A ducted air conditioner

Abstract

The application discloses a ducted air conditioner, which aims to improve the ventilation volume of the ducted air conditioner. The shell of the ducted air conditioner has a mounting cavity and a return air inlet, and fan assemblies and indoor heat exchangers are located in the mounting cavity and are spaced apart along a first linear direction. The fan assemblies are centrifugal fans and are used to drive air to enter the mounting cavity from the return air inlet and flow through the indoor heat exchangers. An electrical box is located in the mounting cavity and is used to control the rotation of the fan assemblies. The first linear direction is perpendicular to the axial direction of the fan assemblies, and the electrical box is arranged along the axial direction of the fan assemblies and close to one side wall of the mounting cavity. Along the axial direction of the fan assemblies, the width dimension of the mounting cavity is greater than or equal to the sum of the width dimension of the return air inlet and the thickness dimension of the electrical box, and the ratio X1 of the thickness dimension of the electrical box to the width dimension of the return air inlet is in the range of 0.1≤X1<0.12 or 0.12≤X1≤0.18. The air conditioner provided by the application is used to improve the heat exchange efficiency of the indoor unit.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of air conditioning technology, and in particular to a ducted air conditioner. BACKGROUND

[0002] The indoor unit of the ducted air conditioner is a ducted unit. The ducted unit has the advantages of hidden installation mode and convenience in cooperation with home ceiling, etc., so that the ducted air conditioner has good aesthetics when installed indoors.

[0003] When the air conditioner is running, the rotation of the impeller of the fan assembly causes the air near the casing to enter the casing. The air exchanges heat with the heat exchanger during the flow through the heat exchanger, and the heat-exchanged air can flow out of the casing and adjust the temperature and / or humidity near the installation area.

[0004] Since the centrifugal fan has the characteristics of high wind pressure, low noise and small size, by setting the fan assembly as a centrifugal fan, the ventilation capacity of the ducted unit is improved and the ventilation noise is reduced. However, at the return air inlet of the ducted unit, the width dimension of the return air inlet along the axial direction of the fan assembly has a great influence on the ventilation capacity of the ducted unit. SUMMARY

[0005] The purpose of the present application is to provide a ducted air conditioner, which aims to improve the ventilation capacity of the ducted unit.

[0006] To achieve the above-mentioned purpose, the present application adopts the following technical scheme:

[0007] The present application provides a ducted air conditioner, which comprises an indoor unit. The indoor unit comprises a casing, an indoor heat exchanger, a fan assembly and an electrical box. The casing has a mounting cavity and a return air inlet. The fan assembly is a centrifugal fan. The fan assembly and the indoor heat exchanger are located in the mounting cavity and are spaced apart along a first straight line direction. The fan assembly is used to drive air to enter the mounting cavity from the return air inlet and flow through the indoor heat exchanger. The electrical box is located in the mounting cavity and is used to control the rotation of the fan assembly. The first straight line direction is perpendicular to the axial direction of the fan assembly. Along the axial direction of the fan assembly, the electrical box is arranged close to one side wall of the mounting cavity. Along the axial direction of the fan assembly, the width dimension of the mounting cavity is greater than or equal to the sum of the width dimension of the return air inlet and the thickness dimension of the electrical box, and the ratio X1 of the thickness dimension of the electrical box to the width dimension of the return air inlet is in the range of 0.1≤X1<0.12 or 0.12≤X1≤0.18.

[0008] In the installation cavity of the indoor unit, the fan assembly of the centrifugal fan structure and the indoor heat exchanger can be arranged along a first linear direction and spaced apart from each other, and the first linear direction is perpendicular to the axial direction of the fan assembly. The fan assembly is used to drive air to enter the installation cavity from the return air inlet and flow through the indoor heat exchanger. Since the fan assembly of the centrifugal fan structure has the characteristics of small volume, low noise, and large air pressure, it is beneficial to improve the air flow in the ducted air conditioner with limited height space.

[0009] Therefore, by setting the ratio X1 of the thickness dimension of the electrical box to the width dimension of the return air inlet as 0.1≤X1<0.12 or 0.12≤X1≤0.18, the electrical box can have sufficient space to accommodate the control elements and dissipate heat, and the return air inlet can have sufficient width dimension to allow the fan assembly in the ducted air conditioner to extract sufficient air around the return air inlet to blow towards the indoor heat exchanger. Therefore, the indoor heat exchanger can be in contact with sufficient air for heat exchange, which is beneficial to improve the overall heat exchange efficiency of the ducted air conditioner.

[0010] In some embodiments, the fan assembly includes a plurality of volutes and a plurality of centrifugal impellers. The volutes have exhaust outlets arranged along a first linear direction towards the indoor heat exchanger. One centrifugal impeller is installed in one volute, and the electrical box is used to control the rotational speed of the centrifugal impeller to drive air flow.

[0011] In some embodiments, the electrical box and the plurality of volutes are arranged along the axial direction of the centrifugal impeller.

[0012] In some embodiments, the number of volutes and the number of centrifugal impellers are two.

[0013] In some embodiments, along the axial direction of the centrifugal impeller, the distance between one volute close to the electrical box and the electrical box is a first distance L1, and the distance between the other volute and the side wall of the installation cavity away from the electrical box is a second distance L2. The ratio X3 of the first distance and the second distance is in the range of 0.9≤X3≤0.1.

[0014] In some embodiments, the ratio X3 of the first distance and the second distance is in the range of 0.1

[0015] In some embodiments, the ratio X3 of the first distance and the second distance is in the range of 1.26

[0016] In some embodiments, the ratio X3 of the first distance and the second distance is in the range of 1.43≤X3≤1.6.

[0017] In some embodiments, the first distance is equal to the second distance.

[0018] In some embodiments, the first spacing dimension and the second spacing dimension are 69.3 mm, 74.3 mm, or 79.3 mm.

[0019] In some embodiments, a ratio X2 of the first spacing dimension to an axial width dimension of the centrifugal impeller is in a range of 0.4≤X2<0.6.

[0020] In some embodiments, a ratio X2 of the first spacing dimension to an axial width dimension of the centrifugal impeller is in a range of 0.6≤X2≤0.66.

[0021] In some embodiments, the axial width dimension w2 of the centrifugal impeller is in a range of 115 mm≤w2<120.5 mm.

[0022] In some embodiments, the axial width dimension w2 of the centrifugal impeller is in a range of 120.5 mm≤w2≤126.

[0023] In some embodiments, the plurality of volutes have the same shape dimension, and the plurality of centrifugal impellers have the same shape dimension.

[0024] In some embodiments, a ratio K1 of a width dimension of the volute to a width dimension of the centrifugal impeller along an axial direction of the centrifugal impeller is in a range of 1.18≤K1<1.24.

[0025] In some embodiments, a ratio K1 of a width dimension of the volute to a width dimension of the centrifugal impeller along an axial direction of the centrifugal impeller is in a range of 1.24≤K1≤1.32.

[0026] In some embodiments, a thickness dimension w3 of the electric appliance box is in a range of 65≤w4<75.

[0027] In some embodiments, a thickness dimension w3 of the electric appliance box is in a range of 75≤w4≤85.

[0028] In some embodiments, a width dimension w of the mounting cavity is in a range of 600≤w<700.

[0029] In some embodiments, a width dimension w of the mounting cavity is in a range of 700≤w≤800. BRIEF DESCRIPTION OF DRAWINGS

[0030] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings needed in the embodiment description will be briefly introduced as follows. Obviously, the drawings in the following description are only some embodiments of the present application, and other drawings can also be obtained by those skilled in the art without any creative effort based on these drawings.

[0031] Figure 1A connection structure diagram of a ducted air conditioner provided in an embodiment of the present application;

[0032] Figure 2 A structure diagram in which a gas-liquid separator and an oil separator are installed between a compressor and a four-way valve shown in the Figure 1

[0033] Figure 3 A connection structure diagram of a compressor and an outdoor heat exchanger and an indoor heat exchanger without a four-way valve shown in the Figure 1

[0034] A side view of an indoor unit of a first ducted air conditioner provided in an embodiment of the present application; Figure 4

[0035] A three-dimensional structure diagram of an indoor heat exchanger shown in the Figure 5 Figure 4 A side view of an indoor unit of a second ducted air conditioner provided in an embodiment of the present application;

[0036] Figure 6 A side view of an indoor unit of a third ducted air conditioner provided in an embodiment of the present application;

[0037] Figure 7 A side view of an indoor unit of a fourth ducted air conditioner provided in an embodiment of the present application;

[0038] Figure 8 A three-dimensional structure diagram of an indoor unit shown in the

[0039] Figure 9 Figure 8 A sectional view of a volute and a centrifugal impeller shown in the

[0040] Figure 10 A side view of a volute and a centrifugal impeller shown in the Figure 9

[0041] A sectional view of a volute and a centrifugal impeller shown in the Figure 11 Figure 9 A sectional view of a volute and a centrifugal impeller shown in the

[0042] Figure 12 Figure 11 A relationship curve diagram of air volume and rotation speed of four sets of centrifugal fans;

[0043] Figure 13 A sectional view of a ducted air conditioner shown in the

[0044] Figure 14 A sectional view of a ducted air conditioner shown in the Figure 9

[0045] A sectional view of a ducted air conditioner shown in the Figure 15 Figure 14 ​​​​​​A top view of the electrical box and fan assembly shown in the middle, spaced apart in the left-right direction;

[0046] Figure 16 A schematic diagram of a wind field simulation before improvement;

[0047] Figure 17 A schematic diagram of a wind field simulation after improvement;

[0048] Figure 18 A graph of the installation position of the volute and the air flow through the indoor heat exchanger. DETAILED DESCRIPTION

[0049] 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. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by a person of ordinary skill in the art without creative effort belong to the scope of protection of the present application.

[0050] In the description of the present application, it should be understood that the terms "upper", "lower", "left", "right", "front", "back", "inner", "outer" and the like indicate the orientation or positional relationship shown in the drawings based on the orientation or relative position shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation. Therefore, it should not be understood as a limitation on the present application. Unless otherwise specified, the above orientation description can be flexibly arranged in the actual application process under the condition of meeting the relative position relationship shown in the drawings.

[0051] The terms "first", "second" are only for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the technical features indicated. Therefore, the features limited by "first", "second" can explicitly or implicitly include one or more of the features. In the description of the present application, unless otherwise specified, the meaning of "a plurality of" is two or more.

[0052] In the description of the present application, it should be noted that, unless otherwise specified and limited, the terms "mounting", "connecting", "connecting", "communicating" should be understood broadly, such as fixed connection, detachable connection, integral connection. It can be directly connected, or indirectly connected through an intermediate medium. It can be the communication between two elements or the electrical connection between two elements. For a person of ordinary skill in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0053] It should be noted that in actual application, due to the limitation of equipment precision or installation error, absolute parallelism or perpendicularity is difficult to achieve. In the present application, the description of perpendicularity, parallelism or same direction is not an absolute limitation, but indicates that the structure of perpendicularity or parallelism can be achieved within a preset error range (such as 5° deviation up and down), and the corresponding preset effect is achieved, so that the technical effect of the limited feature can be maximized, and the corresponding technical solution is easy to implement and has high feasibility.

[0054] In the embodiments of the present application, the terms "comprising", "containing" or any other variant thereof are intended to cover non-exclusive inclusion, so that the process, article or device including a series of elements not only includes those elements, but also includes other elements not explicitly listed or inherent to such process, article or device. Without more limitation, the element defined by the sentence "including a…" does not exclude the presence of other identical elements in the process, article or device including the element.

[0055] In the embodiments of the present application, the words such as "exemplary" or "for example" are used to represent an example, illustration or description. In the embodiments of the present application, any embodiment or design scheme described as "exemplary" or "for example" should not be interpreted as more preferred or more advantageous than other embodiments or design schemes, and in fact, the words such as "exemplary" or "for example" are intended to present the relevant concept in a specific manner.

[0056] The air conditioner is a device that can adjust and control the temperature, humidity and circulating air of the environment air in a building or structure.

[0057] As shown in Figure 1 , the present application provides a duct type air conditioner (hereinafter referred to as air conditioner 100), which can include a compressor 10, a four-way valve 20, an outdoor heat exchanger 30, a throttling device 40 and an indoor heat exchanger 50. For example, referring to Figure 1 , the four-way valve 20 can have a first port A, a second port B, a third port C and a fourth port D, and the compressor 10 can have a gas return end and a gas outlet end (not shown in the figure).

[0058] The gas return end of the compressor 10 can be connected with the first port A of the four-way valve, the gas outlet end of the compressor 10 can be connected with the second port B of the four-way valve, the third port C of the four-way valve can be connected with one end of the outdoor heat exchanger 30, the other end of the outdoor heat exchanger 30 can be connected with one end of the indoor heat exchanger 50 through the throttling device 40, and the other end of the indoor heat exchanger 50 can be connected with the fourth port D of the four-way valve.

[0059] The air conditioner 100 can include an indoor unit and an outdoor unit, the compressor 10, the four-way valve 20, and the outdoor heat exchanger 30 can be part of the outdoor unit, and the corresponding indoor heat exchanger 50 can be part of the indoor unit. The throttling device 40 can be a capillary structure or an electronic expansion valve structure. The throttling device 40 can be installed in the outdoor unit, or installed in the indoor unit, or installed in the refrigerant pipeline between the outdoor unit and the indoor unit. As long as the throttling device 40 is located between the indoor heat exchanger 50 and the outdoor heat exchanger 30 along the flow direction of the refrigerant.

[0060] Based on this, under the driving of the compressor 10, the refrigerant can circulate between the indoor unit and the outdoor unit and undergo reversible phase change, and the refrigerant can release or absorb heat through the heat exchanger while undergoing phase change.

[0061] For example, the refrigerant in the outdoor unit can exchange heat with the surrounding medium (such as air) through the outdoor heat exchanger 30, thereby releasing heat and heating the surrounding air (or absorbing heat and cooling the surrounding air). The refrigerant in the indoor unit can exchange heat with the surrounding air through the indoor heat exchanger 50, thereby absorbing heat to cool the surrounding air (or releasing heat to heat the surrounding air).

[0062] Through the arrangement of the four-way valve 20, the operation mode of the air conditioner 100 can be flexibly adjusted between the heating and cooling conditions, so that the air conditioner 100 can be applied to more use scenarios.

[0063] When the air conditioner 100 is in a cooling or dehumidifying condition, the four-way valve 20 can be adjusted to make the second port B and the third port C conductive, and the fourth port D and the first port A conductive. Figure 1 For example, as shown by the solid arrows in FIG. 1, the four-way valve 20 can be adjusted to make the second port B and the third port C conductive, and the fourth port D and the first port A conductive.

[0064] In this way, the high-pressure gaseous refrigerant compressed by the compressor 10 can flow from the gas outlet to the outdoor heat exchanger 30 through the second port B and the third port C of the four-way valve 20, so that the high-temperature and high-pressure gaseous refrigerant can be liquefied and release heat at the outdoor heat exchanger 30 to heat the air near the outdoor heat exchanger 30.

[0065] Subsequently, under the action of the throttling device 40, the liquid refrigerant passing through the throttling device 40 and flowing into the indoor heat exchanger 50 can reduce the pressure of the liquid refrigerant, so that the liquid refrigerant can absorb heat and vaporize at the indoor heat exchanger 50, thereby exchanging and transferring heat between the outdoor heat exchanger 30 and the indoor heat exchanger 50 and cooling the air near the indoor heat exchanger 50. The refrigerant flowing out of the indoor heat exchanger 50 after vaporization can flow through the fourth port D and the first port A of the four-way valve 20 in turn, and then the gaseous refrigerant can be sucked into the compressor 10 through the gas inlet and compressed, thereby realizing the circulation of the refrigerant.

[0066] When the air conditioner 100 is in the heating mode, the four-way valve 20 is adjusted to make the second port B and the fourth port D conductive, and the third port C and the first port A conductive. Figure 1 For example, as shown by the dashed arrow, the four-way valve 20 can be adjusted to make the second port B and the fourth port D conductive, and the third port C and the first port A conductive.

[0067] Thus, the high-temperature and high-pressure gaseous refrigerant compressed by the compressor 10 can flow from the outlet end to the indoor heat exchanger 50 through the second port B and the fourth port D of the four-way valve 20, so that the high-temperature and high-pressure gaseous refrigerant can be liquefied and release heat at the indoor heat exchanger 50 to heat the air near the indoor heat exchanger 50.

[0068] Subsequently, under the action of the throttling device 40, the pressure of the liquid refrigerant flowing through the throttling device 40 and into the outdoor heat exchanger 30 is reduced, so that the liquid refrigerant can absorb heat and vaporize at the outdoor heat exchanger 30, thereby exchanging and transferring heat between the outdoor heat exchanger 30 and the indoor heat exchanger 50 and cooling the air around the outdoor heat exchanger 30. The vaporized refrigerant can flow through the third port C and the first port A of the four-way valve 20 in turn, and then the gaseous refrigerant can be sucked into the compressor 10 through the gas inlet end and compressed, thereby realizing the circulation of the refrigerant.

[0069] In order to avoid that the gaseous refrigerant sucked into the compressor 10 through the gas inlet end of the compressor 10 is mixed with liquid refrigerant or impurities, as shown in Figure 2 The air conditioner 100 can further include a gas-liquid separator 61, which can be installed between the first port A of the four-way valve 20 and the gas inlet end of the compressor 10, so that the first port A can be connected and conductive with the gas inlet end of the compressor 10 through the gas-liquid separator 61. Thus, when the gaseous refrigerant mixed with liquid refrigerant or impurities such as lubricating oil flows to the gas inlet end of the compressor 10 through the gas-liquid separator 61, the gas-liquid separator 61 can separate the non-gaseous impurities (such as liquid refrigerant, liquid lubricating oil or other impurities) to avoid the above impurities entering the compressor 10 and affecting the stable operation of the compressor 10.

[0070] Continuing to refer to Figure 2 The air conditioner 100 can further include an oil separator 62, and the outlet end of the compressor 10 and the second port B of the four-way valve 20 can also be connected and conductive through the oil separator 62. Thus, the lubricating oil mixed in the high-temperature and high-pressure gaseous refrigerant can be separated during the flow through the oil separator 62, thereby avoiding the lubricating oil adhering to the inner walls of the outdoor heat exchanger 30 and the indoor heat exchanger 50 when the refrigerant flows through them, so that the indoor heat exchanger 50 and the outdoor heat exchanger 30 have higher heat exchange efficiency.

[0071] In other embodiments, the four-way valve can also not be provided.

[0072] AsFigure 3 As shown, the outlet end of the compressor 10 can be communicated with one end of the throttling device 40 through the outdoor heat exchanger 30, and the return end of the compressor 10 can be communicated with the other end of the throttling device 40 through the indoor heat exchanger 50 and the gas-liquid separator 61 in sequence. In this way, the refrigerant can circulate between the compressor 10, the outdoor heat exchanger 30, the throttling device 40, the indoor heat exchanger 50, the gas-liquid separator 61 and the compressor 10. At this time, the outdoor heat exchanger 30 can be used to heat the surrounding air, and the indoor heat exchanger 50 can be used to cool the surrounding air, so that the air conditioner 100 operates in a cooling mode or a dehumidifying mode (i.e. a single cold mode air conditioner).

[0073] Based on this, Figure 4 As shown, the indoor unit of the duct type structure can include a shell 70, a fan assembly 80 and an indoor heat exchanger 50. The shell 70 can have a mounting cavity 71, and the fan assembly 80 and the indoor heat exchanger 50 can be arranged in the mounting cavity 71. For example, the fan assembly 80 and the indoor heat exchanger 50 in the mounting cavity 71 are distributed in the front-rear direction (i.e. the first linear direction), the shell 70 can be provided with an air outlet 72 on the front side of the mounting cavity 71, and the shell 70 can be provided with an air return port 73 on the rear side of the mounting cavity 71. In this way, the fan assembly 80 can drive air to enter the mounting cavity 71 from the air return port 73 and flow through the indoor heat exchanger 50.

[0074] Based on this, in the mounting cavity 71, the indoor heat exchanger 50 can be arranged close to the air outlet 72 on the front side, and the fan assembly 80 can be arranged close to the air return port 73 on the rear side. In this way, when the air conditioner operates, the fan assembly 80 can rotate to drive air to enter the mounting cavity 71 from the air return port 73 and can be blown to the indoor heat exchanger 50 from the outlet end of the fan assembly 80. In this way, the refrigerant flowing in the indoor heat exchanger 50 can quickly exchange heat with the air flowing through it.

[0075] As shown in Figure 4 and Figure 5 The length direction of the indoor heat exchanger 50 and the shell 70 can be the left-right direction, the indoor heat exchanger 50 can include a plurality of refrigerant pipes 51 and a plurality of fins 52, the refrigerant pipes 51 can extend in the left-right direction, and the fins 52 can be an integral sheet structure. The plurality of fins 52 can be distributed in the left-right direction (i.e. the length direction of the indoor heat exchanger 50), and the refrigerant pipes 51 can pass through each fin 52 in the left-right direction and be connected with the plurality of fins 52 to form an integral indoor heat exchanger 50.

[0076] In combination with Figure 4A plurality of insertion holes 53 can be formed on one fin 52, and the plurality of insertion holes 53 on the plurality of fins 52 are arranged in alignment in the left-right direction, so that the refrigerant pipes 51 which pass through the fins 52 through the insertion holes 53 can be in contact with the fins 52, and the plurality of refrigerant pipes 51 can also be distributed in the plane of the fins 52. In this way, the plurality of refrigerant pipes 51 can be connected to form one or more refrigerant passages, so that the flowing refrigerant can fully contact with the air through the refrigerant pipes 51 and the fins 52, thereby improving the heat exchange efficiency of the indoor heat exchanger 50.

[0077] Taking the fin 52 as a rectangular sheet structure, the plurality of fins 52 and the plurality of refrigerant pipes 51 can be connected to form a flat plate type heat exchanger as shown in Figure 5 Figure 4 As shown in the installation cavity 71, due to the limited height dimension of the installation cavity 71 in the up-down direction (i.e. the second straight direction), the upper edge of the indoor heat exchanger 50 of the flat plate type structure can be arranged to be inclined backward, so as to improve the heat exchange area of the indoor heat exchanger 50, such as the length dimension of the fin 52, in the limited height space.

[0078] In other embodiments, as shown in Figure 6 , a plurality of flat plate type heat exchangers can also be arranged in splicing, such as two heat exchangers can be installed in splicing in the up-down direction, and the lower edge of the upper heat exchanger can be connected with the upper edge of the lower heat exchanger to form a spliced indoor heat exchanger 50. Taking the indoor heat exchanger 50 formed by splicing two flat plate type heat exchangers as an example, in the up-down direction, the upper end of the indoor heat exchanger 50 can be arranged to be inclined backward or bent, and the lower end of the indoor heat exchanger 50 can also be arranged to be inclined backward or bent, so that the indoor heat exchanger 50 can form an opening facing the fan assembly 80.

[0079] In this way, in the plane perpendicular to the left-right direction, the cross section of the indoor heat exchanger 50 can be approximately V-shaped structure, such as the opening of the indoor heat exchanger 50 can be arranged to face backward to the fan assembly 80. That is, the upper end and the lower end of the indoor heat exchanger 50 can be arranged to be inclined backward in the installation cavity 71, so as to improve the contact area of the indoor heat exchanger 50 (especially the fin 52) with the air in the installation cavity 71.

[0080] In the above embodiments, if the height space of the installation cavity 71 is sufficient, or the width dimension of the flat plate type heat exchanger is small, one or more flat plate type heat exchangers can also be connected between the two flat plate type heat exchangers arranged in inclination in the up-down direction. In this way, the indoor heat exchanger 50 can be in the shape of C or W or other splicing structures in the cross section perpendicular to the left-right direction, which is not limited.

[0081] In addition, in combination with Figure 7 ​The indoor heat exchanger 50 can also be of an integrated structure and have a rear opening structure. The fins 52 can be provided in the form of an integrated sheet structure, and the fins 52 can include a first connecting sheet 521 and a second connecting sheet 522, and the first connecting sheet 521 can be connected to the second connecting sheet 522.

[0082] The fins 52 can be in the form of a sheet structure arranged perpendicular to the left-right direction, i.e., the included angle between the windward side (i.e., the rear side) edge of the first connecting sheet 521 and the windward side edge of the second connecting sheet 522 is an opening included angle. In this way, the plurality of fins 52 can be spaced apart in the left-right direction, and the plurality of refrigerant tubes 51 can be sequentially penetrated through the plurality of insertion holes 53 in the left-right direction for contacting and connecting the plurality of fins 52, thereby forming the indoor heat exchanger 50 of an integrated structure.

[0083] During installation of the indoor heat exchanger 50, the refrigerant tubes 51 only need to be sequentially penetrated through the plurality of fins 52, and the refrigerant tubes 51 and the plurality of fins 52 can be connected by a brazing process to satisfy the contact heat exchange therebetween. No additional splicing operation is required, and the structure is simple.

[0084] Alternatively, the insertion holes 53 can be provided as corresponding insertion slots, and in this case, the refrigerant tubes 51 can be in the form of a round tube structure or a flat tube structure, which is not limited.

[0085] It should be noted that, in the embodiment shown in Figure 7 , the first connecting sheet 521 and the second connecting sheet 522 are connected by bending, which can make the opening of the indoor heat exchanger 50 approximately in the form of a V-shaped structure in a plane perpendicular to the left-right direction (as shown in Figure 5 ).

[0086] In addition, the first connecting sheet 521 and the second connecting sheet 522 can be connected by a chamfered structure or a rounded structure. This is advantageous in making the included angle between the chamfered or rounded structure of the windward side edge of the indoor heat exchanger 50 and most of the air flowing therethrough be 60°-90°, so that the air can flow smoothly from rear to front into the gap between the adjacent two fins 52, thereby making the indoor heat exchanger 50 take into account the ventilation volume and the heat exchange effect, to improve the overall heat exchange effect of the indoor unit.

[0087] In the installation cavity 71, due to the limited height dimension of the duct type indoor unit, as shown in Figure 7 , the height dimension H of the installation cavity 71 in the up-down direction can be 185-195 mm, i.e., 185 mm≤H≤195 mm. That is, the height dimension H of the indoor heat exchanger 50 in the up-down direction can be a maximum, such as the height dimension of the installation cavity 71 can be 185 mm, 187 mm, 190 mm, 192 mm, or 195 mm, which is not limited.

[0088] In some other embodiments, as shown in Figure 8 The fin 52 can further include a third connecting piece 523, which can be an arc-shaped or circular-arc-shaped piece structure, such as an arc-shaped third connecting piece 523, the center of which can be located at the back side thereof. Correspondingly, the first connecting piece 521 can be connected with the second connecting piece 522 through the third connecting piece 523, so that the first connecting piece 521 and the second connecting piece 522 are located at the back side of the third connecting piece 523, and the included angle between the windward side edge of the first connecting piece 521 and the windward side edge of the second connecting piece 522 is the opening of the indoor heat exchanger 50 arranged towards the back.

[0089] In the above embodiments, the first connecting piece 521 and the second connecting piece 522 can be approximately rectangular structures or rhombic structures, i.e. parallelogram piece structures. Alternatively, the first connecting piece 521 and the second connecting piece 522 can also be arranged as arc-shaped piece structures, which are not limited herein.

[0090] In some other embodiments, the fin 52 can also include a first connecting piece 521, a fourth connecting piece, a fifth connecting piece and a second connecting piece 522 connected in sequence, so as to form a piece-shaped fin 52 approximately in the shape of a W letter. Alternatively, the fourth connecting piece and the fifth connecting piece can also be connected through a third connecting piece in a rectangular structure, so as to have a gap between the two openings of the W letter in the up-down direction, which is beneficial to improve the heat exchange area and heat exchange efficiency of the indoor heat exchanger.

[0091] In the case where the fin 52 includes the fourth connecting piece and the fifth connecting piece, the windward side edge line and / or the leeward side edge line between the adjacent two connecting pieces can be connected through a round corner or a chamfer.

[0092] As shown in Figure 8 The fan assembly 80 located in the mounting cavity 71 is a centrifugal fan structure, which includes a volute 81 and a centrifugal impeller 82 installed in the volute 81. Referring to Figure 8 and Figure 9 The volute 81 has an air outlet 84 and an air inlet 85. The air outlet 84 can be located at the position of the volute 81 close to the volute tongue 83, and the air outlet 84 can be arranged towards the indoor heat exchanger 50 in the front direction, and the air outlet 84 can be arranged close to the upper side of the mounting cavity 71 in the up-down direction.

[0093] Thus, in the installation cavity, the axial direction of the centrifugal impeller 82 can be parallel to the left-right direction, i.e., the centrifugal impeller 82 can rotate around an axis parallel to the left-right direction, for driving air to flow through the return air port 73 and the air inlet 85 in sequence and can be blown to the indoor heat exchanger 50 by the air outlet 84. Among them, the axial direction of the centrifugal impeller 82 can also be regarded as the axial direction of the fan assembly 80, i.e., the first straight direction, the second straight direction and the axial direction of the centrifugal impeller 82 can be perpendicular to each other. Since the centrifugal fan has the characteristics of small volume, low noise and large air pressure, it is beneficial to improve the air flow in the ducted air conditioner with limited height space.

[0094] In the installation cavity 71, a volute 81 and a corresponding centrifugal impeller 82 can be installed. A plurality of volutes 81 can also be arranged in the left-right direction, and the number of centrifugal impellers 82 can correspond to the number of volutes 81 one by one, i.e., one centrifugal impeller 82 can be installed in one volute 81.

[0095] The number of centrifugal impellers 82 and volutes 81 can be two, three, four or more, which can be flexibly set according to the width dimension of the volute 81 in the left-right direction and the length dimension of the indoor heat exchanger 50 in the left-right direction. In this way, by arranging a plurality of centrifugal fans in the left-right direction and blowing air forward, it is beneficial to improve the uniformity of the air received by the indoor heat exchanger 50 in the left-right direction.

[0096] It should be noted that in the installation cavity 71, the amount of air flowing through the indoor heat exchanger 50 has a greater impact on the heat exchange efficiency of the indoor unit of the ducted air conditioner structure. Therefore, by adjusting the structural size of the fan assembly 80, the installation position of the fan assembly 80 and the structural size of the return air port 73, etc., the air flow in the installation cavity 71, i.e., the amount of air flowing through the indoor heat exchanger 50, can be improved.

[0097] In some embodiments, as shown in Figure 10 , Figure 10 , Figure 9 A sectional view of the volute 81 and the centrifugal impeller 82 shown in the above embodiment. In the left-right direction, the width dimension of the volute 81 is defined as w1, and the width dimension of the centrifugal impeller 82 is defined as w2. The ratio k1 of the width dimension of the volute 81 to the width dimension of the centrifugal impeller 82 can be set as k1 = w1 / w2, and the value range of the ratio k1 can be set as 1.18-1.32.

[0098] If the ratio k1 is greater, such as greater than 1.32, the distance between the left and right ends of the centrifugal impeller 82 and the left and right side walls of the volute 81 is greater, which significantly increases the air leakage between the centrifugal impeller 82 and the volute 81. If the ratio k1 is smaller, such as less than 1.18, the distance between the left and right ends of the centrifugal impeller 82 and the left and right side walls of the volute 81 is smaller, that is, the left and right ends of the rotating centrifugal impeller 82 will contact the volute 81 and generate noise, and the too small distance is not convenient for the installation of the centrifugal impeller 82 and reduces the rotating speed of the centrifugal impeller 82.

[0099] Therefore, when the ratio k1 is in the range of 1.18-1.32, that is, 1.18≤k1≤1.32, the appropriate installation distance between the left and right ends of the centrifugal impeller 82 and the volute 81 can be maintained. The centrifugal impeller 82 in the volute 81 can rotate smoothly and quickly to drive the air to be quickly blown out of the air outlet 84, which is beneficial to reduce the air leakage between the left and right ends of the centrifugal impeller 82 and the volute 81, thereby improving the air output of the fan assembly 80 and reducing the air outlet noise.

[0100] According to the simulation test comparison, when the ratio of the width size of the volute 81 to the width size of the centrifugal impeller 82 is 1.24, the centrifugal fan can have better static pressure resistance (avoid air leakage) and lower noise. That is, the volute 81 and the centrifugal impeller 82 at this time can improve the air output by 2% and reduce the damper noise by 0.4 dB(A), and the air lifting and noise reduction effect is significant.

[0101] Based on this, the ratio k1 can also be set in the range of 1.18≤k1<1.24 or 1.24≤k1≤1.32, so that Figure 10 The distance size ΔX between the left and right ends of the centrifugal impeller 82 and the volute 81 in the range of 1.18-1.32 is greater than or equal to 3 mm, so as to improve the air output of the centrifugal fan and reduce the noise. For example, the ratio k1 can be set to 1.18, 1.20, 1.22, 1.24, 1.26, 1.28, 1.30 and 1.32, and the ratio k1 can also be flexibly set in the range of 1.18-1.32.

[0102] For example, the width size w2 of the centrifugal impeller 82 can be set to 115-126 mm, and the width size of the centrifugal impeller 82 and the number of centrifugal fans can be adjusted according to the length size of the indoor heat exchanger 50 in the left and right directions, so that the air blown out of the air outlet 84 can flow through the indoor heat exchanger more uniformly. It should be noted that when the fan assembly 80 includes a plurality of volutes 81 and a plurality of centrifugal impellers 82, the plurality of volutes 81 can have opposite shapes and sizes, and the plurality of centrifugal impellers 82 have the same shape and size, that is, the same specification of volute 81 and centrifugal impeller 82.

[0103] In some embodiments, as shown in FIG. 1, the volute 81 can be provided with two air inlets 85 at the left and right ends thereof, and the centrifugal fan assembly 80 can further include a flow collecting ring 86. Figure 10 Figure 11 The diameter of the air inlet 85 can be defined as d. The two air inlets 85 can be directly formed at the left and right sides of the volute 81.

[0104] Alternatively, as shown in FIG. 2, the centrifugal fan assembly 80 can further include a flow collecting ring 86, and the outer edge of the flow collecting ring 86 can be connected to the edge of the air inlet 85 of the volute 81, and the inner diameter of the flow collecting ring 86 is equal to the diameter d of the air inlet 85. Figure 11 Due to the installation gap between the left and right ends of the centrifugal impeller 82 and the volute 81, the air flow leaked from the gap between the left and right ends of the centrifugal impeller 82 and the volute 81 can form a vortex between the centrifugal impeller 82 and the flow collecting ring 86, thereby preventing the continuous leakage of air flow and improving the air supply efficiency and air supply volume of the centrifugal fan.

[0105] Figure 12 On this basis, as shown in FIG. 3, the outer diameter of the centrifugal impeller 82 can be defined as D1, and the inner diameter of the centrifugal impeller 82 can be defined as D2. When arranging the air inlet 85 and the centrifugal impeller 82, the ratio K2 of the air inlet diameter of the air inlet 85 to the blade profile length of the centrifugal impeller 82 can be K2 = (D1-d) / (D1-D2), and the ratio K2 can be 0.84-0.96.

[0106] It should be noted that in the above embodiments, the diameter (i.e. the inner diameter) of the air inlet 85 is greater than the inner diameter of the centrifugal impeller 82 and less than the outer diameter of the centrifugal impeller 82, i.e. the edge of the air inlet 85 is formed between the outer edge and the inner edge of the centrifugal impeller 82.

[0107] Through simulation experiments, it can be known that when the ratio K2 is 0.84 or 0.96, the air supply volume of the centrifugal fan can be increased by 2%, and the noise of the centrifugal fan can be reduced by 0.3 dB(A). When the ratio K2 is 0.89, the air supply volume of the centrifugal fan can be increased by 4.6, and the noise of the centrifugal fan can be reduced by 0.6 dB(A).

[0108] When the ratio K2 increases from 0.84 to 0.89, if the inner diameter and the outer diameter of the centrifugal impeller 82 remain unchanged, it means that the diameter of the air inlet 85 gradually decreases, and the air supply volume of the centrifugal fan gradually increases and the noise gradually decreases. When the ratio K2 increases from 0.89 to 0.96, if the inner diameter and the outer diameter of the centrifugal impeller 82 remain unchanged, it means that the diameter of the air inlet 85 gradually decreases, and the air supply volume of the centrifugal fan gradually decreases and the noise gradually increases.

[0109] ​​Based on this, the value range of the ratio K2 can also be set as 0.84≤K2<0.89 or 0.89≤K2≤0.96. Alternatively, the ratio K2 can also be adjusted between 0.84, 0.86, 0.88, 0.89, 0.90, 0.92, 0.94 or 0.96 and the like parameters, so that the centrifugal fan has a larger air volume and has smaller noise.

[0110] Wherein, since the plurality of blades of the centrifugal impeller 82 are spaced apart around the axis thereof, and the length direction of the blades is arranged parallel to the axis. Based on this, the outer diameter size of the centrifugal impeller 82 is the diameter size of the largest concentric circle of the plurality of blades, and the inner diameter size of the centrifugal impeller 82 is the diameter size of the smallest concentric circle of the plurality of blades, and does not include the size of the annular ring fixedly connected to the plurality of blades.

[0111] In some embodiments, the diameter size d of the air inlet 85 can be set as 112.5mm~117.5mm. Based on this, taking the width size w1 of the volute 81 as 150mm~154mm, through ①d=114.5 and w1=154mm, ②d=112.5 and w1=154mm, ③d=117.5 and w1=154mm, ④d=112.5 and w1=150mm four groups of schemes, the air volume and noise and other parameters of the centrifugal fan of the four groups of schemes are tested under the same static pressure or the same rotation.

[0112] Table I

[0113] Scheme Inlet diameter Volute width Static pressure Flow rate ① 114.5 mm 154 mm 30 Pa 547 m3 / h ② 112.5 mm 154 mm 30 Pa 570 m3 / h ③ 117.5 mm 154 mm 30 Pa 555 m3 / h ④ 114.5 mm 150 mm 30 Pa 558 m3 / h

[0114] Table II

[0115]

[0116]

[0117] And, combined with the air volume data of the above four groups of centrifugal fans with different sizes at different speeds, the air volume-speed relationship curve of the four groups of centrifugal fans can be obtained as shown in Figure 13 The diameter size d of the air inlet 85 can be set as 112.5mm≤d<114.5mm or 114.5mm≤d≤117.5mm.

[0118] Keeping the width dimension of the volute 81 unchanged (e.g. 154mm), from the scheme 1 and 2 in Table 1, it can be seen that when the diameter dimension of the air inlet 85 changes from 114.5mm to 112.5mm, the air volume of the ducted fan is increased under different external static pressures, especially when the diameter dimension of the air inlet 85 is 112.5mm and the external static pressure is 30pa, the air volume can be increased by about 4.2%.

[0119] Keeping the width dimension of the volute 81 unchanged (e.g. 154mm), from the scheme 1 and 2 in Table 1, it can be seen that when the diameter dimension of the air inlet 85 changes from 114.5mm to 112.5mm, the air volume of the ducted fan is increased under different external static pressures, especially when the diameter dimension of the air inlet 85 is 112.5mm and the external static pressure is 30pa, the air volume can be increased by about 4.2%.

[0120] Keeping the width dimension of the volute 81 unchanged (e.g. 154mm), from the scheme 1 and 2 in Table 1, it can be seen that when the diameter dimension of the air inlet 85 changes from 114.5mm to 112.5mm, the air volume of the ducted fan is increased under different external static pressures, especially when the diameter dimension of the air inlet 85 is 112.5mm and the external static pressure is 30pa, the air volume can be increased by about 4.2%.

[0121] From Table 2, it can be seen that when the width dimension of the volute 81 is unchanged, the noise level is similar when the diameter of the air inlet 85 is 114.5mm and 117.5mm, and when the diameter dimension of the air inlet 85 decreases from 114.5mm to 112.5mm, the noise level of the centrifugal fan can be reduced by 0.6dB(A).

[0122] In combination Figure 13 Under the condition that the centrifugal impeller 82 has the same rotating speed, the air volume of the scheme 2, the scheme 4, the scheme 3 and the scheme 1 is decreasing, and the air volume of the scheme 4 and the scheme 3 has little difference under the same rotating speed.

[0123] In summary, the width dimension of the volute 81 can be set to 150mm, 152mm or 154mm, wherein the width dimension of the volute 81 is 150mm, which has obvious effect of reducing noise at medium speed, and the width dimension of the volute is 154mm, which has obvious effect of reducing noise at low speed, which can be flexibly set according to needs.

[0124] In some embodiments, such as Figure 14The air conditioner 100 can further include an electrical box 90, which can be arranged close to or attached to the left or right side wall of the installation cavity 71 along the left-right direction. The electrical box 90 is used to install control elements such as circuit boards, so that the electrical box 90 can be electrically connected to the fan assembly 80 through the control elements to control the rotation of the fan assembly 80.

[0125] As shown in the examples, Figure 9 and Figure 14 The fan assembly 80 can further include a motor 87, which can be installed between the two adjacent volutes 81 along the left-right direction, and the output shafts at the left and right ends of the motor 87 can be inserted into the volutes 81 on both sides along the left-right direction and connected to the centrifugal impellers 82. In this way, the control elements in the electrical box 90 can be electrically connected to the motor 87 to control the rotational speed of the centrifugal impellers 82 through the motor 87, i.e., to adjust the air volume of the ducted air conditioner.

[0126] In the above embodiments, the number of volutes 81 and centrifugal impellers 82 can be two, and the motor 87 can be located between the two volutes 81 along the left-right direction. Alternatively, the number of volutes 81 and centrifugal impellers 82 can also be three or more, i.e., the motor 87 can be located between two volutes 81 along the left-right direction, and the output shafts at the left and right ends of the motor 87 can be inserted into all the volutes 81 along the left-right direction and can drive the corresponding centrifugal impellers 82 to rotate, which is beneficial to reduce the number of motors 87.

[0127] In addition, the fan assembly 80 can also be configured with multiple motors 87, such as the number of motors 87, volutes 81 and centrifugal impellers 82 can be the same, i.e., one volute 81 can be installed with one motor 87 and one centrifugal impeller 82. Alternatively, if the number of volutes 81 and centrifugal impellers 82 is three or more, the left and right ends of the first motor 87 can drive two centrifugal impellers to rotate, and the second motor 87 can be installed in the third volute 81 and drive the corresponding centrifugal impeller 82 to rotate, which is convenient for adjusting the rotational speed of part of the centrifugal impellers 82 through the control elements in the electrical box 90.

[0128] As shown in the examples, Figure 14 The width dimension w of the installation cavity 71 in the left-right direction can be 600mm-800mm, and the width dimension of the installation cavity 71 is the width dimension of the shell 70, which can be flexibly adjusted according to the length dimension of the indoor heat exchanger 50. As an example, since the air conditioner 100 has different specifications such as 1 ton, 1.5 tons, 2 tons or 3 tons, the length of the indoor heat exchanger 50 in different specifications of the ducted air conditioner 100 is not completely the same, i.e., the length dimension of the indoor heat exchanger 50 and the width dimension of the shell 70 can be adjusted according to different specifications of the air conditioner 100.

[0129] For example, the width w of the mounting cavity 71 can also be set to: 600mm≤w<700mm or 700mm≤w≤800mm, such as 600mm, 650mm, 700mm, 750mm or 800mm.

[0130] If the width of the mounting cavity 71 is greater than 800mm, it will result in a large gap between two adjacent centrifugal fans in the left-right direction, leading to a smaller airflow to the windward area of ​​the indoor heat exchanger 50 in front of this gap. Conversely, if the width of the mounting cavity 71 is less than 600mm, it will result in a smaller gap between two adjacent centrifugal fans in the left-right direction, causing the airflow from the two centrifugal fans to form vortices or turbulence in the gap area, thus affecting and reducing the airflow of the ducted air conditioner.

[0131] Thus, when the width of the mounting cavity 71 is 600mm-700mm or 700mm-800mm, the airflow to the windward side of the indoor heat exchanger 50 can be more evenly distributed in the left-right direction, which is beneficial to improving the heat exchange efficiency of the indoor heat exchanger 50. At the same time, it can also avoid the influence of turbulence and other eddies formed between the centrifugal fan and the indoor heat exchanger 50 and reduce the air volume of the ducted air conditioner.

[0132] In some embodiments, such as Figure 8 As shown, within the mounting cavity 71, the installation distance L between the indoor heat exchanger 50 and the fan assembly 80 in the front-to-back direction can be 136mm to 166mm. While keeping the fan assembly 80 speed and other dimensions of the indoor heat exchanger 50 constant, simulation experiments show that as the installation distance between the indoor heat exchanger 50 and the fan assembly 80 increases from 136mm to 166mm, the airflow through the indoor heat exchanger 50 per unit time first increases and then decreases.

[0133] If the indoor heat exchanger 50 is a flat plate heat exchanger, then the distance between the centerline of the windward side of the inclined indoor heat exchanger 50 in the front-to-back direction and the distance between the exhaust port 84 in the front-to-back direction is the installation distance L between the indoor heat exchanger 50 and the fan assembly 80. If the indoor heat exchanger 50 has a structure that is bent backward at both ends or is inclined, then the maximum distance between the windward side of the indoor heat exchanger 50 and the exhaust port 84 in the front-to-back direction is the installation distance L between the indoor heat exchanger 50 and the fan assembly 80.

[0134] For example, the airflow through the indoor heat exchanger 50 with an installation spacing of 136 mm is approximately 580.5 m³ / s. 3 / h, the airflow through indoor heat exchanger 50 with an installation spacing of 146mm is approximately 584.1m³ / h. 3 / h, the air volume flowing through the indoor heat exchanger 50 with the installation spacing of 156mm is approximately 581m 3 / h, the air volume flowing through the indoor heat exchanger 50 with the installation spacing of 156mm is approximately 575m 3 / h. Based on this, the installation spacing L of the indoor heat exchanger 50 and the fan assembly 80 can also be set as: 136mm≤L<146mm, 146mm≤L<156mm or 156mm≤L≤166mm, in the above four installation spacing intervals, the air volume flowing through the indoor heat exchanger 50 can be linearly changed.

[0135] Based on this, for the installation spacing L of the indoor heat exchanger 50, it can also be set as 141mm≤L≤151mm, so that the air volume flowing through the indoor heat exchanger 50 is 582.5m 3 / h or more, and has a larger fitting error range when assembling the indoor heat exchanger 50 and the fan assembly 80 (convenient for assembling the indoor unit). And at this time, it is beneficial to make the angle between the fin at the windward side edge and the flowing direction of the air flow be 60°-90°, so that the indoor heat exchanger 50 can balance the ventilation volume and the heat exchange effect, so as to improve the overall heat exchange effect of the indoor unit.

[0136] In some embodiments, as Figure 12 shown, the fan assembly 80 can also include at least one of a first air guide part 88 and a second air guide part 89. Among them, the upper side wall of the part of the volute 81 close to the air outlet 84 (i.e. the side away from the volute tongue 83) is the first air guide part 88, and correspondingly, the lower side wall of the part of the volute 81 close to the air outlet 84 (i.e. the side close to the volute tongue 83) is the second air guide part 89. Based on this, in combination with Figure 8 and Figure 12 , the rear end of the first air guide part 88 can be bent and inclined downward, and the rear end of the second air guide part 89 can also be bent and inclined downward. So that the air blown forward by the air outlet 84 will not be concentrated in the upper area of the indoor heat exchanger 50 (i.e. the indoor heat exchanger 50 corresponding to the first connecting piece 521), so that the air can flow more to the middle area of the indoor heat exchanger (i.e. the indoor heat exchanger 50 corresponding to the third connecting piece 523) and the lower area (i.e. the indoor heat exchanger 50 corresponding to the second connecting piece 522), which is beneficial to improve the wind uniformity of the windward side of the indoor heat exchanger 50, thereby improving its heat exchange efficiency.

[0137] In other embodiments, the width dimension of the air return port 73 in the left-right direction can also be adjusted, as Figure 14As shown, on the rear side of the installation cavity 71, the electric appliance box 90 is arranged close to one side of the installation cavity 71 along the left-right direction. That is, the width dimension W of the installation cavity 71 can be greater than or equal to the sum of the width dimension W3 of the return air inlet 73 and the thickness dimension W4 of the electric appliance box 90, that is, W≥W3+W4, and on this basis, the ratio X1 of the thickness dimension of the electric appliance box 90 to the width dimension of the return air inlet 73 can be 0.1-0.18.

[0138] For example, when the width dimension of the installation cavity 71 is W=700 mm, if the ratio X1 is less than 0.1, the thickness dimension of the electric appliance box 90 is less than 63.6 mm, which can result in insufficient space in the electric appliance box 90 for installing the control elements or insufficient space for heat dissipation of the control elements. If the ratio X1 is greater than 0.18, the width dimension of the return air inlet 73 is less than 594 mm, which can result in too small width dimension of the return air inlet 73, that is, the fan assembly in the installation cavity 71 cannot extract sufficient air through the small return air inlet 73 and blow it to the indoor heat exchanger 50.

[0139] Therefore, by setting the ratio of the thickness dimension of the electric appliance box 90 to the width dimension of the return air inlet 73 to be between 0.1 and 0.18, the electric appliance box 90 can have sufficient space for accommodating the control elements and dissipating heat, and the return air inlet 73 can have sufficient width dimension, so that the fan assembly 80 in the ducted air conditioner can extract sufficient air around the return air inlet 73 to blow it to the indoor heat exchanger 50. Thus, the indoor heat exchanger 50 can be in contact with sufficient air for heat exchange, which is beneficial to improving the overall heat exchange efficiency of the ducted air conditioner.

[0140] For example, the ratio X1 can be selected from any value between 0.1 and 0.18, which is beneficial to improving the air supply amount of the fan assembly 80 to make the ducted air conditioner have higher heat exchange efficiency. For example, the ratio X1 can be 0.1, 0.12, 0.14, 0.16 or 0.18. For example, when the ratio of the thickness dimension of the electric appliance box 90 to the width dimension of the return air inlet 73 is 0.12, when the width dimension of the installation cavity 71 is 700 mm, the thickness dimension of the electric appliance box 90 and the width dimension of the return air inlet 73 can be 65 mm and 725 mm, that is, the sum of the thickness dimension of the electric appliance box 90 and the width dimension of the return air inlet 73 can be the width dimension of the installation cavity 71, and at this time, the air volume of the ducted air conditioner can be increased by 2.1%.

[0141] Based on this, the ratio X1 of the thickness of the housing 90 to the width of the return air vent 73 can be set to a range of 0.1 ≤ X1 < 0.12 or 0.12 ≤ X1 ≤ 0.18. As the ratio X1 increases from 0.1 to 0.12, the air volume of the fan assembly 80 inside the duct unit can gradually increase. As the ratio X1 decreases from 0.12 to 0.18, the air volume of the fan assembly 80 inside the duct unit can gradually decrease, but the change trend is relatively gentle.

[0142] Based on this, the thickness of the electrical box 90 can be set to 65mm to 85mm. This avoids the problem of a thinner electrical box 90 hindering the installation and heat dissipation of internal components, while also preventing a thicker electrical box 90 from affecting the increase in the width of the return air vent 73. This facilitates increasing the airflow of the fan assembly 80 through the design of the return air vent 73. Since a 75mm thickness of the electrical box 90 has a significant boost effect on the airflow of the fan assembly 80, the thickness w3 of the electrical box 90 can be set to a range of 65 ≤ w4 < 75 or 75 ≤ w4 ≤ 85.

[0143] For example, the thickness of the electrical box can also be flexibly selected between 65mm, 70mm, 75mm, 80mm and 85mm.

[0144] Within the mounting cavity 71, a partition can be provided between the fan assembly 80 and the indoor heat exchanger 50 along the front-to-back direction to divide the mounting cavity 71 into a fan cavity and a heat exchange cavity distributed front and back. The fan cavity is located in front of the heat exchange cavity, and the partition also has a notch connecting the fan cavity and the heat exchange cavity corresponding to the exhaust port 84. The indoor heat exchanger 50 can be installed in the heat exchange cavity, and the fan assembly 80 and the electrical box 90 can be located in the fan cavity, with the exhaust port 84 of the volute 81 facing forward toward the indoor heat exchanger 50 through the notch in the partition.

[0145] Therefore, within the fan cavity, the installation positions of the electrical box 90 and the multiple volutes 81 also affect the airflow of the fan assembly 80. For example... Figure 15 As shown, taking the electrical box 90 and the two volutes distributed from right to left as an example, the distance between the volute 81 closest to the electrical box 90 (the volute 81 on the right) and the electrical box 90 is the first distance dimension L1, and the distance between the other volute 81 (i.e. the volute 81 on the left) and the side wall of the mounting cavity 71 away from the electrical box 90 (i.e. the left side wall of the mounting cavity 71) is the second distance dimension L2.

[0146] Since the two air inlets 85 of the centrifugal fan are located on the left and right sides of the volute 81, that is, in the left and right direction, the size of the first distance between the volute 81 and the electrical box 90 or the size of the second distance between the side wall of the mounting cavity 71 will affect the air intake of the centrifugal fan.

[0147] Based on this, combined Figure 10 and Figure 15 The ratio X2 of the first spacing dimension L1 to the width dimension w1 of the centrifugal impeller 82 can be set to 0.4 to 0.66. The ratio of the second spacing dimension L2 to the width dimension w1 of the centrifugal impeller 82 can also be set to 0.4 to 0.66.

[0148] Inside the volute 81, the centrifugal fan primarily draws air into the volute 81 through the rotation of the centrifugal impeller 82, and then, driven by the centrifugal impeller 82, the air is quickly blown towards the indoor heat exchanger 50 through the exhaust port 84. During this process, the larger the axial width and radial dimensions of the centrifugal impeller 82, the stronger the air delivery capacity of the centrifugal fan. Correspondingly, the size of the return air port 73 and the axial spacing of the volute 81 need to be increased to enhance the centrifugal fan's air intake (or suction) capacity.

[0149] For example, the ratio of the first spacing dimension to the width dimension of the centrifugal impeller 82 can be 0.4, 0.45, 0.5, 0.55, 0.6, 0.65, or 0.66, etc., and this application does not limit it in this way. Taking the width dimension of the centrifugal impeller as 120.5 mm and X2 = 0.6 as an example, the first spacing dimension can be set to 72.3 mm, at which time the air volume of the right-side centrifugal fan can be increased by 3.2%.

[0150] It should be noted that since a ratio X2 ranging from 0.4 to 0.66 is beneficial for increasing the airflow of the fan assembly 80, and the centrifugal fan has a larger airflow when X2 = 0.6, the ratio X2 between the first spacing dimension and the width dimension of the centrifugal impeller 82 can also be set to a range of 0.4 ≤ X2 < 0.6, or a range of 0.6 ≤ X2 ≤ 0.66, both of which are beneficial for increasing the airflow of the centrifugal fan.

[0151] Combination Figure 14 Taking the electrical box 90 located on the right side of the mounting cavity 71 as an example, between the right side volute and the electrical box 90 ( Figure 16 Within the elliptical area shown, the original air inlet 85 (as shown) Figure 11 The area near the low-speed zone (as shown) has many sections, which will form vortices, reducing the airflow and increasing aerodynamic noise. By setting the ratio X2 of the first spacing dimension to the width dimension of the centrifugal impeller 82 to a range of 0.4 ≤ X2 < 0.6 or 0.6 ≤ X2 ≤ 0.66, combined with... Figure 17 Between the volute and the electrical box 90 on the right side (i.e., within the elliptical area in the figure), the low-speed wind zone is less and more evenly distributed, which helps to increase the air intake volume of the air inlet 85 and reduce aerodynamic noise.

[0152] Taking the fan assembly 80, which includes two volutes 81 and two centrifugal impellers 82, as an example, the two volutes 81 can have the same shape and size, and the two centrifugal impellers 82 can also have the same shape and size, which facilitates the standardized production and installation of the air conditioner 100 components. Based on this, the second distance between the left volute 81 and the left side wall of the mounting cavity 71 can also be set to 72.3mm, so that the two volutes 81 have approximately the same air intake and air outlet volume.

[0153] The two adjacent volutes 81 are arranged at intervals in the left-right direction and are used to install and fix the motor 87 so that the air inlet 85 of the two volutes 81 near the motor 87 can smoothly draw air.

[0154] In some embodiments, the ratio X3 of the first spacing dimension to the second spacing dimension can be set to 0.93 to 1.6 within the mounting cavity 71. Thus, by adjusting the installation of the two volutes 81 in the left-right direction, it is also beneficial to increase the airflow of the fan assembly 80, i.e., the airflow at the indoor heat exchanger 50.

[0155] For example, taking a centrifugal impeller 82 with an axial width w2 of 120.5 mm and a second spacing dimension L2 of 61.2 mm as an example, as shown in Table 3 below, simulation tests can be conducted on ducted air conditioners with four schemes where X3 is 0.93, 12.6, 1.43, and 1.6 respectively, and the airflow of the ducted air conditioners can be statistically analyzed. The values ​​of X2 can be further refined between schemes 1 to 4, and the airflow in the ducted air conditioners of the corresponding schemes can be statistically analyzed. Based on this, data such as... Figure 15 The graph shows the installation position of the volute and the airflow rate through the indoor heat exchanger.

[0156] Table 3

[0157] Scheme Ratio X3 L1 (mm) L2 (mm) Flow (m 3 / h) 1 0.93 56.9 61.2 719.2 2 1.26 77.1 61.2 721.7 3 1.43 87.5 61.2 716.3 4 1.6 97.9 61.2 713.5

[0158] Combining Table 3 and Figure 18 It can be seen that when the ratio X3 increases within the range of 0.93 to 1.26, the airflow through the indoor heat exchanger increases, but the range of the first spacing dimension corresponding to this ratio range is 20.2 mm. When the ratio X3 increases within the range of 1.26 to 1.6, the airflow through the indoor heat exchanger decreases, and the range of the first spacing dimension corresponding to this ratio range is 20.8 mm. However, when X3 = 1.43, the change in the airflow of the indoor heat exchanger also conforms to the overall trend of 1.26 to 1.6.

[0159] Exemplarily, the ratio X3 can be set in the range of 0.9≤X3≤1.26, 1.26<X3≤1.43 and / or 1.43≤X3≤1.6. In the above four schemes, the air flow through the indoor heat exchanger 50 is increased as a whole, and therefore, the setting schemes of 0.9<X3≤1.26, 1.26<X3≤1.43 and / or 1.43≤X3≤1.6 are beneficial to increase the air flow at the indoor heat exchanger 50.

[0160] In combination Figure 18 It can be known that when the ratio X3 is less than 0.9, the air flow through the indoor heat exchanger can continue to increase, i.e. the air flow is greater than 719.2m 3 / h. However, at this time, the first spacing size L1 will be less than 55.08mm, i.e. the smaller ventilation space between the right side volute 81 (as shown) and the electrical box 90 will cause larger noise when the air is diverted at this place. Figure 15

[0161] In addition, when the ratio X3 is greater than 1.6, the air flow through the indoor heat exchanger 50 is less increased. Based on this, when 0.9≤X3≤1.6, the air flow through the indoor heat exchanger 50 can be increased, especially when 0.9≤X3≤1.26 and 1.26<X3≤1.43, the gain effect of the air flow through the indoor heat exchanger 50 is more significant.

[0162] It should be noted that since the span of the first spacing size in the ratio interval of 0.9≤X3≤1.26 is larger (20.2mm), the first spacing size can be set equal to the second spacing size, i.e. the ratio X3=1, so that the two centrifugal fans located on the same side of the electrical box 90 can be approximately symmetrically arranged. Correspondingly, the value range of the ratio X3 can also be set as 0.9≤X3≤0.1 and / or 0.1<X3≤1.26.

[0163] On this basis, the schemes 2-4 in Table 3 can be taken as a reference group, and by setting the comparison schemes 2a-4a in Table 4, the air flow at the indoor heat exchanger 50 in the reference group and the comparison group has been detected. Exemplarily, the first spacing size and the second spacing size of the comparison scheme 2a are 69.3mm, and the thickness size w3 of the electrical box 90 is 85mm, L1=L2=74.3mm and w3=75mm in the comparison scheme 3a, and L1=L2=79.3mm and w3=65mm in the comparison scheme 4a.

[0164] Table 4

[0165] Scheme w4 (mm) Ratio X3 L1 (mm) L2 (mm) Flow (m 3 / h) 2a 85 1 69.3 69.3 728.1 3a 75 1 74.3 74.3 731.4 4a 65 1 79.3 79.3 724.1

[0166] ​In the comparative scheme 2a, the sum of the first spacing size and the second spacing size is approximately equal to the sum of the first spacing size and the second spacing size in the reference scheme 2, and the error between the sum in the two schemes is calculated into the thickness size of the electric appliance box 90. In this way, the spacing size of the two volutes 81 in the left-right direction can be kept consistent, so that the air inlets on the left and right sides of the two volutes 81 in the comparative schemes 3a and 4a are also kept consistent, and so on.

[0167] For example, in the comparative schemes 2a-4a, the thickness size of the electric appliance box 90 can be 85 mm, 75 mm and 65 mm respectively, so that the spacing size of the adjacent two volutes 81 in the left-right direction is kept consistent. Correspondingly, in the reference schemes 1-4, the thickness size of the electric appliance box 90 can also be adjusted to make the adjacent two volutes 81 have the same spacing size in the left-right direction.

[0168] It can be known from Table 4 that in the comparative schemes 2a-4a, the air flow at the indoor heat exchanger 50 is 728.1 m 3 / h, 731.4 m 3 / h and 724.1 m 3 / h respectively. In combination with the data shown in Table 3, the comparative scheme 2a can improve the air flow by 0.8% compared with the reference scheme 2, the comparative scheme 3a can improve the air flow by 2.1% compared with the reference scheme 3, and the comparative scheme 4a can improve the air flow by 1.5% compared with the reference scheme 4, which has a significant effect.

[0169] On this basis, the value range of the ratio X3 of the first spacing size to the second spacing size can also be set as 0.9≤X3≤0.1 and / or 0.1

[0170] It should be noted that in the comparative schemes 2a-4a of Table 4, the sum of the width size of the return air inlet 73 and the thickness size of the electric appliance box 90 can be 700 mm. That is, in the comparative scheme 3a, the thickness size of the electric appliance box 90 is 75 mm, and the width size of the return air inlet 73 can be 625 mm, that is, the ratio X1=75 / 625=0.12, and the ratio X2 of the first spacing size to the axial width size of the centrifugal impeller 82 is 74.3 / 120.5=0.617.

[0171] Based on this, the air flow at the four air inlets 85 on the left and right sides of the two volutes 81 can be simulated and detected. For example, Figure 15As shown, the left air flow of the left one volute 81 can be 194.1m 3 / h, the right air flow of the left one volute 81 can be 196.1m 3 / h, the left air flow of the right one volute 81 can be 196.5m 3 / h, and the right air flow of the right one volute 81 can be 199.2m 3 / h.

[0172] The above air flow data is the air flow at the air inlet 85 of the corresponding side wall of the volute 81. As known from the above, the air flow at the four air inlets 85 of the two volutes 81 is quite even, and based on this, the air speed gradient in the cross section of the air outlet 84 of the volute 81 perpendicular to the front-rear direction can be evenly distributed (i.e. the uniformity of the air speed distribution is improved), so that the air blown by the volute 81 to the indoor heat exchanger 50 (as shown) has a good uniformity, which is beneficial to the indoor heat exchanger 50 to be in contact with the air and exchange heat in a more uniform manner. Figure 14

[0173] In the description of the present specification, specific features, structures, materials or characteristics can be combined in any one or more embodiments or examples in a suitable manner.

[0174] The above is only a specific implementation of the present application, but the protection scope of the present application is not limited thereto, and any person skilled in the art can easily think of changes or replacements within the technical range disclosed by the present application, which should be covered within the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.​

Claims

1. A ducted air conditioner comprising an indoor unit, characterized by, The indoor unit comprises: a housing having a mounting cavity and an air return port; an indoor heat exchanger; a fan assembly, the fan assembly being a centrifugal fan, the fan assembly and the indoor heat exchanger being located in the mounting cavity and being spaced apart along a first linear direction, the fan assembly being configured to drive air to enter the mounting cavity from the air return port and flow through the indoor heat exchanger; and an electrical box located in the mounting cavity and configured to control rotation of the fan assembly; the first linear direction being perpendicular to an axial direction of the fan assembly, along the axial direction of the fan assembly, the electrical box being arranged close to a side wall of the mounting cavity; along the axial direction of the fan assembly, a width dimension of the mounting cavity is greater than or equal to a sum of a width dimension of the air return port and a thickness dimension of the electrical box; a ratio X1 of the thickness dimension of the electrical box to the width dimension of the air return port is in a range of 0.1≤X1<0.12 or 0.12≤X1≤0.

18.

2. The ducted air conditioner according to claim 1, wherein The fan assembly comprises: a plurality of volutes having air discharge ports, the air discharge ports being arranged along a first linear direction towards the indoor heat exchanger; and a plurality of centrifugal impellers, one centrifugal impeller being installed in one volute, the electrical box being configured to control a rotational speed of the centrifugal impellers to drive air flow; the electrical box and the plurality of volutes being spaced apart along an axial direction of the centrifugal impellers.

3. The ducted air conditioner according to claim 2, wherein The number of the volutes and the number of the centrifugal impellers are two; along the axial direction of the centrifugal impellers, a spacing between one volute close to the electrical box and the electrical box is a first spacing dimension L1, and a spacing between another volute and a side wall of the mounting cavity away from the electrical box is a second spacing dimension L2; a ratio X3 of the first spacing dimension to the second spacing dimension is in a range of 0.9≤X3≤0.1 or 0.1 4. The ducted air conditioner according to claim 2, wherein The number of the volutes and the number of the centrifugal impellers are two; along the axial direction of the centrifugal impellers, a spacing between one volute close to the electrical box and the electrical box is a first spacing dimension L1, and a spacing between another volute and a side wall of the mounting cavity away from the electrical box is a second spacing dimension L2; a ratio X3 of the first spacing dimension to the second spacing dimension is in a range of 1.26 5. The ducted air conditioner according to claim 3, wherein The first spacing dimension is equal to the second spacing dimension.

6. The ducted air conditioner according to claim 5, wherein The first spacing dimension and the second spacing dimension are 69.3 mm, 74.3 mm or 79.3 mm.

7. The ducted air conditioner according to any one of claims 2 to 6, wherein along the axial direction of the centrifugal impellers, a spacing between one volute close to the electrical box and the electrical box is a first spacing dimension; a ratio X2 of the first spacing dimension to an axial width dimension of the centrifugal impeller is in a range of 0.4≤X2<0.6 or 0.6≤X2≤0.

66.

8. The ducted air conditioner according to claim 7, wherein The axial width dimension w2 of the centrifugal impeller is in a range of 115 mm≤w2<120.5 mm or 120.5 mm≤w2≤126.

9. The ducted air conditioner according to any one of claims 2 to 6, wherein the plurality of volutes have the same shape size, and the plurality of centrifugal impellers have the same shape size; and / or, The ratio K1 of the width dimension of the volute to the width dimension of the centrifugal impeller in the axial direction of the centrifugal impeller is in the range of 1.18≤K1<1.24 or 1.24≤K1≤1.

32.

10. The ducted air conditioner according to any one of claims 1 to 6, wherein The thickness dimension w3 of the electric appliance box is in the range of 65≤w3<75 or 75≤w3≤85; and / or, The width dimension w of the mounting cavity is in the range of 600≤w<700 or 700≤w≤800.

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