Air pipe type air conditioner

Abstract

The invention discloses an air duct type air conditioner which aims at improving the air outlet amount of a centrifugal fan in an air duct type air conditioner. The air pipe type air conditioner comprises an indoor unit, a shell of the indoor unit is provided with 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 is provided with an air outlet. The exhaust outlet is arranged towards the indoor heat exchanger in the first linear direction, and the exhaust outlet is arranged close to one side of the mounting cavity in the second linear direction. The centrifugal impeller is installed in the volute and used for driving 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. In the axial direction of the centrifugal impeller, the value range of the ratio K1 of the width size of the volute to the width size of the centrifugal impeller is that K1 is larger than or equal to 1.18 and smaller than 1.24, or K1 is larger than or equal to 1.24 and smaller than or equal to 1.32. The air conditioner is used for improving the heat exchange efficiency of the indoor unit.

Description

Technical Field

[0001] The present invention relates to the technical field of air conditioning, and in particular to a duct type air conditioner. Background Art

[0002] The indoor unit of the duct air conditioner is a duct unit. Due to the advantages of the duct unit such as concealed installation and easy coordination with home ceiling decoration, the duct air conditioner has better aesthetics when installed indoors.

[0003] When the air conditioner is running, inside the duct unit, the impeller of the fan assembly rotates so that the air near the shell enters the shell. The air exchanges heat with the heat exchanger while passing through the heat exchanger. The air after heat exchange can flow out of the shell and adjust the temperature and / or humidity near the installation area.

[0004] Since centrifugal fans have the characteristics of high wind pressure, low noise and small size, setting the fan assembly as a centrifugal fan is conducive to increasing the ventilation volume of the duct fan and reducing the ventilation noise. However, in the volute of the centrifugal fan, along the axial direction of the fan assembly, the volute width of the centrifugal fan and the width of the impeller have a great influence on the air intake and air outlet of the centrifugal fan. Summary of the invention

[0005] The object of the present invention is to provide a duct type air conditioner, aiming to increase the air output of a centrifugal fan in the duct type air conditioner.

[0006] In order to achieve the above object, the present invention adopts the following technical scheme:

[0007] The present invention provides a duct air conditioner, the air conditioner includes an indoor unit, the indoor unit includes a shell, an indoor heat exchanger and a fan assembly. The shell has an installation cavity, and the indoor heat exchanger and the fan assembly are located in the installation cavity. The fan assembly includes a volute and a centrifugal impeller, and the volute has an exhaust port. The exhaust port is arranged toward the indoor heat exchanger along a first straight line direction, and the exhaust port is arranged near one side of the installation cavity along a second straight line 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 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 dimension of the volute to the width dimension of the centrifugal impeller has a value 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 be rotated around its axis in the volute to drive the air from the exhaust port to the indoor heat exchanger. Since the axial direction of the centrifugal impeller is the axial direction of the fan assembly, that is, 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, and since the fan assembly of the centrifugal fan structure has the characteristics of small size, low noise and high wind pressure, it is beneficial to increase the air circulation in the duct machine with limited height space.

[0009] Based on this, by adjusting the ratio k1 of the width of the volute to the width of the centrifugal impeller to a value range of 1.18≤k1<1.24 or 1.24≤K1≤1.32, a suitable installation spacing is maintained between the axial ends of the centrifugal impeller and the volute. The centrifugal impeller in the volute can rotate smoothly and quickly to drive the air to be blown out quickly from the exhaust port, which is conducive to reducing the air flow leakage between the axial ends of the centrifugal impeller and the volute, thereby increasing the air volume 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 also includes a first air guide portion, and the side of the volute casing close to the exhaust port along the second straight line direction away from the volute tongue is the first air guide portion; one end of the first air guide portion close to the indoor heat exchanger is inclined toward the volute tongue along the second straight line direction.

[0011] In some embodiments, the value range of the air outlet angle α formed by the first air guide portion and the first straight line direction is 2°≤α<5°.

[0012] In some embodiments, the value range of the air outlet angle α formed by the first air guide portion and the first straight line direction is 5°<α≤8°.

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

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

[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 rotation length of the centrifugal impeller is: K2 = (D1-d) / (D1-D2).

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

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

[0018] In some embodiments, the diameter dimension d of the air inlet has a value range of 112.5 mm ≤ d < 114.5 mm.

[0019] In some embodiments, the diameter dimension d of the air inlet has a value range of 114.5 mm ≤ d ≤ 117.5 mm.

[0020] In some embodiments, along the circumference of the centrifugal impeller, the width of the volute is 150 mm to 154 mm.

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

[0022] In some embodiments, 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.

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

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

[0025] In some embodiments, along the first straight line direction, opposite ends of the indoor heat exchanger in the second straight line direction are bent toward the fan assembly, so that the indoor heat exchanger has an opening facing the fan assembly.

[0026] In some embodiments, the fan assembly also includes a second air guide portion, and the side of the volute casing close to the exhaust port along the second straight line direction close to the volute tongue is the second air guide portion, and the end of the second air guide portion close to the indoor heat exchanger is inclined toward the volute tongue along the second straight line direction.

[0027] In some embodiments, an air guiding angle formed by the second air guiding portion and the first straight line direction is 12.1° to 19.6°.

[0028] In some embodiments, the indoor heat exchanger includes a plurality of refrigerant tubes and a plurality of fins, the fins are an integrated sheet structure, the plurality of fins are spaced apart along the length direction of the indoor heat exchanger, and the refrigerant tubes vertically penetrate the plurality of fins along the length direction of the indoor heat exchanger and are in contact with and connected to the plurality of fins.

[0029] In some embodiments, the edge of the fin close to the fan assembly along the first straight line direction is its windward edge. The fin includes a first connecting piece, a second connecting piece and a third connecting piece. The third connecting piece is an arc-shaped structure with a center close to the fan assembly. The first connecting piece is connected to the second connecting piece through the third connecting piece, and the angle formed by the windward edge of the first connecting piece and the windward edge of the second connecting piece is the opening of the indoor heat exchanger. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required for use in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

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

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

[0033] Figure 3 for Figure 1 A schematic diagram of a connection structure in which no four-way valve is provided between the compressor and the outdoor heat exchanger and the indoor heat exchanger as shown in FIG.

[0034] Figure 4 A side view of an indoor unit of a first duct-type air conditioner provided in an example of the present application;

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

[0036] Figure 6 A side view of an indoor unit of a second duct-type air conditioner provided in the present application example;

[0037] Figure 7 A side view of an indoor unit of a third duct-type air conditioner provided in the present application example;

[0038] Figure 8 A side view of an indoor unit of a fourth duct-type air conditioner provided in the present application example;

[0039] Fig. 9 for Figure 8 A three-dimensional structural schematic diagram of an indoor unit is shown;

[0040] Fig.10 for Fig. 9A cross-sectional view of the volute and the centrifugal impeller shown;

[0041] Fig.11 for Fig. 9 A side view of the volute and centrifugal impeller shown in;

[0042] Fig.12 for Fig.11 A cross-sectional view of the volute and the centrifugal impeller shown;

[0043] Fig.13 The graphs are the relationship between the air volume and the rotation speed of four groups of centrifugal fans;

[0044] Fig.14 for Fig. 9 A cross-sectional view of a duct machine shown in ;

[0045] Fig.15 This is a simulated side view of a wind field when the wind outlet angle is 2°;

[0046] Fig.16 This is a side view of a wind field simulation when the wind outlet angle is 5°;

[0047] Fig.17 This is a side view of a wind field simulation when the wind outlet angle is 8°;

[0048] Fig.18 It is the air flow variation trend diagram of the upper area and the lower area of ​​the indoor heat exchanger;

[0049] Fig.19 It is the air flow variation trend diagram of the middle area of ​​the indoor heat exchanger;

[0050] Fig. 20 It is the air flow trend diagram of the upper area, middle area and lower area of ​​the indoor heat exchanger at different air outlet angles.

[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-connecting hole;

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

[0056] 70-housing; 71-installation cavity; 72-air outlet; 73-return air outlet;

[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; 89-second air guide;

[0058] 90-Electrical box. DETAILED DESCRIPTION

[0059] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0060] In the description of the present invention, it should be understood that the terms "upper", "lower", "left", "right", "front", "back", "inside", "outside" and the like indicate directions or positional relationships based on the directions or relative positional relationships shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific direction, be constructed and operated in a specific direction. Therefore, it should not be understood as a limitation to the present invention. Unless otherwise specified, the above-mentioned directional description can be flexibly set in the process of actual application under the condition of satisfying the relative positional relationship shown in the drawings.

[0061] The terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, unless otherwise specified, "plurality" means two or more.

[0062] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", and "connected" should be understood in a broad sense, such as fixed connection, detachable connection, and integral connection. It can be directly connected or indirectly connected through an intermediate medium, and it can be the internal connection of two components or the electrical connection between two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0063] It should be noted that in actual applications, due to the limitations of equipment accuracy or installation errors, absolute parallel or perpendicular effects are difficult to achieve. The description of perpendicularity, parallelism or co-ordination in this application is not an absolute limiting condition, but means that a perpendicular or parallel structure setting can be achieved within a preset error range (such as an upper and lower deviation of 5°) and the corresponding preset effect can be achieved, thereby maximizing the technical effect of the defined feature and making the corresponding technical solution easy to implement and having high feasibility.

[0064] In the embodiments of the present invention, the terms "comprises", "comprising" or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, article or device including a series of elements includes not only those elements, but also includes other elements not explicitly listed, or also includes elements inherent to such process, article or device. In the absence of further restrictions, an element defined by the sentence "comprising a ..." does not exclude the presence of other identical elements in the process, article or device including the element.

[0065] In the embodiments of the present invention, words such as "exemplary" or "for example" are used to indicate examples, illustrations or explanations. Any embodiment or design scheme described as "exemplary" or "for example" in the embodiments of the present invention should not be interpreted as being more preferred or more advantageous than other embodiments or designs. Specifically, the use of words such as "exemplary" or "for example" is intended to present the relevant concepts in a specific way.

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

[0067] like Figure 1 As shown, the present application provides a duct type air conditioner (hereinafter referred to as air conditioner 100), which may 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 may have a first port A, a second port B, a third port C and a fourth port D, and the compressor 10 may have a return air port and an outlet air port (not shown in the figure).

[0068] The return air end of the compressor 10 can be connected to the first port A of the four-way valve, the outlet air 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 may include an indoor unit and an outdoor unit. The compressor 10, the four-way valve 20 and the outdoor heat exchanger 30 may be part of the outdoor unit, and the corresponding indoor heat exchanger 50 may be part of the indoor unit. The throttling device 40 may be a capillary structure or an electronic expansion valve structure. The throttling device 40 may be installed in the outdoor unit or in the indoor unit. The throttling device 40 may also be installed in the refrigerant pipeline between the outdoor unit and the indoor unit. The throttling device 40 only needs to be located between the indoor heat exchanger 50 and the outdoor heat exchanger 30 along the flow direction of the refrigerant.

[0070] Based on this, driven by the compressor 10, the refrigerant can circulate between the indoor unit and the outdoor unit and produce a reversible phase change, and while the refrigerant produces a phase change, it can release or absorb heat through the heat exchanger.

[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 to cool the nearby 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 nearby air).

[0072] By setting the four-way valve 20, the operation mode of the air conditioner 100 can be flexibly adjusted between the hot-cooling condition and the heating condition, so that the air conditioner 100 can be applied to more usage scenarios.

[0073] When the air conditioner 100 is in cooling or dehumidification mode, Figure 1 Taking the solid arrow shown in FIG. 2 as an example, the four-way valve 20 can be adjusted to connect the second port B and the third port C, and to connect the fourth port D and the first port A.

[0074] In this way, the high-pressure gaseous refrigerant compressed by the compressor 10 can flow from the outlet end through the second port B and the third port C of the four-way valve 20 to the outdoor heat exchanger 30, 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 passing through the throttling device 40 and flowing 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 sequence, and then the gaseous refrigerant can be sucked into the compressor 10 through the return air end and compressed, thereby realizing the circulation of the refrigerant.

[0076] When the air conditioner 100 is in the heating state, Figure 1 Taking the dashed arrow shown in FIG. 2 as an example, the four-way valve 20 can be adjusted to connect the second port B and the fourth port D, and to connect the third port C and the first port A.

[0077] In this way, the high-temperature and high-pressure gaseous refrigerant compressed by the compressor 10 can flow from the outlet end through the second port B and the fourth port D of the four-way valve 20 to the indoor heat exchanger 50, 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 passing through the throttling device 40 and flowing 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 sequence, and then the gaseous refrigerant can be sucked into the compressor 10 through the return air end and compressed, thereby realizing the circulation of the refrigerant.

[0079] In order to prevent the gaseous refrigerant sucked into the compressor 10 from being mixed with liquid refrigerant or impurities, Figure 2 As shown, the air conditioner 100 may further include a gas-liquid separator 61, which may be installed between the first port A of the four-way valve 20 and the return air end of the compressor 10, so that the first port A can be connected and conducted with the return air end of the compressor 10 through the gas-liquid separator 61. In this way, when the gaseous refrigerant mixed with impurities such as liquid refrigerant or lubricating oil flows to the return air end of the compressor 10 through the gas-liquid separator 61, the gas-liquid separator 61 can separate non-gaseous impurities (such as liquid refrigerant, liquid lubricating oil or other impurities) to prevent the above impurities from entering the compressor 10 and affecting the stable operation of the compressor 10.

[0080] Continue to refer to Figure 2 The air conditioner 100 may 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 may also be connected and conducted through the oil separator 62. In this way, the lubricating oil mixed in the high-temperature and high-pressure gaseous refrigerant can be separated in the process of flowing through the oil separator 62, thereby preventing the lubricating oil from adhering to the inner walls of the outdoor heat exchanger 30 and the indoor heat exchanger 50 when the refrigerant flows through the outdoor heat exchanger 30 and the indoor heat exchanger 50, so that the indoor heat exchanger 50 and the outdoor heat exchanger 30 have a higher heat exchange efficiency.

[0081] In some other embodiments, it is not necessary to provide a four-way valve.

[0082] like Figure 3 As shown, the air outlet of the compressor 10 can be connected to one end of the throttling device 40 through the outdoor heat exchanger 30, and the air return end of the compressor 10 can be connected to the other end of the throttling device 40 through the gas-liquid separator 61 and the indoor heat exchanger 50 in sequence. So that the refrigerant can circulate among 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 nearby air, and the indoor heat exchanger 50 can be used to cool the nearby air, so that the air conditioner 100 operates in a cooling condition or a dehumidification condition (i.e., a cooling-only mode air conditioner).

[0083] Based on this, Figure 4 As shown, the indoor unit of the duct structure may include a housing 70, a fan assembly 80 and an indoor heat exchanger 50, the housing 70 may have an installation cavity 71, and the fan assembly 80 and the indoor heat exchanger 50 may be arranged at intervals in the installation cavity 71. Taking the fan assembly 80 and the indoor heat exchanger 50 in the installation cavity 71 as an example of being arranged at intervals along the front-to-back direction (i.e., the first straight line direction), the housing 70 may be provided with an air outlet 72 at the front side of the installation cavity 71, and the housing 70 may be provided with a return air outlet 73 at the rear side of the installation cavity 71, so that the fan assembly 80 can drive air to enter the installation cavity 71 through the return air outlet 73 and flow through the indoor heat exchanger 50.

[0084] Based on this, the indoor heat exchanger 50 can be arranged near the front air outlet 72 in the installation cavity 71, and the fan assembly 80 can be arranged near the rear return air outlet 73. In this way, when the air conditioner is running, the fan assembly 80 can rotate to drive air into the installation cavity 71 from the return air outlet 73 and can be blown toward the indoor heat exchanger 50 from the air 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 it.

[0085] like Figure 4 and Figure 5 As shown, the length direction of the indoor heat exchanger 50 and the shell 70 can be the left-right direction, and 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 integrated sheet structure. The plurality of fins 52 can be spaced apart in the left-right direction (i.e., the length direction of the indoor heat exchanger 50), and the refrigerant tube 51 can pass through the plurality of fins 52 in the left-right direction and be in contact with and connected to the plurality of fins 52 to form an indoor heat exchanger 50 of an integrated structure.

[0086] Combination Figure 4, a plurality of plug holes 53 may be provided on a fin 52, and the plurality of plug holes 53 on the plurality of fins 52 may be aligned in the left-right direction, so that the refrigerant tube 51 passing through the plug hole 53 and through the fin 52 may be in contact with the fin 52 while the plurality of refrigerant tubes 51 may be distributed at intervals in the plane of the fin 52. In this way, the plurality of refrigerant tubes 51 may be connected to form one or more refrigerant passages, so that the flowing refrigerant may fully contact the air through the refrigerant tube 51 and the fin 52, thereby improving the heat exchange efficiency of the indoor heat exchanger 50.

[0087] Taking the fin 52 as a rectangular sheet structure as an example, a plurality of fins 52 and a plurality of refrigerant tubes 51 can be connected to form a Figure 5 The flat plate heat exchanger shown. Figure 4 In the installation cavity 71 shown, since the height dimension of the installation cavity 71 in the up and down direction (i.e., the second straight line direction) is limited, the upper side edge of the flat-plate structure indoor heat exchanger 50 can be arranged to tilt backward, so that the heat exchange area of ​​the indoor heat exchanger 50, such as the length dimension of the fin 52, can be increased within the limited height space.

[0088] In some other embodiments, such as Figure 6 As shown, multiple flat plate heat exchangers can also be spliced ​​together, such as two heat exchangers can be spliced ​​together in the up-down direction, and the lower edge of an upper heat exchanger can be connected to the upper edge of a lower heat exchanger to form a spliced ​​structure indoor heat exchanger 50. Taking the indoor heat exchanger 50 formed by splicing two flat plate heat exchangers as an example, along the up-down direction, the upper end of the indoor heat exchanger 50 can be tilted or bent backward, and the lower end of the indoor heat exchanger 50 can also be tilted or bent backward, so that the indoor heat exchanger 50 can form an opening toward the fan assembly 80.

[0089] In this way, in a plane perpendicular to the left-right direction, the cross section of the indoor heat exchanger 50 can be approximately V-shaped, and the opening of the indoor heat exchanger 50 can be arranged backward toward the fan assembly 80. That is, the upper end and the lower end of the indoor heat exchanger 50 can be arranged backward in the installation cavity 71 to increase the contact area between the indoor heat exchanger 50 (especially the fins 52) and the air in the installation cavity 71.

[0090] In the above embodiment, if the height space of the installation cavity 71 is sufficient, or the width dimension of the flat plate heat exchanger is small, one or more flat plate heat exchangers may be connected between the upper and lower inclined flat plate heat exchangers, so that the indoor heat exchanger 50 may be a C-shaped or W-shaped splicing structure in a cross section perpendicular to the left and right directions, which is not limited.

[0091] In addition, combined Figure 7The indoor heat exchanger 50 may also be an integrated structure and have a rearward opening structure. The fin 52 may be an integrated sheet structure, and the fin 52 may include a first connecting sheet 521 and a second connecting sheet 522 , and the first connecting sheet 521 may be connected to the second connecting sheet 522 .

[0092] The fin 52 may be a sheet-like structure arranged perpendicular to the left-right direction, that is, the angle formed by the windward side (i.e., rear side) edge of the first connecting piece 521 and the windward side edge of the second connecting piece 522 is an opening angle. In this way, a plurality of fins 52 may be spaced apart in the left-right direction, and a plurality of refrigerant pipes 51 may pass through the plug holes 53 in sequence along the left-right direction, so as to contact and connect the plurality of fins 52, thereby forming an indoor heat exchanger 50 of an integrated structure.

[0093] During the installation of the indoor heat exchanger 50, the refrigerant pipe 51 only needs to be passed through the plurality of fins 52 in sequence, and the refrigerant pipe 51 and the plurality of fins 52 can be connected by brazing to meet the contact heat exchange between the two. No additional splicing operation is required, and the structure is simple.

[0094] Alternatively, the plug hole 53 may be set as a corresponding plug groove. In this case, the refrigerant pipe 51 may be a round tube structure or a flat tube structure, which is not limited.

[0095] It should be noted that in Figure 7 In the embodiment shown, the first connecting piece 521 and the second connecting piece 522 are bent and connected, so that the opening of the indoor heat exchanger 50 is perpendicular to the left and right directions (such as Figure 5 The structure is approximately V-shaped in the plane shown in FIG.

[0096] In addition, the first connecting piece 521 and the second connecting piece 522 may be connected by a chamfered structure or a rounded structure. This is beneficial to make the angle between the chamfered or rounded structure of the windward side edge of the indoor heat exchanger 50 and most of the air flowing through 60° to 90°, so that the air can flow smoothly from back to front into the gap between two adjacent fins 52, so that the indoor heat exchanger 50 can take into account both the ventilation volume and the heat exchange effect, so as to improve the overall heat exchange effect of the indoor unit.

[0097] In the installation cavity 71, due to the limited height of the indoor unit of the duct structure, such as Figure 7 As shown, the height dimension H of the installation cavity 71 in the vertical direction can be 185-195 mm, that is, 185 mm ≤ H ≤ 195 mm. In other words, the maximum height dimension of the indoor heat exchanger 50 in the vertical direction can be H, such as the height dimension of the installation cavity 71 can be 185 mm, 187 mm, 190 mm, 192 mm or 195 mm, etc., without limitation.

[0098] In some other embodiments, such as Figure 8 As shown, the fin 52 may also include a third connecting piece 523, and the third connecting piece 523 may be an arc-shaped or circular arc-shaped sheet structure, such as the arc-shaped third connecting piece 523, the center of which may be located at the rear side thereof. Correspondingly, the first connecting piece 521 may be connected to the second connecting piece 522 via the third connecting piece 523, so that the first connecting piece 521 and the second connecting piece 522 may be located at the rear side of the third connecting piece 523, and the angle formed by 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 set toward the rear.

[0099] In the above embodiment, the first connecting sheet 521 and the second connecting sheet 522 can be approximately parallelogram-shaped sheet structures such as rectangular structures or rhombus structures. Alternatively, the first connecting sheet 521 and the second connecting sheet 522 can also be configured as arc-shaped sheet structures, which is not limited thereto.

[0100] In some other embodiments, the fin 52 may also include a first connecting piece 521, a fourth connecting piece, a fifth connecting piece, and a second connecting piece 522 that are bent and connected in sequence to form a sheet-like fin 52 that is approximately in the shape of a letter W. Alternatively, the fourth connecting piece and the fifth connecting piece may also be connected by a third connecting piece of a rectangular structure, so that there is a gap between the two openings of the letter W in the vertical direction, which is beneficial to improving the heat exchange area and heat exchange efficiency of the indoor heat exchanger.

[0101] In which case, when 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 two adjacent connecting pieces may be connected by rounded corners or chamfered corners.

[0102] like Figure 8 As shown, the fan assembly 80 located in the installation cavity 71 is a centrifugal fan structure, and the fan assembly 80 includes a volute 81 and a centrifugal impeller 82, and the centrifugal impeller 82 is installed in the volute 81. Figure 8 and Fig. 9 The volute 81 has an exhaust port 84 and an air inlet 85. The exhaust port 84 can be located at a position of the volute 81 close to the volute tongue 83. The exhaust port 84 can be set forward toward the indoor heat exchanger 50, and the exhaust port 84 can be arranged close to the upper side of the installation cavity 71 in the up and down directions.

[0103] Thus, in the installation cavity, the axial direction of the centrifugal impeller 82 can be arranged parallel to the left-right direction, that is, the centrifugal impeller 82 can rotate around an axis parallel to the left-right direction, and is used to drive the 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 from the exhaust port 84. Among them, the axial direction of the centrifugal impeller 82 can also be regarded as the axial direction of the fan assembly 80, that is, the first straight line direction, the second straight line direction and the axial direction of the centrifugal impeller 82 can be arranged perpendicular to each other. Since the centrifugal fan has the characteristics of small size, low noise and high wind pressure, it is beneficial to increase the air circulation in the duct fan with limited height space.

[0104] A volute 81 and a corresponding centrifugal impeller 82 can be installed in the installation cavity 71. A plurality of volutes 81 can be arranged in a spaced relationship along the left-right direction, and the number of centrifugal impellers 82 can correspond to the number of volutes 81, that is, one centrifugal impeller 82 can be installed in one volute 81.

[0105] For example, the number of the centrifugal impeller 82 and the volute 81 can be two, three, four or more, and can be flexibly arranged according to the width of the volute 81 in the left-right direction and the length of the indoor heat exchanger 50 in the left-right direction. In this way, by distributing a plurality of centrifugal fans at intervals in the left-right direction and blowing air forward, it is beneficial to improve the uniformity of the wind received by the indoor heat exchanger 50 in the left-right direction.

[0106] It should be noted that the amount of air flowing through the indoor heat exchanger 50 in the installation cavity 71 has a great influence on the heat exchange efficiency of the indoor unit of the duct unit structure. Thus, the air flow in the installation cavity 71, that is, the amount of air flowing through the indoor heat exchanger 50, can be increased by adjusting the structural dimensions of the fan assembly 80, the installation position of the fan assembly 80, and the structural dimensions of the return air port 73.

[0107] In some embodiments, Fig.10 As shown, Fig.10 for Fig. 9 A cross-sectional view of the volute 81 and the centrifugal impeller 82 is shown in FIG. 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 to k1=w1 / w2, and the value range of the ratio k1 can be set to 1.18 to 1.32.

[0108] Among them, if the ratio k1 is larger, such as k1 is greater than 1.32, the distance between the left and right ends of the centrifugal impeller 82 and the left and right walls of the volute 81 is larger, which will significantly increase the airflow leakage between the centrifugal impeller 82 and the volute 81. If the ratio k1 is smaller, such as k1 is less than 1.18, the distance between the left and right ends of the centrifugal impeller 82 and the left and right 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 too small a distance is not convenient for the installation of the centrifugal impeller 82 and will reduce the rotation speed of the centrifugal impeller 82.

[0109] Therefore, when the ratio k1 is in the range of 1.18 to 1.32, i.e., 1.18≤k1≤1.32, a suitable installation distance can be maintained between the left and right ends of the centrifugal impeller 82 and the volute 81. This allows the centrifugal impeller 82 in the volute 81 to rotate smoothly and quickly, driving the air to be blown out quickly from the air outlet 84, which is beneficial to reducing the air flow leakage between the left and right ends of the centrifugal impeller 82 and the volute 81, thereby increasing the air output of the fan assembly 80 and reducing the air output noise.

[0110] Through simulation test comparison, it can be known that when the ratio of the width dimension of the volute 81 to the width dimension of the centrifugal impeller 82 is 1.24, the centrifugal fan can have better anti-static pressure capability (avoiding airflow leakage) and lower noise. That is, the volute 81 and the centrifugal impeller 82 at this time can increase the air volume by 2% and reduce the windshield noise by 0.4dB(A), with significant airflow increase and noise reduction effects.

[0111] Based on this, the value range of the ratio k1 can also be set to: 1.18≤k1<1.24 or 1.24≤K1≤1.32, so that Fig.10 The distance dimension △X between the left and right ends of the centrifugal impeller 82 and the volute 81 is greater than or equal to 3 mm to increase the air volume of the centrifugal fan and reduce noise. For example, the parameter of 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 parameter of the ratio k1 can also be flexibly set in 1.18-1.32.

[0112] Exemplarily, the width dimension w2 of the centrifugal impeller 82 can be set to 115 mm to 126 mm, and the width dimension of the centrifugal impeller 82 and the number of centrifugal fans can be adjusted according to the length dimension of the indoor heat exchanger 50 in the left-right direction, so that the air blown out from the exhaust port 84 can flow through the indoor heat exchanger more evenly. 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 relative shapes and sizes, and the plurality of centrifugal impellers 82 have the same shape and size, that is, the volutes 81 and the centrifugal impellers 82 have the same specifications.

[0113] In some embodiments, Fig.10 As shown, two air inlets 85 may be provided at the left and right ends of the volute 81. Fig.11 , the diameter of the air inlet 85 can be defined as d. Two air inlets 85 can be directly opened on the left and right sides of the volute 81 .

[0114] Or, if Fig.11 As shown, the fan assembly 80 may further include a collector ring 86, the outer ring edge of the collector ring 86 may be connected to the edge of the volute 81 corresponding to the air inlet 85, and the inner diameter of the inner ring of the collector ring 86 is the diameter size d of the air inlet 85. Since there is an installation gap between the left and right ends of the centrifugal impeller 82 and the volute 81, the collector ring 86 is provided so that the airflow leaking 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 collector ring 86, thereby preventing the airflow from continuing to leak, so as to improve the air supply efficiency and air supply volume of the centrifugal fan.

[0115] On this basis, if Fig.12 As shown, 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 the air inlet 85 and the centrifugal impeller 82 are arranged, the ratio K2 of the air inlet diameter of the air inlet 85 to the blade rotation 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 embodiment, the diameter size (i.e., the inner diameter size) of the air inlet 85 is larger than the inner diameter size of the centrifugal impeller 82 and smaller than the outer diameter size of the centrifugal impeller, i.e., the edge of the air inlet 85 is opened between the outer edge and the inner edge of the centrifugal impeller 82.

[0117] Through simulation experiments, it can be seen that when the ratio K2 is 0.84 or 0.96, the air volume of the centrifugal fan can be increased by 2%, and the noise of the centrifugal fan can be reduced by 0.3dB(A). When the ratio K2 is 0.89, the air volume of the centrifugal fan can be increased by 4.6, and the noise of the centrifugal fan can be reduced by 0.6dB(A).

[0118] Among them, when the ratio K2 increases from 0.84 to 0.89, if the inner diameter and outer diameter of the centrifugal impeller 82 remain unchanged, it means that the diameter of the air inlet 85 gradually decreases, and the air volume of the corresponding 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 outer diameter of the centrifugal impeller 82 remain unchanged, it means that the diameter of the air inlet 85 gradually decreases, and the air volume of the corresponding centrifugal fan gradually decreases and the noise gradually increases.

[0119] Based on this, the value range of the ratio K2 can also be set to 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 less noise.

[0120] Among them, since the multiple 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 of the centrifugal impeller 82 is the diameter of the largest concentric circle of the multiple blades, and the inner diameter of the centrifugal impeller 82 is the diameter of the smallest concentric circle of the multiple blades, and does not include the size of the annular ring that fixes the multiple blades.

[0121] In some embodiments, the diameter dimension d of the air inlet 85 can be set to 112.5 mm to 117.5 mm. Based on this, taking the width dimension w1 of the volute 81 between 150 mm and 154 mm as an example, through four groups of solutions of ①d=114.5 and w1=154 mm, ②d=112.5 and w1=154 mm, ③d=117.5 and w1=154 mm, and ④d=112.5 and w1=150 mm, under the same static pressure or the same rotation, the air volume and noise and other parameters of the centrifugal fans of the four groups of solutions are tested.

[0122] Table 1

[0123] plan Air inlet diameter Volute width Static Pressure flow ① 114.5mm 154mm 30Pa 547m3 / h ② 112.5mm 154mm 30Pa 570m3 / h ③ 117.5mm 154mm 30Pa 555m3 / h ④ 114.5mm 150mm 30Pa 558m3 / h

[0124] Table 2

[0125]

[0126] In addition, by combining the air volume data of the above four groups of centrifugal fans of different sizes at different speeds, we can obtain the following: Fig.13 The relationship curves between the air volume and the rotation speed of the four groups of centrifugal fans are shown, wherein scheme ① can be regarded as the control group of the basic scheme. The value range of the diameter dimension d of the air inlet 85 can be: 112.5mm≤d<114.5mm or 114.5mm≤d≤117.5mm.

[0127] Keeping the width of the volute 81 unchanged (such as 154 mm), it can be seen from schemes ① and ② in Table 1 that when the diameter of the air inlet 85 decreases from 114.5 mm to 112.5 mm, the air volume of the duct air conditioner is improved at different external static pressures, especially when the external static pressure is 30 Pa and the diameter of the air inlet 85 is 112.5 mm, the air volume can be increased by about 4.2%.

[0128] Keeping the width of the volute 81 unchanged (such as 154 mm), it can be seen from solutions ① and ③ in Table 1 that when the diameter of the air inlet 85 changes from 114.5 mm to 117.5 mm, the air volume of the duct air conditioner is increased at different external static pressures, especially when the external static pressure is 30 Pa and the diameter of the air inlet 85 is 117.5 mm, the air volume can be increased by about 1.5%.

[0129] Keeping the diameter of the air inlet 85 unchanged (such as 114.5mm), it can be seen from solutions ① and ④ in Table 1 that when the width of the volute 81 changes from 154mm to 150mm, the air volume of the duct fan increases at different external static pressures, especially when the external static pressure is 30pa and the width of the volute 81 is 150mm, the air volume can be increased by about 2%. It can be seen from solutions ① and ④ in Table 2 that when the width of the volute 81 changes from 154mm to 150mm, the high gear noise of the centrifugal fan remains approximately unchanged, the middle gear noise of the centrifugal fan can be reduced by 0.4dB(A), and the low gear noise of the centrifugal fan increases by 0.6dB(A).

[0130] It can be seen from Table 2 that when the width of the volute 81 remains unchanged, the noise levels are similar when the diameters of the air inlet 85 are 114.5 mm and 117.5 mm. When the diameter 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] Combination Fig.13 When the rotation speed of the centrifugal impeller 82 is the same, the air output of scheme ②, scheme ④, scheme ③ and scheme ① is decreasing, and the difference between the air output of scheme ④ and scheme ③ is small under the same rotation speed.

[0132] In summary, the width dimension of the volute 81 can be set to 150mm, 152mm or 154mm, among which the width dimension of the volute 81 has an obvious noise reduction effect at medium gear speed when it is 150mm, and the width dimension of the volute has an obvious noise reduction effect at low gear speed when it is 154mm, and can be flexibly set as needed.

[0133] In some embodiments, Fig.14 The air conditioner 100 shown may also include an electrical box 90, and the electrical box 90 may be arranged close to or in contact with the left or right 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.

[0134] For example, Fig. 9 and Fig.14As shown, the fan assembly 80 may further include a motor 87, which may be installed between two adjacent volutes 81 in the left-right direction, and the output shafts at the left and right ends of the motor 87 may be inserted into the volutes 81 on both sides in the left-right direction and connected to the centrifugal impeller 82. In this way, the control element in the electrical box 90 may be electrically connected to the motor 87, so as to control the rotation speed of the centrifugal impeller 82 through the motor 87, that is, to adjust the air volume of the duct fan.

[0135] In the above embodiment, the number of the volutes 81 and the centrifugal impellers 82 may be two, and the motor 87 may be located between the two volutes 81 in the left-right direction. Alternatively, the number of the volutes 81 and the centrifugal impellers 82 may be three or more, that is, the motor 87 may be located between two of the volutes 81 in the left-right direction, and the output shafts at the left and right ends of the motor 87 may be inserted into all the volutes 81 in the left-right direction and may drive the corresponding centrifugal impellers 82 to rotate, which is conducive to reducing the number of motors 87 arranged.

[0136] In addition, the fan assembly 80 may also be configured with multiple motors 87, such as the number of motors 87, volute 81 and centrifugal impellers 82 may be the same, that is, one motor 87 and one centrifugal impeller 82 may be installed in one volute 81. Alternatively, if there are three or more volutes 81 and centrifugal impellers 82, the left and right ends of the first motor 87 may drive the two centrifugal impellers to rotate, and the second motor 87 may be installed in the third volute 81 and drive the corresponding centrifugal impeller 82 to rotate, so as to facilitate adjusting the rotation speed of some centrifugal impellers 82 through the control element in the electrical box 90.

[0137] like Fig.14 As shown, the width dimension w of the installation cavity 71 in the left-right direction can be 600 mm to 800 mm, and the width dimension of the installation cavity 71 is the width dimension of the housing 70, and the width dimension of the installation cavity 71 can be flexibly adjusted according to the length dimension of the indoor heat exchanger 50. For example, since the air conditioner 100 has a variety of different specifications such as 1 horsepower, 1.5 horsepower, 2 horsepower or 3 horsepower, the length of the indoor heat exchanger 50 in the air duct machine of different specifications is not exactly the same, that is, the length dimension of the indoor heat exchanger 50 and the width dimension of the housing 70 can be adjusted accordingly according to the air conditioner 100 of different specifications.

[0138] Exemplarily, the value range of the width dimension w of the installation cavity 71 may also be set to: 600mm≤w<700mm or 700mm≤w≤800mm, such as the width dimension of the installation cavity 71 may be 600mm, 650mm, 700mm, 750mm or 800mm.

[0139] If the width of the installation cavity 71 is greater than 800 mm, a large gap will be formed between two adjacent centrifugal fans in the left-right direction, resulting in a small amount of air being received by the windward area of ​​the indoor heat exchanger 50 corresponding to the front of the gap. Correspondingly, if the width of the installation cavity 71 is less than 600 mm, a small gap will be formed between two adjacent centrifugal fans in the left-right direction, resulting in the airflow from the two centrifugal fans to the gap area forming a vortex or turbulence, thereby affecting and reducing the air output of the duct fan.

[0140] Thus, when the width of the installation cavity 71 is 600 mm to 700 mm or 700 mm to 800 mm, the windward side of the indoor heat exchanger 50 can be evenly exposed to wind in the left and right directions, which is beneficial to improving the heat exchange efficiency of the indoor heat exchanger 50. At the same time, the influence of eddy currents such as turbulence formed between the centrifugal fan and the indoor heat exchanger 50 can be avoided and the air output of the duct fan can be reduced.

[0141] In some embodiments, Figure 8 As shown, in the installation cavity 71, in the front-to-back direction, the installation spacing L between the indoor heat exchanger 50 and the fan assembly 80 can be arranged to be 136 mm to 166 mm. Under the condition that the rotation speed of the fan assembly 80 and other dimensions of the indoor heat exchanger 50 remain unchanged, it can be known through simulation and comparison experiments that when the installation spacing between the indoor heat exchanger 50 and the fan assembly 80 increases from 136 mm to 166 mm, the air volume flowing 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, the distance between the center line of the windward side of the inclined indoor heat exchanger 50 in the front-to-back direction 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. If the indoor heat exchanger 50 is a structure with upper and lower ends bent backward or inclined, 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 air volume flowing through the indoor heat exchanger 50 when the installation spacing is 136 mm is approximately 580.5 m 3 / h, the air volume flowing through the indoor heat exchanger 50 when the installation spacing is 146mm is approximately 584.1m 3 / h, the air volume flowing through the indoor heat exchanger 50 when the installation spacing is 156mm is approximately 581m 3 / h, the air volume flowing through the indoor heat exchanger 50 when the installation spacing is 156mm is approximately 575m 3Based on this, the installation distance L between the indoor heat exchanger 50 and the fan assembly 80 can also be set to: 136mm≤L<146mm, 146mm≤L<156mm or 156mm≤L≤166mm. In the above four installation distance intervals, the air volume flowing through the indoor heat exchanger 50 can change linearly.

[0144] Based on this, the installation spacing L of the indoor heat exchanger 50 can also be set to 141 mm ≤ L ≤ 151 mm, so that the air volume flowing through the indoor heat exchanger 50 is 582.5 m 3 / h or more, and a larger adaptation error range is provided when assembling the indoor heat exchanger 50 and the fan assembly 80 (facilitating the assembly of the indoor unit). In addition, it is advantageous to make the angle between the fins at the windward edge and the flow direction of the air flowing through 60° to 90°, so that the indoor heat exchanger 50 can take into account both the ventilation volume and the heat exchange effect, thereby improving the overall heat exchange effect of the indoor unit.

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

[0146] In some embodiments, Fig.12 As shown, the fan assembly 80 may further include a first air guide portion 88. The portion of the volute 81 close to the air outlet 84 and away from the upper side of the volute tongue 83 is the first air guide portion 88, that is, the first air guide portion 88 may be an upper guide plate structure at the air outlet 84. The first air guide portion 88 may be arranged close to the indoor heat exchanger 50 (such as Figure 8 One end (i.e., the front end) of the worm gear 82 is inclined toward the worm tongue 83 in the up-down direction (i.e., inclined downward).

[0147] In the installation cavity 71, since the exhaust port 84 is arranged close to the upper side of the volute 81 and is located in the upper space of the installation cavity 71 so as to be arranged toward the indoor heat exchanger 50, the air blown forward from the exhaust port 84 will be concentrated in the upper area of ​​the windward side of the indoor heat exchanger 50. Based on this, by arranging the front end of the first air guide portion 88 to be tilted downward, the upper air guide plate of the volute 81 can make the air blown forward flow tilted downward, so as to increase the amount of air received by the indoor heat exchanger 50 below its windward side, that is, by improving the wind uniformity of the windward side of the indoor heat exchanger 50 in the up and down directions, its heat exchange efficiency is improved.

[0148] Or, if Fig.12As shown, the fan assembly 80 may further include a second air guide portion 89. The portion of the volute 81 close to the air outlet 84 and close to the lower side of the volute tongue 83 is the second air guide portion 89, that is, the second air guide portion 89 may be a lower guide plate structure at the air outlet 84. The second air guide portion 89 may be arranged close to the indoor heat exchanger 50 (such as Figure 8 One end (i.e., the front end) of the worm gear 82 is inclined toward the worm tongue 83 in the up-down direction (i.e., inclined downward).

[0149] For example, Fig.12 As shown, the wind guide angle β formed by the second wind guide portion 89 and the front-to-rear direction or the horizontal plane perpendicular to the up-down direction can be 12.1° to 19.6°, that is, 12.1°≤β≤19.6°.

[0150] Since the height dimension of the installation cavity 71 is relatively small and the indoor heat exchanger 50 (such as Figure 8 The installation spacing L between the fan assembly 80 and the fan assembly 80 in the front-to-rear direction is limited.

[0151] If the inclination angle of the front end of the second air guide 89 is large, such as the air guide angle β is greater than 19.6°, part of the air will be blown toward the bottom wall of the installation cavity 71 during the process of flowing forward and downward, thereby affecting the air output of the indoor heat exchanger 50. If the inclination angle of the front end of the second air guide 89 is small, such as the air guide angle β is less than 12.1°, the air will not be blown toward the lower end of the indoor heat exchanger 50 during the process of flowing forward and downward, thereby causing the lower end of the indoor heat exchanger 50 to have a lower exchange efficiency.

[0152] Thus, by setting 12.1°≤β≤19.6°, the air blown out from the exhaust port 84 can flow downward through the lower end of the indoor heat exchanger 50, and will not blow toward the bottom wall of the installation cavity 71, which is beneficial to improving the heat exchange efficiency of the indoor heat exchanger 50. For example, the air guide angle of the second air guide portion 89 can be set to 12.1°, 13°, 14°, 15°, 16°, 17°, 18°, 19° or 19.6°, which is not limited in the present application.

[0153] In some embodiments, Fig.12 As shown, the air outlet angle α formed by the first air guide portion 88 and the front-to-back direction or a horizontal plane perpendicular to the up-down direction can be set to 2° to 8°.

[0154] Taking the case where the air outlet angle of the first air guide portion 88 is 2°, 5° and 8° as an example, the wind field simulation of the air duct machine when the upper and lower ends of the indoor heat exchanger 50 are bent backwards is performed. Fig.15 , Fig.16 and Fig.17 It can be seen that Fig.15 This is a simulated side view of a wind field when the wind outlet angle is 2°. Fig.16This is a simulated side view of a wind field when the wind outlet angle is 5°. Fig.17 This is a simulated side view of a wind field when the wind outlet angle is 8°. Fig.15 As shown, it is taken as an example that the first connecting plate 521 of the multiple fins 52 corresponds to the upper area of ​​the indoor heat exchanger 50, the second connecting plate 522 of the multiple fins 52 corresponds to the lower area of ​​the indoor heat exchanger 50, and the third connecting plate 523 of the multiple fins 52 corresponds to the middle area of ​​the indoor heat exchanger 50.

[0155] Based on this, Fig.15 , Fig.16 and Fig.17 It can be seen that when the air 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 area, but there is a larger vortex behind the lower area of ​​the indoor heat exchanger 50. As the air outlet angle gradually increases, the area with higher wind speed on the windward side of the indoor heat exchanger 50 will gradually move downward, so that the vortex area behind the lower area of ​​the indoor heat exchanger 50 will decrease, but a new vortex will be formed in the area between the exhaust port 84 and the upper area and above.

[0156] Table 3

[0157]

[0158] Combined with the data shown in Table 3, the air outlet angle can be further subdivided, and the air flow in the upper area, middle area and lower area of ​​the indoor heat exchanger 50 can be detected and counted, and the total amount of air flowing through the indoor heat exchanger 50 can be detected. In Table 3, the upper, middle and lower positions of the indoor heat exchanger 50 refer to the upper area, middle area and lower area of ​​the indoor heat exchanger 50, respectively. Based on this, through multiple test schemes with different air outlet angles, the air flow in the upper area and lower area of ​​the indoor heat exchanger 50 can be tested and counted, and with α / 4° as the horizontal coordinate, the following can be obtained: Fig.18 The air flow rate variation trend diagram of the upper area (i.e., the upper heat exchanger) and the lower area (i.e., the lower heat exchanger) of the indoor heat exchanger 50 is shown in FIG. As the air outlet angle α gradually increases, the air flow rate of the upper area of ​​the indoor heat exchanger 50 will be V1=-24.997X 2 +25.098X+174.74, and the air flow rate in the lower area of ​​the indoor heat exchanger 50 increases in a linear curve of V2=24.443X+101.16. V in the above formula represents the air flow rate (m 3 / h), and X represents the dimensionless quantized value α / 4° and its value range is 0.5~2.

[0159] exist Fig.18In the curve of the air flow rate change trend of the upper area and the lower area of ​​the indoor heat exchanger 50 shown in FIG. 3, the air flow rate of the upper area and the lower area of ​​the indoor heat exchanger 50 can be 294.4m 3 / h(α=2°),298.74m 3 / h (α=5°) and 274.9m 3 / h (α=8°), that is, the total air flow rate in the upper area and the lower area of ​​the indoor heat exchanger 50 first increases and then decreases with the increase of the air outlet angle, and the total air flow rate increases but at a small amplitude when 2°≤α≤5°.

[0160] Correspondingly, through multiple test schemes with different air outlet angles, the air flow rate in the middle area of ​​the indoor heat exchanger 50 can be tested and counted, and with α / 4° as the horizontal coordinate, the following can be obtained: Fig.19 The air flow rate variation trend diagram of the middle area of ​​the indoor heat exchanger 50 is shown in FIG. As the air outlet angle α gradually increases, the air flow rate of the middle area of ​​the indoor heat exchanger 50 will be V3=35.671X 2 The quadratic curve of -86.746X+458.86 decreases first and then increases.

[0161] In summary, combined Fig.18 , Fig.19 By comparing the data shown in Table 3, the air flow 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, and the following can be obtained: Fig. 20 The air flow trend diagram is shown in Figure 1. Fig. 20 The dimensionless quantized values ​​1, 2, and 3 of the middle horizontal axis represent the upper region, the middle region, and the lower region of the indoor heat exchanger 50, respectively.

[0162] like Fig. 20 As shown, in the upper area of ​​the indoor heat exchanger 50, the air flow rate gradually decreases with the increase of the outlet angle α, and in the lower area of ​​the indoor heat exchanger 50, the air flow rate gradually increases with the increase of the outlet angle α. In the middle area of ​​the indoor heat exchanger 50, when the outlet angles are 8°, 2° and 5° respectively, the air flow rate therein decreases respectively.

[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, that is, the total air flow curve equation of the indoor heat exchanger 50 is V=10.674X 2-37.205X+734.76. Since the flow curve equation V shows a trend of decreasing first and then increasing, at its lowest critical point, the air outlet angle α=(37.205÷10.674÷2)×2=6.97°, at which time X=1.743 and V=702.34m3 / h, that is, the indoor heat exchanger 50 as a whole has a relatively small air flow rate.

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

[0165] It should be noted that on the windward side of the indoor heat exchanger 50 of the duct unit, the wind speed range of 0.5m / s to 2.5m / s will significantly affect the heat exchange effect of the indoor heat exchanger 50, that is, the main heat exchange wind speed range. By simulating the wind field of the indoor heat exchanger 50 when α=2°, α=5° and α=8°, it can be seen that the main heat exchange wind speed range on the windward side of the indoor heat exchanger 50 gradually moves downward.

[0166] If the outlet angle is between 2° and 6°, the main heat exchange wind speed interval of the indoor heat exchanger 50 is distributed at the top (i.e., at the first connecting piece 521); if the outlet angle is between 6° and 8°, the main heat exchange wind speed interval of the indoor heat exchanger 50 is distributed at the middle (i.e., at the third connecting piece 523), but the wind receiving of the windward side of the indoor heat exchanger 50 is relatively uniform as a whole. Based on this, the outlet angle can be set to 2°, 3°, 4° or 5°, which can ensure that the indoor heat exchanger 50 receives wind uniformly as a whole, and at the same time, the air flow rate flowing through the indoor heat exchanger 50 can be relatively large.

[0167] Alternatively, the outlet fan angle may be set to 6°, 7° or 8°, in which case the windward area of ​​the indoor heat exchanger 50 is more uniform, although the air flow rate is slightly reduced. However, the wind resistance at the middle heat exchanger can be increased to make the wind in the upper and lower areas more uniform.

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

[0169] For example, when increasing the air resistance of the indoor heat exchanger 50 in the middle area corresponding to the third connecting piece 523, the distribution density of the refrigerant pipe 51 on the third connecting piece 523 can be increased, the third connecting piece 523 can be provided with a convex structure distributed left and right, or the width of the third connecting piece 523 in the front-to-back direction can be increased, etc., all of which can achieve the above purpose.

[0170] In the description of this specification, specific features, structures, materials or characteristics may be combined in an appropriate manner in any one or more embodiments or examples.

[0171] The above are only specific embodiments of the present invention, but the protection scope of the present invention is not limited thereto. Any person skilled in the art who is familiar with the technical field can easily think of changes or substitutions within the technical scope disclosed by the present invention, which should be included in the protection scope of the present invention. Therefore, the protection scope of the present invention should be based on the protection scope of the claims.

Claims

1. A duct type air conditioner, comprising an indoor unit, characterized in that: The indoor unit comprises: A housing having a mounting cavity; An indoor heat exchanger is located in the installation cavity; and a fan assembly, located in the installation cavity; The fan assembly comprises: A volute having an exhaust port; the exhaust port is arranged along a first straight line direction toward the indoor heat exchanger, and the exhaust port is arranged along a second straight line direction close to one side of the installation cavity; and a centrifugal impeller installed in the volute, the centrifugal impeller being used to drive 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; Wherein, along the axial direction of the centrifugal impeller, a ratio K1 of the width dimension of the volute to the width dimension of the centrifugal impeller has a value range of: 1.18≤K1<1.24 or 1.24≤K1≤1.

32.

2. The duct type air conditioner according to claim 1, characterized in that: The fan assembly also includes: The first air guide portion, the part of the volute close to the exhaust port along the second straight line direction away from the volute tongue is the first air guide portion; the end of the first air guide portion close to the indoor heat exchanger is inclined toward the volute tongue along the second straight line direction.

3. The duct type air conditioner according to claim 2, characterized in that: The value range of the air outlet angle α formed by the first air guide portion and the first straight line direction is: 2°≤α<6° or 6°≤α≤8°.

4. The duct type air conditioner according to claim 2, characterized in that: An air outlet angle formed by the first air guide portion and the first straight line direction is 2°, 5°, 7° or 8°.

5. The duct type air conditioner according to any one of claims 1 to 4, characterized in that: Two air inlets are also provided on opposite sides of the volute along the axial direction of the centrifugal impeller; 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 of the air inlet to the blade rotation length of the centrifugal impeller is: K2 = (D1-d) / (D1-D2); The value range of the ratio K2 of the air inlet inner diameter of the air inlet to the blade rotation length of the centrifugal impeller is: 0.84≤K2<0.89 or 0.89≤K2≤0.

96.

6. The duct type air conditioner according to any one of claims 1 to 4, characterized in that: Two air inlets are also provided on opposite sides of the volute along the axial direction of the centrifugal impeller; The diameter dimension d of the air inlet has a value range of: 112.5 mm ≤ d < 114.5 mm or 114.5 mm ≤ d ≤ 117.5 mm; and / or, Along the circumference of the centrifugal impeller, the width of the volute is 150 mm to 154 mm.

7. The duct type air conditioner according to claim 5, characterized in that: The ratio of the air inlet inner diameter of the air inlet to the blade rotation length of the centrifugal impeller is 0.89; and / or, Along the axial direction of the centrifugal impeller, the ratio of the width of the volute to the width of the centrifugal impeller is 1.24; and / or, The diameter of the air inlet is 112.5 mm; and / or, Along the axial direction of the centrifugal impeller, the width of the volute is 150 mm or 154 mm.

8. The duct type air conditioner according to any one of claims 1 to 4, characterized in that: Along the first straight line direction, the indoor heat exchanger is bent toward the fan assembly at two opposite ends in the second straight line direction, so that the indoor heat exchanger has an opening toward the fan assembly.

9. The duct type air conditioner according to any one of claims 1 to 4, characterized in that: The fan assembly also includes: A second air guide portion, wherein the side of the part of the volute close to the air outlet along the second straight line direction close to the volute tongue is the second air guide portion, and one end of the second air guide portion close to the indoor heat exchanger is inclined toward the volute tongue along the second straight line direction; An air guiding angle formed by the second air guiding portion and the first straight line direction is 12.1° to 19.6°.

10. The duct type air conditioner according to claim 8, characterized in that: The indoor heat exchanger comprises: Multiple refrigerant pipes: and a plurality of fins, wherein the fins are an integrated sheet structure; the plurality of fins are spaced apart along the length direction of the indoor heat exchanger, and the refrigerant pipe vertically penetrates the plurality of fins along the length direction of the indoor heat exchanger and is in contact with and connected to the plurality of fins; The edge of the fin close to the fan assembly along the first straight line direction is its windward side edge; the fin includes: a first connecting piece; A second connecting piece; And a third connecting piece is an arc-shaped structure whose center is close to the fan assembly; the first connecting piece is connected to the second connecting piece through the third connecting piece, and the angle formed by the windward side edge of the first connecting piece and the windward side edge of the second connecting piece is the opening of the indoor heat exchanger.

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