Duct type air conditioner

Abstract

The utility model discloses a duct type air conditioner, and relates to the technical field of air conditioners. An air conditioner air inlet and an air conditioner air outlet are formed in the two ends of the machine body in the width direction respectively. The indoor heat exchanger is arranged in the machine body and is close to the air conditioner air inlet; the cross-flow fan is arranged in the machine body and located between the indoor heat exchanger and the air conditioner air outlet. A gap is formed between the front volute tongue and the cross-flow fan, and the front volute tongue is arranged in an arc shape; the minimum gap between the front volute tongue and the cross-flow fan is defined as delta 3, the diameter of the outer edge of the cross-flow fan is defined as D, delta 3 is larger than or equal to 0.03D, and delta 3 is smaller than or equal to 0.06 D. In the utility model, the bending deformation of the cross-flow fan is considered, and the minimum gap delta 3 between the cross-flow fan and the front volute tongue is arranged in a reasonable range, so that serious air flow leakage and air volume attenuation caused by overlarge distance between the cross-flow fan and the front volute tongue are avoided, and meanwhile, the high noise value caused by overlarge distance is avoided; and the working efficiency of the cross-flow fan is effectively improved.

Description

Technical Field

[0001] The utility model relates to the technical field of air conditioners, in particular to a duct air conditioner. Background Art

[0002] With the popularity of air conditioners, more and more users choose to install central air conditioners at home. As a type of central air conditioner, duct air conditioners are favored by users for their low cost, simple structure, hidden installation and other advantages. Existing duct air conditioners can usually be installed in the ceiling, which mainly includes a body and a cross-flow fan and an indoor heat exchanger installed inside the body. The body is provided with an air conditioning inlet and an air conditioning outlet. The cross-flow fan introduces air from the air conditioning inlet into the body, and after heat exchange in the indoor heat exchanger, air conditioning air is formed and sent out through the air conditioning outlet.

[0003] In the related art, the duct air conditioner also includes a front volute tongue, and the crossflow fan is located above the front volute tongue and there is a gap between the crossflow fan and the front volute tongue. The gap between the crossflow fan and the front volute tongue is an important design parameter that affects the air volume and sound quality. Within a reasonable design range, the air volume of the crossflow air duct increases as the gap between the crossflow fan and the front volute tongue decreases. The crossflow fan in the duct air conditioner is arranged horizontally, that is, the two ends of the crossflow fan are fixed and placed horizontally. The crossflow fan is not a rigid body. When placed horizontally, the crossflow fan as a whole will present a concave shape under the action of its own gravity, and the longer the fan, the more obvious the flexural deformation.

[0004] In the related art, the gap between the crossflow fan and the front volute tongue in the ducted air conditioner is set without considering the flexural deformation of the crossflow fan. When the crossflow fan is partially located above the front volute tongue, the deformation of the crossflow fan will directly affect the gap between the crossflow fan and the front volute tongue, which will not only deteriorate the sound quality of the air conditioner, but also increase the risk of the front volute tongue hitting the crossflow fan during transportation, affecting the user experience. Utility Model Content

[0005] The utility model aims to solve one of the technical problems in the related art at least to a certain extent. To this end,

[0006] The utility model provides a duct machine, comprising:

[0007] The machine body has air-conditioning inlets and air-conditioning outlets at both ends in the width direction;

[0008] An indoor heat exchanger is disposed in the machine body and close to the air inlet of the air conditioner;

[0009] A cross-flow fan is disposed in the machine body and located between the indoor heat exchanger and the air outlet of the air conditioner; under the action of the cross-flow fan, indoor air enters the machine body through the air inlet of the air conditioner, and is output to the room through the air outlet of the air conditioner after heat exchange through the indoor heat exchanger;

[0010] A front volute tongue, with a gap between it and the cross-flow fan, and the front volute tongue is arranged in an arc shape;

[0011] The minimum gap between the front volute tongue and the crossflow fan is defined as δ3, and the diameter of the outer edge of the crossflow fan is defined as D, δ3≥0.03D, δ3≤0.06D;

[0012] The air duct comprises:

[0013] An air outlet duct is formed between the cross-flow fan and the air-conditioning outlet. The sides of the air outlet duct facing each other at both ends in the length direction of the body are air outlet sides. In the direction from the cross-flow fan to the air-conditioning outlet, a constriction structure is formed between the two air outlet sides.

[0014] The duct fan provided by the technical solution sets the front volute tongue into an arc shape, so that when an eccentric vortex is generated, the airflow of the eccentric vortex can pass through the front volute tongue more smoothly, thereby reducing wind resistance. The minimum gap δ3 between the crossflow fan and the front volute tongue is set within the above reasonable range to avoid serious airflow leakage and air volume attenuation due to the large distance between the crossflow fan and the front volute tongue, and at the same time, avoid high noise values ​​due to the small distance between the crossflow fan and the front volute tongue, thereby effectively improving the working efficiency of the crossflow fan and reducing noise.

[0015] The utility model also provides a duct machine, comprising:

[0016] The machine body has air-conditioning inlets and air-conditioning outlets at both ends in the width direction;

[0017] An indoor heat exchanger is disposed in the machine body and close to the air inlet of the air conditioner;

[0018] A cross-flow fan is disposed in the machine body and located between the indoor heat exchanger and the air outlet of the air conditioner; under the action of the cross-flow fan, indoor air enters the machine body through the air inlet of the air conditioner, and is output to the room through the air outlet of the air conditioner after heat exchange through the indoor heat exchanger;

[0019] A front volute tongue, with a gap between it and the cross-flow fan, and the front volute tongue is arranged in an arc shape;

[0020] The minimum gap between the front volute tongue and the cross-flow fan is defined as δ3, and the diameter of the outer edge of the cross-flow fan is defined as D, δ3≥0.03D, δ3≤0.06D; wherein the vertical distance between the end of the front volute tongue close to the air inlet of the air conditioner and the cross-flow fan is the minimum gap δ3;

[0021] The air duct comprises:

[0022] An air outlet duct is formed between the cross-flow fan and the air-conditioning outlet. The sides of the air outlet duct facing each other at both ends in the length direction of the body are air outlet sides. In the direction from the cross-flow fan to the air-conditioning outlet, a constriction structure is formed between the two air outlet sides.

[0023] The duct machine provided by the technical solution sets the front volute tongue into an arc shape. When an eccentric vortex is generated, the airflow of the eccentric vortex can pass through the front volute tongue more smoothly, thereby reducing wind resistance. The minimum gap δ3 between the crossflow fan and the front volute tongue is set within the above-mentioned reasonable range to avoid serious airflow leakage and air volume attenuation due to the large distance between the crossflow fan and the front volute tongue. At the same time, it is avoided that the noise value is too high due to the small distance between the crossflow fan and the front volute tongue, thereby effectively improving the working efficiency of the crossflow fan and reducing noise. In addition, the vertical distance between the end of the front volute tongue close to the air inlet of the air conditioner and the crossflow fan is the minimum distance δ3, thereby ensuring the optimal wind resistance performance of the air duct in the machine body.

[0024] In some of the embodiments, when the length of the cross-flow fan is no more than 800 mm, δ3≥0.03D, δ3≤0.045D.

[0025] In some of the embodiments, when the length of the cross-flow fan exceeds 800 mm, δ3>0.045D, δ3≤0.06D.

[0026] In some of the embodiments, the maximum gap between the front volute tongue and the cross-flow fan is defined as δ4, the difference between δ4 and δ3 is Δδ, Δδ≥0.02D, Δδ≤0.04D, and Δδ is set within a reasonable range so that the maximum gap δ4 is within a reasonable numerical range, thereby improving the air intake and wind resistance performance.

[0027] In some of the embodiments, the vertical distance between an end of the front volute tongue close to the air outlet of the air conditioner and the cross-flow fan is the maximum gap δ4.

[0028] In some of the embodiments, in the radial direction of the cross-flow fan, the contour line of the front volute tongue has an endpoint A1 close to the air inlet of the air conditioner, and an endpoint An close to the air outlet of the air conditioner, and the gap between the front volute tongue and the cross-flow fan is gradually increased from endpoint A1 to endpoint An.

[0029] In some of the embodiments, the duct air conditioner further includes an air guide surface, wherein the air guide surface is arranged relative to the front volute tongue and toward the air outlet of the air conditioner, and the air guide surface and the front volute tongue are connected by an arc transition to form a volute tongue.

[0030] In some of the embodiments, the duct machine further includes a volute, which is disposed in the body and above the volute tongue, and the cross-flow fan is located between the volute and the volute tongue.

[0031] In some embodiments, the indoor heat exchanger includes at least two sections of heat exchangers, and the at least two sections of the heat exchangers are sequentially connected from top to bottom to form a half-enclosed structure, and the half-enclosed structure half-encloses the cross-flow fan. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] Figure 1 It is a structural schematic diagram of an embodiment of the utility model air duct machine;

[0033] Figure 2 This is a schematic structural diagram of an embodiment of the utility model duct machine from another perspective;

[0034] Figure 3 It is a front view of an embodiment of the utility model air duct machine;

[0035] Figure 4 yes Figure 3 Sectional view in the AA direction;

[0036] Figure 5 This is a schematic diagram of the connection between the electric auxiliary heating component and the heat exchanger component in one embodiment of the utility model air duct machine;

[0037] Figure 6 It is a structural schematic diagram of an embodiment of the utility model duct machine from another perspective;

[0038] Figure 7 yes Figure 6 A partial enlarged view of the G in the middle;

[0039] Figure 8 It is an exploded view of a fan assembly in one embodiment of the utility model duct fan;

[0040] Figures 9 to 11 It is a cross-sectional view of a body of an embodiment of the utility model air duct machine;

[0041] Fig.12 It is a structural schematic diagram of another embodiment of the utility model air duct machine;

[0042] Fig.13 It is a rear view of another embodiment of the utility model air duct machine;

[0043] Fig.14 yes Fig.13 Cross-sectional view in the BB direction;

[0044] Fig.15It is a cross-sectional view of the internal structure of another embodiment of the utility model duct machine along the horizontal direction;

[0045] Fig.16 It is a partial cross-sectional view of another embodiment of the utility model air duct machine;

[0046] Fig.17 It is a cross-sectional view of the internal structure of the prior art duct machine along the horizontal direction;

[0047] Fig.18 It is a schematic diagram of the cooperation between the cross-flow fan and the accommodation part in the prior art duct machine;

[0048] Fig.19 It is a partial cross-sectional view of the body of another embodiment of the duct machine of the utility model;

[0049] Fig. 20 This is a cross-sectional view of the body of another embodiment of the utility model duct machine Figure 1 ;

[0050] Fig.21 This is a partial cross-sectional view of the body of another embodiment of the utility model duct machine Figure 1 ;

[0051] Fig. 22 It is a cross-sectional view of a base in another embodiment of the utility model air duct machine;

[0052] Fig.23 It is a cross-sectional view of the internal structure of the body of another embodiment of the utility model air duct machine;

[0053] Fig.24 This is a schematic diagram of flow diversion of a guide plate in another embodiment of the utility model air duct machine;

[0054] Fig.25 This is a cross-sectional view of the body of another embodiment of the utility model duct machine Figure 2 ;

[0055] Fig.26 This is a partial cross-sectional view of the body of another embodiment of the utility model duct machine Figure 2 ;

[0056] Fig. 27 It is a front view of another embodiment of the utility model air duct machine;

[0057] Fig.28 It is a structural schematic diagram of an indoor heat exchanger in one embodiment of the utility model air duct machine;

[0058] Fig.29 yes Fig.28 A cross section of an indoor heat exchanger is shown;

[0059] Fig.30 Is has Fig.28 A cross-sectional view of an air duct unit of an indoor heat exchanger is shown;

[0060] Fig.31 Is has Fig.28 A partial cross-sectional view of an air duct unit of an indoor heat exchanger shown;

[0061] Fig.32 This is a cross section of the first section of the heat exchanger in one embodiment of the utility model air duct machine;

[0062] Fig.33 It is a velocity cloud diagram of the first section heat exchanger in one embodiment of the utility model air duct machine and the existing conventional direction;

[0063] Figure 34-35 It is a cross-sectional view along the width direction of the body of another embodiment of the utility model duct machine;

[0064] Figure 36-37 It is a partial cross-sectional view along the width direction of the body of another embodiment of the duct machine of the utility model;

[0065] Fig.38 It is the noise spectrum under different minimum gaps δ3 when L7=1000mm in one embodiment of the utility model duct machine;

[0066] Fig.39 It is a cross-sectional view along the length direction of the body of another embodiment of the duct machine of the utility model;

[0067] Fig.40 It is a schematic diagram of the installation of a duct machine in the prior art;

[0068] Fig.41 It is a cross-sectional view of an embodiment of the utility model of the air duct machine, in which a lower air inlet is provided at the bottom of the machine body;

[0069] Fig.42 It is a schematic diagram of the lower air inlet and the air conditioning air inlet in one embodiment of the utility model air duct machine;

[0070] Fig.43 It is a partial structural schematic diagram of an embodiment of the utility model of a duct machine in which a lower air inlet is provided on the bottom plate;

[0071] Figure 44-45 It is a cross-sectional view of an embodiment of the utility model of the air duct machine with a lower air inlet;

[0072] Fig.46 It is a schematic diagram of the air inlet of the air conditioner and the lower air inlet in one embodiment of the air duct machine of the utility model;

[0073] Fig.47It is an exploded view of the base and the bottom plate in one embodiment of the duct machine of the utility model.

[0074] In the above figures: body 10; accommodating chamber 101; air inlet 102; air outlet 103; top plate 104; bottom plate 105; first side plate 106; second side plate 107; guide plate 108; lower air inlet 109; air inlet filter assembly 1; heat exchanger assembly 2; indoor heat exchanger 21; reference heat exchanger 211; first section heat exchanger 212; first windward surface 2121; second windward surface 2122; second section heat exchanger 213; third section heat exchanger 214; fan assembly 3; cross-flow fan 3 1; end cover 311; drive motor 32; base 38; first mounting groove 381; volute 384; volute tongue 385; front volute tongue 3851; air guide surface 3852; accommodating portion 3861; air outlet portion 389; air outlet side 3891; air outlet duct 3892; electric auxiliary heating component 4; water receiving tray 5; avoidance portion 51; first water receiving tray 52; second baffle 521; retaining edge 522; second water receiving tray 53; first baffle 531; connecting portion 54; water receiving portion 55; temperature detection component 6; electronic control component 7. DETAILED DESCRIPTION

[0075] The present invention is described in detail below by way of exemplary embodiments. However, it should be understood that, without further description, elements, structures and features in one embodiment may also be beneficially combined in other embodiments.

[0076] Reference to "embodiments" in the present invention means that a particular feature, structure, or characteristic described in conjunction with the embodiments may be included in at least one embodiment of the present application. The appearance of the phrase in various locations in the specification does not necessarily refer to the same embodiment, nor is it an independent or alternative embodiment that is mutually exclusive with other embodiments. It is explicitly and implicitly understood by those of ordinary skill in the art that the embodiments described in the present application may be combined with other embodiments without conflict.

[0077] In the description of the present invention, it should be understood that the terms "center", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present invention.

[0078] The terms "first", "second" are used only for descriptive purposes and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Thus, the features defined as "first", "second" may explicitly or implicitly include one or more of the features.

[0079] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be the internal communication of 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.

[0080] In the present application, the central air-conditioning duct-type indoor unit (duct unit for short) belongs to an air conditioner, which includes a duct unit (i.e., the indoor unit of the air conditioner) and an outdoor unit (i.e., the outdoor unit of the air conditioner). The air conditioner performs a refrigeration cycle of the indoor unit by using a compressor, a condenser, an expansion valve, and an evaporator. The refrigeration cycle includes a series of processes involving compression, condensation, expansion, and evaporation, and supplies refrigerant to the conditioned and heat-exchanged air.

[0081] The air duct machine provided by the embodiment of the utility model can have various implementation forms.

[0082] in, Figure 1 to Figure 47 This is an illustrative embodiment of the duct air conditioner 100 of the utility model. The duct air conditioner 100 is arranged indoors, can be installed in the ceiling and on the ceiling, and can be used as a living room air conditioner, a curtain air conditioner, and a ceiling air conditioner for heat exchange with the indoor environment. The air conditioner can include an air conditioner outdoor unit, which is usually arranged outdoors to bring indoor heat to the outdoors.

[0083] refer to Figure 1 to Figure 3 The duct machine 100 includes a machine body 10. The machine body 10 can be installed in a suspended ceiling.

[0084] The machine body 10 has a top end and a bottom end, and the top end and the bottom end of the machine body 10 are two ends of the machine body 10 that are oppositely arranged in the vertical direction (the height direction of the machine body 10). The left side of the machine body 10 and the right side of the machine body 10 are two opposite sides in the length direction of the machine body 10, and the front side of the machine body 10 and the rear side of the machine body 10 are two opposite sides in the width direction of the machine body 10.

[0085] refer to Figure 4The housing 10 defines a receiving chamber 101 inside. The receiving chamber 101 is used to receive and fix various components in the duct machine 100, which can prevent foreign objects from colliding with various components in the housing 10, thereby improving the reliability of the duct machine 100 during transportation or installation.

[0086] In some embodiments of the present application, reference Figure 2 The body 10 may include an air conditioning air inlet 102 .

[0087] The air inlet 102 is in communication with the accommodating chamber 101 . The air inlet 102 serves as an inlet for the external air of the machine body 10 to flow in, allowing the indoor air to enter the accommodating chamber 101 through the air inlet 102 .

[0088] In some embodiments of the present application, the duct air conditioner 100 may include an air inlet filter assembly 1. The air inlet filter assembly 1 is installed at the air inlet 102 of the air conditioner, and can filter the indoor air entering the air inlet 102 of the air conditioner to prevent dust and impurities from entering the interior of the body 10.

[0089] In some embodiments of the present application, reference Figure 3 The body 10 may include an air conditioning outlet 103 .

[0090] The air conditioning outlet 103 is in communication with the accommodating chamber 101 , and serves as an outlet for the heat exchange airflow in the machine body 10 to flow out, allowing the airflow in the accommodating chamber 101 to flow out through the air conditioning outlet 103 .

[0091] The air inlet 102 and the air outlet 103 are respectively disposed at two ends of the machine body 10 in the width direction thereof. That is, the air inlet 102 and the air outlet 103 are disposed opposite to each other in the width direction of the machine body 10 .

[0092] refer to Figure 5 The body 10 may include a top plate 104 . The top plate 104 forms the top end of the body 10 .

[0093] The body 10 may include a bottom plate 105. The bottom plate 105 forms the bottom end of the body 10, and the top end and the bottom end are two opposite ends of the body 10 in the thickness direction thereof.

[0094] The machine body 10 may include two side panels. The two side panels are two opposite ends of the machine body 10 in its length direction and are connected to the left and right sides of the top plate 104. The two side panels are a first side panel 106 and a second side panel 107.

[0095] The machine body 10 may include a front panel. The front panel forms the front end of the machine body 10 and is provided with an air conditioning outlet 103 .

[0096] The machine body 10 may include a rear panel. The front panel forms the rear end of the machine body 10, and the rear panel is provided with an air-conditioning air inlet 102.

[0097] The top plate 104 , the bottom plate 105 , the two side plates, the front plate and the rear plate together form a receiving cavity 101 .

[0098] The top plate 104, the bottom plate 105, the side plates, the front plate and the rear plate may be connected in a separate manner or in an integrated manner.

[0099] In this embodiment, the two ends of the side panels in the width direction of the body 10 are bent and extended toward the opposite side to form a part of the front panel and the rear panel. Therefore, the top panel 104, the bottom panel 105 and the end portions surrounded by the two side panels form the air-conditioning inlet 102 located at the rear side of the body 10 and the air-conditioning outlet 103 located at the front side of the body 10. The two side panels are the first side panel 106 and the second side panel 107.

[0100] It should be noted that the direction described in the article is based on the direction in which the user faces the duct machine 100, wherein the side facing the user when the duct machine 100 is in use is defined as the front side, the opposite side is defined as the rear side, the left and right sides are distinguished by the direction in which the user faces the duct machine 100, and the upper and lower sides of the duct machine 100 when it is generally working normally are defined to distinguish the up and down.

[0101] The air duct machine 100 may include a heat exchanger assembly 2. The heat exchanger assembly 2 is disposed in the accommodating chamber 101. Figure 4 The heat exchanger assembly 2 may include an indoor heat exchanger 21. The indoor heat exchanger 21 is used to perform heat exchange with the air entering the body 10.

[0102] The air duct machine 100 may include a fan assembly 3. The fan assembly 3 is disposed in the accommodating chamber 101. Figure 4 The fan assembly 3 may include a cross-flow fan 31. Under the action of the cross-flow fan 31, the indoor air outside the body 10 enters the accommodating chamber 101 through the air conditioning inlet 102, and the air in the accommodating chamber 101 may flow along the air conditioning inlet 102 toward the air conditioning outlet 103.

[0103] When the duct air conditioner 100 is in operation, under the action of the cross-flow fan 31, the indoor air enters the accommodating chamber 101 through the air-conditioning air inlet 102, and the indoor air in the accommodating chamber 101 flows through the indoor-indoor heat exchanger 21 for heat exchange, and the heat exchanged air flows outwardly to the room through the air-conditioning air outlet 103, thereby making the air conditioner cool and heat, play the role of regulating the indoor temperature to achieve a comfortable temperature for the user.

[0104] In this embodiment, due to the characteristics of the cross-flow fan 31 , the cross-flow fan 31 is disposed close to the air outlet 103 of the air conditioner, and the indoor heat exchanger 21 is disposed close to the air inlet 102 of the air conditioner.

[0105] That is to say, the cross-flow fan 31 is located between the air-conditioning outlet 103 and the indoor heat exchanger 21 , and the cross-flow fan 31 rotates to introduce indoor air into the machine body 10 from the air-conditioning inlet 102 , and after heat exchange in the indoor heat exchanger 21 , the air-conditioned wind is formed and delivered out from the air-conditioning outlet 103 .

[0106] The cross-flow fan 31 is extended along the length direction of the machine body 10. That is, the length direction of the machine body 10 is the axial direction of the cross-flow fan 31. Since the cross-flow fan 31 is small in size, the volume of the duct machine 100 is further reduced, the depth of the ceiling is reduced, the narrow depth requirement is met, the problem of the oppressive feeling in the room is solved, and the aesthetics of the room is improved.

[0107] In this embodiment, the indoor heat exchanger 21 can be a multi-stage heat exchanger. The indoor heat exchanger 21 includes a multi-stage heat exchanger, so that the indoor heat exchanger 21 is a semi-enclosed structure, and part of the cross-flow fan 31 is arranged in the semi-enclosed structure of the indoor heat exchanger 21, so that the cross-flow fan 31 and the indoor heat exchanger 21 are originally separated and arranged to overlap the cross-flow fan 31 and the indoor heat exchanger 21, and the space occupied by the indoor heat exchanger 21 and the cross-flow fan 31 is greatly reduced under the condition that the volume of the cross-flow fan 31 and the indoor heat exchanger 21 remains unchanged.

[0108] The fan assembly 3 may include a driving motor 32. The driving motor 32 is connected to one end of the cross-flow fan 31 in the axial direction to drive the cross-flow fan 31 to rotate.

[0109] In some embodiments of the present application, the air duct unit 100 may include a base 38. The base 38 is disposed in the accommodating cavity 101 to install the fan assembly 3 and the heat exchanger assembly 2.

[0110] In some embodiments of the present application, referring to 5, the duct machine 100 may include an electric auxiliary heating component 4. The electric auxiliary heating component 4 is detachably connected to the heat exchanger component 2 and is used to heat the airflow in the machine body 10.

[0111] The duct machine 100 may include a temperature detection component 6. Figure 6 , Figure 7 The temperature detection component 6 is provided on the machine body 10 to detect the indoor environment temperature. The temperature detection component 6 is connected to the electric control board in communication to transmit the detected indoor environment temperature to the electric control board, so as to control various actions of the subsequent air duct machine 100.

[0112] In some embodiments of the present application, reference Figure 8The base 38 is provided with a first mounting groove 381 at one end in the length direction thereof. The first mounting groove 381 is located at one end in the axial direction of the cross-flow fan 31 .

[0113] The driving motor 32 is installed in the first installation groove 381 , and the output shaft of the driving motor 32 is connected to the shaft sleeve of the cross-flow fan 31 through a fixing screw to drive the cross-flow fan 31 to rotate.

[0114] In some embodiments of the present application, the air duct machine 100 may include a water receiving tray 5. The water receiving tray 5 is disposed at the bottom of the accommodating chamber 101 and is used to receive condensed water flowing down from the indoor heat exchanger 21 when the air duct machine 100 is working. The water receiving tray 5 is provided with a drain port for discharging the condensed water in the water receiving tray 5 out of the air duct machine 100.

[0115] The air conditioner outer unit may include an outdoor housing. An outdoor heat exchange air duct may be provided in the outdoor housing. The outdoor housing may include an outdoor air inlet. The outdoor air inlet may be connected to the outdoor heat exchange air duct. The outdoor air inlet may be used to introduce outdoor air into the outdoor heat exchange air duct.

[0116] The outdoor housing may include an outdoor air outlet, which may be connected to the outdoor heat exchange air duct, and may be used to lead the air in the outdoor heat exchange air duct out of the outdoor heat exchange air duct.

[0117] The air conditioner outdoor unit may include an outdoor heat exchanger. The outdoor heat exchanger may be arranged in an outdoor heat exchange air duct. The air conditioner outdoor unit may include an outdoor fan. The outdoor fan may be arranged in the outdoor heat exchange air duct. The rotation of the outdoor fan causes outdoor air to enter the heat exchange air duct from the outdoor air inlet to exchange heat with the outdoor heat exchanger, and the outdoor air after heat exchange flows out of the outdoor heat exchange air duct from the outdoor air outlet.

[0118] The air conditioner may include a compressor. The compressor is disposed in an outdoor heat exchange air duct. The compressor compresses a low-temperature and low-pressure refrigerant gas to discharge a high-temperature and high-pressure refrigerant gas, and the discharged refrigerant gas flows into a condenser.

[0119] The air conditioner may include a throttling device. The throttling device is used for throttling. The throttling device may be provided in the duct unit 100 or the air conditioner outdoor unit.

[0120] The air conditioner performs the refrigeration cycle of the air conditioner by using a compressor, a condenser, a throttling device and an evaporator. The refrigeration cycle includes a series of processes involving compression, condensation, expansion and evaporation, and supplies refrigerant to the air that has been conditioned and heat exchanged.

[0121] The condenser condenses the compressed refrigerant into liquid phase, and the heat is released to the surrounding environment through the condensation process.

[0122] The throttling device expands the high-temperature and high-pressure liquid refrigerant condensed in the condenser into a low-pressure liquid refrigerant. The throttling device may be an expansion valve.

[0123] The evaporator evaporates the refrigerant expanded in the throttling device and returns the refrigerant gas in a low temperature and low pressure state to the compressor.

[0124] The evaporator can achieve a refrigeration effect by utilizing the latent heat of evaporation of the refrigerant to exchange heat with the material to be cooled. In the whole cycle, the air conditioner can adjust the temperature of the indoor space.

[0125] Among the indoor heat exchanger 21 and the outdoor heat exchanger, one is a condenser and the other is an evaporator. When the indoor heat exchanger 21 is used as a condenser, the air conditioner is used as a heater in the heating mode, and when the indoor heat exchanger 21 is used as an evaporator, the air conditioner is used as a cooler in the cooling mode.

[0126] The duct machine 100 may include an electric control component 7. The electric control component 7 may include an electric control board, and the electric control board is electrically connected to the electrical components inside the machine body 10 through an electric control line.

[0127] It can be understood that the electric control board is configured to be electrically connected to the above-mentioned compressor, expansion valve and cross-flow fan 31 at least through electric control, so as to control at least the compressor, expansion valve and cross-flow fan 31, thereby controlling the operation of the entire duct machine 100 and realizing various predetermined functions of the air conditioner.

[0128] The electric control board can transmit signals with the wire controller or remote controller via a communication line. The wire controller or remote controller sends an air conditioning control signal to control the air conditioner, and the electric control board receives the air conditioning control signal to control the duct air conditioner 100 to work.

[0129] refer to Figure 8 to Figure 11 In some other embodiments, the fan assembly 3 may include a volute tongue 385, and the volute tongue 385 is disposed in the body 10. The volute tongue 385 is substantially in a tongue-shaped structure.

[0130] The fan assembly 3 may include a volute 384 , which is disposed in the body 10 and above the volute tongue 385 .

[0131] An air duct is formed between the volute 384 and the volute tongue 385 . The volute 384 forms the top wall of the air duct, the volute tongue 385 forms the bottom wall of the air duct, and the cross-flow fan 31 is located in the air duct between the volute 384 and the volute tongue 385 .

[0132] refer to Fig. 9 The volute tongue 385 may include a front volute tongue 3851, and the front volute tongue 3851 is arranged toward the cross-flow fan 31. In other words, the front volute tongue 3851 is the windward surface of the volute tongue 385.

[0133] In this embodiment, the front volute tongue 3851 is arranged in an arc shape. By arranging the front volute tongue 3851 in an arc shape, when an eccentric vortex is generated, the airflow of the eccentric vortex can pass through the front volute tongue 3851 more smoothly, thereby reducing wind resistance.

[0134] That is to say, the volute tongue 385 is provided with an arc surface on the side close to the cross-flow fan 31, and the noise generated by the airflow in the air duct can be reduced by providing the arc surface.

[0135] Continue to refer Fig. 9 The indoor heat exchanger 21 may include at least two sections of heat exchangers, wherein the section of the heat exchanger closest to the front volute tongue 3851 among the at least two sections of heat exchangers is defined as the reference heat exchanger 211 .

[0136] The direction of the perpendicular line from the center O of the cross-flow fan 31 to the reference heat exchanger 211 is defined as the X direction, the direction rotated 90° from the X direction toward the air-conditioning outlet 103 is defined as the Y direction, the point at which the front volute tongue 3851 is closest to the cross-flow fan 31 is defined as point A1, and the point on the reference heat exchanger 211 in the Y direction that is farthest from the center O is defined as point B.

[0137] Define the orthographic projection of point A1 on the Y axis as point A1', the orthographic projection of point O on the Y axis as point O', and the orthographic projection of point B on the Y axis as point B'. On the Y axis, point A1' is between point O' and point B'.

[0138] The duct air conditioner provided in this embodiment reasonably arranges the relative positions of the cross-flow fan 31, the indoor heat exchanger 21 and the front volute tongue 3851 by arranging the point A1′, the orthographic projection of point A1 on the Y-axis, between the point O′, the orthographic projection of point O on the Y-axis and the point B′, the orthographic projection of point B on the Y-axis, so that the cross-flow air duct can achieve a larger air volume and stronger wind resistance resistance.

[0139] In some other embodiments of this application, continue to refer to Fig. 9 , the indoor heat exchanger 21 may include two sections of heat exchangers, and a vertical line from point A1 to the reference heat exchanger 211 is defined as a first vertical line P. Point B is located on the side of the first vertical line P away from the cross-flow fan 31. By setting point B on the side of the first vertical line where point A1 is located away from the cross-flow fan 31, the relative positions of the cross-flow fan 31, the indoor heat exchanger 21 and the front volute tongue 3851 are reasonably set, so that the cross-flow air duct can achieve a larger air volume and stronger wind resistance performance.

[0140] The duct air conditioner provided in this embodiment, point B is located on the side of the first vertical line P away from the cross-flow fan 31. The duct air conditioner and the duct air conditioner with point B located on the side of the first vertical line close to the cross-flow fan 31 are actually tested together. At the same speed, the air volume of the duct air conditioner with point B located on the side of the first vertical line away from the cross-flow fan 31 is 9% higher than that of the duct air conditioner with point B located on the side of the first vertical line close to the cross-flow fan 31, and the wind resistance performance is improved by 4 layers of 40-mesh filters.

[0141] In some other embodiments of the present application, the volute tongue 385 may include an air guide surface 3852. The air guide surface 3852 is arranged relative to the front volute tongue 3851 toward the air outlet 103 of the air conditioner to achieve a linear guiding effect on the air flow in the air duct, so as to further avoid the problem of air volume loss at the air outlet 103 of the air conditioner during the operation of the air duct machine.

[0142] In some other embodiments of the present application, the air duct unit may include a water receiving pan 5 , which is located below the indoor heat exchanger 21 and is used to receive condensed water dripping from the indoor heat exchanger 21 .

[0143] In this embodiment, the water receiving tray 5 and the volute tongue 385 are an integrally formed structure. The bottom wall of the water receiving tray 5 and the front volute tongue 3851 are connected by a water retaining portion.

[0144] In some other embodiments of this application, refer to Fig.10 , in the Y direction, the distance between point A1 and point B is d. 10mm≤d. d≤18mm.

[0145] The distance dimension d between point A1 and point B cannot be too large. If it is too large, the wall surface (water retaining portion) between point A1 and point B in the air duct will block the airflow of the reference heat exchanger 211. In order not to block the airflow of the reference heat exchanger 211, the distance dimension d is set to be no greater than the first parameter value. For example, the first parameter value can be 18 mm, 17.5 mm, or 17 mm. Consider selecting a suitable and specific parameter in the specific design.

[0146] The distance dimension d between point A1 and point B cannot be too small, otherwise it will not be conducive to improving the wind resistance performance. In order to improve the wind resistance performance, the distance dimension d is set to be not less than the second parameter value. For example, the second parameter value can be 10 mm, 10.5 mm, or 11 mm. Consider selecting a suitable and specific parameter in the specific design.

[0147] In some other embodiments of the present application, at least two sections of heat exchangers are plate heat exchangers. At least two plate heat exchangers are connected in sequence from top to bottom to form a half-enclosed structure. The half-enclosed structure has an opening for the cross-flow fan 31. The indoor heat exchanger 21 under this structure at least partially surrounds the outer periphery of the cross-flow fan 31, thereby improving the heat exchange efficiency and reducing the volume of the ducted air conditioner.

[0148] Continue to refer Fig.10 The indoor heat exchanger 21 may include two sections of heat exchangers, namely, a reference heat exchanger 211 and a second section of heat exchanger 213. The second section of heat exchanger 213 is located above the reference heat exchanger 211, and one end of the second section of heat exchanger 213 is connected to one end of the reference heat exchanger 211 to form a V-shaped structure with an opening toward the cross-flow fan 31.

[0149] In some other embodiments of the present application, the minimum distance between the reference heat exchanger 211 and the cross-flow fan 31 is δ5, wherein δ5≥15mm and δ5≤20mm.

[0150] The minimum distance δ5 cannot be too small. If it is too small, the distance between the reference heat exchanger 211 and the crossflow fan 31 will be too small, and the airflow driven by the crossflow fan 31 will impact the reference heat exchanger 211, causing heterogeneous frequency noise and increasing the noise of the duct machine. In order to improve the sound quality level, the minimum distance δ5 is set to be not less than the third parameter value. For example, the third parameter value can be 15mm, 15.5mm, or 16mm. Consider selecting a suitable and specific parameter in the specific design.

[0151] The minimum distance δ5 cannot be too large, otherwise it will be unfavorable for air intake. In order to increase the air intake volume, the minimum distance δ5 is set to be no greater than the fourth parameter value. For example, the fourth parameter value can be 20 mm, 19.5 mm, or 19 mm. Consider selecting a suitable and specific parameter in the specific design.

[0152] In some other embodiments of the present application, the reference heat exchanger 211 is arranged at an angle to the horizontal plane, and the height of the free end of the reference heat exchanger 211 is lower than the height of the connection end of the reference heat exchanger 211 .

[0153] The free end of the reference heat exchanger 211 (the end not connected to other sections of the heat exchanger) is closer to the air conditioning outlet 103 than its connection end. The height of the free end of the reference heat exchanger 211 is lower than the height of the connection end of the reference heat exchanger 211, so that the condensed water on the indoor heat exchanger 21 flows to the free end of the reference heat exchanger 211.

[0154] In some other embodiments of the present application, the front volute tongue 3851 is arranged in an arc shape.

[0155] refer to Fig.11 In the cross section of the cross flow fan 31, the front volute tongue 3851 is spaced apart from the cross flow fan 31. The distance between the point A1 and the cross flow fan 31 is the minimum distance δ1. δ1≥0.03D. δ1≤0.045D.

[0156] The cross-flow fan 31 has end covers 311 at both ends, and the cross-flow fan 31 has a plurality of intermediate plates arranged at intervals in the axial direction thereof, that is, the plurality of intermediate plates are arranged at intervals between the two end covers 311. The intermediate plates are in a circular ring shape.

[0157] It should be noted that the outer edge diameter of the cross-flow fan 31 described herein is the outer edge diameter of the middle section plate.

[0158] The minimum distance δ1 cannot be too large, otherwise it will cause serious airflow leakage and reduced air volume. In order to ensure air volume performance, the minimum distance δ1 is set to be no greater than the fifth parameter value. For example, the fifth parameter value can be 0.045D, 0.044D, or 0.042D. Consider selecting a suitable and specific parameter in the specific design.

[0159] The minimum distance δ1 cannot be too small. If it is too small, the noise value will be too high, and there is a risk of collision between the crossflow fan 31 and the front volute tongue 3851. In order to improve the sound quality of the duct machine, improve the working efficiency of the crossflow fan 31, and reduce noise, the minimum distance δ1 is set to be not less than the sixth parameter value. For example, the sixth parameter value can be 0.03D, 0.032D, or 0.034D. Consider selecting a suitable and specific parameter in the specific design.

[0160] In some other embodiments of the present application, the distance between point A1 and the cross-flow fan 31 is the minimum distance δ1. 0.03D≤δ1≤0.045D.

[0161] The minimum distance δ1 between the front volute tongue 3851 and the cross-flow fan 31 is set within a reasonable range to ensure the air intake of the gap while avoiding serious whistling noise. At the same time, the cross-flow fan 31 is prevented from shaking and bumping against the front volute tongue 3851 during transportation.

[0162] In some other embodiments of the present application, the maximum distance between the front volute tongue 3851 and the cross-flow fan 31 is δ2, where δ2≥0.06D, δ2≤0.075D, and D is the diameter of the outer edge of the cross-flow fan 31.

[0163] The maximum distance δ2 cannot be too small. If the maximum distance δ2 is too small, the eddy noise generated by the airflow will increase significantly. In order to improve the sound quality level of the duct air conditioner, the maximum distance δ2 is set to be no less than the seventh parameter value. For example, the seventh parameter value can be 0.06D, 0.063D, or 0.065D. Consider selecting a suitable and specific parameter in the specific design.

[0164] The maximum distance δ2 cannot be too large. When the maximum distance δ2 is too large, the return air may increase at a low speed of the cross-flow fan 31, resulting in flow loss and serious leakage on the air guide side, which may lead to a decrease in the air output. In order to reduce air leakage and increase the air output, the maximum distance δ2 is set to be no greater than the eighth parameter value. For example, the eighth parameter value may be 0.075D, 0.073D, or 0.071D. Consider selecting a suitable and specific parameter in the specific design.

[0165] In some embodiments of the present application, the volute tongue 385 may include a wind guide surface 3852. Fig.11 The air guide surface 3852 is arranged relative to the front volute tongue 3851 and close to the air-conditioning outlet 103 .

[0166] Among them, the air guide surface 3852 is set toward the air-conditioning outlet 103 to achieve a linear guiding effect on the air flow in the air duct, so as to further avoid the problem of air volume loss at the air-conditioning outlet 103 during the operation of the air duct machine.

[0167] In some embodiments of the present application, the air guide surface 3852 and the front volute tongue 3851 are connected by an arc transition to form the volute tongue 385. This setting can make the connection between the front volute tongue 3851 and the air guide surface 3852 smoother, and the air flow transition is more natural and smooth, thereby further improving the air flow stability of the cross-flow fan 31.

[0168] refer to Figure 12 to Figure 16 , Fig.19 In some embodiments of the present application, the air duct may include an air outlet duct 3892 . The air outlet duct 3892 is formed between the cross-flow fan 31 and the air outlet 103 of the air conditioner.

[0169] Specifically, under the action of the cross-flow fan 31, indoor air enters the body 10 through the air conditioning inlet 102, enters the air outlet duct 3892 after heat exchange through the indoor heat exchanger 21, and the heat exchange airflow in the air outlet duct 3892 is output to the room through the air conditioning outlet 103.

[0170] In some embodiments of the present application, the fan assembly 3 may include two air outlets 389. Fig.14 The two air outlet portions 389 respectively form two ends of the air outlet duct 3892 in the length direction of the body 10.

[0171] The top end of the air outlet portion is connected to the volute tongue, and the bottom end of the air outlet portion is connected to the volute tongue.

[0172] The side of the two air outlet portions 389 facing each other is an air outlet side surface 3891. The air outlet side surface 3891 has an air inlet end and an air outlet end. In this embodiment, the air inlet end is closer to the cross-flow fan 31 than the air outlet end.

[0173] Continue to refer Fig.14 In some embodiments of the present application, an air outlet end of at least one air outlet side surface 3891 is closer to the center of the air-conditioning outlet 103 relative to the air inlet end.

[0174] Specifically, the outlet end of at least one outlet side surface 3891 is closer to the center of the air-conditioning outlet 103 relative to the inlet end, so that the air flow channel between at least one outlet side surface 3891 and the air-conditioning outlet 103 is a constricted structure. In other words, in the length direction of the body 10, there is a distance dimension between the inlet end and the outlet end of at least one outlet side surface 3891.

[0175] In this embodiment, the air outlet end of at least one air outlet side surface 3891 is arranged to be close to the center of the air-conditioning outlet 103 relative to the air inlet end, so that the air outlet end of at least one air outlet side surface 3891 shrinks from the air inlet end toward the mid-vertical line of the air-conditioning outlet 103. On the one hand, the speed of the air outlet airflow in the end area of ​​the cross-flow fan 31 corresponding to at least one air outlet side surface 3891 is improved. On the other hand, a forward pressure gradient is formed along the direction of the air outlet airflow on at least one air outlet side surface 3891, which can effectively suppress the airflow separation and return air phenomenon that may occur on the air outlet side surface 3891, enhance the anti-wind resistance performance, and avoid the generation of surging and return air phenomenon.

[0176] In some embodiments of the present application, the air outlet ends of the two air outlet side surfaces 3891 are closer to the center of the air-conditioning outlet 103 relative to the air inlet end.

[0177] refer to Fig.15 The air outlet ends of the two air outlet side surfaces 3891 are arranged to be close to the center of the air-conditioning air outlet 103 relative to the air inlet end, so that the air outlet ends of the two air outlet side surfaces 3891 shrink from the air inlet end to the mid-vertical line of the air-conditioning air outlet 103, so that a shrinkage structure is formed between the two air outlet side surfaces 3891 in the direction from the cross-flow fan 31 to the air-conditioning air outlet 103.

[0178] Specifically, the air outlet ends of the two air outlet sides 3891 are arranged to be close to the center of the air-conditioning outlet 103 relative to the air inlet end. On the one hand, the speed of the air outlet air flow in the two end areas of the cross-flow fan 31, that is, the wind speed at both ends of the air duct machine, is increased. On the other hand, a forward pressure gradient is formed along the direction of the air outlet air flow on the two air outlet sides 3891, thereby enhancing the anti-wind resistance performance and avoiding surge and backflow phenomena.

[0179] In some embodiments of the present application, the air outlet portion 389 may be an air outlet side plate whose air outlet end is bent or inclined relative to the air inlet end toward the mid-perpendicular line of the air-conditioning outlet 103 .

[0180] In some embodiments of the present application, in the width direction of the machine body 10, the distance between the two ends of the air outlet side surface 3891 is L3, where L3≥10mm and L3≤15mm.

[0181] It can be understood that the distance dimension L3 between the two ends of the air outlet side surface 3891 in the width direction of the body 10 can be determined by the length dimension of the air outlet duct 3892 .

[0182] The distance dimension L3 cannot be too large, otherwise the length dimension of the air outlet duct 3892 will be too large, thereby increasing the width dimension of the body 10. In order to reduce the volume of the duct machine, the distance dimension L3 is set to be no greater than the ninth parameter value. For example, the ninth parameter value can be 15mm, 14.5mm, or 14mm. Consider selecting a suitable and specific parameter in the specific design.

[0183] The distance dimension L3 cannot be too small. If it is too small, the length dimension of the air outlet duct 3892 will be too small, affecting the air volume and wind resistance performance of the duct. In order not to reduce the air volume of the duct, the distance dimension L3 is set to be not less than the tenth parameter value. For example, the tenth parameter value can be 10mm, 10.5mm, or 11mm. Consider selecting a suitable and specific parameter in the specific design.

[0184] In some embodiments of the present application, in the width direction of the body 10, the distance between the two ends of the air outlet side surface 3891 is L3. 10mm≤L3≤15mm.

[0185] In this embodiment, by setting the distance dimension L3 within a reasonable range, the length dimension of the air outlet duct 3892 is within a reasonable range, thereby reducing the volume of the duct unit while avoiding affecting the air volume and wind resistance performance.

[0186] In some embodiments of the present application, reference Fig.16 In the length direction of the machine body 10 , the distance between the two ends of the air outlet side surface 3891 is L4. L4≥0.5D. L4≤D. Wherein, D is the diameter of the outer edge of the cross-flow fan 31 .

[0187] The distance dimension L4 cannot be too large, otherwise it will affect the normal air flow velocity in the middle of the cross-flow fan 31. In order to reduce the volume of the duct machine and not affect the air flow in the middle area of ​​the cross-flow fan 31, the distance dimension L4 is set to be no greater than the eleventh parameter value. For example, the eleventh parameter value can be D, 0.95D, or 0.9D. Consider selecting a suitable and specific parameter in the specific design.

[0188] The distance dimension L4 cannot be too small, otherwise it cannot play the role of gathering the low-speed airflow at one end of the cross-flow fan 31. In order to make the wind-out side surface 3891 play the role of the low-speed airflow at one end of the cross-flow fan 31, the distance dimension L4 is set to be not less than the twelfth parameter value. For example, the twelfth parameter value can be 0.5D, 0.55D, or 0.6D. Consider selecting a suitable and specific parameter in the specific design.

[0189] In some embodiments of the present application, in the length direction of the machine body 10, the distance dimension between the two ends of the air outlet side surface 3891 is L4. 0.5D≤L4≤D. By setting the distance dimension L4 within a reasonable range between 0.5D and D, on the one hand, the air outlet side surface 3891 can play a role in gathering the low-speed airflow at the end of the cross-flow fan 31, and on the other hand, it will not affect the normal flow rate of the airflow in the middle area of ​​the cross-flow fan 31, thereby increasing the wind speed at the end of the duct machine and improving the overall wind resistance performance.

[0190] In some embodiments of the present application, in a horizontal cross section of the air outlet portion 389, the air outlet side surface 3891 is arranged in a curve, and the curve (contour line) of the air outlet side surface 3891 is a single-segment curve or a multi-segment curve.

[0191] Specifically, a single-segment curve can be an arc or a straight line. Fig.15 , the curve of the air outlet side surface 3891 is an arc, that is, when the air outlet side surface 3891 is an arc surface, the arc surface protrudes toward the outside of the air outlet duct. When the curve of the air outlet side surface 3891 is a straight line, the air outlet side surface 3891 is a plane inclined toward the mid-perpendicular line of the air outlet 103 from the cross-flow fan 31 to the air-conditioning outlet 103.

[0192] The multiple line segments in the multi-segment curve can be continuous curve segments or straight line segments. In other words, the curve of the air outlet side surface 3891 can be a continuous curve or multiple straight lines, so that the air outlet side surface 3891 bends from the direction of the cross-flow fan 31 to the air-conditioning outlet 103 to the mid-perpendicular direction of the air-conditioning outlet 103.

[0193] In some embodiments of the present application, the outlet portion 389 forms a tapered structure between the outlet side surface 3891 and the center line of the air-conditioning outlet 103 in the horizontal cross section. This arrangement effectively forms a pressure gradient along the outlet airflow direction on the side surface, thereby effectively suppressing the airflow separation and return air phenomenon that may occur in the side area.

[0194] In some embodiments of the present application, the fan assembly 3 may include two accommodating portions 3861 arranged opposite to each other, and the two ends of the cross-flow fan 31 are respectively placed in the two accommodating portions 3861. The accommodating portions 3861 are cylindrical groove structures.

[0195] In the related art, reference Fig.17 , Fig.18 In order to improve the wind resistance performance of the air duct, the cross-flow fan 31 is installed by wrapping the roots of both ends of the cross-flow fan 31 with the accommodating portion 3861. The depth of the accommodating portion 3861 is L5, and the actual insertion depth of the cross-flow fan 31 is L6. Although this setting can improve the wind resistance performance of the duct machine, it also directly sacrifices the working capacity of the cross-flow fan 31 with a length of 2*L6, which is not conducive to fully demonstrating the capacity of the cross-flow fan 31.

[0196] In order to solve the above technical problems, in this embodiment, the accommodating portion 3861 is disposed around the outer circumference of the end cover, and a portion of the end cover is extended into the accommodating portion 3861 in the axial direction of the cross-flow fan 31 .

[0197] That is to say, reference Fig.19 In this embodiment, only the end cover parts at both ends of the cross-flow fan 31 are inserted into the accommodating portion 3861, that is, the accommodating portion 3861 wraps the end of the end cover 311 away from the opposite end cover 311, ensuring that the blades of the cross-flow fan 31 are all located in the air duct, thereby ensuring that all the blades of the cross-flow fan 31 can work normally.

[0198] refer to Fig.12 , Fig.14 In this embodiment, the air inlet ends of the two air outlet side surfaces 3891 are respectively connected to the two accommodating portions 3861, and the air outlet ends of the two air outlet side surfaces 3891 are bent relative to the air inlet ends toward the mid-perpendicular direction of the air conditioning outlet 103, so that the two air outlet side surfaces 3891 can timely gather the airflow at the end area of ​​the cross-flow fan 31. The air outlet ends of the two air outlet side surfaces 3891 are respectively connected to the two side walls in the length direction of the air conditioning outlet 103.

[0199] refer to Figure 20 to Figure 26 In some other embodiments of the present application, the indoor heat exchanger 21 may include at least two sections of heat exchangers. The at least two sections of heat exchangers are sequentially connected from top to bottom to form a half-enclosed structure. The half-enclosed structure half-encloses the cross-flow fan 31.

[0200] Among them, a heat exchanger relatively close to the bottom plate 105 among the at least two heat exchangers is defined as a first heat exchanger 212 .

[0201] refer to Fig. 20 The first stage heat exchanger 212 is located below the cross-flow fan 31 .

[0202] In some embodiments of the present application, the duct unit may include a water receiving tray 5. The water receiving tray 5 is disposed on the bottom plate 105, and the water receiving tray 5 is located below the indoor heat exchanger 21, and is used to receive condensed water dripping from the indoor heat exchanger 21.

[0203] The first stage heat exchanger 212 and the plane where the bottom plate 105 is located form an angle with the opening facing the air inlet 102 of the air conditioner. The first stage heat exchanger 212 is a plate-shaped heat exchanger.

[0204] Specifically, an angle is formed between the first section heat exchanger 212 and the plane where the bottom plate 105 is located, so that the first section heat exchanger 212 is tilted, and the opening of the angle faces the air inlet 102 of the air conditioner, so that the free end of the first section heat exchanger 212 is lower than its connection end. When the duct mechanism is in cooling operation, the condensed water on the indoor heat exchanger 21 can be collected at its free end and drip into the water receiving tray 5.

[0205] In the related art, there is a technical solution in which the first section heat exchanger 212 is arranged in parallel with the bottom plate 105, which will cause the condensed water on the indoor heat exchanger 21 to gather on the first section heat exchanger 212, which is not conducive to improving the heat exchange efficiency. In addition, there is also a technical solution in which the first section heat exchanger 212 is arranged obliquely. In this solution, when the air duct machine is in refrigeration operation, the condensed water on the indoor heat exchanger 21 gradually flows down along the evaporator, and finally converges in the area of ​​the first section heat exchanger 212 close to the water receiving pan 5, causing the air intake resistance of the area to increase; on the other hand, the first section heat exchanger 212 is plate-shaped. Due to the presence of the water receiving pan 5, the air intake height of the first section heat exchanger 212 on the side away from the air inlet 102 of the air conditioner is extremely small, which will have a negative impact on the air intake volume of the side area, not only affecting the air intake uniformity of the first section heat exchanger 212 and its heat exchange efficiency, but also the air intake effect of the area is highly related to the wind resistance performance of the air duct machine. Insufficient air intake will also significantly reduce the wind resistance performance of the air duct machine, and the user experience is poor.

[0206] In order to solve the above technical problems, refer to Fig. 20 , the minimum distance between the first stage heat exchanger 212 and the water receiving pan 5 is H1. H1≥6mm.

[0207] The minimum distance between the first-stage heat exchanger 212 and the water receiving pan 5 is the vertical distance between the free end of the first-stage heat exchanger 212 and the water receiving pan 5 .

[0208] The duct air conditioner provided in this embodiment, by setting the first section heat exchanger 212 to form an angle with the bottom plate 105, allows the condensed water on the indoor heat exchanger 21 to flow from the free end of the first section heat exchanger 212 to the water receiving pan 5, thereby facilitating the collection of the condensed water; at the same time, the minimum distance between the first section heat exchanger 212 and the water receiving pan 5 is set to be no less than 6 mm, thereby increasing the air intake volume of the area of ​​the indoor heat exchanger 21 closest to the water receiving pan 5 (the free end of the first section heat exchanger 212), thereby improving the wind resistance resistance of the duct air conditioner, improving the air intake uniformity of the first heat exchanger, improving the heat exchange efficiency of the first heat exchanger, and then improving the heat exchange efficiency of the indoor heat exchanger 21.

[0209] In some embodiments of the present application, the first section heat exchanger 212 extends obliquely from top to bottom toward the direction close to the air outlet 103 of the air conditioner. The minimum distance between the first section heat exchanger 212 and the water receiving tray 5 is H1. H1 ≥ 6 mm.

[0210] Specifically, the first section heat exchanger 212 extends obliquely from top to bottom toward the direction close to the air outlet 103 of the air conditioner, so that the free end of the first section heat exchanger 212 is lower than the connection end of the first heat exchanger. The minimum distance between the first section heat exchanger 212 and the water receiving pan 5 is H1, that is, the vertical distance between the free end of the first section heat exchanger 212 and the water receiving pan 5 is the minimum distance H1.

[0211] The duct air conditioner provided in this embodiment tilts the first heat exchanger 212 so that condensed water on the indoor heat exchanger 21 can flow from the free end of the first heat exchanger 212 to the water receiving pan 5, thereby facilitating the collection of condensed water. At the same time, the minimum distance between the first heat exchanger 212 and the water receiving pan 5 is set to be no less than 6 mm, thereby increasing the air intake volume of the area of ​​the indoor heat exchanger 21 closest to the water receiving pan 5 (the free end of the first heat exchanger), thereby improving the wind resistance performance of the duct air conditioner, improving the air intake uniformity of the first heat exchanger, and improving the heat exchange efficiency of the indoor heat exchanger 21.

[0212] In order to further increase the air intake volume of the first stage heat exchanger 212 near the water receiving tray 5 and further improve the wind resistance performance of the air duct unit, in some embodiments of the present application, the air duct unit may include a guide plate 108.

[0213] refer to Figure 20 to Figure 23 The guide plate 108 is located between the first stage heat exchanger 212 and the water receiving tray 5 . The guide plate 108 extends along the length direction of the machine body 10 .

[0214] In this embodiment, two ends of the guide plate 108 in the length direction are connected to two side walls in the length direction of the air duct. In the cross section of the guide plate 108, the guide plate 108 has an air inlet end and an air outlet end.

[0215] The height of the air inlet end of the guide plate 108 is greater than the height of the air outlet end of the guide plate 108. In other words, the guide plate 108 extends from the back to the front in a direction close to the bottom plate 105.

[0216] In this embodiment, reference Fig.24By setting the guide plate 108, the air flow of the first stage heat exchanger 212 is forced to be split. The air outlet end is spaced apart from the water receiving tray 5, so that the air flow of the first stage heat exchanger 212 of the guide plate 108 is divided into two streams, one of which flows from the top of the guide plate 108 to the top of the first stage heat exchanger 212, and the other flows from the bottom of the guide plate 108 to the bottom of the first stage heat exchanger 212.

[0217] This forced diversion method ensures that sufficient airflow flows through the area where the free end of the first heat exchanger 212 is located. On the one hand, it ensures the uniformity of the overall air intake of the first heat exchanger 212. On the other hand, it avoids the wind resistance problem caused by insufficient air intake in the area where the free end of the first heat exchanger 212 is located, thereby improving the wind resistance performance.

[0218] In some embodiments of the present application, reference Fig.25 In the cross section of the indoor heat exchanger 21, the length dimension of the first section heat exchanger 212 is L1, and the length dimension of the guide plate 108 is L2.

[0219] In some embodiments of the present application, the ratio between L2 and L1 is m. 0.6≤m. m≤0.8.

[0220] In this embodiment, the ratio m between L2 and L1 is set to m≥0.6 to exert a forced diversion effect, and the ratio m is set to m≤0.8 to prevent the guide plate 108 from being too long and extending below the free end of the first section heat exchanger 212, affecting the air intake in this area.

[0221] The ratio m between L2 and L1 cannot be too small. If it is too small, the length L2 of the guide plate 108 will be too short, which will affect the forced diversion effect of the guide plate 108. In order to make the guide plate 108 play a forced diversion effect, the ratio m is set to be not less than the thirteenth parameter value. For example, the thirteenth parameter value can be 0.6, 0.63, or 0.65. Consider selecting a suitable specific parameter in the specific design.

[0222] The ratio m between L2 and L1 cannot be too large. If it is too large, the length L2 of the guide plate 108 will be too long. The too long guide plate 108 will extend below the free end of the first heat exchanger 212, affecting the air intake. In order to ensure that there is sufficient air intake airflow to the free end of the first heat exchanger, the ratio m is set to be no greater than the fourteenth parameter value. For example, the fourteenth parameter value can be 0.8, 0.78, or 0.75. Consider selecting a suitable specific parameter in the specific design.

[0223] In some embodiments of the present application, the ratio between L2 and L1 is m, wherein 0.6≤m≤0.8.

[0224] In this embodiment, the ratio m between L2 and L1 is set to any value between 0.6 and 0.8, so that the length of the guide plate 108 is set within a reasonable range, ensuring the forced diversion effect of the guide plate 108, ensuring that there is sufficient incoming air flow to the lower part of the first end heat exchanger, and improving the wind resistance performance.

[0225] In some embodiments of the present application, the minimum distance between the guide plate 108 and the water receiving tray 5 is H7. H7≥5mm.

[0226] refer to Fig.26 The minimum distance H7 between the guide plate 108 and the water receiving tray 5 is set to be no less than 5 mm, so that more sufficient intake air flow flows to the area where the free end of the first stage heat exchanger 212 is located.

[0227] In some embodiments of the present application, the water receiving tray 5 may include a water receiving portion 55. The water receiving portion 55 is horizontally arranged and extends along the length direction of the machine body 10. The water receiving portion 55 can be used to store condensed water.

[0228] refer to Fig.21 , an acute angle α is formed between the first stage heat exchanger 212 and the water receiving portion 55 , and an angle β is formed between the guide plate 108 and the water receiving portion 55 .

[0229] In some embodiments of the present application, the ratio between β and α is n. 0.4≤n, n≤0.6.

[0230] The ratio n between β and α cannot be too small. If it is too small, the angle β will be too small, which will make the distance between the air inlet end of the guide plate 108 and the water receiving tray 5 too small, affecting the air inlet volume under the guide plate 108, and further affecting the forced diversion effect. In order to increase the air inlet volume under the guide plate 108, the ratio n is set to be not less than the fifteenth parameter value. For example, the fifteenth parameter value can be 0.4, 0.43, or 0.45. Consider selecting a suitable and specific parameter in the specific design.

[0231] The ratio n between β and α cannot be too large. If it is too large, the angle β will be too large, which will make the distance between the air inlet end of the guide plate 108 and the first stage heat exchanger 212 too small, affecting the air inlet volume above the guide plate 108, and further affecting the forced diversion effect. In order to increase the air inlet volume above the guide plate 108, the ratio n is set to be no greater than the sixteenth parameter value. For example, the sixteenth parameter value can be 0.6, 0.58, or 0.55. Consider selecting a suitable and specific parameter in the specific design.

[0232] In some embodiments of the present application, the ratio between β and α is n. 0.4≤n≤0.6.

[0233] In this embodiment, the ratio n between β and α is set within a reasonable range, so that there is sufficient air intake above and below the guide plate 108, thereby ensuring that there is sufficient air intake airflow to the end of the first section heat exchanger 212 close to the air-conditioning outlet 103, further ensuring the uniformity of the overall air intake of the first end heat exchanger, and further improving the wind resistance performance.

[0234] In some embodiments of the present application, the distance between the first-stage heat exchanger 212 and the air inlet end of the guide plate 108 is greater than the distance between the first-stage heat exchanger 212 and the air outlet end of the guide plate 108 .

[0235] refer to Fig.26 The distance between the first heat exchanger 212 and the air inlet end is H4, and the distance between the first heat exchanger 212 and the air outlet end of the guide plate 108 is H3, wherein H4>H3.

[0236] In this embodiment, by setting H4 to be greater than H3, the inlet area of ​​the flow channel formed between the guide plate 108 and the first stage heat exchanger 212 is larger than the outlet area thereof, thereby further ensuring the air intake volume flowing through the first stage heat exchanger 212.

[0237] In some embodiments of the present application, 2 mm ≤ H3. H3 ≤ 4 mm.

[0238] The distance H3 cannot be too small. If it is too small, the air outlet area of ​​the flow channel between the guide plate 108 and the first stage heat exchanger 212 will be small, which will affect the air intake above the guide plate 108. In order to increase the air intake above the guide plate 108, the distance H3 is set to be not less than the seventeenth parameter value. For example, the seventeenth parameter value may be 2 mm, 2.2 mm, or 2.4 mm. Consider selecting a suitable and specific parameter in the specific design.

[0239] The distance H3 cannot be too large. If it is too large, the distance between the guide plate 108 and the free end of the first heat exchanger 212 will be too far, which will reduce the forced diversion effect or increase the height of the body 10. In order to increase the air intake volume of the free end area of ​​the first heat exchanger 212 and avoid increasing the volume of the body 10, the distance H3 is set to be no greater than the eighteenth parameter value. For example, the eighteenth parameter value can be 4mm, 3.8mm, or 3.5mm. Consider selecting a suitable and specific parameter in the specific design.

[0240] In some embodiments of the present application, reference Fig.25 The indoor heat exchanger 21 may include a second stage heat exchanger 213. The second stage heat exchanger 213 is located above the first stage heat exchanger 212, and one end of the second stage heat exchanger 213 is connected to one end of the first stage heat exchanger 212.

[0241] The indoor heat exchanger 21 may include a third-stage heat exchanger 214 , wherein the third-stage heat exchanger 214 is located above the second-stage heat exchanger 213 , and the third-stage heat exchanger 214 is connected to the other end of the second-stage heat exchanger 213 .

[0242] That is, the third heat exchanger 214, the second heat exchanger 213 and the first heat exchanger 212 are connected in sequence from top to bottom to form a semi-enclosed structure, wherein the opening of the semi-enclosed structure faces the cross-flow fan 31 to semi-surround the outer periphery of the cross-flow fan 31 to improve heat exchange efficiency.

[0243] refer to Figure 27 to Figure 33 In some other embodiments of the present application, in order to increase the air intake volume of the first heat exchanger 212 in the area on one side close to the air-conditioning outlet 103, the first heat exchanger 212 is provided with a V-shaped structure with an opening facing upward.

[0244] Specifically, refer to Fig.29 In the cross section of the first stage heat exchanger 212 , the middle portion of the first stage heat exchanger 212 protrudes toward the bottom plate 105 relative to both ends thereof to form a convex point E. The convex point E is spaced apart from the water receiving tray 5 .

[0245] It can be understood that the protrusion E is located on the side of the first-stage heat exchanger 212 facing away from the cross-flow fan 31 .

[0246] When the air duct machine is in cooling operation, the condensed water on the indoor heat exchanger 21 may flow to the convex point E, where the condensed water gathers and drips into the water receiving tray 5 .

[0247] Specifically, in the air duct machine provided in this embodiment, the middle part of the first section heat exchanger 212 protrudes relative to its two ends toward the bottom plate 105 to form a convex point E, so that the first section heat exchanger 212 is a V-shaped structure with the opening upward. The convex point E on the first section heat exchanger 212 is set as the lowest point of the indoor heat exchanger 21 and is spaced from the water receiving pan 5, so that the condensed water on the indoor heat exchanger 21 can drip from the convex point E to the water receiving pan 5, avoiding the condensed water from gathering at one end of the first section heat exchanger 212 close to the air outlet 103 of the air conditioner, improving the uniformity and air volume of the air intake of the first section heat exchanger 212, and improving the wind resistance performance of the cross-flow air duct.

[0248] In some embodiments of the present application, the first-stage heat exchanger 212 may include a first windward surface 2121 , and the first windward surface 2121 is disposed toward the air inlet 102 of the air conditioner.

[0249] The first stage heat exchanger 212 may include a second windward surface 2122. The first windward surface 2121 and one end of the second windward surface 2122 are connected to each other to form a convex point E.

[0250] refer to Fig.31One end of the first windward surface 2121 and the second windward surface 2122 are connected to each other to form a convex point E. The other ends of the first windward surface 2121 and the second windward surface 2122 extend upward in a direction away from the convex point E. The convex point E is spaced from the water receiving pan 5, and the condensed water on the indoor heat exchanger 21 can drip from the convex point E to the water receiving pan 5.

[0251] When the indoor air entering the machine body 10 through the air inlet 102 of the air conditioner passes through the indoor heat exchanger 21 for heat exchange, the indoor air can pass through the first windward surface 2121 and the second windward surface 2122 and pass through the first stage heat exchanger 212 for heat exchange.

[0252] In this embodiment, the first section heat exchanger 212 is set to a V-shaped structure with an opening upward, so that when the air duct mechanism is in refrigeration operation, the condensed water on the indoor heat exchanger 21 can be gathered at the convex point E by the first windward surface 2121 and the second windward surface 2122 and drip onto the water receiving tray 5, and will not gather in the area (framed area) from the convex point E to the volute tongue 385 on the first section heat exchanger 212, thereby reducing the negative impact of the condensation on the fins of the first section heat exchanger 212 on the air volume of the air intake in this area. The good air intake of the airflow in this area can significantly improve the wind resistance performance of the cross-flow air duct.

[0253] In some embodiments of the present application, the distance between the protrusion E and the water receiving tray 5 is H8, wherein H8≥6mm.

[0254] The distance H8 is set to be no less than 6 mm, so that sufficient air flow enters the area between the protrusion E and the volute tongue 385 on the first stage heat exchanger 212, thereby improving the heat exchange effect of the first stage heat exchanger 212.

[0255] The distance H8 between the convex point E and the water receiving tray 5 cannot be too small, otherwise it will affect the air intake of the heat exchanger area where the second windward surface 2122 is located. In order to increase the air intake of the first section heat exchanger 212, the distance H8 is set to be not less than the nineteenth parameter value. For example, the nineteenth parameter value can be 6mm, 7mm, or 8mm. Consider selecting a suitable specific parameter in the specific design.

[0256] The distance H8 between the protrusion E and the water receiving tray 5 cannot be too large, otherwise the height of the body 10 will be too large, which will increase the volume of the body 10. It is understandable that the distance H8 may not be greater than the 20th parameter value. The 20th parameter value is limited by the height of the body 10 and can be set according to the height requirements of the body 10.

[0257] The first section heat exchanger 212 has a plurality of U-tubes, which are connected by bending tubes to form at least one refrigeration flow path.

[0258] In some embodiments of the present application, reference Fig.30The first section heat exchanger 212 between the convex point E and the volute tongue 385 has at least two U tubes. This arrangement can prevent the distance between the convex point E and the volute tongue 385 from being too close, which affects the air intake of the first section heat exchanger 212 in the area between the convex point E and the volute tongue 385.

[0259] The duct air conditioner provided in this embodiment increases the air flow velocity in the at least two U-tube areas (framed areas) of the first heat exchanger 212 near the volute tongue 385, which not only increases the air volume, but also makes the air flow velocity of the entire first heat exchanger 212 more uniform. Fig.33 , which is a velocity cloud comparison diagram of the wind field simulation of the conventional plate-shaped first stage heat exchanger 212 and the V-shaped first stage heat exchanger 212 of the present application, Fig.33 It can be seen that the flow rate in the right area 1 of the first-stage heat exchanger 212 in the present application is significantly higher than the flow rate in area 1 of the conventional plate-shaped first-stage heat exchanger 212, which effectively improves the heat exchange efficiency of the indoor heat exchanger 21.

[0260] In some embodiments of the present application, reference Fig.32 The first windward surface 2121 forms an angle γ with the horizontal plane where the convex point E is located. 15°≤γ. γ<45°.

[0261] In this embodiment, the angle γ is ≥ 15°, so that the condensed water gathers at the convex point E, avoiding condensation on the first windward surface 2121, and improving the heat exchange effect of the first stage heat exchanger 212. The angle γ is < 45°, so that the first stage heat exchanger 212 where the first windward surface 2121 is located can be as close to the cross-flow fan 31 as possible, reducing the height of this part.

[0262] The angle γ cannot be too large, otherwise the first windward surface 2121 of the same length will be too high, which will make the first heat exchanger 212 too high, resulting in an increase in the height of the body 10. In order to reduce the volume of the body 10, the angle γ is set to be less than the 21st parameter value. For example, the 21st parameter value can be 45°, 43°, or 41°. Consider selecting a suitable and specific parameter in the specific design.

[0263] The angle γ cannot be too small. If it is too small, the condensed water on the first windward surface 2121 cannot drip smoothly from the convex point E. Moreover, for the first windward surface 2121 of the same length, the smaller the angle γ is, the larger the size of the first side surface in the width direction of the body 10 will be, which will lead to a larger width of the body 10. In order to ensure that the condensed water drips from the convex point E and reduce the volume of the body 10, the angle γ is set to be not less than the twenty-second parameter value. For example, the twenty-second parameter value can be 15°, 17°, or 19°. Consider selecting a suitable and specific parameter in the specific design.

[0264] In some embodiments of the present application, an angle γ is formed between the first windward surface 2121 and the horizontal plane where the convex point E is located. 15°≤γ<45°.

[0265] In this embodiment, the angle γ is set within a reasonable range so that the condensed water on the first windward surface 2121 can smoothly gather and drip at the protrusion E, thereby reducing the negative impact of condensation on the air volume in the area on the side of the protrusion E close to the air-conditioning outlet 103. In addition, the increase in the volume of the duct machine can be avoided.

[0266] In some embodiments of the present application, an angle θ is formed between the second windward surface 2122 and the horizontal plane where the convex point E is located. 15°≤θ. θ<45°.

[0267] In this embodiment, the angle θ is ≥ 15°, so that the condensed water gathers at the convex point E, avoiding condensation on the second windward surface 2122, thereby improving the heat exchange effect of the first stage heat exchanger 212. The angle θ is < 45°, so that the first stage heat exchanger 212 where the second windward surface 2122 is located can be as close to the cross-flow fan 31 as possible, reducing the height of this part.

[0268] The angle θ cannot be too large, otherwise the second windward surface 2122 of the same length will be too high, which will in turn make the first section heat exchanger 212 too high, resulting in an increase in the height of the body 10. In order to reduce the volume of the body 10, the angle θ is set to be less than the twenty-third parameter value. For example, the twenty-third parameter value can be 45°, 43°, or 41°. Consider selecting a suitable and specific parameter in the specific design.

[0269] The angle θ cannot be too small. If it is too small, the condensed water on the second windward surface 2122 cannot drip smoothly from the convex point E. Moreover, for the second windward surface 2122 of the same length, the smaller the angle θ is, the larger the size of the first side surface in the width direction of the body 10 will be, which will increase the width of the body 10. In order to ensure that the condensed water drips from the convex point E and reduce the volume of the body 10, the angle θ is set to be not less than the twenty-fourth parameter value. For example, the twenty-fourth parameter value can be 15°, 17°, or 19°. Consider selecting a suitable and specific parameter in the specific design.

[0270] In some embodiments of the present application, an angle θ is formed between the second windward surface 2122 and the horizontal plane where the convex point E is located. 15°≤θ<45°.

[0271] In this embodiment, the angle θ is set within a reasonable range so that the condensed water on the second windward surface 2122 can smoothly gather and drip at the convex point E, thereby reducing the negative impact of condensation on the air volume in the area on the side of the convex point E close to the air-conditioning outlet 103, and avoiding increasing the volume of the body 10.

[0272] In some embodiments of the present application, the first windward surface 2121 and the second windward surface 2122 are connected to form an obtuse angle ψ with the opening facing the cross-flow fan 31. ψ≤150°.

[0273] In this embodiment, the obtuse angle ψ is set to be less than or equal to 150°, so that the first stage heat exchanger 212 fits the cross-flow fan 31 to a great extent, thereby improving the heat exchange efficiency.

[0274] The angle value of ψ cannot be too large, otherwise the size of the first section heat exchanger 212 in the width direction of the body 10 will become larger, resulting in an increase in the width of the body 10, and it is impossible to ensure that the condensed water on the first windward surface 2121 and the second windward surface 2122 gather at the convex point E. In order to reduce the volume of the body 10, the obtuse angle ψ is set to be not less than the twenty-fifth parameter value. For example, the twenty-fifth parameter value can be 150°, 145°, or 140°. Consider selecting a suitable and specific parameter in the specific design.

[0275] The angle value of ψ cannot be too small. If it is too small, the height of the first heat exchanger 212 will be too high, and the first heat exchanger 212 will not fit the cross-flow fan 31, which will increase the height of the machine body 10 and affect the heat exchange efficiency of the first heat exchanger 212. In order to reduce the volume of the machine body 10 and meet a narrower depth, ψ is set to an obtuse angle.

[0276] refer to Fig.34 The indoor heat exchanger 21 may include three sections of heat exchangers, namely, a first section of heat exchanger 212, a second section of heat exchanger 213, and a third section of heat exchanger 214. The first section of heat exchanger 212, the second section of heat exchanger 213, and the third section of heat exchanger 214 are sequentially connected from bottom to top to form a half-enclosed structure with an opening.

[0277] An air duct is formed between the volute 384 and the volute tongue 385, and the cross-flow fan 31 is located between the volute 384 and the volute tongue 385. The volute tongue 385 may include a front volute tongue 3851 disposed toward the cross-flow fan 31. That is, the front volute tongue 3851 is the windward surface of the volute tongue 385.

[0278] There is a gap between the front volute tongue 3851 and the crossflow fan 31. It should be noted that the gap between the crossflow fan 31 and the front volute tongue 3851 in the crossflow air duct in the machine body 10 is an important design parameter that affects the air volume and sound quality.

[0279] The cross-flow fan 31 is not a rigid body. Fig.14The crossflow fan 31 is extended along the length direction of the body 10, that is, when its two ends are fixed and placed horizontally, the crossflow fan 31 as a whole will present a concave shape under the action of its own gravity, and the longer the crossflow fan 31 is, the more obvious the deformation is. When the crossflow fan 31 is located above the front volute tongue 3851, the deformation of the crossflow fan 31 will directly affect the gap between the crossflow fan 31 and the front volute tongue 3851, thereby affecting the overall air volume and sound quality of the air duct.

[0280] In the related art, the gap between the crossflow fan 31 and the front volute tongue 3851 in the duct air conditioner is set without considering the flexural deformation of the crossflow fan 31. When the crossflow fan 31 is partially located above the front volute tongue 3851, the deformation of the crossflow fan 31 will directly affect the gap between the crossflow fan 31 and the front volute tongue 3851, which will not only deteriorate the sound quality of the air conditioner, but also increase the risk of the front volute tongue 3851 hitting the crossflow fan 31 during transportation, affecting the user experience.

[0281] In order to solve the above technical problems, in some embodiments of the present application, the gap between the front volute tongue 3851 and the cross-flow fan 31 is reasonably set in consideration of the flexural deformation of the cross-flow fan 31 along the length direction of the body 10 .

[0282] refer to Fig.34 , the minimum gap between the front volute tongue 3851 and the crossflow fan 31 is defined as δ3, and the diameter of the outer edge of the crossflow fan 31 is defined as D. Considering various sizes of the crossflow fan 31, the minimum gap δ3 is set to: δ3≥0.03D. δ3≤0.06D.

[0283] It should be noted that, within a reasonable design range, the air volume of the cross-flow air duct will increase as the gap between the cross-flow fan 31 and the front volute tongue 3851 decreases.

[0284] The minimum gap δ3 cannot be too large, otherwise the air volume will decrease. In order not to reduce the air volume performance, the minimum gap δ3 is set to be no greater than the 26th parameter value. For example, the 26th parameter value can be 0.06D, 0.058D, or 0.056D. Consider selecting a suitable specific parameter in the specific design.

[0285] The minimum gap δ3 cannot be too small. If it is too small, the airflow of the crossflow fan 31 will aggravate the impact on the front volute tongue 3851, thereby generating a serious whistling sound. In more serious cases, the crossflow fan 31 may shake and directly hit the front volute tongue 3851 during transportation. In order to ensure good sound quality and ensure that the crossflow fan 31 does not hit the front volute tongue 3851 during transportation, the minimum gap δ3 is set to be not less than the twenty-seventh parameter value. For example, the twenty-seventh parameter value can be 0.03D, 0.032D, or 0.034D. Consider selecting a suitable and specific parameter in the specific design.

[0286] The duct machine provided in this embodiment takes into account the flexural deformation of the crossflow fan 31, and sets the minimum gap δ3 between the crossflow fan 31 and the front volute tongue 3851 to: δ3≥0.03D, δ3≤0.06D. The minimum gap δ3 is set within a reasonable range to avoid serious airflow leakage and air volume attenuation due to the excessive distance between the crossflow fan 31 and the front volute tongue 3851, and at the same time, avoid high noise values ​​due to the small distance between the crossflow fan 31 and the front volute tongue 3851, thereby effectively improving the working efficiency of the crossflow fan 31 and reducing noise.

[0287] In some embodiments of the present application, the minimum gap between the front volute tongue 3851 and the crossflow fan 31 is defined as δ3, and the diameter of the outer edge of the crossflow fan 31 is defined as D. Considering various sizes of the crossflow fan 31, the minimum gap δ3 is set to: 0.03D≤δ3≤0.06D.

[0288] In this embodiment, the minimum gap δ3 from the crossflow fan 31 to the front volute tongue 3851 is adjusted by comprehensively considering the circulation efficiency, air volume and noise of the airflow near the front volute tongue 3851 and the length of the crossflow fan 31, and the minimum gap δ3 is set to any value between 0.03D and 0.06D, thereby improving the sound quality of the duct air conditioner without reducing the air volume performance. Not only does it avoid that a too small minimum gap will increase the risk of collision between the crossflow fan 31 and the front volute tongue 3851 during operation, but it will also lead to an enhanced interaction between the airflow excited by the crossflow fan 31 and the surface of the front volute tongue 3851, thereby increasing the noise level of the air conditioner and worsening the sound quality, and it also avoids the problem of a decrease in air volume due to an excessively large minimum gap.

[0289] In some embodiments of the present application, the vertical distance between the end of the front volute tongue 3851 close to the air inlet 102 of the air conditioner and the cross-flow fan 31 is the minimum gap δ3. The vertical distance between the end of the front volute tongue 3851 close to the air inlet 102 of the air conditioner and the cross-flow fan 31 is set to the minimum distance δ3 to ensure that the wind resistance performance of the air duct in the body 10 is optimal.

[0290] When the fan is located above the front volute tongue 3851 of the air duct, in order to further achieve higher air volume and better sound quality, the minimum gap between the corresponding cross-flow fan 31 and the front volute tongue 3851 can be matched according to the length of different cross-flow fans 31.

[0291] Specifically, when the length of cross-flow fan 31 does not exceed 800 mm, the minimum gap δ3 may be set to: δ3 ≥ 0.03D, δ3 ≤ 0.045D.

[0292] It is understandable that when the crossflow fan 31 is extended along the length direction of the body 10, the crossflow fan 31 as a whole will present a concave shape under the action of its own gravity. The length of the crossflow fan 31 is defined as L7. When L7≤800mm, its concave deformation is relatively small.

[0293] When L7≤800mm, the minimum gap δ3 cannot be too large, otherwise it will cause serious airflow leakage and reduced air volume. In order to ensure air volume performance, when L2≤800mm, the minimum gap δ3 is set to be no greater than the 28th parameter value. For example, the 28th parameter value can be 0.045D, 0.042D, or 0.040D. Consider selecting a suitable and specific parameter in the specific design.

[0294] When L7≤800mm, the minimum gap δ3 cannot be too small. If it is too small, the noise value will be high and there will be a risk of collision between the crossflow fan 31 and the front volute tongue 3851. In order to improve the sound quality of the duct machine, improve the working efficiency of the crossflow fan 31, and reduce noise, the minimum gap δ3 is set to be not less than the twenty-ninth parameter value. For example, the twenty-ninth parameter value can be 0.03D, 0.032D, or 0.034D. Consider selecting a suitable and specific parameter in the specific design.

[0295] In some embodiments of the present application, when L7≤800mm, 0.03D≤δ3≤0.045D. In this embodiment, considering the deformation corresponding to the length of the cross-flow fan 31, when the length L7≤800mm of the cross-flow fan 31, its deformation is relatively small. The minimum gap δ3 between the cross-flow fan 31 and the front volute tongue 3851 under this length size range is set within a relatively small size range, so that the length L7 of the cross-flow fan 31 is ≤800mm, with a higher air volume and better sound quality.

[0296] In some embodiments of the present application, when the length of the cross-flow fan 31 exceeds 800 mm, the minimum gap δ3 may be set to: δ3>0.045D. δ3≤0.06D.

[0297] Specifically, when the cross-flow fan 31 is extended along the length direction of the body 10, the cross-flow fan 31 as a whole will present a concave shape under the action of its own gravity. The length of the cross-flow fan 31 is defined as L7. When L7>800mm, its concave deformation is relatively large.

[0298] When L7>800mm, the minimum gap δ3 cannot be too large, otherwise it will cause serious airflow leakage and reduced air volume. In order to ensure air volume performance, the minimum gap δ3 is set to be no greater than the 30th parameter value. For example, the 30th parameter value can be 0.06D, 0.058D, or 0.056D. Consider selecting a suitable specific parameter in the specific design.

[0299] When L7>800mm, the minimum gap δ3 cannot be too small. If it is too small, after the crossflow fan 31 is deformed, the minimum gap δ3 will be smaller, which will lead to a high noise value. At the same time, there is a risk of collision between the crossflow fan 31 and the front volute tongue 3851. In order to improve the sound quality of the duct machine, improve the working efficiency of the crossflow fan 31, and reduce noise, the minimum gap δ3 is set to be not less than the thirty-first parameter value. For example, the thirty-first parameter value can be 0.046D, 0.048D, or 0.049D. Consider selecting a suitable and specific parameter in the specific design.

[0300] In some embodiments of the present application, when L7>800mm, 0.045D<δ3≤0.06D. In this embodiment, considering the deformation corresponding to the length of the cross-flow fan 31, when the length L7 of the cross-flow fan 31 is greater than 800mm, the deformation is relatively large. The minimum gap δ3 between the cross-flow fan 31 and the front volute tongue 3851 under this length size range is set within a relatively large size range, so that the length L7 of the cross-flow fan 31 is greater than 800mm, with a higher air volume and better sound quality.

[0301] In some embodiments of the present application, the maximum gap between the front volute tongue 3851 and the cross-flow fan 31 is defined as δ4, and the difference between δ4 and δ3 is Δδ, wherein Δδ≥0.02D and Δδ≤0.04D.

[0302] Δδ cannot be too small. If it is too small, the maximum gap δ4 will be too small. If the maximum gap δ4 is too small, the eddy noise generated by the airflow will increase significantly. In order to improve the sound quality level of the duct air conditioner, the difference Δδ is set to be no less than the thirty-second parameter value. For example, the thirty-second parameter value can be 0.02D, 0.023D, or 0.025D. Consider selecting a suitable and specific parameter in the specific design.

[0303] Δδ cannot be too large, otherwise the maximum gap δ4 will be too large. When the maximum gap δ4 is too large, it is easy to cause the return air to increase at a low speed of the cross-flow fan 31, resulting in flow loss and serious leakage on the air guide side, resulting in a decrease in air output. In order to reduce air leakage and increase air output, the difference Δδ is set to be no greater than the thirty-third parameter value. For example, the thirty-third parameter value can be 0.04D, 0.038D, or 0.055D. Consider selecting a suitable and specific parameter in the specific design.

[0304] In some embodiments of the present application, the maximum gap between the front volute tongue 3851 and the cross-flow fan 31 is defined as δ4, and the difference between δ4 and δ3 is Δδ, wherein 0.02D≤Δδ≤0.04D.

[0305] In this embodiment, Δδ is set to any value between 0.02D and 0.04D, which improves the wind resistance performance of the duct air conditioner. It effectively avoids the problem of flow loss and serious leakage on the air guide side caused by the maximum gap δ4 being too large, and the problem of significantly increasing the eddy noise generated by the airflow caused by the maximum gap δ4 being too small.

[0306] In some embodiments of the present application, the vertical distance between the end of the front volute tongue 3851 close to the air-conditioning outlet 103 and the cross-flow fan 31 is the maximum gap δ4.

[0307] In this embodiment, there is a gap between the front volute tongue 3851 and the outer contour of the cross-flow fan 31 to form an airflow channel for returning air. The maximum gap δ4 is set at the channel inlet of the airflow channel for returning air of the front volute tongue 3851, so that the airflow can flow more smoothly, and the obstruction at the channel inlet is prevented to form noise, which can effectively improve the working efficiency of the cross-flow fan 31 and reduce noise.

[0308] In some embodiments of the present application, in the cross-section of the cross-flow fan, the contour line of the front volute tongue 3851 has an end point A1, wherein the end point A1 is located on the contour line of the front volute tongue 3851 and is close to the air inlet 102 of the air conditioner.

[0309] In the cross-section of the cross-flow fan, the contour line of the front volute tongue 3851 has an end point An, wherein the end point An is the end point of the contour line of the front volute tongue 3851 close to the air outlet 103 of the air conditioner.

[0310] refer to Figure 35 to Figure 37 The gap between the front volute tongue 3851 and the cross-flow fan 31 is gradually increased from the end point A1 to the end point An.

[0311] Specifically, the gap between the front volute tongue 3851 and the cross-flow fan 31 is gradually increased from end point A1 to end point An, so that the airflow channel between the front volute tongue 3851 and the outer contour of the cross-flow fan 31 gradually decreases along the flow direction of the airflow, forming a gradual channel, reducing the size of the eccentric vortex inside the cross-flow fan 31, gradually differentiating and mitigating the impact of the airflow, so as to adapt to the changes in the airflow driven by the cross-flow fan 31 when it returns from the side of the front volute tongue 3851 to the inside of the air duct, so that the airflow returns smoothly to the inside of the air duct, reducing the disturbance to the operation of the cross-flow fan 31, and making the airflow of the cross-flow fan 31 stable, especially when the resistance increases, maintaining the stability of the airflow, and avoiding abnormal noise caused by airflow fluctuations.

[0312] In some embodiments of the present application, the volute tongue 385 may include a wind guide surface 3852. Fig.35The air guide surface 3852 faces and is close to the air conditioner outlet 103 relative to the front volute tongue 3851. The air guide surface 3852 faces the air conditioner outlet 103 to achieve a linear guiding effect on the air flow in the air duct, so as to further avoid the problem of air volume loss at the air conditioner outlet 103 during the operation of the air duct machine.

[0313] In some embodiments of the present application, the wind guide surface 3852 and the front volute tongue 3851 are connected by an arc transition to form the volute tongue 385 .

[0314] This arrangement can make the gradual passage between the front volute tongue 3851 and the outer contour of the cross-flow fan 31 smoother, and the airflow transition more natural and smooth, thereby achieving the purpose of further improving the airflow stability of the cross-flow fan 31.

[0315] In some embodiments of the present application, the indoor heat exchanger 21 may be a multi-stage heat exchanger.

[0316] Continue to refer Fig.35 The indoor heat exchanger 21 may include three sections of heat exchangers, namely the first section heat exchanger 212, the second section heat exchanger 213 and the third section heat exchanger 214. The first section heat exchanger 212, the second section heat exchanger 213 and the third section heat exchanger 214 are connected in sequence from bottom to top to form a half-enclosed structure with an opening. The open end of the half-enclosed structure faces the cross-flow fan 31, and the closed end of the half-enclosed structure faces the air inlet 102102 of the air conditioner. This arrangement allows the airflow entering the body 10 from the air inlet 102 of the air conditioner to be almost completely blown to the indoor heat exchanger 21, thereby increasing the heat exchange area of ​​the indoor heat exchanger 21, improving the heat exchange efficiency of the air duct machine 100, and increasing the amount of air exchanged.

[0317] refer to Fig.38 , which is the duct fan provided by the present application, taking L7=1000mm as an example, adopts the noise spectrum under different minimum gaps δ3. In actual implementation, the size L7 of the cross-flow fan 31 is 1000mm, the diameter D of the cross-flow fan 31 is 111.5mm, and the air volume and noise of the air duct under different minimum gaps δ3 are tested at a fan speed of 1300rpm (strong gear). During the test, the test environment and test position are the same.

[0318] It can be seen from Table 1 that when the minimum gap δ3 between the cross-flow fan 31 and the front volute tongue 3851 is less than 0.045D, the OA-Peak value is less than 15dB, and the sound quality is poor. Among them, the OA-Peak value represents the difference between the overall noise level of the duct air conditioner and the highest noise peak at each frequency. When the value is <15dB, the sound quality is poor; when the value is >15dB, the sound quality is good. When the minimum gap δ3 increases to more than 0.045D, the OA-Peak value is greater than 19dB, and the sound quality is good. This is mainly because the larger the minimum gap δ3, the weaker the impact of the airflow driven by the cross-flow fan 31 on the surface of the front volute tongue 3851, thereby reducing the noise peak corresponding to the blade impact frequency (near 760Hz) in the spectrum.

[0319] from Fig.38 It can be seen that when the minimum gap δ3 increases from 0.043Dmm to 0.051D, the peak value of the frequency multiplication decreases from 28.2dB to 22.3dB. When the minimum gap δ3 is further increased to 0.059Dmm, the peak value of the frequency multiplication basically disappears. Moreover, compared with Case 1, the sound quality of Case 2 is significantly improved, while the air volume only decreases by 1.6%, which remains basically unchanged. Compared with Case 2, the sound quality of Case 3 is improved, but the air volume further decreases. Therefore, the minimum gap δ3 cannot be too large, otherwise it will cause serious airflow leakage and seriously affect the air volume.

[0320] Table 1

[0321] plan δ3(mm) δ3 / D Air volume (m3 / h) OA-Peak value (dB) Case 1 4.8 0.043 1281 13.7 Case 2 5.7 0.051 1261 19.0 Case 3 6.6 0.059 1236 19.5

[0322] In order to solve the problem that the cross-flow fan 31 as a whole is deformed under the action of its own gravity, resulting in the deterioration of the sound quality of the noise duct machine and increasing the risk of the front volute tongue 3851 hitting the fan during transportation.

[0323] refer to Fig.39 In some other embodiments of the present application, the front volute tongue 3851 is set as a whole as a front volute tongue 3851 structure with concave opposite ends in the middle, so that the corresponding cross-flow fan 31 as a whole presents a concave shape under the action of its own gravity, and the gap between the cross-flow fan 31 and the front volute tongue 3851 is controlled to be consistent along the length direction (span direction) of the air duct machine, thereby avoiding the occurrence of heterodyne noise caused by the reduction of the gap due to the flexural deformation of the cross-flow fan 31, and the collision between the cross-flow fan 31 and the front volute tongue 3851, thereby improving the sound quality level and transportation reliability of the air duct machine.

[0324] Specifically, refer to Fig.39 In the longitudinal section of the front volute 384, the front volute 384 is arranged in a curve. In the longitudinal section of the front volute 384, the front volute tongue curve (the outline of the front volute tongue 3851) gradually sinks downward from both ends to the middle position. Fig.39, the red curve in the figure is the anterior modiolar tongue curve.

[0325] That is to say, in the longitudinal section of the front volute 384 , the curve of the front volute tongue 3851 is an arc-shaped curve opening upward, so that it can match the cross-flow fan 31 having flexural deformation in the length direction of the body 10 .

[0326] In this embodiment, by adjusting the degree of deflection of the front volute tongue 3851, the consistency of the gap between the cross-flow fan 31 and the front volute tongue 3851 along the length direction (span direction) of the body 10 is ensured, thereby avoiding the single-frequency noise caused by the reduction of the gap of the front volute tongue 3851 of the fan due to the deflection deformation of the fan, and the collision between the fan and the front volute tongue 3851, thereby improving the sound quality level and transportation reliability of the air conditioner.

[0327] In this embodiment, on the longitudinal section of the front volute 384, the front volute tongue 3851 is set to be a curve that gradually sinks downward from its two ends to the middle position, so that the shape of the front volute tongue 3851 can be determined according to the flexural form of the cross-flow fan 31 along the length direction of the body 10 when it is supported and placed horizontally at both ends, thereby avoiding deformation of the cross-flow fan 31 that affects the gap between the cross-flow fan 31 and the front volute tongue 3851, so as to achieve a better sound quality level and transportation reliability.

[0328] In some embodiments of the present application, in the longitudinal section of the front volute 384 , the front volute 384 is arranged in a curve, and the line connecting the two ends of the curve of the front volute 384 is located above the curve of the front volute tongue 3851 .

[0329] refer to Fig.39 In the longitudinal section of the front volute 384 , the line connecting the two ends of the curve of the front volute 384 is K, and there is a concave amount between the line K and the curve of the front volute tongue 3851 .

[0330] The concave amount gradually decreases from the middle position of the curve of the front volute tongue 3851 to its two ends, that is, the concave amount decreases continuously and smoothly from the middle position to the two ends. In other words, the concave amount between the middle position of the curve of the front volute tongue 3851 and the connecting line M is the maximum concave amount. The concave amount between the two ends of the curve of the front volute tongue 3851 and the connecting line M is 0.

[0331] The duct air conditioner provided in this embodiment has a longitudinal section of the front volute 384, by setting the connecting line of the two ends of the curve of the front volute 384 above the curve of the front volute tongue 3851, and there is a concave amount between the curve of the front volute tongue 3851 and the connecting line of the two ends of the curve of the front volute 384, so that the shape of the front volute tongue 3851 can be determined according to the flexural form of the cross-flow fan 31 along the length direction of the body 10 when the cross-flow fan 31 is supported and placed horizontally at both ends, thereby avoiding deformation of the cross-flow fan 31 affecting the gap between the cross-flow fan 31 and the front volute tongue 3851, so as to achieve a better sound quality level and transportation reliability.

[0332] In some embodiments of the present application, on the longitudinal section of the front volute 384 , the line between the two ends of the curve of the front volute 384 extends in the horizontal direction; this arrangement ensures that the front volute 384 extends along the length direction of the body 10 .

[0333] The concave amount between the middle position of the curve of the front volute tongue 3851 and the line M connecting its two ends is the maximum concave amount a.

[0334] In some embodiments of the present application, when the length of the cross-flow fan 31 is not greater than 800 mm, 0.4 mm ≤ a, a ≤ 0.6 mm.

[0335] Specifically, when the crossflow fan 31 is arranged horizontally along the length direction of the body 10, the crossflow fan 31 as a whole will present a concave shape under the action of its own gravity. The length of the crossflow fan 31 is defined as L7. When L7≤800mm, its downward deflection is relatively small.

[0336] When L7≤800mm, the maximum concave amount a cannot be too large, otherwise it will cause the gap between the crossflow fan 31 and the front volute tongue 3851 to be too large, resulting in serious airflow leakage and reduced air volume. In order to ensure air volume performance, when L7≤800mm, the maximum concave amount a is set to be no greater than the thirty-fourth parameter value. For example, the thirty-fourth parameter value can be 0.6mm, 0.58mm, or 0.56mm. Consider selecting a suitable and specific parameter in the specific design.

[0337] When L7≤800mm, the maximum concave amount a cannot be too small. If it is too small, the spanwise consistency of the gap between the crossflow fan 31 and the front volute tongue 3851 cannot be guaranteed. The deformation of the crossflow fan 31 will directly affect the gap between the crossflow fan 31 and the front volute tongue 3851, which will not only cause a high noise value, but also a risk of collision between the crossflow fan 31 and the front volute tongue 3851. In order to improve the sound quality of the duct machine, improve the working efficiency of the crossflow fan 31, and reduce noise, the maximum concave amount a is set to be not less than the thirty-fifth parameter value. For example, the thirty-fifth parameter value can be 0.4mm, 0.42mm, or 0.44mm. Consider selecting a suitable and specific parameter in the specific design.

[0338] In some embodiments of the present application, when L7≤800mm, 0.4mm≤a≤0.6mm.

[0339] In this embodiment, the maximum concave amount a is reasonably set in consideration of the degree of flexural deformation corresponding to the length of the crossflow fan 31. When the length L7 of the crossflow fan 31 is ≤800 mm, the deformation is relatively small, and the maximum concave amount a is set within a relatively small size range to ensure the spanwise consistency of the gap between the crossflow fan 31 and the front volute tongue 3851, so that the length L7 of the crossflow fan 31 is ≤800 mm, with a higher air volume and better sound quality.

[0340] In some embodiments of the present application, when the length of the cross-flow fan 31 exceeds 800 mm, 0.6 mm<a, a≤0.8 mm.

[0341] Specifically, when the cross-flow fan 31 is arranged horizontally along the length direction of the machine body 10, the cross-flow fan 31 as a whole will present a concave shape under the action of its own gravity. When L7>800mm, its downward flexural deformation is relatively large.

[0342] When L7>800mm, the maximum concave amount a cannot be too large, otherwise it will cause the gap between the crossflow fan 31 and the front volute tongue 3851 to be too large, resulting in serious air leakage and reduced air volume. In order to ensure air volume performance, when L7>800mm, the maximum concave amount a is set to be no greater than the thirty-sixth parameter value. For example, the thirty-sixth parameter value can be 0.8mm, 0.78mm, or 0.76mm. Consider selecting a suitable and specific parameter in the specific design.

[0343] When L7>800mm, the maximum concave amount a cannot be too small. If it is too small, the long cross-flow fan 31 will be deformed, which will directly affect the gap between the cross-flow fan 31 and the front volute tongue 3851, which will not only lead to a high noise value, but also the risk of collision between the cross-flow fan 31 and the front volute tongue 3851. In order to improve the sound quality of the duct machine and reduce the risk of collision, the maximum concave amount a is set to be greater than the thirty-seventh parameter value. For example, the thirty-seventh parameter value can be 0.6mm, 0.62mm, or 0.64mm. Consider selecting a suitable and specific parameter in the specific design.

[0344] In some embodiments of the present application, when L7>800mm, 0.6mm<a≤0.8mm.

[0345] In this embodiment, the maximum concave amount a is reasonably set in consideration of the degree of flexural deformation corresponding to the length of the cross-flow fan 31. When the length L7 of the cross-flow fan 31 is greater than 800 mm, the deformation is relatively large, and the maximum concave amount a is set within a relatively large size range, so that the length L7 of the cross-flow fan 31 is greater than 800 mm, which has a higher air volume and better sound quality.

[0346] In the air duct machine provided in this embodiment, when the cross-flow fan 31 is located above the front volute tongue 3851, the degree of deflection of the front volute tongue 3851 can be adjusted according to the length of the cross-flow fan 31 to ensure the spanwise consistency of the gap between the cross-flow fan 31 and the front volute tongue 3851.

[0347] In other words, according to the difference in the degree of flexural deformation of the cross-flow fans 31 of different lengths along the length direction of the body 10, the front volute tongue 3851 structures with different concave shapes can be matched to avoid the single-frequency noise and collision risk caused by the reduction of the gap between the cross-flow fan 31 and the front volute tongue 3851 due to the flexural deformation of the cross-flow fan 31, so as to achieve a better sound quality level and transportation reliability.

[0348] In some embodiments of the present application, on the longitudinal section of the front volute 384 , the curve of the front volute tongue 3851 includes but is not limited to a quadratic curve, a catenary curve, and the like.

[0349] In some embodiments of the present application, in the cross-section of the cross-flow fan 31 , the front volute tongue 3851 is arranged in an arc shape, and there is a gap between the front volute tongue 3851 and the cross-flow fan 31 .

[0350] In some embodiments of the present application, the minimum distance between the front volute tongue 3851 and the cross-flow fan 31 is δ1, and the maximum distance between the front volute tongue 3851 and the cross-flow fan 31 is δ2. Wherein, δ1≥0.03D. δ1≤0.045D. δ2≥0.06D. δ2≤0.075D,

[0351] By setting the concave amount, when setting the minimum distance between the front volute tongue 3851 and the cross-flow fan 31, there is no need to consider the degree of deflection of the cross-flow fan 31 at different lengths. Therefore, the numerical range of the minimum distance δ1 between the front volute tongue 3851 and the cross-flow fan 31 here is consistent with the numerical range of the minimum distance δ1 in some of the aforementioned embodiments, and similarly, the maximum distance δ2 is consistent with the numerical range of the maximum distance δ2 in some of the aforementioned embodiments, which will not be described in detail here.

[0352] It can be understood that, in this embodiment, the minimum distance δ1 is the distance between the two ends of the front volute tongue 3851 and the cross-flow fan 31. On the cross section of any front volute tongue 3851, the minimum distance between the front volute tongue 3851 and the cross-flow fan 31 is the sum of δ1 and the corresponding concave amount. Similarly, on the cross section of any front volute tongue 3851, the maximum distance between the front volute tongue 3851 and the cross-flow fan 31 is the sum of δ2 and the corresponding concave amount.

[0353] In some embodiments of the present application, the gap between the front volute tongue 3851 and the cross-flow fan 31 is gradually expanded from one end thereof close to the air inlet 102 of the air conditioner to the other end thereof.

[0354] Specifically, on the cross section of the cross flow fan 31, the gap between the front volute tongue 3851 and the outer contour of the cross flow fan 31 forms an air flow channel for returning air. The gap between the front volute tongue 3851 and the cross flow fan 31 is gradually expanded from one end close to the air inlet 102 of the air conditioner to the other end, so that the maximum distance δ2 is located at the channel inlet of the air flow channel, and the minimum distance δ1 is set to be less than the gap value at the channel inlet, so that the air flow is smoother, and the channel inlet of the return air of the front volute tongue 3851 is prevented from being blocked and causing noise, which can improve the working efficiency of the cross flow fan 31 and reduce noise.

[0355] It should be noted that the duct air conditioner with a cross-flow fan 31 has a narrower depth than the duct air conditioner with a centrifugal fan, which can broaden its installation scenario. Therefore, the duct air conditioner with a cross-flow fan 31 can be installed in the ceiling and at the beam position of the living room curtain hanging point.

[0356] In the related art, due to the limitation of the height size of the body 10 in the installation scenario, the height of the duct air conditioner needs to be compressed as much as possible, which results in the height H of the air inlet 102 of the air conditioner being limited, thus limiting the air intake volume of the duct air conditioner.

[0357] In addition, in the related art, due to the requirements of the actual installation location, when installing the duct machine, refer to Fig.40 , the horizontal distance L between the air-conditioning air inlet 102 and the beam (or wall) needs to be between 80mm and 120mm, and a separation zone will be formed above it, which further reduces the air supply of the ducted air conditioner. Furthermore, in this installation environment, the resistance of the air-conditioning air inlet 102 of the ducted air conditioner is too large, which will increase the risk of wind resistance noise in the whole machine, resulting in a decline in user experience and reduced product competitiveness.

[0358] In order to increase the air intake of the duct machine, refer to Figures 41 to 47 In some embodiments of the present application, the duct machine 100 may include a lower air inlet 109 .

[0359] refer to Fig.43 , the lower air inlet 109 is opened on the bottom plate 105 along the length direction of the machine body 10. That is to say, the length direction of the lower air inlet 109 is the length direction of the machine body 10.

[0360] Among them, the lower air inlet 109 is connected to the air conditioning inlet 102. Under the action of the cross-flow fan 31, the indoor air enters the body 10 through the air conditioning inlet 102 and the lower air inlet 109, and is output to the room through the air conditioning outlet 103 after heat exchange through the indoor heat exchanger 21.

[0361] refer to Figures 41 to 46The water receiving tray 5 may include a first water receiving tray 52. ​​The first water receiving tray 52 is located between the air inlet 102 and the lower air inlet 109 of the air conditioner.

[0362] The water receiving tray 5 may include a second water receiving tray 53 , wherein the lower air inlet 109 is located between the first water receiving tray 52 and the second water receiving tray 53 .

[0363] refer to Fig.45 In the width direction of the machine body 10 , a avoidance portion 51 is provided between the first water receiving tray 52 and the second water receiving tray 53 . The avoidance portion 51 is provided corresponding to the lower air inlet 109 , and the lower air inlet 109 is connected to the air inlet 102 of the air conditioner through the avoidance portion 51 .

[0364] In this embodiment, a lower air inlet 109 is provided on the bottom plate 105, which cooperates with the air-conditioning air inlet 102 located on the rear side of the body 10 to realize double air inlet air intake. Compared with the technical solution in the prior art which only has the air-conditioning air outlet 103, the air intake area is increased, thereby increasing the air intake volume of the duct machine.

[0365] The duct air conditioner provided in this embodiment is suitable for installation environments where there is a small horizontal distance between the air inlet 102 of the air conditioner and the wall (beam or crossbeam), meeting the requirements of the actual installation location and further broadening its installation scenarios. By setting the lower air inlet 109, not only the air supply volume of the duct air conditioner is increased, but also the air inlet resistance of the duct air conditioner is reduced, thereby improving the wind resistance performance of the air duct.

[0366] In some other embodiments, reference Fig.41 The water receiving pan 5 is arranged below the indoor heat exchanger 21, and the lower air inlet 109 is directly arranged at the bottom of the body 10 to communicate with the air inlet 102 of the air conditioner. The lower air inlet 109 divides the indoor heat exchanger 21 into a first water receiving pan 52 and a second water receiving pan 53. In this embodiment, the water receiving pan 5 is an integrated arrangement. Under the action of the cross-flow fan 31, the indoor air enters the body 10 through the air inlet 102 and the lower air inlet 109, and is output to the room through the air outlet 103 of the air conditioner after heat exchange in the indoor heat exchanger 21.

[0367] In some embodiments of the present application, the indoor heat exchanger 21 may include a three-stage heat exchanger.

[0368] refer to Fig.44 , Fig.45 The three sections of heat exchangers are respectively the first section heat exchanger 212, the second section heat exchanger 213 and the third section heat exchanger 214. The first section heat exchanger 212, the second section heat exchanger 213 and the third section heat exchanger 214 are connected in sequence from bottom to top to form a half-enclosed structure with an opening. The open end of the half-enclosed structure faces the cross-flow fan 31, and the closed end of the half-enclosed structure faces the air inlet 102102 of the air conditioner.

[0369] Part of the cross-flow fan 31 is arranged in the half-enclosed structure of the indoor heat exchanger 21, so that the cross-flow fan 31 and the indoor heat exchanger 21 are changed from being originally separately arranged to being overlappingly arranged. While the volumes of the cross-flow fan 31 and the indoor heat exchanger 21 remain unchanged, the space occupied by the indoor heat exchanger 21 and the cross-flow fan 31 is greatly reduced.

[0370] The second-stage heat exchanger 213 has a first connection end, and the first connection end is connected to the third-stage heat exchanger 214 .

[0371] In some embodiments of the present application, in the cross-section of the cross-flow fan 31 , the first water receiving tray 52 is located between the air conditioning air inlet 102 and the lower air inlet 109 .

[0372] refer to Fig.44 On the cross section of the cross flow fan 31, the end point of the first connection end away from the cross flow fan 31 is point C. The downward projection of point C in the vertical direction falls into the first water receiving tray 52, which is used to receive the condensed water dripping from the connection between the third stage heat exchanger 214 and the second stage heat exchanger 213.

[0373] That is, the downward projection of point C along the vertical direction falls within the downward projection range of the first water receiving tray 52 along the vertical direction, so that the first water receiving tray 52 is located below point C.

[0374] Specifically, when the ducted air conditioner is running in cooling mode, there is a greater risk of condensed water droplets dripping at the connection between the third heat exchanger 214 and the second heat exchanger 213. The first water receiving tray 52 is arranged below point C so that the water droplets at point C can drip into the first water receiving tray 52, thereby preventing the water droplets from falling through the lower air inlet 109 and affecting the user experience.

[0375] In some embodiments of the present application, the downward projection of the first-stage heat exchanger 212 along the vertical direction completely falls into the second water receiving tray 53 .

[0376] refer to Fig.44 On the cross-section of the cross-flow fan 31, the first section heat exchanger 212 is tilted from top to bottom toward the air outlet 103 of the air conditioner, so that when the duct unit operates in the cooling mode, the condensed water on the indoor heat exchanger 21 will flow into the second water receiving tray 53 from one end of the first section heat exchanger 212 close to the air outlet 103 of the air conditioner.

[0377] In some embodiments of the present application, the downward projection of the connection between the first section heat exchanger 212 and the second section heat exchanger 213 in the vertical direction completely falls into the second water receiving tray 53, which is used to receive condensed water dripping from the connection between the first section heat exchanger 212 and the second section heat exchanger 213, and prevent water droplets at the connection from falling through the lower air inlet 109 and affecting the user experience.

[0378] In some embodiments of the present application, the first-stage heat exchanger 212 has a second connection end connected to the second-stage heat exchanger 213 .

[0379] refer to Fig.45 On the cross section of the cross flow fan 31, the end point of the second connection end away from the cross flow fan 31 is point F, and the distance between point F and the second water receiving pan 53 is H5, H5 ≥ 20 mm. In this embodiment, by setting the distance H5 between point F and the second water receiving pan 53 to be not less than 20 mm, it is ensured that sufficient airflow flows to the first stage heat exchanger 212, thereby increasing the air intake volume of the first stage heat exchanger 212.

[0380] The distance H5 between point F and the second water receiving tray 53 cannot be too small. If it is too small, the air intake of the first heat exchanger 212 will be small. In order to ensure the air intake of the first heat exchanger 212, the distance H5 is set to be not less than the thirty-eighth parameter value. For example, the thirty-eighth parameter value can be 21mm, 22mm, or 23mm. Consider selecting a suitable specific parameter in the specific design.

[0381] The larger the distance H5 between point F and the second water receiving tray 53, the larger the air intake of the first stage heat exchanger 212. The thickness of the body 10 will limit the distance H5 between point F and the second water receiving tray 53 from being too large, so as to avoid increasing the volume of the body 10. Therefore, the maximum value of the distance H5 can be set according to the actual needs of the size of the body 10.

[0382] In some embodiments of the present application, a first baffle 531 is disposed on the second water receiving tray 53 .

[0383] refer to Fig.44 , Fig.47 The first baffle 531 is disposed on the second water receiving tray 53, and a flow channel for air flow is formed between one end of the first baffle 531 and the second stage heat exchanger 213. The distance H6 between the first baffle 531 and the second stage heat exchanger 213 is set to be greater than the distance H5 between point F and the second water receiving tray 53, so that the inlet area of ​​the flow channel is larger, ensuring that sufficient air flow flows through the first stage heat exchanger 212.

[0384] In some embodiments of the present application, the difference between the distance H6 and the distance H5 is c. c>5mm. In this embodiment, the distance H6 is set to be 5mm larger than the distance H5 to prevent the distance H6 from becoming a bottleneck limiting the air intake of the first stage heat exchanger 212.

[0385] In some embodiments of the present application, the first water receiving tray 52 and the second water receiving tray 53 are respectively located on both sides of the lower air inlet 109 .

[0386] The second water receiving tray 53 is provided with a first baffle 531 close to the lower air inlet. The first water receiving tray 52 is provided with a second baffle 521 close to the lower air inlet 109. The first water receiving tray 52 has a retaining edge 522 on one side away from the first baffle 531. The top of the first baffle 531 is located on the same horizontal plane as the top of the second baffle 521 and the top of the retaining edge 522.

[0387] Two ends of the first baffle plate 531 are connected to two ends of the second baffle plate 521 through two third baffle plates respectively. The two third baffle plates, the second baffle plate 521 and the first baffle plate 531 are enclosed to form the avoidance portion 51 .

[0388] In this embodiment, the top of the first baffle 531 is arranged to be located on the same horizontal plane as the top of the second baffle 521 and the top of the retaining edge 522 to ensure the normal water storage function of the second water receiving tray 53 and the first water receiving tray 52 .

[0389] refer to Fig.46 In this embodiment, the distance between the top of the first baffle 531 and the bottom plate 105 is H9, the distance between the top of the second baffle 521 and the bottom plate 105 is H10, and the distance between the top of the retaining edge 522 and the bottom plate 105 is H11, wherein H11=H9=H10.

[0390] In some embodiments of the present application, the first water receiving tray 52 and the second water receiving tray 53 are connected via a connecting portion 54 .

[0391] Specifically, refer to Fig.47 The connecting portion 54 is located at both ends of the length direction of the lower air inlet 109, and the connecting portion 54 is arranged to be inclined downward from the first water receiving tray 52 to the second water receiving tray 53. By arranging the connecting portion 54 in an inclined manner, the condensed water in the first water receiving tray 52 flows into the second water receiving tray 53 through the connecting portion 54 and merges with the condensed water in the second water receiving tray 53. The drain port is arranged on the second water receiving tray 53 to facilitate the discharge of the condensed water.

[0392] Finally, it should be noted that the above embodiments are only used to illustrate the technical solution of the utility model, rather than to limit it. Although the utility model has been described in detail with reference to the aforementioned embodiments, ordinary technicians in the field should understand that they can still modify the technical solutions recorded in the aforementioned embodiments, or replace some or all of the technical features therein with equivalents. However, these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the scope of the technical solutions of the embodiments of the utility model.

[0393] For the convenience of explanation, the above description has been made in conjunction with specific embodiments. However, the above exemplary discussion is not intended to be exhaustive or limit the embodiments to the specific forms disclosed above. Based on the above teachings, various modifications and variations can be obtained. The selection and description of the above embodiments are to better explain the principles and practical applications, so that those skilled in the art can better use the embodiments and various different variations of the embodiments suitable for specific use considerations.

Claims

1. A duct machine, characterized in that: include: The machine body has air-conditioning inlets and air-conditioning outlets at both ends in the width direction; An indoor heat exchanger is disposed in the machine body and close to the air inlet of the air conditioner; A cross-flow fan is disposed in the machine body and located between the indoor heat exchanger and the air outlet of the air conditioner; under the action of the cross-flow fan, indoor air enters the machine body through the air inlet of the air conditioner, and is output to the room through the air outlet of the air conditioner after heat exchange through the indoor heat exchanger; A front volute tongue, with a gap between it and the cross-flow fan, and the front volute tongue is arranged in an arc shape; The minimum gap between the front volute tongue and the crossflow fan is defined as δ3, and the diameter of the outer edge of the crossflow fan is defined as D, δ3≥0.03D, δ3≤0.06D; An air duct is formed in the body, and the air duct includes: An air outlet duct is formed between the cross-flow fan and the air-conditioning outlet. The sides of the air outlet duct facing each other at both ends in the length direction of the body are air outlet sides. In the direction from the cross-flow fan to the air-conditioning outlet, a constriction structure is formed between the two air outlet sides.

2. A duct machine, characterized in that: include: The machine body has air-conditioning inlets and air-conditioning outlets at both ends in the width direction; An indoor heat exchanger is disposed in the machine body and close to the air inlet of the air conditioner; A cross-flow fan is disposed in the machine body and located between the indoor heat exchanger and the air outlet of the air conditioner; under the action of the cross-flow fan, indoor air enters the machine body through the air inlet of the air conditioner, and is output to the room through the air outlet of the air conditioner after heat exchange through the indoor heat exchanger; A front volute tongue, with a gap between it and the cross-flow fan, and the front volute tongue is arranged in an arc shape; The minimum gap between the front volute tongue and the cross-flow fan is defined as δ3, and the diameter of the outer edge of the cross-flow fan is defined as D, δ3≥0.03D, δ3≤0.06D; wherein the vertical distance between the end of the front volute tongue close to the air inlet of the air conditioner and the cross-flow fan is the minimum gap δ3; An air duct is formed in the body, and the air duct includes: An air outlet duct is formed between the cross-flow fan and the air-conditioning outlet. The sides of the air outlet duct facing each other at both ends in the length direction of the body are air outlet sides. In the direction from the cross-flow fan to the air-conditioning outlet, a constriction structure is formed between the two air outlet sides.

3. The air duct machine according to claim 1 or 2, characterized in that: When the length of the cross-flow fan is not greater than 800 mm, δ3≥0.03D, δ3≤0.045D.

4. The air duct machine according to claim 1 or 2, characterized in that: When the length of the cross-flow fan exceeds 800 mm, δ3>0.045D, δ3≤0.06D.

5. The air duct machine according to claim 1 or 2, characterized in that: The maximum gap between the front volute tongue and the cross-flow fan is defined as δ4, the difference between δ4 and δ3 is Δδ, Δδ≥0.02D, Δδ≤0.04D.

6. The air duct machine according to claim 5, characterized in that: The vertical distance between the end of the front volute tongue close to the air outlet of the air conditioner and the cross-flow fan is the maximum gap δ4.

7. The air duct machine according to claim 6, characterized in that: In the cross-section of the cross-flow fan, the contour line of the front volute tongue has an endpoint A1 close to the air inlet of the air conditioner, and an endpoint An close to the air outlet of the air conditioner, and the gap between the front volute tongue and the cross-flow fan is gradually increased from endpoint A1 to endpoint An.

8. The air duct machine according to claim 1 or 2, characterized in that: It also includes an air guide surface, which is arranged relative to the front volute tongue and toward the air outlet of the air conditioner. The air guide surface and the front volute tongue are connected by an arc transition to form a volute tongue.

9. The air duct machine according to claim 8, characterized in that: It also includes a volute, which is arranged in the body and above the volute tongue, and the cross-flow fan is located between the volute and the volute tongue.

10. The air duct machine according to claim 1 or 2, characterized in that: The indoor heat exchanger comprises at least two sections of heat exchangers, and the at least two sections of the heat exchangers are sequentially connected from top to bottom to form a half-enclosed structure, and the half-enclosed structure half-encloses the cross-flow fan.

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