A ducted air conditioner

Abstract

The application discloses a ducted air conditioner, which aims to improve the air volume of a centrifugal fan in a ducted air conditioner. The ducted air conditioner comprises an indoor unit, a shell of the indoor unit has a mounting cavity, and an indoor heat exchanger and a fan assembly are located in the mounting cavity. The fan assembly comprises a volute and a centrifugal impeller, and the volute has an air outlet. The air outlet is arranged towards the indoor heat exchanger along a first linear direction, and the air outlet is arranged close to one side of the mounting cavity along a second linear direction. The centrifugal impeller is installed in the volute, and the centrifugal impeller is used to drive air to flow through the indoor heat exchanger. The first linear direction, the second linear direction and the axial direction of the centrifugal impeller are perpendicular to each other. Wherein, along the axial direction of the centrifugal impeller, the ratio K1 of the width dimension of the volute to the width dimension of the centrifugal impeller is in the range of 1.18≤K1<1.24 or 1.24≤K1≤1.32. 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 and easy cooperation with a house 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, in the volute of the centrifugal fan, along the axial direction of the fan assembly, the width of the volute of the centrifugal fan and the width of the impeller have a great influence on the air intake and air output of the centrifugal fan. SUMMARY

[0005] The purpose of the present application is to provide a ducted air conditioner, which aims to improve the air output of the centrifugal fan in the ducted unit.

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

[0007] The present application provides a ducted air conditioner, which comprises an indoor unit. The indoor unit comprises a casing, an indoor heat exchanger and a fan assembly. The casing has a mounting cavity, and the indoor heat exchanger and the fan assembly are located in the mounting cavity. The fan assembly comprises a volute and a centrifugal impeller, and the volute has an air outlet. The air outlet is arranged towards the indoor heat exchanger along a first straight line direction, and the air outlet is arranged close to one side of the mounting cavity along a second straight line direction. The centrifugal impeller is installed in the volute, and the centrifugal impeller is used to drive the air to flow through the indoor heat exchanger. The first straight line direction, the second straight line direction and the axial direction of the centrifugal impeller are perpendicular to each other. Among them, along the axial direction of the centrifugal impeller, the ratio K1 of the width of the volute to the width of the centrifugal impeller is in the range of 1.18≤K1<1.24 or 1.24≤K1≤1.32.

[0008] In the installation cavity of the indoor unit, the centrifugal impeller of the fan assembly can rotate around its axis in the volute for driving air to be blown from the air outlet to the indoor heat exchanger. Since the axial direction of the centrifugal impeller, i.e. the axial direction of the fan assembly, i.e. the first straight line direction, the second straight line direction and the axial direction of the centrifugal impeller can be arranged perpendicular to each other, the fan assembly of the centrifugal fan structure has the characteristics of small volume, low noise and large air pressure, which is beneficial to improve the air flow in the ducted air conditioner with limited height space.

[0009] Therefore, by adjusting the ratio k1 of the width dimension of the volute to the width dimension of the centrifugal impeller, the value range of k1 is 1.18≤k1<1.24 or 1.24≤K1≤1.32, so that the installation space between the both ends of the axial direction of the centrifugal impeller and the volute is kept appropriate. The centrifugal impeller in the volute can rotate smoothly and quickly to drive air to be quickly blown out of the air outlet, which is beneficial to reduce the air leakage between the both ends of the axial direction of the centrifugal impeller and the volute, thereby improving the air output of the fan assembly and reducing the air outlet noise, so as to improve the overall heat exchange efficiency of the indoor unit.

[0010] In some embodiments, the fan assembly further comprises a first air guide portion, and the part of the volute close to the air outlet away from one side of the volute tongue in the second straight line direction is the first air guide portion; and the end of the first air guide portion close to the indoor heat exchanger is arranged inclinedly towards the volute tongue in the second straight line direction.

[0011] In some embodiments, the outflow included angle α between the first air guide portion and the first straight line direction is in the range of 2°≤α<5°.

[0012] In some embodiments, the outflow included angle α between the first air guide portion and the first straight line direction is in the range of 5°<α≤8°.

[0013] In some embodiments, the outflow included angle between the first air guide portion and the first straight line direction is 2°, 5°, 7° or 8°.

[0014] In some embodiments, along the axial direction of the centrifugal impeller, the opposite sides of the volute are further provided with two air inlets.

[0015] In some embodiments, the diameter of the air inlet is d, the outer diameter of the centrifugal impeller is D1, the inner diameter of the centrifugal impeller is D2, and the ratio K2 of the air inlet diameter to the blade profile rotation length of the centrifugal impeller is K2=(D1-d) / (D1-D2).

[0016] In some embodiments, the ratio K2 of the air inlet diameter to the blade profile rotation length of the centrifugal impeller is in the range of 0.84≤K2<0.89.

[0017] In some embodiments, the ratio K2 of the inlet inner diameter of the air inlet to the blade profile rotation length of the centrifugal impeller is in the range of 0.89≤K2≤0.96.

[0018] In some embodiments, the diameter size d of the air inlet is in the range of 112.5mm≤d<114.5mm.

[0019] In some embodiments, the diameter size d of the air inlet is in the range of 114.5mm≤d≤117.5mm.

[0020] In some embodiments, the width size of the volute along the circumferential direction of the centrifugal impeller is 150mm~154mm.

[0021] In some embodiments, the ratio of the inlet inner diameter of the air inlet to the blade profile rotation length of the centrifugal impeller is 0.89.

[0022] In some embodiments, the ratio of the width size of the volute along the axial direction of the centrifugal impeller to the width size of the centrifugal impeller is 1.24.

[0023] In some embodiments, the diameter size of the air inlet is 112.5mm.

[0024] In some embodiments, the width size of the volute along the axial direction of the centrifugal impeller is 150mm or 154mm.

[0025] In some embodiments, the indoor heat exchanger is bent towards the fan assembly at the opposite ends in the second linear direction, so that the indoor heat exchanger has openings towards the fan assembly.

[0026] In some embodiments, the fan assembly further comprises a second air guide portion, the part of the volute close to the air outlet along the side of the volute tongue close to the second linear direction is the second air guide portion, and the end of the second air guide portion close to the indoor heat exchanger is inclined towards the volute tongue along the second linear direction.

[0027] In some embodiments, the air guide included angle between the second air guide portion and the first linear direction is 12.1°~19.6°.

[0028] In some embodiments, the indoor heat exchanger comprises a plurality of refrigerant pipes and a plurality of fins, and the fins are in an integrated sheet structure. The plurality of fins are distributed at intervals along the length direction of the indoor heat exchanger, and the refrigerant pipes vertically pass through the plurality of fins and are in contact with the plurality of fins along the length direction of the indoor heat exchanger.

[0029] In some embodiments, the fins are positioned along a first straight line, with their windward edge near the edge of the fan assembly. The fins include a first connecting piece, a second connecting piece, and a third connecting piece. The third connecting piece is an arc-shaped structure with its center near the fan assembly. The first connecting piece is connected to the second connecting piece via the third connecting piece, and the angle formed by the windward edges of the first and second connecting pieces constitutes the opening of the indoor heat exchanger. Attached Figure Description

[0030] To more clearly illustrate the technical solutions of the embodiments of this application, the drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0031] Figure 1 This is a schematic diagram of the connection structure of a duct-type air conditioner provided in an embodiment of this application;

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

[0033] Figure 3 for Figure 1 The diagram shows a connection structure where no four-way valve is provided between the compressor and the outdoor heat exchanger and the indoor heat exchanger.

[0034] Figure 4 A side view of the indoor unit of the first type of ducted air conditioner provided for the purposes of this application;

[0035] Figure 5 for Figure 4 A three-dimensional structural schematic diagram of the indoor heat exchanger shown in the figure;

[0036] Figure 6 A side view of the indoor unit of a second type of ducted air conditioner provided as an example of this application;

[0037] Figure 7 A side view of the indoor unit of a third type of ducted air conditioner provided as an example of this application;

[0038] Figure 8 A side view of the indoor unit of the fourth type of ducted air conditioner provided in this application example;

[0039] Figure 9 for Figure 8 A three-dimensional structural diagram of the indoor unit shown;

[0040] Figure 10 for Figure 9A sectional view of the volute and centrifugal impeller shown in FIG. 1;

[0041] Figure 11 A sectional view of the volute and centrifugal impeller shown in FIG. 1; Figure 9 A sectional view of the volute and centrifugal impeller shown in FIG. 1;

[0042] Figure 12 A sectional view of the volute and centrifugal impeller shown in FIG. 1; Figure 11 A sectional view of the volute and centrifugal impeller shown in FIG. 1;

[0043] Figure 13 A sectional view of the volute and centrifugal impeller shown in FIG. 1;

[0044] Figure 14 A sectional view of the volute and centrifugal impeller shown in FIG. 1; Figure 9 A sectional view of the volute and centrifugal impeller shown in FIG. 1;

[0045] Figure 15 A sectional view of the volute and centrifugal impeller shown in FIG. 1;

[0046] Figure 16 A sectional view of the volute and centrifugal impeller shown in FIG. 1;

[0047] Figure 17 A sectional view of the volute and centrifugal impeller shown in FIG. 1;

[0048] Figure 18 A sectional view of the volute and centrifugal impeller shown in FIG. 1;

[0049] Figure 19 A sectional view of the volute and centrifugal impeller shown in FIG. 1;

[0050] Figure 20 A sectional view of the volute and centrifugal impeller shown in FIG. 1;

[0051] Reference numerals:

[0052] 100 - air conditioner;

[0053] 10 - compressor; 20 - four-way valve; 30 - outdoor heat exchanger; 40 - throttling device;

[0054] 50 - indoor heat exchanger; 51 - refrigerant pipe; 52 - fin; 521 - first connecting piece; 522 - second connecting piece; 53 - insertion hole;

[0055] 61 - gas-liquid separator; 62 - oil separator;

[0056] 70 - housing; 71 - mounting cavity; 72 - air outlet; 73 - air inlet;

[0057] 80 - fan assembly; 81 - volute; 82 - centrifugal impeller; 83 - volute tongue; 84 - air outlet; 85 - air inlet; 86 - collector ring; 87 - motor; 88 - first air guide part; 89 - second air guide part;

[0058] 90 - electrical box. DETAILED DESCRIPTION

[0059] 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 those skilled in the art without creative work fall within the scope of protection of the present application.

[0060] 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 based on the orientation or relative position shown in the drawings, and are only for the purpose of facilitating the description of 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 cannot be understood as a limitation on the present application. Unless otherwise specified, the above directional description can be flexibly arranged in the process of actual application, as long as the relative positional relationship shown in the drawings is met.

[0061] 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 with "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.

[0062] In the description of the present application, it should be noted that, unless otherwise specified and limited, the terms "mounting", "connection", "connection", "communication" 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 those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0063] 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.

[0064] 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 another identical element in the process, article or device including the element.

[0065] 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. On the contrary, the words such as "exemplary" or "for example" are intended to present the relevant concept in a specific manner.

[0066] The air conditioner is a device that can adjust and control the temperature, humidity and circulating air of the environment in a building or structure.

[0067] As shown in Figure 1 The present application provides a ducted 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).

[0068] The gas return end of the compressor 10 can be connected to the first port A of the four-way valve, the gas outlet end of the compressor 10 can be connected to the second port B of the four-way valve, the third port C of the four-way valve can be connected to one end of the outdoor heat exchanger 30, the other end of the outdoor heat exchanger 30 can be connected to 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 to the fourth port D of the four-way valve.

[0069] 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.

[0070] 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.

[0071] 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).

[0072] 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.

[0073] 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.

[0074] 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.

[0075] Subsequently, under the action of the throttling device 40, the pressure of the liquid refrigerant flowing through the throttling device 40 and into the indoor heat exchanger 50 is reduced, 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.

[0076] When the air conditioner 100 is in the heating mode, 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. Figure 1 For example, as shown by the dashed arrow in the middle, 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.

[0077] In this way, 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.

[0078] 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.

[0079] In order to avoid the gaseous refrigerant sucked into the compressor 10 through the gas inlet end being mixed with liquid refrigerant or impurities, as shown in Figure 2 As shown, the air conditioner 100 can also 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. In this way, 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.

[0080] Continuing to refer to Figure 2 , the air conditioner 100 can also 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. In this way, 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.

[0081] In other embodiments, the four-way valve can also not be provided.

[0082] AsFigure 3 As shown, the gas 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 gas 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. So that 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).

[0083] 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. Taking the fan assembly 80 and the indoor heat exchanger 50 in the mounting cavity 71 as an example, the fan assembly 80 and the indoor heat exchanger 50 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. So that 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.

[0084] 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 gas outlet end of the fan assembly 80. So that the refrigerant flowing in the indoor heat exchanger 50 can quickly exchange heat with the air flowing through.

[0085] 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 tubes 51 and a plurality of fins 52. The refrigerant tubes 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 tubes 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.

[0086] 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.

[0087] 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.

[0088] 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.

[0089] 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.

[0090] 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 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.

[0091] 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.

[0092] 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.

[0093] 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.

[0094] 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.

[0095] 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 ).

[0096] 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.

[0097] 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.

[0098] 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.

[0099] 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.

[0100] 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.

[0101] 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.

[0102] 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.

[0103] 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.

[0104] 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.

[0105] 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.

[0106] 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.

[0107] In some embodiments, as shown in FIG. Figure 10 , Figure 10 As shown in FIG. Figure 9 , a cross-sectional view of the volute 81 and the centrifugal impeller 82 shown in FIG. 1 is shown. 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.

[0108] 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.

[0109] 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.

[0110] Through 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 effect of increasing air and reducing noise is significant.

[0111] 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, etc., and the ratio k1 can also be flexibly set in the range of 1.18-1.32.

[0112] 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.

[0113] 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 air fan assembly 80 can further include a flow collecting ring 86. Figure 10 The diameter of the air inlets 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. Figure 11

[0114] Alternatively, as shown in FIG. 2, the air fan assembly 80 can further include a flow collecting ring 86, and the outer edge of the flow collecting ring 86 can be connected with the edge of the air inlets 85 of the volute 81, and the inner diameter of the flow collecting ring 86 can be equal to the diameter d of the air inlets 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 can form a vortex between the centrifugal impeller 82 and the flow collecting ring 86, so as to prevent the continuous leakage of the air flow, thereby improving the air supply efficiency and air supply volume of the centrifugal fan.

[0115] 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. Figure 12 When arranging the air inlets 85 and the centrifugal impeller 82, the ratio K2 of the air inlet diameter of the air inlets 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.

[0116] It should be noted that in the above embodiments, the diameter of the air inlets 85 (i.e., the inner diameter) 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 inlets 85 is formed between the outer edge and the inner edge of the centrifugal impeller 82.

[0117] 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).

[0118] 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 inlets 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 inlets 85 gradually decreases, and the air supply volume of the centrifugal fan gradually decreases and the noise gradually increases.

[0119] ​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 parameters such as 0.84, 0.86, 0.88, 0.89, 0.90, 0.92, 0.94 or 0.96, so that the centrifugal fan has a larger air volume and has smaller noise.

[0120] Wherein, since the plurality of blades of the centrifugal impeller 82 are spaced 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.

[0121] 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 an example between 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 parameters of the centrifugal fan of the four groups of schemes are tested under the same static pressure or the same rotation.

[0122] Table I

[0123] 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

[0124] Table II

[0125]

[0126] 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 , wherein scheme ① can be regarded as a control group of the basic scheme. The diameter size d of the air inlet 85 can be in the value range of 112.5mm≤d<114.5mm or 114.5mm≤d≤117.5mm.

[0127] Keeping the width size of the volute 81 unchanged (such as 154mm), from schemes ① and ② in Table I, it can be known that when the diameter size of the air inlet 85 changes and decreases from 114.5mm to 112.5mm, the air volume of the ducted fan increases under different external static pressures, especially when the external static pressure is 30pa and the diameter size of the air inlet 85 is 112.5mm, the air volume can be increased by about 4.2%.

[0128] Keeping the width dimension of the volute 81 unchanged (e.g. 154 mm), it can be seen from the scheme 1 and 3 in Table 1 that when the diameter dimension of the air inlet 85 is increased from 114.5 mm to 117.5 mm, the air volume of the ducted fan is increased under different external static pressures, and in particular, the air volume can be increased by about 1.5% when the diameter dimension of the air inlet 85 is 117.5 mm and the external static pressure is 30 pa.

[0129] Keeping the diameter dimension of the air inlet 85 unchanged (e.g. 114.5 mm), it can be seen from the scheme 1 and 4 in Table 1 that when the width dimension of the volute 81 is decreased from 154 mm to 150 mm, the air volume of the ducted fan is increased under different external static pressures, and in particular, the air volume can be increased by about 2% when the width dimension of the volute 81 is 150 mm and the external static pressure is 30 pa. It can be seen from the scheme 1 and 4 in Table 2 that when the width dimension of the volute 81 is decreased from 154 mm to 150 mm, the high gear noise of the centrifugal fan is approximately unchanged, the medium gear noise of the centrifugal fan can be reduced by 0.4 dB(A), and the low gear noise of the centrifugal fan is increased by 0.6 dB(A).

[0130] It can be seen from Table 2 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 114.5 mm and 117.5 mm, and when the diameter dimension of the air inlet 85 is reduced from 114.5 mm to 112.5 mm, the noise level of the centrifugal fan can be reduced by 0.6 dB(A).

[0131] In combination Figure 13 , the air volume of the scheme 2, the scheme 4, the scheme 3 and the scheme 1 is decreasing under the same rotating speed of the centrifugal impeller 82, and the air volume of the scheme 4 and the scheme 3 is less different under the same rotating speed.

[0132] In summary, the width dimension of the volute 81 can be set to 150 mm, 152 mm or 154 mm, wherein the width dimension of the volute 81 is 150 mm, which has the obvious effect of reducing the noise of the medium gear rotating speed, and the width dimension of the volute is 154 mm, which has the obvious feature of reducing the noise of the low gear rotating speed, and can be flexibly set according to the needs.

[0133] In some embodiments, as Figure 14 shown, the air conditioner 100 can further include an electrical box 90, and the electrical box 90 can be arranged close to or attached to the left side wall or the right side wall of the installation cavity 71 along the left-right direction. The electrical box 90 is used to install a circuit board and other control elements, 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.

[0134] For example, as Figure 9 and Figure 14As shown, the fan assembly 80 can further include a motor 87, which can be mounted between 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 with the centrifugal impellers 82. In this way, the control elements in the electric box 90 can be electrically connected with the motor 87 for controlling the rotating speed of the centrifugal impellers 82 through the motor 87, i.e. adjusting the air volume of the ducted air conditioner.

[0135] In the above embodiment, 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 volutes 81 along the left-right direction and can drive the corresponding centrifugal impellers 82 to rotate, which is beneficial to reducing the number of motors 87.

[0136] 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 motor 87 and one centrifugal impeller 82 can be installed in one volute 81. 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 rotating speed of part of the centrifugal impellers 82 through the control elements in the electric box 90.

[0137] As shown, Figure 14 The width dimension w of the mounting cavity 71 along the left-right direction can be 600mm-800mm, and the width dimension of the mounting cavity 71, i.e. the width dimension of the shell 70, can be flexibly adjusted according to the length dimension of the indoor heat exchanger 50. For example, since the air conditioner 100 has different specifications such as 1P, 1.5P, 2P or 3P, the length of the indoor heat exchanger 50 in the ducted air conditioner of different specifications is not completely the same, i.e. the length of the indoor heat exchanger 50 and the width of the shell 70 can be adjusted according to the different specifications of the air conditioner 100.

[0138] For example, the width dimension 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.

[0139] 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.

[0140] 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.

[0141] 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.

[0142] 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.

[0143] 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 the indoor heat exchanger 50 with an installation spacing of 146mm is approximately 584.1m³ / h. 3 / h, the airflow through the indoor heat exchanger 50 with an installation spacing of 156mm is approximately 581m³ / h. 3 / h, the airflow through the indoor heat exchanger 50 with an installation spacing of 156mm is approximately 575m³ / h. 3mm≤L≤166mm, in the above four installation intervals, the air volume flowing through the indoor heat exchanger 50 can be linearly changed.

[0144] Therefore, for the installation interval L of the indoor heat exchanger 50, 141mm≤L≤151mm can also be set, so that the air volume flowing through the indoor heat exchanger 50 is greater than 582.5m 3 / h, and has a large range of fitting errors when assembling the indoor heat exchanger 50 and the fan assembly 80 (facilitating assembly of the indoor unit). Moreover, at this time, it is beneficial to make the angle between the fin at the windward side edge and the flow direction of the air flowing through 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.

[0145] In the embodiments of the present application, the windward surface on the rear side of the indoor heat exchanger 50 can also be adjusted to make the wind uniformity of the windward surface of the indoor heat exchanger 50 in the up-down direction, so that the indoor heat exchanger 50 can exchange heat with the air efficiently.

[0146] In some embodiments, as shown in Figure 12 The fan assembly 80 can also include a first air guide part 88, and the part of the volute 81 close to the air outlet 84 away from the upper side of the volute tongue 83 is the first air guide part 88, that is, the first air guide part 88 can be an upper side flow guide plate structure at the air outlet 84. Figure 8 The first air guide part 88 can be arranged to be inclined (i.e., downwardly inclined) in the up-down direction towards the volute tongue 83 at one end (i.e., the front end) close to the indoor heat exchanger 50 (as shown in

[0147] In the installation cavity 71, since the air outlet 84 is arranged close to the upper side of the volute 81 and located in the upper side space of the installation cavity 71 to be arranged towards the indoor heat exchanger 50, the air blown forward by the air outlet 84 will be concentrated in the upper region of the windward side of the indoor heat exchanger 50. Therefore, by arranging the front end of the first air guide part 88 to be inclined downwardly, the upper side air guide plate of the volute 81 can make the air blown forward flow obliquely downwardly, so as to improve the wind volume on the lower side of the windward side of the indoor heat exchanger 50, that is, by improving the wind uniformity of the windward side of the indoor heat exchanger 50 in the up-down direction to improve its heat exchange efficiency.

[0148] Alternatively, as shown in Figure 12As shown, the fan assembly 80 can further include a second air guide portion 89, and the portion of the volute 81 close to the lower side of the volute tongue 83 close to the air outlet 84 is the second air guide portion 89, that is, the second air guide portion 89 can be a lower side flow guide plate structure at the air outlet 84. The second air guide portion 89 can be arranged to be inclined (i.e., downwardly inclined) toward the volute tongue 83 along the up-down direction at one end (i.e., the front end) close to the indoor heat exchanger 50 (as shown). Figure 8 As shown, the fan assembly 80 can further include a second air guide portion 89, and the portion of the volute 81 close to the lower side of the volute tongue 83 close to the air outlet 84 is the second air guide portion 89, that is, the second air guide portion 89 can be a lower side flow guide plate structure at the air outlet 84. The second air guide portion 89 can be arranged to be inclined (i.e., downwardly inclined) toward the volute tongue 83 along the up-down direction at one end (i.e., the front end) close to the indoor heat exchanger 50 (as shown).

[0149] As shown, the fan assembly 80 can further include a second air guide portion 89, and the portion of the volute 81 close to the lower side of the volute tongue 83 close to the air outlet 84 is the second air guide portion 89, that is, the second air guide portion 89 can be a lower side flow guide plate structure at the air outlet 84. The second air guide portion 89 can be arranged to be inclined (i.e., downwardly inclined) toward the volute tongue 83 along the up-down direction at one end (i.e., the front end) close to the indoor heat exchanger 50 (as shown). Figure 12 As shown, the fan assembly 80 can further include a second air guide portion 89, and the portion of the volute 81 close to the lower side of the volute tongue 83 close to the air outlet 84 is the second air guide portion 89, that is, the second air guide portion 89 can be a lower side flow guide plate structure at the air outlet 84. The second air guide portion 89 can be arranged to be inclined (i.e., downwardly inclined) toward the volute tongue 83 along the up-down direction at one end (i.e., the front end) close to the indoor heat exchanger 50 (as shown).

[0150] As shown, the fan assembly 80 can further include a second air guide portion 89, and the portion of the volute 81 close to the lower side of the volute tongue 83 close to the air outlet 84 is the second air guide portion 89, that is, the second air guide portion 89 can be a lower side flow guide plate structure at the air outlet 84. The second air guide portion 89 can be arranged to be inclined (i.e., downwardly inclined) toward the volute tongue 83 along the up-down direction at one end (i.e., the front end) close to the indoor heat exchanger 50 (as shown). Figure 8 As shown, the fan assembly 80 can further include a second air guide portion 89, and the portion of the volute 81 close to the lower side of the volute tongue 83 close to the air outlet 84 is the second air guide portion 89, that is, the second air guide portion 89 can be a lower side flow guide plate structure at the air outlet 84. The second air guide portion 89 can be arranged to be inclined (i.e., downwardly inclined) toward the volute tongue 83 along the up-down direction at one end (i.e., the front end) close to the indoor heat exchanger 50 (as shown).

[0151] As shown, the fan assembly 80 can further include a second air guide portion 89, and the portion of the volute 81 close to the lower side of the volute tongue 83 close to the air outlet 84 is the second air guide portion 89, that is, the second air guide portion 89 can be a lower side flow guide plate structure at the air outlet 84. The second air guide portion 89 can be arranged to be inclined (i.e., downwardly inclined) toward the volute tongue 83 along the up-down direction at one end (i.e., the front end) close to the indoor heat exchanger 50 (as shown).

[0152] As shown, the fan assembly 80 can further include a second air guide portion 89, and the portion of the volute 81 close to the lower side of the volute tongue 83 close to the air outlet 84 is the second air guide portion 89, that is, the second air guide portion 89 can be a lower side flow guide plate structure at the air outlet 84. The second air guide portion 89 can be arranged to be inclined (i.e., downwardly inclined) toward the volute tongue 83 along the up-down direction at one end (i.e., the front end) close to the indoor heat exchanger 50 (as shown).

[0153] As shown, the fan assembly 80 can further include a second air guide portion 89, and the portion of the volute 81 close to the lower side of the volute tongue 83 close to the air outlet 84 is the second air guide portion 89, that is, the second air guide portion 89 can be a lower side flow guide plate structure at the air outlet 84. The second air guide portion 89 can be arranged to be inclined (i.e., downwardly inclined) toward the volute tongue 83 along the up-down direction at one end (i.e., the front end) close to the indoor heat exchanger 50 (as shown). Figure 12 As shown, the fan assembly 80 can further include a second air guide portion 89, and the portion of the volute 81 close to the lower side of the volute tongue 83 close to the air outlet 84 is the second air guide portion 89, that is, the second air guide portion 89 can be a lower side flow guide plate structure at the air outlet 84. The second air guide portion 89 can be arranged to be inclined (i.e., downwardly inclined) toward the volute tongue 83 along the up-down direction at one end (i.e., the front end) close to the indoor heat exchanger 50 (as shown).

[0154] As shown, the fan assembly 80 can further include a second air guide portion 89, and the portion of the volute 81 close to the lower side of the volute tongue 83 close to the air outlet 84 is the second air guide portion 89, that is, the second air guide portion 89 can be a lower side flow guide plate structure at the air outlet 84. The second air guide portion 89 can be arranged to be inclined (i.e., downwardly inclined) toward the volute tongue 83 along the up-down direction at one end (i.e., the front end) close to the indoor heat exchanger 50 (as shown). Figure 15 Figure 16 Figure 17 Figure 15 Figure 16 ​​​​This is a side view of a simulated wind field when the air outlet angle is 5°. Figure 17 This is a side view simulating a wind field when the outlet angle is 8°. (Example) Figure 15 As shown, the first connecting piece 521 of the multiple fins 52 corresponds to the upper region of the indoor heat exchanger 50, the second connecting piece 522 of the multiple fins 52 corresponds to the lower region of the indoor heat exchanger 50, and the third connecting piece 523 of the multiple fins 52 corresponds to the middle region of the indoor heat exchanger 50.

[0155] Based on this, by Figure 15 , Figure 16 and Figure 17 It can be seen that when the outlet angle is 2°, the area with higher wind speed on the windward side of the indoor heat exchanger 50 is concentrated in the upper region, but there is a large vortex behind the lower region of the indoor heat exchanger 50. As the outlet angle gradually increases, the area with higher wind speed on the windward side of the indoor heat exchanger 50 will gradually move downward, thereby reducing the vortex area behind the lower region of the indoor heat exchanger 50. However, a new vortex will be formed in the upper region between the exhaust port 84 and the upper region.

[0156] Table 3

[0157]

[0158] Based on the data shown in Table 3, and by further subdividing the outlet air angle, the airflow in the upper, middle, and lower regions of the indoor heat exchanger 50 can be measured and statistically analyzed, and the total amount of air flowing through the indoor heat exchanger 50 can also be measured. In Table 3, the upper, middle, and lower positions of the indoor heat exchanger 50 refer to the upper, middle, and lower regions of the indoor heat exchanger 50, respectively. Based on this, through multiple test schemes with different outlet air angles, the airflow in the upper and lower regions of the indoor heat exchanger 50 can be tested and statistically analyzed. Using α / 4° as the horizontal axis, the following data can be obtained: Figure 18 The diagram shows the airflow variation trends in the upper and lower regions (i.e., the upper heat exchanger) of the indoor heat exchanger 50. As the outlet angle α gradually increases, the airflow in the upper region of the indoor heat exchanger 50 will exhibit a trend of V1 = -24.997X. 2 The quadratic curve of +25.098X+174.74 decreases, and the airflow in the lower region of the indoor heat exchanger 50 increases linearly with a curve of V2 = 24.443X+101.16, where V represents the airflow rate (m³ / s). 3 / h), and X represents the dimensionless quantization value α / 4° with a value range of 0.5 to 2.

[0159] exist Figure 18In the curves showing the airflow variation trends in the upper and lower regions of the indoor heat exchanger 50, the airflow in the upper region gradually decreases, while the airflow in the lower region gradually increases. Referring to Figure 3, the airflow in both the upper and lower regions of the indoor heat exchanger 50 could be 294.4 m³. 3 / h (when α=2°), 298.74m 3 / h (α=5°) and 274.9m 3 / h (α=8°), that is, the total air flow rate of the upper and lower regions of the indoor heat exchanger 50 first increases and then decreases as the air outlet angle increases, and the total air flow rate increases but the magnitude is small when 2°≤α≤5°.

[0160] Correspondingly, by using multiple test schemes with different air outlet angles, the airflow rate in the middle region of the indoor heat exchanger 50 can be tested and statistically analyzed. Using α / 4° as the abscissa, the following data can be obtained: Figure 19 The diagram shows the airflow variation trend in the central region of the indoor heat exchanger 50. As the outlet angle α gradually increases, the airflow in the central region of the indoor heat exchanger 50 will show a trend of V3 = 35.671X. 2 The quadratic curve of -86.746X+458.86 first decreases and then increases.

[0161] In summary, combining Figure 18 , Figure 19 Based on the data shown in Table 3, the airflow rates in the upper, middle, and lower regions of the indoor heat exchanger 50 at α = 2°, α = 5°, and α = 8° can be analyzed and compared, yielding results such as... Figure 20 The airflow trend chart shown is as follows. Among them, Figure 20 The dimensionless values ​​1, 2, and 3 on the horizontal axis represent the upper, middle, and lower regions of the indoor heat exchanger 50, respectively.

[0162] like Figure 20 As shown, in the upper region of the indoor heat exchanger 50, the airflow gradually decreases with the increase of the outlet angle α, while in the lower region of the indoor heat exchanger 50, the airflow gradually increases with the increase of the outlet angle α. In the middle region of the indoor heat exchanger 50, the airflow decreases sequentially when the outlet angles are 8°, 2°, and 5°.

[0163] In summary, the air flow functions V1, V2, and V3 of the upper, middle, and lower regions of the indoor heat exchanger 50 can be added together, resulting in the equation for the total air flow curve of the indoor heat exchanger 50: V = 10.674X 2-37.205X + 734.76. Since the flow curve equation V is a change trend of decreasing first and then increasing, the lowest critical point of which is when the air outlet angle a = (37.205 ÷ 10.674 ÷ 2) x 2 = 6.97°, at this time X = 1.743 and V = 702.34 m3 / h, that is, the indoor heat exchanger 50 as a whole has a smaller air flow.

[0164] Wherein, when the air outlet angle a = 6°, the air flow V at the indoor heat exchanger 50 is 702.9 m3 / h, that is, approximately equal to the total air flow when the air outlet angle is 8°. Based on this, the value range of the air outlet angle can be set as: 2°≤a<6° or 6°≤a≤8°, when 2°≤a<6°, the total air flow of the indoor heat exchanger 50 gradually decreases, and when 6°≤a≤8°, the total air flow of the indoor heat exchanger 50 gradually decreases first and then increases, but the latter is distributed to the lower wind area.

[0165] It should be noted that the wind speed range of 0.5 m / s to 2.5 m / s on the windward side of the indoor heat exchanger 50 of the air pipe machine will significantly affect the heat exchange effect of the indoor heat exchanger 50, that is, the main heat exchange wind speed interval. Through wind field simulation of the indoor heat exchanger 50 when a = 2°, a = 5° and a = 8°, it can be known that the main heat exchange wind speed interval of the windward side of the indoor heat exchanger 50 gradually moves downward.

[0166] If the air outlet angle is between 2° and 6°, the main heat exchange wind speed interval of the indoor heat exchanger 50 is distributed to the upper part (i.e., at the first connecting piece 521), and if the air outlet angle is between 6° and 8°, the main heat exchange wind speed interval of the indoor heat exchanger 50 is distributed to the middle part (i.e., at the third connecting piece 523), but the wind on the windward side of the indoor heat exchanger 50 is relatively uniform as a whole. Based on this, the air outlet angle can be set as 2°, 3°, 4° or 5°, which can not only satisfy the uniform wind of the indoor heat exchanger 50 as a whole, but also make the air flow through the indoor heat exchanger 50 larger.

[0167] Alternatively, the air outlet angle can also be set as 6°, 7° or 8°, at this time the wind area on the windward side of the indoor heat exchanger 50 is more uniform, although the air flow is slightly reduced. But the wind resistance at the middle part of the heat exchanger can be increased to make the wind of the upper and lower areas more uniform.

[0168] For example, since the middle part of the indoor heat exchanger 50 is the main distribution area of the main heat exchange wind speed interval, the air resistance of the indoor heat exchanger 50 in the middle part corresponding to the third connecting piece 523 can be appropriately increased. So that the main heat exchange wind speed interval can spread upward and downward, that is, to improve the uniformity and distribution range of the main heat exchange wind speed interval at the upper and lower ends of the indoor heat exchanger 50, and thus to improve the heat exchange efficiency of the indoor heat exchanger 50.

[0169] For example, in order to increase the air resistance of the indoor heat exchanger 50 at the middle region corresponding to the third connection piece 523, the distribution density of the refrigerant pipe 51 on the third connection piece 523 can be increased, the third connection piece 523 can be provided with protruding structures distributed left and right, or the width of the third connection piece 523 in the front-rear direction can be increased, etc., all of which can achieve the above purpose.

[0170] 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.

[0171] The above merely describes specific embodiments 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 scope 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; an indoor heat exchanger located in the mounting cavity; and a fan assembly located in the mounting cavity; the fan assembly comprises: a volute having an air outlet; the air outlet is arranged along a first linear direction towards the indoor heat exchanger, and the air outlet is arranged along a second linear direction close to one side of the mounting cavity; and a centrifugal impeller installed in the volute, the centrifugal impeller is used to drive air to flow through the indoor heat exchanger; the first linear direction, the second linear direction and the axial direction of the centrifugal impeller are perpendicular to each other; wherein, along the axial direction of the centrifugal impeller, the ratio K1 of the width dimension of the volute to the width dimension of the centrifugal impeller is in the range of 1.18≤K1<1.24 or 1.24≤K1≤1.32; along the axial direction of the centrifugal impeller, two air inlets are further arranged on the opposite sides of the volute; the ratio K2 of the air inlet diameter of the air inlet to the profile rotation length of the centrifugal impeller is: K2=(D1-d) / (D1-D2); wherein, the ratio K2 of the air inlet diameter of the air inlet to the profile rotation length of the centrifugal impeller is in the range of 0.84≤K2<0.89 or 0.89≤K2≤0.

96.

2. The ducted air conditioner according to claim 1, wherein the fan assembly further comprises: a first air guide part, the part of the volute close to the air outlet along the second linear direction away from one side of the volute tongue is the first air guide part; one end of the first air guide part close to the indoor heat exchanger is arranged inclinedly along the second linear direction towards the volute tongue.

3. The ducted air conditioner according to claim 2, wherein the air outlet included angle α between the first air guide part and the first linear direction is in the range of 2°≤α<6° or 6°≤α≤8°.

4. The ducted air conditioner according to claim 2, wherein the air outlet included angle between the first air guide part and the first linear direction is 2°, 5°, 7° or 8°.

5. The ducted air conditioner according to any one of claims 1 to 4, wherein along the axial direction of the centrifugal impeller, two air inlets are further arranged on the opposite sides of the volute; the value range of the diameter dimension d of the air inlet is: 112.5mm≤d<114.5mm or 114.5mm≤d≤117.5mm; and / or, along the circumferential direction of the centrifugal impeller, the width dimension of the volute is 150mm~154mm.

6. The ducted air conditioner according to any one of claims 1 to 4, wherein the ratio of the air inlet inner diameter of the air inlet to the profile rotation length of the centrifugal impeller is 0.89; and / or, along the axial direction of the centrifugal impeller, the ratio of the width dimension of the volute to the width dimension of the centrifugal impeller is 1.24; and / or, the diameter dimension of the air inlet is 112.5mm; and / or, along the axial direction of the centrifugal impeller, the width dimension of the volute is 150mm or 154mm.

7. The ducted air conditioner according to any one of claims 1 to 4, wherein along the first linear direction, the indoor heat exchanger is arranged bent at the opposite ends in the second linear direction towards the fan assembly, so that the indoor heat exchanger has an opening towards the fan assembly.

8. The ducted air conditioner according to any one of claims 1 to 4, wherein the fan assembly further comprises: A second air guide part, a part of the volute close to the air outlet along the second straight line direction close to one side of the volute tongue, the second air guide part close to one end of the indoor heat exchanger along the second straight line direction is inclined to the volute tongue; The air guide angle between the second air guide part and the first straight line direction is 12.1°-19.6°.

9. The ducted air conditioner according to claim 7, wherein The indoor heat exchanger comprises: A plurality of refrigerant pipes: And a plurality of fins, the fin is an integral sheet structure; a plurality of fins are distributed along the length direction of the indoor heat exchanger, and the refrigerant pipe vertically penetrates through a plurality of fins along the length direction of the indoor heat exchanger and is connected with a plurality of fins; The edge of the fin along the first straight line direction close to the fan assembly is the windward side edge; the fin comprises: A first connecting sheet; A second connecting sheet; And a third connecting sheet, which is an arc structure with the center close to the fan assembly; the first connecting sheet is connected with the second connecting sheet through the third connecting sheet, and the included angle between the windward side edge of the first connecting sheet and the windward side edge of the second connecting sheet is the opening of the indoor heat exchanger.

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