare 4 can with the downside direct contact of top side board 11 laminate even be connected, compare in the mode of installing water conservancy diversion spare 4 with the avris board 13 interval that is close to, need not additionally to set up and connect support piece, only need through glue, screw or rivet connection can, the installation of the water conservancy diversion spare 4 of being convenient for.

In order to increase the structural strength of the top side plate 11 and the bottom side plate 12 of the housing 1, generally, a reinforcing rib or a structural groove having a groove structure is provided on each of the top side plate 11 and the bottom side plate 12 to increase the structural strength of the top side plate 11 and the bottom side plate 12 in the vertical direction. However, since the air flowing between the air outlet and the first end 33 flows close to the top side plate 11, the flow velocity of the air is not affected by the uneven surface of the top side plate 11. The housing 1 may further include a guide plate, which may be installed between the top side plate 11 and the guide member 4, for improving the flatness of the lower side surface (the area between the air outlet and the air outlet 16) of the top side plate 11. The air flow velocity is improved, and the noise generated by the flow type is reduced.

If a baffle is attached to the lower surface of the top side plate 11, the baffle may be a part of the top side plate 11, that is, the lower surface of the top side plate 11 corresponds to the lower plane of the baffle. At this moment, the guide member 4 can be in plane contact with the lower side of the guide plate or even be attached to the lower side of the guide plate. If the guide plate is not installed on the lower side surface of the top side plate 11, the lower side surface of the area, corresponding to the fan assembly 2 and between the air outlets, of the top side plate 11 can be set to be of a plane structure.

In the present embodiment, the flow guide 4 may be installed between the first air outlet 214 and the first end 33. Furthermore, the baffle 4 may also be mounted between the second air outlet 224 and the first end 33. Even in the case where the number of the air outlets is one or more, the flow guide 4 may be installed between any air outlet and the first end 33.

As for the air guiding element 4, the air guiding element 4 installed between the fan assembly 2 and the first end 33 is taken as an example. A cross section of the flow guide 4 perpendicular to the front-rear direction may be defined as a flow guide longitudinal section. The cross section of the flow guide member 4 perpendicular to the up-down direction is a flow guide flat cross section. Based on this, from the back to the front, the area of water conservancy diversion longitudinal section increases gradually. The area of the flow guide flat section is gradually reduced from top to bottom. Illustratively, the rear end of the flow guide 4 is in a tip structure in the front-rear direction, and the lower end of the flow guide 4 is in a tip structure in the up-down direction. Therefore, after passing through the flow guide piece 4, the air can be dispersed left and right and below by the flow guide piece 4, so that the air is prevented from being concentrated at the area of the rear side of the fin heat exchanger 3, which is right opposite to the air outlet, and the reduction of fin sound generated when the indoor unit 10 runs is facilitated.

Illustratively, the main structure of the flow guide 4 may be approximately a triangular pyramid structure, wherein a sharp corner is aligned backwards with an air outlet. Or, the main structure of the flow guide member 4 may also be similar to a triangular prism, one of the right-angle surfaces may be disposed upward and connected to the top side plate 11, and the other right-angle surface may be disposed forward and face the air outlet 16. Or, the main structure of the flow guide piece can be similar to a semi-cone structure, the part of the semi-cone structure close to the tip end can be arranged towards the air outlet, and the semi-cone structure can be attached to the top side plate. The air flowing through the air guide member 4 can be dispersed and flowed towards the left and right or the lower part, and the air guide member is not limited.

The flow guide member 4 may be a tapered block structure, or may be a triangular cone structure formed by connecting two plate-like structures with the top side plate 11.

In the embodiment of the present application, the structural size of the flow guide element 4 itself and the installation position of the flow guide element 4 both affect the flow guide effect of the flow guide element 4, and further affect the noise reduction effect of the fin noise when the indoor unit 10 operates.

In some embodiments, as shown in fig. 11, the left or right side cross section of the finned heat exchanger 3 may be approximately rectangular or square. However, since the fin heat exchanger 3 may be disposed to be inclined rearward, an acute angle region toward the rear may be formed between the fin heat exchanger 3 and the top side plate 11. In order to facilitate the first end 33 and the second end 34 to contact the top side plate 11 and the bottom side plate 12 respectively (as shown in fig. 3), a right-angled region on the lower side of the first end 33 may be removed, and a right-angled region on the upper side of the second end may also be removed, so as to increase the contact area between the first end 33 and the top side plate 11, and increase the contact area between the second end 34 and the bottom side plate 12. The air can have longer contact time when flowing through the fin heat exchanger 3, and the heat exchange efficiency of the fin heat exchanger 3 is improved.

With continued reference to fig. 11, the distance between the first end 33 and the second end 34 in the up-down direction may be defined as the height dimension H of the finned heat exchanger 3. Since the first end 33 can be disposed close to the lower side surface contacting the top side plate 11, the distance between the fin heat exchanger 3 and the top side plate 11 can be ignored, and the height dimension H of the fin heat exchanger 3 can be regarded as the distance in the up-down direction between the second end 34 and the top side plate 11 (i.e., the installation height dimension of the fin heat exchanger 3). Correspondingly, the upper side surface of the flow guide part 4 can contact or even be attached to the top side plate 11, so that the maximum distance between the lower end of the flow guide part 4 and the top side plate can be defined as the height h of the flow guide part 4. When the height dimension of the flow guide piece 4 and the height dimension of the fin heat exchanger 3 meet the relationship that H/H is more than or equal to 3 and less than or equal to 5, the self-oscillation of the vortex at the rear side of the fin heat exchanger 3 can be well improved, the noise reduction effect of fin sound can be improved, and the fin heat exchanger 3 at the first end 33 has good heat exchange efficiency.

For example, if H/H > 5, the air branched by the flow guide 4 will be more concentrated in the area near the first end 33, which is not favorable for improving the noise reduction effect of the fin noise. If H/H is less than 3, the air branched by the flow guide member 4 will be blown more to the area near the second end 34, which will improve the noise reduction effect of the fin sound, but will greatly reduce the air flow passing through the first end 33, thereby reducing the heat exchange efficiency of the fin heat exchanger 3 at the first end 33.

Since the first air outlet 214 and the second air outlet 224 may be approximately aligned in the left-right direction, in conjunction with fig. 11, a distance dimension d between the air outlets (including the first air outlet 214 and the second air outlet 224) and the rear end of the flow guide 4 in the front-rear direction may be defined. And the distance between the first end 33 and the second end 34 in the front-rear direction may be defined as the length dimension L1 of the fin heat exchanger 3. Referring to fig. 12, fig. 12 is a bottom view of the baffle 4 shown in fig. 10. The maximum flow guide dimension of the flow guide 4 in the front-rear direction may be defined as a length dimension L2 of the flow guide 4. And the maximum flow guide size of the flow guide 4 in the left-right direction may be defined as a width size L3 of the flow guide 4.

Based on the above dimensions, when the width dimension and the length dimension of the flow guide member 4 satisfy 1 ≤ L2/L3 ≤ 3, the flow guide member 4 itself can have a better flow guide effect. For the installation position of the flow guide part 4, when the distance between the rear end of the flow guide part 4 and the air outlet satisfies d/L2 which is more than or equal to 1.5 and less than or equal to 3, the flow guide part 4 has a better flow guide effect. And when the length dimension of the flow guide piece 4 and the length dimension of the fin heat exchanger 3 meet the condition that L1/L2 is more than or equal to 3 and less than or equal to 4, the flow guide piece 4 has a better flow guide effect. The improvement of the noise reduction effect of the fin sound is facilitated, and the fin heat exchanger 3 at the first end 33 has better heat exchange efficiency.

For example, in any of the embodiments of L2/L3 < 1, d/L2 > 5, and L1/L2 > 4, the air branched by the flow guide 4 may be concentrated at a certain region near the first end 33, which is not beneficial to improving the noise reduction effect of the fin sound. However, in any embodiment where L2/L3 is greater than 3, d/L2 is less than 1.5, and L1/L2 is less than 3, the air divided by the flow guide 4 will be blown upwards or dispersed to the left and right, which results in a great reduction in the air flowing through the partial area of the first end 33 facing the air outlet, and although the noise reduction effect of the fin sound will be improved, the air flow flowing through the first end 33 will be greatly reduced, thereby reducing the heat exchange efficiency of the fin heat exchanger 3 at the first end 33.

In some embodiments, as shown in fig. 12, the baffle 4 may include a first wing plate 41 and a second wing plate 42. Wherein the wing plate positioned at the left side of the air guide 4 may be the first wing plate 41.

For example, when the baffle 4 is installed in the installation cavity 14 or the air outlet cavity 14, the upper ends of the first wing plate 41 and the second wing plate 42 may be connected to the top side plate 11, respectively, and then the edges of the first wing plate 41 and the second wing plate 42 near the upper side may be connected to form the baffle 4 for dispersing air. When the first blade 41 and the second blade 42 are connected to the top side plate 11, they may be connected by bonding or welding. The upper ends of the first wing plate 41 and the second wing plate 42 may be respectively provided with a connecting lug or a positioning column, and connected to the top side plate 11 by means of clamping, screws, rivets, or the like.

In addition, as shown in fig. 12, the baffle 4 may further include a connecting plate 43, and the connecting plate 43 may be respectively connected to the upper ends of the first wing plate 41 and the second wing plate 42, so that the connecting plate 43 contacts or even abuts the top side plate 11 (as shown in fig. 11) and is connected to the top side plate 11. Illustratively, a plurality of mounting holes 44 may be formed in the connecting plate 43, so that the top side plate 11 and the connecting plate 43 may be connected by screws or rivets penetrating through the mounting holes 44.

It should be noted that, in the embodiment of the present application, the definition of the flow guiding size of the flow guiding element 4 refers to the size of the main structure of the flow guiding element 4 for dispersing air. In general, the flow guide size does not include a structure of the flow guide 4 that mainly plays a role of fixed connection, but does not play a role of a small flow guide effect. For example, in the above embodiment, the length, width, and height dimensions of the main structure formed by connecting the first wing plate 41 and the second wing plate 42 in the front-rear, left-right, and up-down directions are the air flow dimensions of the air guide.

In some embodiments, as shown in fig. 13, fig. 13 is a perspective view of the baffle 4 shown in fig. 12. The first wing plate 41 may include a first bottom edge 411, a first connecting edge 412, and a first leeward edge 413 connected in sequence. Correspondingly, the second wing panel 42 may include a second bottom edge 421, a second connecting edge 422, and a second leeward edge 423, which are connected in sequence. In this way, the first connecting edge 412 and the second connecting edge 422 are connected to each other, the first bottom edge 411 and the second bottom edge 421 are connected to the top side plate 11 (as shown in fig. 11), and the first leeward edge 413 and the second leeward edge 423 are attached to face forward. In this manner, the rear end of the baffle 4 formed by connecting the first wing plate 41 and the second wing plate 42 has a pointed structure so as to make the air flowing through the first wing plate 41 and the second wing plate 42 dispersedly flow toward the left and right sides and the upper side, respectively. Moreover, the flow guide piece 4 is made of a plate-shaped material, so that the structure is simple and the material is saved.

In the above embodiment, the first wing plate 41 and the second wing plate 42 may be approximately triangular, approximately quadrangular or pentagonal, or arc-shaped, and only need to disperse and guide the flowing air, which is not limited herein.

For example, as shown in fig. 13, an included angle between the first connecting edge 412 and the first bottom edge 411 may be defined as α, and an included angle between the second connecting edge 422 and the second bottom edge 421 is defined as β, and when α + β ≦ 90 °, the air flowing through the air guide 4 is favorable for reducing the fin noise of the indoor unit 10 (shown in fig. 10), and the fin heat exchanger 3 has better heat exchanger efficiency.

Wherein, in order to avoid the process that high-speed air blows to the air guide element 4 from backward to forward, the air vibrates at the edge of the air guide element 4 and produces noise. As shown in fig. 13, the first connecting edge 412, the second connecting edge 422, the first bottom edge 411, the second bottom edge 421 and the connecting plate 43 may be connected by a chamfering process or a rounding process, respectively. Illustratively, the first connecting edge 412 and the second connecting edge 422 may be connected by a chamfering or rounding process. The first bottom edge 411 and the connection plate 43 may be connected by a chamfering or rounding process. The second bottom edge 421 and the connecting plate 43 can be connected by a chamfering or rounding process. Also, the edge of the left connecting plate 43 away from the first wing plate 41 may be chamfered or rounded, and the edge of the right connecting plate 43 away from the second wing plate 42 may be correspondingly rounded or chamfered.

Therefore, the edges and the included angles of the windward side of the flow guide part 4 are provided with the chamfers or the fillet structures, so that air can smoothly flow through the flow guide part when flowing through the part, and further more noise is avoided. Which is advantageous for reducing the amount of noise generated when the indoor unit 10 is operated.

In some embodiments, the first wing plate 41, the second wing plate 42, and the connecting plate 43 may be a same piece of sheet metal structure. The flow guide piece 4 can be formed by a stamping process, and the structure is simple and the processing is convenient.

In some embodiments, to facilitate controlling the fan assembly 2 in the indoor unit 10, as shown in fig. 5, the indoor unit 10 may further include an electrical enclosure assembly 5. Illustratively, the electrical box assembly 5 can be located in the installation cavity 14 or the air inlet cavity 141, for example, the electrical box assembly 5 can be installed at the left end or the right end of the fan assembly 2, and can be electrically connected with a motor (such as the driving motor 23) in the fan assembly 2, so as to adjust the air circulation amount flowing through the fin heat exchanger 3 in the indoor unit 10 by controlling the rotation speed of the driving motor 23.

Referring to fig. 5, the electrical box assembly 5 can be installed in the air inlet chamber 141 and is disposed at the right side of the first centrifugal fan 21 and spaced from the first centrifugal fan 21. Since the electrical box assembly 5 is disposed close to the first centrifugal fan 21, the first centrifugal fan 21 has a larger air intake space and an air blowing space. Referring to fig. 8, at the same rotation speed, the first centrifugal fan 21 can bring a larger air flow rate than the second centrifugal fan 22 is disposed far from the electrical box assembly 5. For the above reason, the fin sound is also caused to be larger in the region of the rear side edge of the fin heat exchanger 3 corresponding to the first centrifugal fan 21.

As such, in some embodiments, the flow guide 4 may also be installed only between the first centrifugal fan 21 and the fin heat exchanger 3. So that the fin sound in the area of the rear side edge of the fin heat exchanger 3 corresponding to the first centrifugal fan 21 can be greatly reduced, thereby improving the use experience of the user. Is simple and effective. In other embodiments, the flow guide element 4 may be disposed between the second centrifugal fan 22 and the fin heat exchanger, so that the fin noise of the indoor unit 10 during operation can be reduced to the maximum.

In some embodiments, when the width dimension L2 and the length dimension L3 of the flow guide 4 satisfy L2/L3=1.8, the height dimension H of the flow guide 4 and the height dimension H of the fin heat exchanger satisfy H/H =4, and the distance dimension d from the rear end of the flow guide 4 to the first air outlet 214 satisfies d/L2= 2. The air blown out from the first air outlet 214 is dispersed and guided by the guide piece 4, so that the strength of fin sound can be well reduced under the condition that the heat exchange efficiency of the fin heat exchanger 3 is ensured. Compared with the situation without the diversion element 4, the experimental simulation shows that. Through the arrangement of the diversion element 4, the noise volume of the indoor unit 10 is obviously reduced in the running process with the same air volume or rotating speed. Especially for the fin sound with the frequency of more than 3000HZ, the average noise reduction data is more than 6dB, and the effect is remarkable.

In other embodiments, in combination with fig. 7 and 14, to solve the problem that the fin sound is easily generated at the rear side of the first end 33 of the fin heat exchanger 3. The first end 33 may be spaced apart from the top side plate 11 in the up-down direction. In this way, when the air blown to the first end 33 from the first air outlet 214 and/or the second air outlet 224 approaches the fin heat exchanger 3, the static pressure of the air chamber in the rear edge area of the first end 33 is greatly reduced because part of the air is blown out from the air outlet 16 to the front or front and lower in the gap between the first end 33 and the top side plate 11. So that the intensity of the fin sound can be greatly reduced to reduce the noise generated when the air conditioner 10 operates.

However, a large amount of air that does not contact the fin heat exchanger 3 for heat exchange is lost due to the gap between the first end 33 and the top side plate 11. That is, although the above configuration can reduce the fin noise in this region, the heat exchange efficiency of the fin heat exchanger 3 is also greatly reduced, and the operating efficiency of the air conditioner 10 is reduced.

In order to solve the above problem, as shown in fig. 15, the air conditioner 10 may further include a porous medium layer 6, and the porous medium layer 6 may be filled between the top side plates 11 of the first end 33. The porous medium layer 6 can be used for passing air, but the fluid resistance coefficient of the porous medium layer 6 is larger than that of the fin heat exchanger 3 (shown in fig. 7) in the front-rear direction. In this way, when the air blown forward from the air outlet to the first end 33 approaches the rear side edge of the fin 32, even though the air may form a vortex in the acute angle area between the first end 33 and the top side plate, since the porous medium layer 6 may pass a certain amount of air, a part of the air may flow to the air outlet 16 through the porous medium layer 6, so that the strength of the vortex in the acute angle area may be reduced, which is beneficial to weakening the strength of the fin sound at this point, so as to reduce the noise of the air conditioner 10 during operation. Meanwhile, as the fluid resistance coefficient of the porous medium layer 6 is greater than that of the fin heat exchanger 3, that is, most of the air still flows through the fin heat exchanger 3 to exchange heat, the problem that the heat exchange efficiency of the air conditioner 10 is greatly reduced is avoided.

Illustratively, the porous medium layer 6 may include sound absorbing cotton or an open-cell type foam material, so that the fluid resistance coefficient of the porous medium layer 6 is larger than that of the fin heat exchanger 3 while air flows through the porous medium layer 6.

The sound absorption cotton forming the porous medium layer 6 may be made of metal or non-metal material. The corresponding open-cell foam material constituting the porous medium layer 6 may also be a metallic material or a non-metallic material. This is not limitative.

The metal material has good heat-conducting property. Illustratively, the porous dielectric layer 6 may be made of a metal material having a good heat conductive formation. Such as a suitable density of wire or metal foam may be filled between the first end 33 and the top side panel 11. Thus, when air passes through the porous medium layer 6, the porous medium layer 6 made of metal material is also contacted with the first end, namely the porous medium layer 6 with good heat conductivity can also exchange heat for the air flowing through. Thereby further improving the heat exchange efficiency of the indoor unit 10.

In some embodiments, the fluid resistivity of the porous media layer 6 includes a porous inertial resistivity and a porous viscous resistivity. Wherein the coefficient of porous inertial resistance is 240000-350000 kg/m ⁴ The coefficient of porous viscous resistance is 350000-500000 kg s/m ³ . When the porous inertia resistance coefficient is 3000000kg/m ⁴ And a porous viscous drag coefficient of 400000kg "s/m ³ In the process, the flow guide effect of the porous medium layer 6 can take the advantages of silencing of the indoor unit 10 and improvement of heat exchange efficiency into consideration.

In some embodiments, as shown in fig. 14 and 15, the housing 1 may further include a drainage member 183, and the drainage member 183 may be in contact with or even in close contact with the top side plate 11. The flow guide 183 may be installed in the air outlet cavity 142 and near the air outlet 16. The lower rear side of the flow guide 4 may have a flow guide surface (not shown), and the distance between the flow guide surface and the top side plate 11 in the up-down direction may gradually increase from the rear to the front, so that the flow guide surface may be opposite to and spaced from the end surface of the first end 33. Thus, by the arrangement of the inclined flow guide surface, the air can be changed in direction by the flow guide surface when flowing to the flow guide surface, so that the air can be blown out from the air outlet 16 along the lower front direction. Since the indoor unit 10 is generally installed in an upper space of a room, the heat-exchanged air can be directly blown to a lower portion of the room (i.e., a ring contacted by a user) to improve the user experience of the user.

However, as shown in fig. 15, since there is a gap between the first end 33 and the top side plate 11, a part of the air on the upper side close to the top side plate 11 passes only through a part of the fins 32 (shown in fig. 5) of the first end 33 from the rear to the front, and thus, the heat exchange efficiency is low.

Based on this, as shown in fig. 16, a porous medium layer 6 may be further filled between the first end 33 and the drainage member 183 (i.e., drainage surface). In this way, when the part of the air on the upper side close to the top side plate 11 approaches the porous medium layer 6 between the first end 33 and the flow guide 183 from the rear direction, the fluid resistance coefficient of the porous medium layer 6 is larger than that of the fin heat exchanger 3 (shown in fig. 5) in the front-rear direction. Therefore, most of air can change the flowing direction after contacting the surface of the porous medium layer 6 at the position, and continuously flows to the air outlet 16 from between the fin heat exchangers 3, and in the process, the air flowing through the fin heat exchangers 3 can continuously exchange heat with the fin heat exchangers 3, which is beneficial to improving the heat exchange efficiency of the air conditioner 10.

As shown in fig. 16, in the outlet chamber 142, the air directly blown out through the porous medium layer 6 between the first end 33 and the top side plate 11 may continue to flow along the porous medium layer 6 between the first end 33 and the drainage member 183. Because the porous medium layer 6 can also be made of a metal material with higher heat conductivity, the porous medium layer 6 can also play a role in heat exchange efficiency of air flowing through by contacting with the fin heat exchanger 3, and the improvement of the heat exchange efficiency is facilitated.

In some embodiments, the air flow guiding and noise reduction effects are prevented from being influenced by mounting gaps at the edges of the porous medium layer 6. The porous medium layer 6 may be in abutting contact with the flow guiding surface and the end surface of the first end 33 facing the flow guiding surface, respectively. Meanwhile, the porous medium layer 6 can be in fit contact with the edge of the top side plate 11 close to the drainage component 183. Thus, the noise phenomenon caused by the flowing air flowing in the gap between the porous medium layer 6 and the contact part can be avoided, and the noise quantity of the indoor unit 10 during operation can be reduced.

At porous inertia resistance coefficientIs 3000000kg/m ⁴ And a porous viscous drag coefficient of 400000kg "s/m ³ In this case, the porous medium layer 6 is provided. Under the condition of ensuring the heat exchange efficiency of the fin heat exchanger 3, the intensity of fin sound can be well reduced. Compared with the situation that the fin heat exchanger 3 is installed in direct contact with the top side plate 11, the installation method is known through experimental simulation. Through the arrangement of the porous medium layer 6, the noise volume of the air conditioner 10 is obviously reduced in the operation process with the same air volume or rotating speed. Especially for the fin sound with the frequency of more than 3000HZ, the average noise reduction data is more than 6dB, and the effect is remarkable.

In order to facilitate installation and fixation of the porous medium layer 6, the porous medium layer 6 may be installed between the first end 33 and the top side plate 11 in an extruding manner, or the porous medium layer 6 may be installed between the first end 33 and the drainage member 183 in an extruding manner. Thereby restricting the displacement of the porous medium layer 6 in the front-rear, left-right, and up-down directions.

In addition, as shown in fig. 17, the casing 1 may further include two support brackets 184, and the two support brackets 184 may be respectively disposed near both ends of the fin heat exchanger 3 in the left-right direction. Referring to fig. 18, a support bracket 184 on the left side may be connected between the left side of first end 33 and drain 183. Correspondingly, the right side of a right support bracket 184 can also be connected between the first end 33 and the drain 183. As such, the porous medium layer 6 may be filled between the two support frames 184 in the left-right direction, so that the displacement of the porous medium layer 6 in the left-right direction may be defined by the two support frames 184.

It should be noted that the length of the flow guide 183 in the left-right direction may be greater than or equal to the length of the fin heat exchanger 3 in the left-right direction. Illustratively, the flow guide member 183 may be approximately a triangular prism structure, and is close to two end faces of an acute angle, one of the end faces may contact or even be attached to the edge of the top side plate 11 close to the air outlet 16, and the other end face may be a flow guide face and contact or be spaced from the end face of the first end 33, so that the structure is stable. In addition, the drainage component 183 can also be a long strip-shaped sheet structure, the rear side edge of the sheet structure can be in contact with or even in fit connection with the top side plate 11 along the front-rear direction, and the sheet structure can be arranged to incline forwards from back to back, so that the distance between the sheet structure and the top side plate 11 increases from back to front, the inclined lower side surface of the sheet structure can be in contact with or arranged at an interval with the end surface of the first end 33, and the drainage component is simple in structure.

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 air inlet and the air outlet are respectively communicated with the accommodating cavity, and the shell comprises a top side plate;

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;

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 is provided with a first end and a second end which are arranged oppositely, the first end is positioned on one side of the fin heat exchanger close to the top side plate and is arranged at intervals with the top side plate, the first end and the air outlet are distributed at intervals along a first linear direction, and the second end is positioned on one side of the first end far away from the top side plate and is arranged on the fan assembly along the first linear direction; and the number of the first and second groups,

the porous medium layer is filled between the first end and the top side plate; along the first straight line direction, the porous medium layer is used for passing through air, and the fluid resistance coefficient of the porous medium layer is larger than that of the fin heat exchanger.

2. The air conditioner according to claim 1, wherein the housing further comprises a flow guide member, the flow guide member being in contact connection with the top side plate; the drainage piece is provided with a drainage surface, and the drainage surface is opposite to the end surface of the first end; along the direction vertical to the top side plate, the distance between the flow guide surface and the top side plate is gradually increased from the fan assembly to the air outlet;

the porous medium layer is also filled between the drainage surface and the first end.

3. The air conditioner of claim 2, wherein the porous medium layer is in abutting contact with the flow guide surface, the end surface of the first end facing the flow guide surface, and the edge of the top side plate close to the flow guide member.

4. The air conditioner of claim 1, wherein the porous medium layer comprises sound absorbing cotton or open cell type foam.

5. The air conditioner according to claim 4, wherein the porous medium layer is made of a metal material.

6. The air conditioner of claim 1, wherein the fluid resistance coefficient of the porous medium layer comprises a porous inertial resistance coefficient and a porous viscous resistance coefficient, and the porous inertial resistance coefficient is 240000-350000 kg/m ⁴ The coefficient of porous viscous resistance is 350000-500000 kg s/m ³ 。

7. The air conditioner of claim 2, wherein the fan assembly is a centrifugal fan;

the shell further comprises two support frames, the two support frames are respectively arranged close to two ends of the fin heat exchanger along the axial direction of the fan assembly and connected between the first end and the drainage piece; and the porous medium layer is filled between the two support frames along the axial direction of the fan assembly.

8. The air conditioner according to any one of claims 1 to 7, wherein the indoor unit further comprises an electric box assembly; the air outlets comprise a first air outlet and a second air outlet, and the air inlets comprise a first air inlet and a second air inlet;

the fan assembly includes:

a first centrifugal fan mounted adjacent to the appliance box assembly; the first centrifugal fan is provided with a first air inlet and a first air outlet, the first air inlet is communicated with the air inlet, and the first air outlet faces the fin heat exchanger and is communicated with the first air inlet; and the number of the first and second groups,

the second centrifugal fan is positioned at one end of the first centrifugal fan, which is far away from the electrical box assembly; the second centrifugal fan is provided with a second air inlet and a second air outlet, the second air inlet is communicated with the air inlet, and the second air outlet faces the fin heat exchanger and is communicated with the second air inlet;

and the fluid resistance coefficient of the porous medium layer corresponding to the first air outlet is smaller than or equal to the fluid resistance coefficient of the porous medium layer corresponding to the second air outlet.

9. The air conditioner according to claim 8, wherein said first centrifugal fan includes a first volute and a first centrifugal impeller, and said first centrifugal impeller is mounted in said first volute;

the second centrifugal fan comprises a second volute and a second centrifugal impeller, and the second centrifugal impeller is arranged in the second volute;

the fan assembly further comprises a drive motor, and the drive motor is installed between the first volute and the second volute; along the axial direction of the first centrifugal impeller, output shafts at two ends of the driving motor are respectively connected with the first centrifugal impeller and the second centrifugal impeller; and the driving motor is electrically connected with the electric box assembly.

10. The air conditioner of claim 8, wherein the housing further comprises:

the two side plates are respectively connected with two opposite edges of the top side plate along the axial direction of the first centrifugal fan;

the bottom side plate is provided with two oppositely arranged edges and is respectively connected with one end of each side plate far away from the top side plate; the top side plate, the bottom side plate and the two side plates form the accommodating cavity in an enclosing mode; along the first straight line direction, the fan assembly is arranged close to the air inlet, and the fin heat exchanger is arranged close to the air outlet; and (c) a second step of,

the middle partition board is arranged between the fan assembly and the fin heat exchanger and divides the accommodating cavity into an air inlet cavity close to the fan assembly and an air outlet cavity close to the fin heat exchanger, and two openings for communicating the air inlet cavity and the air outlet cavity are respectively formed in the first air outlet and the second air outlet corresponding to the middle partition board.