CN222578371U

CN222578371U - Duct machine

Info

Publication number: CN222578371U
Application number: CN202421306612.9U
Authority: CN
Inventors: 陈科挺; 徐超
Original assignee: Hisense Air Conditioning Co Ltd
Current assignee: Hisense Air Conditioning Co Ltd
Priority date: 2024-06-07
Filing date: 2024-06-07
Publication date: 2025-03-07
Anticipated expiration: 2034-06-07

Abstract

The utility model discloses an air duct machine, and relates to the technical field of air conditioners. The air pipe machine comprises a machine body, an indoor heat exchanger and a cross-flow fan, wherein an air conditioner air inlet and an air conditioner air outlet are respectively formed in two ends of the machine body in the width direction, a water receiving disc is arranged below the indoor heat exchanger and comprises a first water receiving disc and a second water receiving disc, a lower air inlet is formed in the bottom plate along the length direction of the machine body and is positioned between the second water receiving disc and the first water receiving disc, the lower air inlet is communicated with the air conditioner air inlet, and under the action of the cross-flow fan, indoor air enters the machine body through the air conditioner air inlet and the lower air inlet, and is output to the indoor through the air conditioner air outlet after heat exchange of the indoor heat exchanger. Through setting up down the air intake, with the cooperation of air conditioner air intake, reached the purpose that has increased the air inlet area, not only increased the air supply amount of air conditioner, still improved its anti windage performance.

Description

Air duct machine

Technical Field

The utility model relates to the technical field of air conditioners, in particular to an air duct machine.

Background

With the popularity of air conditioning, more and more users choose to install central air conditioning in their homes. The air duct machine is used as a central air conditioner and is favored by users due to the advantages of low manufacturing cost, simple structure, hidden installation and the like. The existing air pipe machine can be installed in a suspended ceiling generally and mainly comprises a machine body, a cross flow fan and an indoor heat exchanger, wherein the cross flow fan and the indoor heat exchanger are installed in the machine body, an air conditioner air inlet and an air conditioner air outlet are formed in the machine body, the cross flow fan introduces air from the air conditioner air inlet into the machine body, and air conditioner air is formed after heat exchange of the indoor heat exchanger and is sent out from the outlet.

Compared with a centrifugal fan air duct machine, the cross flow air duct machine has narrower depth, and can widen the installation scene, such as the position of a cross beam which can be installed at a hanging point of a curtain in a living room. However, due to the limitation of the installation scene on the height and the size of the machine body, the height H of the air inlet of the air conditioner of the through-flow type air pipe machine is limited, and the air inlet quantity of the air pipe machine is limited. In addition, in the related art, due to the requirement of the actual installation position, the horizontal distance between the air conditioner air inlet and the house beam (or the wall surface) is mostly 80-120 mm, the horizontal distance is smaller, the air supply quantity of the air pipe machine is further reduced, the resistance of the air conditioner air inlet of the air pipe machine is overlarge, the risk of wind resistance noise of the whole machine is increased, the performance of the air pipe machine is influenced, the user experience is reduced, and the product competitiveness is reduced.

Disclosure of utility model

The present utility model aims to solve at least one of the technical problems in the related art to some extent. For this purpose,

The utility model provides an air duct machine, comprising:

the air conditioner comprises a machine body, wherein an air conditioner air inlet and an air conditioner air outlet are respectively formed in two ends of the machine body in the width direction, and the machine body comprises a top plate and a bottom plate which are oppositely arranged along the vertical direction;

The indoor heat exchanger is arranged in the machine body and is close to the air inlet of the air conditioner;

The cross-flow fan is arranged in the machine body and is positioned between the indoor heat exchanger and the air outlet of the air conditioner;

the water receiving disc is arranged below the indoor heat exchanger and comprises a first water receiving disc and a second water receiving disc;

The lower air inlet is formed in the bottom plate in the length direction of the machine body and located between the second water receiving disc and the first water receiving disc, the lower air inlet is communicated with the air conditioner air inlet, and under the action of the through-flow fan, indoor air enters the machine body through the air conditioner air inlet and the lower air inlet, and is output to the indoor through the air conditioner air outlet after being subjected to heat exchange through the indoor heat exchanger.

The air pipe machine that this technical scheme provided through setting up down the air intake with be located the air conditioner air intake of one side of organism, compares in prior art only has the technical scheme of air conditioner air outlet, has increased the air inlet area, has not only increased the air supply amount of wind of air conditioner, has still improved its anti windage performance.

The utility model also provides an air duct machine, which comprises:

The machine body is provided with an air conditioner air inlet and an air conditioner air outlet at two ends in the width direction, wherein the horizontal distance between the air conditioner air inlet and a wall is L, L is more than or equal to 80mm and less than or equal to 120mm;

the water receiving disc is arranged below the indoor heat exchanger;

The indoor air enters the machine body through the air conditioner air inlet and the lower air inlet under the action of the through-flow fan, exchanges heat through the indoor heat exchanger and then is output to the indoor through the air conditioner air outlet.

The air duct machine provided by the technical scheme is applicable to the installation environment with smaller horizontal distance between the air conditioner air inlet and the wall, and compared with the technical scheme that the air duct machine only has an air conditioner air outlet in the prior art, the air duct machine has the advantages that the air inlet area is increased, the air supply quantity of the air conditioner is increased, and the wind resistance performance of the air conditioner is improved.

In some embodiments, the indoor heat exchanger comprises a first section heat exchanger, a second section heat exchanger and a third section heat exchanger, the first section heat exchanger, the second section heat exchanger and the third section heat exchanger are sequentially connected from bottom to top to form a half-package structure, and an opening of the half-package structure faces the through-flow fan

In some embodiments, the second heat exchanger is provided with a first connecting end connected with the third heat exchanger, the first water receiving disc is positioned between the air conditioner air inlet and the lower air inlet on the cross section of the through-flow fan, the end point of the first connecting end far away from the through-flow fan is a C point, and the projection of the C point in the vertical direction is positioned in the first water receiving disc and used for receiving condensed water dripped at the joint of the third heat exchanger and the second heat exchanger, so that water drops are prevented from falling through the lower air inlet and user experience is prevented from being influenced.

In some embodiments, the projection of the first section heat exchanger in the vertical direction and the projection of the connection of the first section heat exchanger and the second section heat exchanger in the vertical direction are located in the second water receiving tray and are used for receiving the second section heat exchanger and the condensed water dropped on the first section heat exchanger, so that condensed water drops on the first section heat exchanger are prevented from falling through the lower air inlet, and user experience is prevented from being influenced.

In some embodiments, the first heat exchanger is provided with a second connecting end connected with the second heat exchanger, the first heat exchanger is obliquely arranged from top to bottom towards the air outlet of the air conditioner on the cross section of the through-flow fan, the end point of the second connecting end far away from the through-flow fan is an F point, the distance between the F point and the second water receiving disc is H5, H5 is more than or equal to 20mm, and the air inlet quantity of the first heat exchanger is ensured.

In some embodiments, the second water receiving tray is provided with a first baffle, and a distance between the first baffle and the second section heat exchanger is H6, and H6> H5, so that sufficient airflow is ensured to flow through the first section heat exchanger.

In some of these embodiments, the difference between the distance H6 and the distance H5 is c, c >5mm, avoiding the distance H6 being a bottleneck limiting the air intake of the first stage heat exchanger.

In some embodiments, the first water-receiving tray and the second water-receiving tray are respectively located at two sides of the lower air inlet, a first baffle close to the lower air inlet is arranged on the second water-receiving tray, a second baffle close to the lower air inlet is arranged on the first water-receiving tray, a flange is arranged on one side, away from the first baffle, of the first water-receiving tray, the top end of the first baffle, the top end of the second baffle and the top end of the flange are located on the same horizontal plane, and the arrangement ensures the normal water storage function of the second water-receiving tray and the first water-receiving tray.

In some embodiments, the first water-receiving tray and the second water-receiving tray are communicated through a communicating part, the communicating part is located at two ends of the lower air inlet in the length direction, the communicating part is obliquely downwards arranged from the first water-receiving tray to the second water-receiving tray, condensed water in the first water-receiving tray flows into the second water-receiving tray and is converged with condensed water in the second water-receiving tray, and the condensed water is conveniently discharged.

Drawings

FIG. 1 is a schematic view of an embodiment of an air duct machine according to the present utility model;

FIG. 2 is a schematic view of an embodiment of an air duct machine according to the present utility model from another perspective;

FIG. 3 is a front view of an embodiment of an air duct machine of the present utility model;

FIG. 4 is a cross-sectional view taken along the direction A-A in FIG. 3;

FIG. 5 is a schematic diagram of the connection of an electric auxiliary heat assembly to a heat exchanger assembly in one embodiment of an air duct machine of the present utility model;

FIG. 6 is a schematic view of an embodiment of a ducted air machine according to the present utility model at yet another perspective;

FIG. 7 is a partial enlarged view at G in FIG. 6;

FIG. 8 is an exploded view of a fan assembly in one embodiment of an air duct machine of the present utility model;

FIGS. 9-11 are cross-sectional views of a housing of an embodiment of an air duct machine according to the present utility model;

FIG. 12 is a schematic view of another embodiment of an air duct machine according to the present utility model;

FIG. 13 is a rear view of another embodiment of an air moving machine according to the present utility model;

FIG. 14 is a cross-sectional view taken in the direction B-B of FIG. 13;

FIG. 15 is a cross-sectional view of an internal structure of another embodiment of an air duct machine according to the present utility model, taken along a horizontal direction;

FIG. 16 is a partial cross-sectional view of another embodiment of an air handler of the present utility model;

FIG. 17 is a cross-sectional view of the internal structure of a prior art ducted air machine taken in a horizontal direction;

FIG. 18 is a schematic diagram illustrating the cooperation of a cross-flow fan and a receiving portion in a prior art ducted air conditioner;

FIG. 19 is a partial cross-sectional view of a housing of another embodiment of an air moving machine in accordance with the present utility model;

FIG. 20 is a cross-sectional view of a housing of a further embodiment of an air duct machine according to the present utility model;

FIG. 21 is a partial cross-sectional view of a housing of a further embodiment of an air duct machine according to the present utility model;

FIG. 22 is a cross-sectional view of a chassis of a further embodiment of an air moving machine according to the present utility model;

FIG. 23 is a cross-sectional view showing the internal structure of a housing in accordance with still another embodiment of the present utility model;

FIG. 24 is a schematic view of a diversion plate of yet another embodiment of a ducted air machine in accordance with the present utility model;

FIG. 25 is a cross-sectional view 2 of a housing of a further embodiment of an air duct machine according to the present utility model;

FIG. 26 is a partial cross-sectional view 2 of a housing of a further embodiment of an air moving machine according to the present utility model;

FIG. 27 is a front view of yet another embodiment of an air moving machine according to the present utility model;

FIG. 28 is a schematic view of an indoor heat exchanger in an embodiment of an air duct machine according to the present utility model;

FIG. 29 is a cross-section of the indoor heat exchanger shown in FIG. 28;

FIG. 30 is a cross-sectional view of an air duct machine having the indoor heat exchanger shown in FIG. 28;

FIG. 31 is a partial cross-sectional view of an air duct machine having the indoor heat exchanger shown in FIG. 28;

FIG. 32 is a cross-section of a first stage heat exchanger in one embodiment of an air moving machine according to the present utility model;

FIG. 33 is a velocity cloud of the first stage heat exchanger versus existing conventional direction in one embodiment of the ducted air machine of the present utility model;

FIGS. 34-35 are cross-sectional views of a further embodiment of an air duct machine according to the present utility model, taken along the width of the machine body;

FIGS. 36-37 are partial cross-sectional views of a further embodiment of an air duct machine according to the present utility model, taken along the width of the machine body;

Fig. 38 is a noise spectrum at different minimum gaps δ3 for l7=1000 mm in one embodiment of the ducted air machine of the present utility model;

FIG. 39 is a cross-sectional view of another embodiment of an air duct machine according to the present utility model taken along the length of the machine body;

FIG. 40 is a schematic view of a prior art ducted air machine installation;

FIG. 41 is a cross-sectional view of a lower air intake provided at the bottom of a housing of an embodiment of an air duct machine according to the present utility model;

FIG. 42 is a schematic diagram of a lower air intake and an air intake of an air conditioner in an embodiment of an air duct machine according to the present utility model;

FIG. 43 is a schematic view of a portion of a floor panel with a lower air intake in an embodiment of an air duct machine according to the present utility model;

FIGS. 44-45 are cross-sectional views of an embodiment of an air duct machine according to the present utility model having a lower air intake;

FIG. 46 is a schematic view of air intake from the lower air intake to the air intake in an embodiment of the ducted air machine of the present utility model;

FIG. 47 is an exploded view of a base and a floor of an embodiment of an air duct machine according to the present utility model.

In the above figures, the housing 10, the housing 101, the air conditioner inlet 102, the air conditioner outlet 103, the top plate 104, the bottom plate 105, the first side plate 106, the second side plate 107, the baffle 108, the lower air inlet 109, the air inlet filter assembly 1, the heat exchanger assembly 2, the indoor heat exchanger 21, the reference heat exchanger 211, the first stage heat exchanger 212, the first windward side 2121, the second windward side 2122, the second stage heat exchanger 213, the third stage heat exchanger 214, the fan assembly 3, the cross-flow fan 31, the end cap 311, the driving motor 32, the base 38, the first mounting groove 381, the volute 384, the volute tongue 385, the front volute tongue 3851, the air guide surface 3852, the accommodating part 3861, the air outlet part 389, the air outlet channel 3891, the electric auxiliary heat assembly 4, the water receiving tray 5, the avoiding part 51, the first water receiving tray 52, the second baffle 521, the baffle 522, the second water receiving tray 53, the first baffle 531, the communicating part 54, the water receiving part 55, the temperature detecting assembly 7.

Detailed Description

The present utility model will be specifically described below by way of exemplary embodiments. It is to be understood that elements, structures, and features of one embodiment may be beneficially incorporated in other embodiments without further recitation.

Reference in the specification to "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment may be included in at least one embodiment of the utility model. The appearances of such phrases in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments. It is to be expressly and implicitly understood by those of ordinary skill in the art that the described embodiments of the utility model can be combined with other embodiments without conflict.

In the description of the present utility model, it should be understood that the orientations or positional relationships indicated by the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. are based on the orientation or positional relationships shown in the drawings, merely to facilitate description of the present utility model and simplify description, and do not indicate or imply that the device or element in question must have a specific orientation, be constructed and operate in a specific orientation, and therefore should not be construed as limiting the present utility model.

The terms "first", "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "first", "second" may explicitly or implicitly include one or more such feature.

In the description of the present utility model, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected, directly connected, indirectly connected through an intermediary, or communicating between two elements. The specific meaning of the above terms in the present utility model will be understood in specific cases by those of ordinary skill in the art.

In the present application, a central air-conditioning ducted indoor unit (abbreviated as ducted air conditioner) belongs to an air conditioner, which includes a ducted air conditioner (i.e., an indoor unit of the air conditioner) and an air-conditioning outdoor unit (i.e., an outdoor unit of the air conditioner), which performs a refrigerating cycle of the indoor unit by using a compressor, a condenser, an expansion valve, and an evaporator, the refrigerating cycle including a series of processes involving compression, condensation, expansion, and evaporation, and supplies a refrigerant to air that has been conditioned and heat-exchanged.

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

Fig. 1 to 47 are schematic views illustrating an embodiment of an air duct machine 100 according to the present utility model. The air duct machine 100 is disposed indoors, can be installed in and on a ceiling, and can be used as a living room air conditioner, a curtain air conditioner, and a ceiling air conditioner for exchanging heat with an indoor environment. The air conditioner may include an air conditioner outdoor unit, which is generally disposed outdoors, for taking heat of the indoor space to the outdoor.

Referring to fig. 1 to 3, an air duct machine 100 includes a machine body 10. The body 10 may be installed in a suspended ceiling.

The body 10 has a top end and a bottom end, and the top end of the body 10 and the bottom end of the body 10 are opposite ends of the body 10 in a vertical direction (a height direction of the body 10). The left side of the body 10 and the right side of the body 10 are opposite sides of the body 10 in the longitudinal direction, and the front side of the body 10 and the rear side of the body 10 are opposite sides of the body 10 in the width direction.

Referring to fig. 4, the body 10 defines a receiving chamber 101 therein. The accommodating cavity 101 is used for accommodating and fixing various components in the air duct machine 100, so that collision between foreign objects and various components in the machine body 10 can be avoided, and reliability in transportation or installation of the air duct machine 100 can be improved.

In some embodiments of the present application, referring to fig. 2, the body 10 may include an air conditioning intake 102.

The air conditioner air intake 102 communicates with the accommodation chamber 101. The air conditioner air intake 102 serves as an inlet into which air outside the machine body 10 flows, allowing indoor air to enter the accommodating chamber 101 from the air conditioner air intake 102.

In some embodiments of the present application, ductwork machine 100 may include an intake air filter assembly 1. The air inlet filter assembly 1 is installed at the air inlet 102 of the air conditioner, and can filter indoor air entering the air inlet 102 of the air conditioner, so that dust and magazines are prevented from entering the machine body 10.

In some embodiments of the present application, referring to fig. 3, the body 10 may include an air conditioner outlet 103.

The air-conditioning outlet 103 communicates with the accommodating chamber 101, and the air-conditioning outlet 103 serves as an outlet for the heat exchange air flow in the machine body 10, allowing the air flow in the accommodating chamber 101 to flow out from the air-conditioning outlet 103.

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

Referring to fig. 5, the body 10 may include a top plate 104. The top plate 104 forms the top end of the machine body 10.

The body 10 may include a base plate 105. The bottom plate 105 forms the bottom end of the body 10, and the top end and the bottom end are opposite ends of the body 10 which are opposite to each other in the thickness direction thereof.

The body 10 may include two side plates. The two side plates are two ends of the machine body 10 which are oppositely arranged along the length direction of the machine body, and are connected to the left side and the right side of the top plate 104. The two side plates are a first side plate 106 and a second side plate 107 respectively.

The 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 conditioner outlet 103.

The body 10 may include a rear panel. The front panel forms the rear end of the body 10 and is provided with an air conditioning inlet 102.

Wherein, the top plate 104, the bottom plate 105, the two side plates, the front panel and the rear panel enclose to form the accommodating cavity 101.

The top plate 104, the bottom plate 105, the side plates, the front plate, and the rear plate may be connected in a split manner or may be integrated.

In this embodiment, both ends of the side plates in the width direction of the body 10 are respectively bent toward opposite side surfaces to form a front panel and a rear panel of the portion. Thus, the end portions surrounded by the top plate 104, the bottom plate 105, and the both side plates form an air-conditioning air intake 102 located at the rear side of the machine body 10 and an air-conditioning air outlet 103 located at the front side of the machine body 10. The two side plates are a first side plate 106 and a second side plate 107, respectively.

It should be noted that the directions described herein are based on the direction in which the user faces the ductwork machine 100, wherein the front side is defined as the side facing the user when the ductwork machine 100 is in use, the rear side is defined as the opposite side, the left side and the right side are distinguished from each other in the direction in which the user faces the ductwork machine 100, and the upper side and the lower side are defined to distinguish between the upper side and the lower side when the ductwork machine 100 is generally operating normally.

Ductwork machine 100 may include a heat exchanger assembly 2. The heat exchanger assembly 2 is arranged in the receiving chamber 101. Referring to fig. 4, the heat exchanger assembly 2 may include an indoor heat exchanger 21. The indoor heat exchanger 21 is for heat exchange with air entering the machine body 10.

The ducted air machine 100 may include a blower assembly 3. The fan assembly 3 is disposed within the receiving cavity 101. With continued reference to fig. 4, the fan assembly 3 may include a cross-flow fan 31. Under the action of the cross-flow fan 31, indoor air outside the machine body 10 enters the accommodating cavity 101 through the air conditioner air inlet 102, and air in the accommodating cavity 101 can flow along the air conditioner air inlet 102 towards the air conditioner air outlet 103.

When the air pipe machine 100 operates, under the action of the through-flow fan 31, indoor air enters the accommodating cavity 101 through the air conditioner air inlet 102, the indoor air in the accommodating cavity 101 exchanges heat through the indoor heat exchanger 21, and the heat exchange air flow after the heat exchange is discharged to the indoor outside through the air conditioner air outlet 103, so that the air conditioner is used for refrigerating and heating, the effect of adjusting the indoor air temperature is achieved, and the comfortable temperature of a user is achieved.

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

That is, the cross flow fan 31 is located between the air conditioner air outlet 103 and the indoor heat exchanger 21, and the cross flow fan 31 rotates to introduce indoor air from the air conditioner air inlet 102 into the machine body 10, and the air conditioner air is formed after heat exchange by the indoor heat exchanger 21 and is sent out from the air conditioner air outlet 103.

The cross flow fan 31 is provided to extend in the longitudinal direction of the machine body 10. That is, the longitudinal direction of the body 10 is the axial direction of the cross flow fan 31. Because the cross-flow fan 31 has smaller volume, the volume of the air duct machine 100 is further reduced, the depth of the suspended ceiling is reduced, the narrow depth requirement is met, the problem of room depression is solved, and the aesthetic property of the room is improved.

In this embodiment, the indoor heat exchanger 21 may be a multi-stage heat exchanger. The indoor heat exchanger 21 comprises a plurality of sections of heat exchangers, so that the indoor heat exchanger 21 is in a half-package structure, part of the cross-flow fans 31 are arranged in the half-package structure of the indoor heat exchanger 21, the original separation arrangement of the cross-flow fans 31 and the indoor heat exchanger 21 is changed into the overlapping arrangement of the cross-flow fans 31 and the indoor heat exchanger 21, and the space occupied by the indoor heat exchanger 21 and the cross-flow fans 31 is greatly reduced under the condition that the volumes of the cross-flow fans 31 and the indoor heat exchanger 21 are unchanged.

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

In some embodiments of the present application, ducted air machine 100 may include a base 38. The base 38 is disposed in the accommodating chamber 101 for mounting the fan assembly 3 and the heat exchanger assembly 2.

In some embodiments of the present application, with continued reference to 5, the ducted air machine 100 may include an electrical auxiliary heat assembly 4. The electric auxiliary heating assembly 4 is detachably connected to the heat exchanger assembly 2 and is used for heating the air flow in the machine body 10.

The air duct machine 100 may include a temperature detection assembly 6. Referring to fig. 6 and 7, the temperature detecting assembly 6 is disposed on the machine body 10 for detecting the indoor environment temperature. The temperature detecting assembly 6 is in communication with the electric control board to transmit the detected indoor environment temperature to the electric control board, so that various actions of the subsequent air duct machine 100 can be controlled.

In some embodiments of the present application, referring to fig. 8, the base 38 is provided at one end thereof in the length direction with a first mounting groove 381. Wherein the first installation groove 381 is located at one end in the axial direction of the cross flow fan 31.

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

In some embodiments of the present application, the ductwork machine 100 may include a drip tray 5. The water pan 5 is arranged at the bottom of the accommodating cavity 101 and is used for accommodating condensed water flowing down from the indoor heat exchanger 21 when the air pipe machine 100 works, and a water outlet is arranged on the water pan 5 and is used for discharging the condensed water in the water pan 5 out of the air pipe machine 100.

The air conditioner outdoor unit may include an outdoor case. An outdoor heat exchange air duct can be arranged in the chamber outer shell. The outdoor housing may include an outdoor air inlet. The outdoor air inlet can be communicated with the outdoor heat exchange air duct. The outdoor air inlet may be used to introduce outdoor air into the outdoor heat exchange air duct.

The outdoor housing may include an outdoor air outlet. The outdoor air outlet can be communicated with the outdoor heat exchange air duct. The outdoor air outlet can be used for leading out air in the outdoor heat exchange air duct to the outside of the outdoor heat exchange air duct.

The air conditioner outdoor unit may include an outdoor heat exchanger. The outdoor heat exchanger can be arranged in the outdoor heat exchange air duct. The air conditioner external unit may include an outdoor fan. The outdoor fan can be arranged in the outdoor heat exchange air duct. The outdoor fan rotates to enable the outdoor air to enter the heat exchange air duct from the outdoor air inlet to exchange heat with the outdoor heat exchanger, and the heat exchanged outdoor air flows out of the outdoor heat exchange air duct from the outdoor air outlet.

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

The air conditioner may include a throttle device. The throttling device is used for throttling. The throttle device may be provided in the ducted air machine 100 or in an external air conditioner.

The air conditioner performs a refrigerating 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 a refrigerant to the air that has been conditioned and heat exchanged.

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

The expansion device expands the liquid-phase refrigerant in a high-temperature and high-pressure state condensed in the condenser into a low-pressure liquid-phase refrigerant. Wherein the throttling means may be an expansion valve.

The evaporator evaporates the refrigerant expanded in the throttle device and returns the refrigerant gas in a low-temperature and low-pressure state to the compressor.

The evaporator may achieve a cooling effect by exchanging heat with a material to be cooled using latent heat of evaporation of a refrigerant. The air conditioner may adjust the temperature of the indoor space throughout the cycle.

In both the indoor heat exchanger 21 and the outdoor heat exchanger, one of them is a condenser and the other is an evaporator, and when the indoor heat exchanger 21 is used as the condenser, the air conditioner is used as a heater of a heating mode, and when the indoor heat exchanger 21 is used as the evaporator, the air conditioner is used as a cooler of a cooling mode.

The air duct machine 100 may include an electronic control assembly 7. The electric control assembly 7 may include an electric control board, and the electric control board is electrically connected to the electric components inside the machine body 10 through electric control wires.

It will be appreciated that the electronic control board is configured to be electrically connected to at least the compressor, the expansion valve and the cross flow fan 31 through at least electronic control, so as to control at least the compressor, the expansion valve and the cross flow fan 31, thereby controlling the operation of the whole air duct machine 100, and realizing each predetermined function of the air conditioner.

The electric control board can be in signal transmission with the wire controller or the remote controller through a connecting communication wire. The line controller or the remote controller sends out an air conditioner control signal for controlling the air conditioner, and the electric control board is used for receiving the air conditioner control signal to control the air duct machine 100 to work.

Referring to fig. 8-11, in other embodiments, the fan assembly 3 may include a volute tongue 385, where the volute tongue 385 is disposed within the body 10. The volute tongue 385 has a substantially tongue-shaped structure.

The fan assembly 3 may include a volute 384, the volute 384 being disposed within the housing 10 above the volute tongue 385.

An air channel is formed between the volute 384 and the volute tongue 385. Wherein the volute 384 forms a top wall of the air duct, the volute tongue 385 forms a 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.

Referring to fig. 9, the volute tongue 385 may include a front volute tongue 3851, with the front volute tongue 3851 being disposed toward the cross-flow fan 31. That is, the front volute tongue 3851 is the windward side of the volute tongue 385.

In this embodiment, the front volute tongue 3851 is configured in an arc shape. By arranging the front volute tongue 3851 in an arc shape, when eccentric vortex is generated, air flow of the eccentric vortex can smoothly pass through the front volute tongue 3851, and wind resistance is reduced.

That is, the scroll 385 has an arc surface at a side close to the cross-flow fan 31, and the arc surface can reduce noise generated by air flow in the air duct.

With continued reference to fig. 9, the indoor heat exchanger 21 may include at least two stage heat exchangers. Wherein, the heat exchanger closest to the front volute tongue 3851 of the at least two heat exchangers is defined as the reference heat exchanger 211.

The direction defining the vertical line from the center O of the cross flow fan 31 to the reference heat exchanger 211 is the X direction, the direction rotating 90 ° toward the air conditioner air outlet 103 is the Y direction, the point of the front volute tongue 3851 closest to the cross flow fan 31 is the A1 point, and the point of the reference heat exchanger 211 farthest from the center O in the Y direction is the B point.

The orthographic projection of the A1 point on the Y axis is defined as the A1' point, the orthographic projection of the O point on the Y axis is defined as the O ' point, and the orthographic projection of the B point on the Y axis is defined as the B ' point. Wherein, on the Y axis, A1' point is located between O ' point and B ' point.

According to the air duct machine provided by the embodiment, the front projection A1' of the A1 point on the Y axis is arranged between the front projection O ' of the O point on the Y axis and the front projection B ' of the B point on the Y axis, and 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 achieves larger air quantity and stronger wind resistance.

In other embodiments of the present application, with continued reference to fig. 9, the indoor heat exchanger 21 may comprise a two-stage heat exchanger defining a perpendicular from point A1 to the reference heat exchanger 211 as a first perpendicular P. The point B is located on a side of the first perpendicular line P away from the cross flow fan 31. Through setting up the B point in the first perpendicular that the A1 point is located and keeping away from one side of cross flow fan 31, carry out reasonable setting to the relative position of cross flow fan 31, indoor heat exchanger 21 and preceding volute tongue 3851 for the cross flow wind channel realizes bigger amount of wind and stronger anti-wind resistance performance.

In the air duct machine provided in this embodiment, the B point is located at a side of the first vertical line P far from the cross flow fan 31, and is actually tested together with the air duct machine located at a side of the first vertical line close to the cross flow fan 31, and under the same rotation speed, the air volume of the air duct machine located at a side of the first vertical line far from the cross flow fan 31 is 9% higher than that of the air duct machine located at a side of the first vertical line close to the cross flow fan 31, so that the wind resistance performance is improved by 4 layers of 40 mesh filter screens.

In other embodiments of the application, the volute tongue 385 may include a wind-guiding surface 3852. The air guiding surface 3852 is disposed opposite to the front volute tongue 3851 towards the air outlet 103, so as to achieve a linear guiding effect on the air flow in the air duct, so as to further avoid the problem of air loss at the air outlet 103 in the working process of the air duct.

In other embodiments of the present application, the ducted air conditioner may include a water tray 5, the water tray 5 being located below the indoor heat exchanger 21 for receiving condensed water dripping on the indoor heat exchanger 21.

In this embodiment, the water receiving tray 5, the volute tongue 385 and the volute tongue 385 are integrally formed. Wherein, the bottom wall of the water receiving disc 5 is connected with the front volute tongue 3851 through a water retaining part,

In other embodiments of the present application, referring to fig. 10, the distance between points A1 and B in the Y direction has a dimension d. D is less than or equal to 10 mm. d is less than or equal to 18mm.

The distance d between the point A1 and the point B cannot be too large, and the wall surface (water retaining part) between the point A1 and the point B in the air channel blocks the air inlet flow of the reference heat exchanger 211. In order not to block the intake air flow of the reference heat exchanger 211, the distance dimension d is set to be not more than the first parameter value. For example, the first parameter value may be 18mm,17.5mm, or 17mm. A specific one of the parameters is selected as appropriate in consideration of the specific design.

The distance d between the point A1 and the point B cannot be too small, and the wind resistance performance is not improved. In order to improve the wind resistance performance, the distance dimension d is set to be not smaller than the second parameter value. For example, the second parameter value may be 10mm,10.5mm, or 11mm. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In other embodiments of the application, at least two of the heat exchangers are plate heat exchangers. At least two plate-shaped heat exchangers are sequentially connected from top to bottom to form a half-package structure. The half-bag structure has an opening of the cross-flow fan 31. The indoor heat exchanger 21 with the structure at least partially surrounds the periphery of the cross-flow fan 31, so that the heat exchange efficiency is improved, and the volume of the air pipe machine is reduced.

With continued reference to fig. 10, the indoor heat exchanger 21 may include two heat exchangers, a reference heat exchanger 211 and a second heat exchanger 213, respectively. The second heat exchanger 213 is located above the reference heat exchanger 211, and one end of the second heat exchanger 213 is connected to one end of the reference heat exchanger 211 to form a V-shaped structure with an opening facing the cross-flow fan 31.

In other embodiments of the present application, the minimum distance between the reference heat exchanger 211 and the cross-flow fan 31 is δ5. Wherein delta 5 is more than or equal to 15mm. Delta 5 is less than or equal to 20mm.

The minimum distance delta 5 cannot be too small, and if too small, the distance between the reference heat exchanger 211 and the cross flow fan 31 is too small, so that the air flow driven by the cross flow fan 31 impacts the reference heat exchanger 211, thereby causing different frequency multiplication noise and increasing the noise of the air duct machine. In order to improve the sound quality level, the minimum distance δ5 is set to be not smaller than the third parameter value. For example, the third parameter value may be 15mm,15.5mm, or 16mm. A specific one of the parameters is selected as appropriate in consideration of the specific design.

The minimum distance delta 5 cannot be too large, and the air intake is not facilitated when the minimum distance delta 5 is too large. In order to increase the intake air volume, the minimum distance δ5 is set to be not greater than the fourth parameter value. For example, the fourth parameter value may be 20mm,19.5mm, or 19mm. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In other embodiments of the present application, the reference heat exchanger 211 is disposed at an angle to the horizontal, and the free end of the reference heat exchanger 211 is lower than the connecting end of the reference heat exchanger 211.

The free end of the reference heat exchanger 211 (the end that is not connected to the other section heat exchanger) is close to the air-conditioning outlet 103 with respect to the connection end thereof. 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 condensed water on the indoor heat exchanger 21 flows to the free end of the reference heat exchanger 211.

In other embodiments of the application, the front volute tongue 3851 is curved.

Referring to fig. 11, in a cross section of the cross-flow fan 31, a front volute tongue 3851 is provided at a distance from the cross-flow fan 31. The distance between the point A1 and the cross-flow fan 31 is the minimum distance δ1. Delta 1 is more than or equal to 0.03D. δ1 is less than or equal to 0.045D.

The cross-flow fan 31 has end caps 311 at both ends, and the cross-flow fan 31 has a plurality of intermediate plates disposed at intervals in the axial direction thereof. That is, a plurality of middle joint plates are disposed between the two end caps 311 at intervals. Wherein, the middle section plate is in a circular ring shape.

The diameter of the outer edge of the cross-flow fan 31 described herein is the diameter of the outer edge of the middle panel.

The minimum distance delta 1 cannot be too large, and the air leakage is serious and the air quantity is reduced due to the too large distance. In order to secure the air volume performance, the minimum distance δ1 is set to be not more than the fifth parameter value. For example, the fifth parameter value may be 0.045D,0.044D, or 0.042D. A specific one of the parameters is selected as appropriate in consideration of the specific design.

The minimum distance δ1 cannot be too small, which would result in a high noise value, and there is a risk of collision of the cross-flow fan 31 with the front volute tongue 3851. In order to improve the sound quality of the ducted air machine, to improve the working efficiency of the cross flow fan 31, to reduce noise, the minimum distance δ1 is set to be not smaller than the sixth parameter value. For example, the sixth parameter value may be 0.03d,0.032D, or 0.034D. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In other embodiments of the present application, the distance between the point A1 and the cross-flow fan 31 is the minimum distance δ1.0.03D is less than or equal to delta 1 and less than or equal to 0.045D.

The minimum distance delta 1 between the front volute tongue 3851 and the cross-flow fan 31 is set within a reasonable range, so that serious whistle noise is avoided while the air inlet quantity of a gap is ensured, and meanwhile, the cross-flow fan 31 is prevented from shaking and colliding with the front volute tongue 3851 in the transportation process.

In other embodiments of the present application, the maximum distance between the front volute tongue 3851 and the cross-flow fan 31 is δ2. Wherein δ2 is greater than or equal to 0.06D, δ2 is less than or equal to 0.075D, D is the diameter of the outer edge of the cross-flow fan 31.

The maximum distance δ2 cannot be too small, and when the maximum distance δ2 is too small, the eddy noise generated by the airflow may increase significantly. In order to improve the sound quality level of the ductwork machine, the maximum distance δ2 is not smaller than the seventh parameter value. For example, the seventh parameter value may be 0.06D,0.063D, or 0.065D. A specific one of the parameters is selected as appropriate in consideration of the specific design.

When the maximum distance δ2 is too large, the return air tends to increase at a low rotation speed of the cross flow fan 31, resulting in serious loss and leakage of the air guide flow, and a decrease in the air output. In order to reduce the air leakage and improve the air output, the maximum distance δ2 is set to be not greater than the eighth parameter value. For example, the eighth parameter value may be 0.075D,0.073D, or 0.071D. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In some embodiments of the application, the volute tongue 385 may include a wind-guiding surface 3852. Referring to fig. 11, the air guiding surface 3852 is disposed near the air outlet 103 of the air conditioner with respect to the front volute tongue 3851.

The air guiding surface 3852 is disposed towards the air outlet 103 of the air conditioner, so as to achieve a linear guiding effect on the air flow in the air duct, and further avoid the problem of air loss at the air outlet 103 in the working process of the air duct.

In some embodiments of the present application, the air guiding surface 3852 and the front volute tongue 3851 are connected in a circular arc transition to form the volute tongue 385. The arrangement can make the connection between the front volute tongue 3851 and the air guiding surface 3852 smoother, and the air flow transition is more natural and smooth, so as to achieve the purpose of further improving the air flow stability of the cross-flow fan 31.

Referring to fig. 12-16, 19, in some embodiments of the application, the wind tunnel may include an outlet wind tunnel 3892. The air outlet channel 3892 is formed between the cross-flow fan 31 and the air outlet 103.

Specifically, under the action of the cross-flow fan 31, indoor air enters the machine body 10 through the air conditioner air inlet 102, enters the air outlet air duct 3892 after exchanging heat through the indoor heat exchanger 21, and the heat exchange air flow in the air outlet air duct 3892 is output to the indoor through the air conditioner air outlet 103.

In some embodiments of the application, the fan assembly 3 may include two air outlets 389. Referring to fig. 14, two air outlet portions 389 form both ends of an air outlet duct 3892 in the longitudinal direction of the machine body 10, respectively.

The top end of the air outlet part is connected with the volute tongue, and the bottom end of the air outlet part is connected with the volute tongue.

The sides of the two air outlet portions 389 facing each other are air outlet sides 3891, and the air outlet sides 3891 have an air inlet end and an air outlet end. In this embodiment, the air inlet end is close to the cross-flow fan 31 relative to the air outlet end.

With continued reference to fig. 14, in some embodiments of the application, the air outlet end of at least one air outlet side 3891 is proximate to the center of the air conditioner outlet 103 relative to the air inlet end.

Specifically, the air outlet end of the at least one air outlet side 3891 is close to the center of the air outlet 103 of the air conditioner relative to the air inlet end, so that the air flow channel between the at least one air outlet side 3891 and the air outlet 103 of the air conditioner is in a necking structure. That is, in the length direction of the machine body 10, the air inlet end and the air outlet end of at least one air outlet side 3891 have a distance dimension therebetween.

In this embodiment, the air outlet end of at least one air outlet side 3891 is set to be close to the center of the air outlet 103 of the air conditioner relative to the air inlet end, so that the air outlet end of at least one air outlet side 3891 is contracted from the air inlet end to the perpendicular bisector of the air outlet 103 of the air conditioner, on one hand, the speed of the air outlet flow of the end region of the through-flow fan 31 corresponding to the at least one air outlet side 3891 is increased, and on the other hand, a forward pressure gradient along the air outlet flow direction is formed on the at least one air outlet side 3891, which can effectively inhibit the air flow separation and return phenomena possibly generated on the air outlet side 3891, enhance the wind resistance performance, and avoid the surge and return phenomena.

In some embodiments of the present application, the air outlet ends of the two air outlet sides 3891 are located near the center of the air conditioner outlet 103 with respect to the air inlet ends.

Referring to fig. 15, the air outlet ends of the two air outlet sides 3891 are disposed near the center of the air conditioner air outlet 103 with respect to the air inlet end, such that the air outlet ends of the two air outlet sides 3891 are contracted from the air inlet end to the perpendicular bisector of the air conditioner air outlet 103, so that a necking structure is formed between the two air outlet sides 3891 in the direction from the cross flow fan 31 to the air conditioner air outlet 103.

Specifically, the air outlet ends of the two air outlet side surfaces 3891 are both set to be close to the center of the air outlet 103 of the air conditioner relative to the air inlet end, so that on one hand, the speed of the air outlet flow of the two end areas of the cross-flow fan 31, namely, the wind speed of the two ends of the air duct machine, is improved, and on the other hand, a forward pressure gradient along the air outlet flow direction is formed on the two air outlet side surfaces 3891, so that the wind resistance performance is enhanced, and the surge and return air phenomena are avoided.

In some embodiments of the present application, the air outlet 389 may be an air outlet side plate with an air outlet end bent or inclined toward a perpendicular bisector of the air outlet 103 of the air conditioner with respect to an air inlet end.

In some embodiments of the present application, the distance between the two ends of the air outlet side 3891 in the width direction of the machine body 10 is L3. Wherein L3 is more than or equal to 10mm. L3 is less than or equal to 15mm.

It is understood that the distance L3 between the two ends of the air outlet side 3891 in the width direction of the machine body 10 may be determined by the length of the air outlet channel 3892.

The distance L3 cannot be too large, which results in an excessively large length of the air outlet duct 3892, thereby increasing the width of the machine body 10. In order to reduce the volume of the ductwork machine, the distance dimension L3 is set to be no greater than the ninth parameter value. For example, the ninth parameter value may be 15mm,14.5mm, or 14mm. A specific one of the parameters is selected as appropriate in consideration of the specific design.

The distance L3 cannot be too small, which results in too small a length of the air outlet air duct 3892, which affects the air volume and the wind resistance of the air duct. In order not to reduce the air volume of the air duct, the distance dimension L3 is set to be not smaller than the tenth parameter value. For example, the tenth parameter value may be 10mm,10.5mm, or 11mm. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In some embodiments of the present application, the distance between the two ends of the air outlet side 3891 in the width direction of the machine body 10 is L3. L3 is less than or equal to 10mm is less than or equal to 15mm.

In this embodiment, by setting the distance L3 within a reasonable range, the length of the air outlet channel 3892 is within a reasonable range, so as to reduce the volume of the air duct machine and avoid affecting the air volume and the wind resistance.

In some embodiments of the present application, referring to fig. 16, a distance between both ends of the air outlet side 3891 in a length direction of the body 10 is L4 in size. L4'0.5D. L4 is less than or equal to D. Wherein D is the diameter of the outer edge of the cross-flow fan 31.

The distance L4 cannot be too large, which would affect the normal outlet airflow velocity in the middle of the cross flow fan 31. In order to reduce the volume of the ducted air machine, the distance dimension L4 is set to be not more than the eleventh parameter value without affecting the air-out air flow in the middle region of the cross flow fan 31. For example, the eleventh parameter value may be D,0.95D, or 0.9D. A specific one of the parameters is selected as appropriate in consideration of the specific design.

The distance L4 cannot be too small to allow the cross flow fan 31 to function as a low-speed air flow at one end. In order for the air outlet side surface 3891 to function as a low-speed air flow at one end of the cross flow fan 31, the distance dimension L4 is set to be not smaller than the twelfth parameter value. For example, the twelfth parameter value may be 0.5D,0.55D, or 0.6D. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In some embodiments of the present application, the distance between the two ends of the air outlet side 3891 in the longitudinal direction of the machine body 10 is L4. L4 is more than or equal to 0.5D and less than or equal to D. Through setting the distance L4 within a reasonable range between 0.5D and D, on one hand, the air outlet side surface 3891 can play a role of gathering low-speed air flow at the end part of the cross flow fan 31, and on the other hand, the normal flow speed of the air flow in the middle area of the cross flow fan 31 is not influenced, so that the air speed at the end part of the air pipe machine is improved, and the overall wind resistance performance is improved.

In some embodiments of the present application, the air outlet 389 is disposed with a curve on the air outlet side 3891 in a horizontal cross section, and the curve (contour line) of the air outlet side 3891 is a single-segment curve or a multi-segment curve.

Specifically, the single-segment curve may be a circular arc or a straight line. With continued reference to 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 from the cross-flow fan 31 to the air outlet 103 toward the perpendicular bisector of the air outlet 103.

The multiple segments in the multi-segment curve may be continuous curve segments or straight segments. That is, the curve of the air outlet side surface 3891 may be a continuous curve or a multi-segment straight line, so that the air outlet side surface 3891 is bent from the direction from the cross flow fan 31 to the air outlet 103 toward the direction of the perpendicular bisector of the air outlet 103.

In some embodiments of the present application, the air outlet 389 has a tapered structure between the air outlet side 3891 and the center line of the air outlet 103 in a horizontal cross section. The arrangement effectively enables the side surface to form a forward pressure gradient along the air flow direction of the air outlet, and further effectively inhibits the air flow separation and air return phenomena possibly generated in the side surface area.

In some embodiments of the present application, the fan assembly 3 may include two receiving portions 3861 disposed opposite to each other, and both ends of the cross-flow fan 31 are disposed in the two receiving portions 3861, respectively. Wherein, the accommodating portion 3861 is a cylindrical groove structure.

In the related art, referring to fig. 17 and 18, in order to improve the wind resistance of the wind tunnel, the through-flow fan 31 is mounted by wrapping the root portions at both ends of the through-flow fan 31 with the receiving portions 3861. The depth of the accommodating portion 3861 is L5, and the actual insertion depth of the cross-flow fan 31 is L6. Although the wind resistance performance of the air duct machine can be improved, the working capacity of the cross-flow fan 31 with the length of 2 x L6 is directly sacrificed, and the full representation of the capacity of the cross-flow fan 31 is not facilitated.

In order to solve the above-mentioned problems, in the present embodiment, the accommodating portion 3861 is wound around the outer periphery of the end cover, and a portion of the end cover extends into the accommodating portion 3861 in the axial direction of the cross-flow fan 31.

That is, referring to fig. 19, in the present embodiment, only the end cap portions at the two ends of the cross-flow fan 31 are inserted into the accommodating portion 3861, i.e. the accommodating portion 3861 wraps the end of the end cap 311 away from the opposite end cap 311, so as to ensure that the blades of the cross-flow fan 31 are all located in the air duct, and further ensure that all the blades of the cross-flow fan 31 can perform work normally.

Referring to fig. 12 and 14, in the present embodiment, the air inlet ends of the two air outlet sides 3891 are respectively connected to the two accommodating portions 3861, and the air outlet ends of the two air outlet sides 3891 are bent toward the direction of the perpendicular bisector of the air outlet 103 of the air conditioner relative to the air inlet ends, so that the two air outlet sides 3891 can collect the air outlet flow in the end region of the cross-flow fan 31 in time. The air outlet ends of the two air outlet sides 3891 are respectively connected to two side walls of the air conditioner air outlet 103 in the length direction.

Referring to fig. 20-26, in other embodiments of the present application, the indoor heat exchanger 21 may include at least two stages of heat exchangers. At least two sections of heat exchangers are sequentially connected from top to bottom to form a half-package structure. Wherein the half-package structure half-packages the cross-flow fan 31.

Wherein one of the at least two heat exchangers that is relatively close to the bottom plate 105 is defined as a first heat exchanger 212.

Referring to fig. 20, the first stage heat exchanger 212 is located below the cross flow fan 31.

In some embodiments of the application, the ducted air machine may include a water tray 5. The water pan 5 is arranged on the bottom plate 105, and the water pan 5 is arranged below the indoor heat exchanger 21 and is used for receiving condensed water dropped from the indoor heat exchanger 21.

Wherein, an included angle that the opening faces the air conditioner air inlet 102 is formed between the first heat exchanger 212 and the plane of the bottom plate 105. Wherein the first stage heat exchanger 212 is a plate heat exchanger.

Specifically, an included angle is formed between the first heat exchanger 212 and the plane where the bottom plate 105 is located, so that the first heat exchanger 212 is obliquely arranged, and an opening of the included angle faces the air conditioner air inlet 102, so that a free end of the first heat exchanger 212 is lower than a connection end of the first heat exchanger 212. When the air duct mechanism is in operation, condensed water on the indoor heat exchanger 21 can be gathered at the free end thereof and dropped into the water pan 5.

In the related art, there is a technical solution that the first stage heat exchanger 212 is disposed parallel to the bottom plate 105, and this solution can cause condensed water on the indoor heat exchanger 21 to gather on the first stage heat exchanger 212, which is not beneficial to improving heat exchange efficiency. In addition, there is also a technical scheme that the first heat exchanger 212 is obliquely arranged, when the air pipe machine is in operation, condensed water on the indoor heat exchanger 21 gradually flows down along the evaporator and finally can be gathered in an area of the first heat exchanger 212 close to the water receiving disc 5 to cause the increase of air inlet resistance of the area, on the other hand, the first heat exchanger 212 is plate-shaped, and due to the existence of the water receiving disc 5, the air inlet height of one side of the first heat exchanger 212 far away from the air conditioner air inlet 102 is extremely small, and can cause negative influence on the air inlet quantity of the side area, so that the air inlet uniformity of the first heat exchanger 212 is influenced, the heat exchange efficiency is influenced, the air inlet effect of the area is highly relevant to the air resistance performance of the air pipe machine, the insufficient air inlet effect can also obviously reduce the air resistance performance of the air pipe machine, and the user experience is poor.

In order to solve the above technical problem, referring to fig. 20, the minimum distance between the first heat exchanger 212 and the water pan 5 is H1. H1 And is more than or equal to 6mm.

The minimum distance between the first heat exchanger 212 and the water receiving tray 5 is the vertical distance between the free end of the first heat exchanger 212 and the water receiving tray 5.

According to the air duct machine provided by the embodiment, the first section of heat exchanger 212 is arranged to form an included angle with the bottom plate 105, so that condensed water on the indoor heat exchanger 21 can flow from the free end of the first section of heat exchanger 212 to the water receiving disc 5, and the condensed water is convenient to receive, meanwhile, the minimum distance between the first section of heat exchanger 212 and the water receiving disc 5 is set to be not less than 6mm, the air inlet quantity of the area, closest to the water receiving disc 5, of the indoor heat exchanger 21 (the free end of the first section of heat exchanger 212) is increased, the wind resistance performance of the air duct machine is improved, the air inlet uniformity of the first heat exchanger is improved, the heat exchange efficiency of the first heat exchanger is improved, and the heat exchange efficiency of the indoor heat exchanger 21 is further improved.

In some embodiments of the present application, the first stage heat exchanger 212 extends obliquely from top to bottom in a direction toward the air conditioner outlet 103. Wherein, the minimum distance between the first heat exchanger 212 and the water receiving tray 5 is H1. H1 And is more than or equal to 6mm.

Specifically, the first heat exchanger 212 extends obliquely from top to bottom in a direction approaching the air outlet 103 of the air conditioner, so that the free end of the first heat exchanger 212 is lower than the connection end of the first heat exchanger. The minimum distance between the first heat exchanger 212 and the water pan 5 is H1, i.e. the vertical distance between the free end of the first heat exchanger 212 and the water pan 5 is the minimum distance H1.

According to the air duct machine provided by the embodiment, the first section of heat exchanger 212 is obliquely arranged, so that condensed water on the indoor heat exchanger 21 can flow from the free end of the first section of heat exchanger 212 to the water receiving disc 5, the condensed water can be conveniently received, meanwhile, the minimum distance between the first section of heat exchanger 212 and the water receiving disc 5 is set to be not less than 6mm, the air inlet quantity of the area, closest to the water receiving disc 5, of the indoor heat exchanger 21 (the free end of the first heat exchanger) is increased, the wind resistance performance of the air duct machine is improved, the air inlet uniformity of the first heat exchanger is improved, and the heat exchange efficiency of the indoor heat exchanger 21 is improved.

To further increase the air intake of the first stage heat exchanger 212 in the area proximate to the drip tray 5, the air resistance of the ductwork may be further increased, and in some embodiments of the present application, the ductwork may include a baffle 108.

Referring to fig. 20-23, the baffle 108 is positioned between the first stage heat exchanger 212 and the drip tray 5. Wherein the baffle 108 extends along the length of the body 10.

In this embodiment, two ends of the deflector 108 in the longitudinal direction are connected to two side walls of the air duct in the longitudinal direction. In cross section of the baffle 108, the baffle 108 has an air inlet end and an air outlet end.

The height of the air inlet end of the deflector 108 is greater than the height of the air outlet end of the deflector 108. That is, the baffle 108 tends to extend from back to front toward a direction approaching the bottom plate 105.

In this embodiment, referring to fig. 24, the flow of the intake air of the first stage heat exchanger 212 is forcibly split by providing the baffle 108. The air outlet end and the water receiving disc 5 are arranged at intervals, so that the air inlet flow of the first section heat exchanger 212 of the guide plate 108 is divided into two flows, one air inlet flow flows to the upper part of the first section heat exchanger 212 from the upper part of the guide plate 108, and the other air inlet flow flows to the lower part of the first section heat exchanger 212 from the lower part of the guide plate 108.

Through the forced flow dividing mode, sufficient airflow is ensured to flow through the area where the free end of the first-section heat exchanger 212 is located, on one hand, the uniformity of the whole air inlet of the lower first-section heat exchanger 212 is ensured, on the other hand, the problem of wind resistance caused by insufficient air inlet of the area where the free end of the first-section heat exchanger 212 is located is avoided, and the wind resistance performance is improved.

In some embodiments of the present application, referring to fig. 25, in a cross section of the indoor heat exchanger 21, the length dimension of the first stage heat exchanger 212 is L1, and the length dimension of the baffle 108 is L2.

In some embodiments of the application, the ratio between L2 and L1 is m. M is more than or equal to 0.6. m is less than or equal to 0.8.

In this embodiment, the ratio m between L2 and L1 is set to be m being greater than or equal to 0.6, so that the forced flow distribution effect is exerted, and the ratio m is set to be m being less than or equal to 0.8, so that the influence on the air intake in the area caused by the fact that the length of the deflector 108 is excessively long and extends below the free end of the first-stage heat exchanger 212 is avoided.

The ratio m between L2 and L1 cannot be too small, which results in too short a length L2 of the baffle 108, affecting the forced flow splitting effect of the baffle 108. In order for the baffle 108 to exert a forced flow dividing effect, the ratio m is set to be not smaller than the thirteenth parameter value. For example, the thirteenth parameter value may be 0.6,0.63, or 0.65. A specific one of the parameters is selected as appropriate in consideration of the specific design.

The ratio m between L2 and L1 cannot be too large, which would result in too long length L2 of the baffle 108, and the too long baffle 108 would extend below the free end of the first stage heat exchanger 212, affecting the air intake. In order to ensure that there is sufficient flow of the inlet air 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 may be 0.8,0.78, or 0.75. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In some embodiments of the application, the ratio between L2 and L1 is m. Wherein, m is more than or equal to 0.6 and less than or equal to 0.8.

In this embodiment, the ratio m between L2 and L1 is set to be within any value of 0.6-0.8, so that the length of the baffle 108 is set within a reasonable range, the forced flow splitting effect of the baffle 108 is ensured, sufficient air inlet airflow is ensured to flow to the lower part of the first-end heat exchanger, and the wind resistance performance is improved.

In some embodiments of the present application, the minimum distance between the baffle 108 and the drip tray 5 is H7. H7 And the diameter is more than or equal to 5mm.

Referring to fig. 26, the minimum distance H7 between the baffle 108 and the drip tray 5 is set to be not less than 5mm so that more sufficient flow of the intake air flows to the area where the free end of the first stage heat exchanger 212 is located.

In some embodiments of the present application, the drip tray 5 may include a water receiving portion 55. The water receiving portion 55 is disposed horizontally and extends along the longitudinal direction of the machine body 10. The water receiving portion 55 may be used to store condensed water.

Referring to fig. 21, the first stage heat exchanger 212 forms an acute angle α with the water receiving portion 55. The baffle 108 forms an angle beta with the water receiving portion 55.

In some embodiments of the application, the ratio between β and α is n. N is more than or equal to 0.4 and less than or equal to 0.6.

The ratio n between beta and alpha cannot be too small, and the included angle beta is too small if too small, so that the distance between the air inlet end of the guide plate 108 and the water receiving disc 5 is too small, the air inlet quantity below the guide plate 108 is affected, and the forced flow distribution effect is further affected. In order to increase the intake air amount below the baffle 108, the ratio n is set to be not less than the fifteenth parameter value. For example, the fifteenth parameter value may be 0.4,0.43, or 0.45. A specific one of the parameters is selected as appropriate in consideration of the specific design.

The ratio n between β and α cannot be too large, and if too large, the included angle β is too large, so that the distance between the air inlet end of the baffle 108 and the first section heat exchanger 212 is too small, which affects the air inlet amount above the baffle 108, and further affects the forced flow distribution effect. In order to increase the air intake above the baffle 108, the ratio n is set to be no greater than the sixteenth parameter value. For example, the sixteenth parameter value may be 0.6,0.58, or 0.55. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In this embodiment, the ratio n between β and α is set within a reasonable range, so that the air inlet volume is sufficient above and below the deflector 108, and further, sufficient air inlet airflow is ensured to flow to one end of the first section heat exchanger 212 close to the air outlet 103 of the air conditioner, so that the uniformity of the overall air inlet of the first section heat exchanger is further ensured, and the wind resistance performance is further improved.

In some embodiments of the application, the distance between the first stage heat exchanger 212 and the air inlet end of the baffle 108 is greater than the distance between the first stage heat exchanger 212 and the air outlet end of the baffle 108.

Referring 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 baffle 108 is H3, wherein H4> H3.

In this embodiment, by setting H4 to be greater than H3, the inlet area of the flow channel formed between the baffle 108 and the first-stage heat exchanger 212 is greater than the outlet area thereof, so as to further ensure the air intake flowing through the first-stage heat exchanger 212.

In some embodiments of the application, 2 mm.ltoreq.H2. H3 is less than or equal to 4mm.

The distance H3 cannot be too small, so that the air outlet area of the flow channel between the deflector 108 and the first-stage heat exchanger 212 is smaller, and the air inlet amount above the deflector 108 is affected. In order to increase the air intake amount above the baffle 108, the distance H3 is set to be not less than the seventeenth parameter value. For example, the seventeenth parameter value may be 2mm,2.2mm, or 2.4mm. A specific one of the parameters is selected as appropriate in consideration of the specific design.

The distance H3 cannot be too large, which would result in too far a distance between the deflector 108 and the free end of the first stage heat exchanger 212, reduce the forced shunting effect, or result in an increase in the height of the machine body 10. In order to increase the air intake of the free end region of the first stage heat exchanger 212, avoiding an increase in the volume of the machine body 10, the distance H3 is set to be not more than the eighteenth parameter value. For example, the eighteenth parameter value may be 4mm,3.8mm, or 3.5mm. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In some embodiments of the present application, referring to 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.

The indoor heat exchanger 21 may include a third stage heat exchanger 214. Wherein, third section heat exchanger 214 is located the top of second section heat exchanger 213, and third section heat exchanger 214 is connected to the other end of second section heat exchanger 213.

That is, the third heat exchanger 214, the second heat exchanger 213 and the first heat exchanger 212 are sequentially connected from top to bottom to form a half-package structure. The opening of the half-package structure faces the through-flow fan 31 to be semi-surrounded on the periphery of the through-flow fan 31, so that the heat exchange efficiency is improved.

Referring to fig. 27 to 33, in other embodiments of the present application, in order to increase the air intake of a side area of the first heat exchanger 212 near the air outlet 103 of the air conditioner, the first heat exchanger 212 is provided with a V-shaped structure with an upward opening.

Specifically, referring to fig. 29, on the cross section of the first heat exchanger 212, the middle portion of the first heat exchanger 212 protrudes toward the bottom plate 105 with respect to both ends thereof to form a bump E. Wherein, bump E and water collector 5 interval sets up.

It will be appreciated that the bump E is located on the side of the first stage heat exchanger 212 facing away from the cross-flow fan 31.

During the air-conditioning operation of the air duct, the condensed water on the indoor heat exchanger 21 may flow to the convex point E, where the condensed water gathers and drops into the water pan 5.

Specifically, in the air duct machine provided in this embodiment, the two opposite ends of the middle part of the first section of heat exchanger 212 protrude towards the direction of the bottom plate 105 to form a bump E, so that the first section of heat exchanger 212 has a V-shaped structure with an upward opening. The salient points E on the first section heat exchanger 212 are arranged to be the lowest point of the indoor heat exchanger 21 and are arranged at intervals with the water receiving disc 5, so that condensed water on the indoor heat exchanger 21 can drop to the water receiving disc 5 through the salient points E, condensation water is prevented from gathering at one end, close to the air outlet 103 of the air conditioner, of the first section heat exchanger 212, the air inlet uniformity and the air inlet quantity of the first section heat exchanger 212 are improved, and the wind resistance performance of the through-flow type air duct is improved.

In some embodiments of the application, the first stage heat exchanger 212 may include a first windward side 2121, the first windward side 2121 being disposed toward the air conditioning intake 102.

The first stage heat exchanger 212 may include a second windward side 2122. Wherein, one end of the first windward surface 2121 and one end of the second windward surface 2122 are connected to each other to form a bump E.

Referring to fig. 31, one ends of the first and second windward surfaces 2121 and 2122 are connected to each other to form a bump E. The other ends of the first windward surface 2121 and the second windward surface 2122 extend upwards towards a direction away from the salient point E, the salient point E is arranged at a distance from the water receiving disc 5, and condensed water on the indoor heat exchanger 21 can drop to the water receiving disc 5 through the salient point E.

When the indoor air entering the machine body 10 from the air conditioner air inlet 102 exchanges heat through the indoor heat exchanger 21, the heat can be exchanged through the first section heat exchanger 212 by the first windward side 2121 and the second windward side 2122.

In this embodiment, the first heat exchanger 212 is configured to have a V-shaped structure with an upward opening, so that when the air duct is in cooling operation, condensed water on the indoor heat exchanger 21 can be collected by the first windward side 2121 and the second windward side 2122 at the salient point E and drop to the water pan 5, but cannot be collected in the area (wire area) from the salient point E to the volute tongue 385 on the first heat exchanger 212, thereby reducing the negative influence of the fin condensation of the first heat exchanger 212 on the air intake of the area. The good air inlet of the air flow in the area can obviously improve the wind resistance of the through-flow air duct.

In some embodiments of the present application, the distance between the bump E and the drip tray 5 is H8. Wherein H8 is more than or equal to 6mm.

The distance H8 is set to be not smaller than 6mm, so that sufficient air inlet quantity enters the area between the salient point E and the volute tongue 385 on the first-stage heat exchanger 212, and the heat exchange effect of the first-stage heat exchanger 212 is improved.

The distance H8 between the protruding point E and the water receiving disc 5 cannot be too small, and if too small, the air intake of the heat exchanger area where the second windward side 2122 is located is affected. In order to increase the intake air volume of the first stage heat exchanger 212, the distance H8 is set to be not less than the nineteenth parameter value. For example, the nineteenth parameter value may be 6mm,7mm, or 8mm. A specific one of the parameters is selected as appropriate in consideration of the specific design.

The distance H8 between the protruding point E and the water receiving tray 5 cannot be too large, and if the distance H is too large, the height of the machine body 10 is too large, so that the volume of the machine body 10 is increased. It is understood that the distance H8 may be no greater than the twentieth parameter value. The twentieth parameter is limited by the height of the machine body 10, and can be set according to the height requirement of the machine body 10.

The first heat exchanger 212 has a plurality of U-tubes, which are connected by bent pipes to form at least one refrigeration flow path.

In some embodiments of the application, referring to fig. 30, the portion of the first stage heat exchanger 212 between the bump E and the scroll tongue 385 has at least two U-tubes. This arrangement can avoid too close a distance between the boss E and the scroll 385, affecting the air intake of the first stage heat exchanger 212 in the area between the boss E and the scroll 385.

The air duct machine provided by the embodiment improves the airflow velocity of the least two U-shaped pipe areas (frame line areas) of the first section heat exchanger 212, which are close to the scroll 385, not only improves the air quantity, but also ensures that the air inlet airflow velocity of the whole first section heat exchanger 212 is more uniform. Referring to fig. 33, which is a velocity cloud comparison graph of 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, as can be seen from fig. 33, the flow rate of the right area 1 of the first-stage heat exchanger 212 is significantly higher than the flow rate of the area 1 of the conventional plate-shaped first-stage heat exchanger 212, so that the heat exchange efficiency of the indoor heat exchanger 21 is effectively improved.

In some embodiments of the present application, referring to fig. 32, an angle γ is formed between the first windward side 2121 and the horizontal plane where the bump E is located. Gamma is less than or equal to 15 degrees. Gamma <45 deg..

In this embodiment, the included angle γ is greater than or equal to 15 °, so that condensed water gathers at the bump 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 smaller than 45 °, so that the first heat exchanger 212 of the first section where the first windward side 2121 is located can be attached to the cross-flow fan 31 as much as possible, and the height of the first section can be reduced.

The included angle γ cannot be too large, which would result in too high a first windward side 2121 of the same length, and thus the first heat exchanger 212 is too high, resulting in an increase in the height of the machine body 10. In order to reduce the volume of the machine body 10, the included angle γ is set to be smaller than the twenty-first parameter value. For example, the twenty-first parameter value may be 45 °,43 °, or 41 °. A specific one of the parameters is selected as appropriate in consideration of the specific design.

The smaller the included angle γ, the more small the included angle γ will cause that the condensed water on the first windward surface 2121 cannot be smoothly dropped from the bump E, and the smaller the included angle γ, the larger the size of the first side surface in the width direction of the machine body 10 will be, and further the width of the machine body 10 will become larger. In order to ensure that condensed water drops from the bump E, the volume of the body 10 is reduced, and the included angle γ is set to be not smaller than the twenty-second parameter value. For example, the twenty-second parameter value may be 15 °,17 °, or 19 °. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In some embodiments of the present application, the first windward surface 2121 forms an angle γ with the horizontal plane where the bump E is located. Gamma is less than or equal to 15 degrees and less than 45 degrees.

In this embodiment, the included angle γ is set within a reasonable range, so that the condensed water on the first windward surface 2121 can be collected and dripped at the bump E smoothly, thereby reducing the negative influence of the condensation on the air intake volume of the bump E near one side area of the air outlet 103 of the air conditioner.

In some embodiments of the present application, the second windward surface 2122 forms an angle θ with the horizontal plane where the bump E is located. Theta is less than or equal to 15 degrees. θ <45 °.

In this embodiment, the included angle θ is greater than or equal to 15 °, so that condensed water gathers at the bump E, avoiding condensation on the second windward surface 2122, and improving the heat exchange effect of the first-stage heat exchanger 212. The angle θ is smaller than 45 °, so that the portion of the first heat exchanger 212 where the second windward side 2122 is located can be attached to the cross-flow fan 31 as much as possible, and the height of the portion can be reduced.

The included angle θ cannot be too large, which would result in too high a second windward side 2122 of the same length, and thus the first heat exchanger 212 is too high, resulting in an increase in the height of the machine body 10. In order to reduce the volume of the machine body 10, the included angle θ is set to be smaller than the twenty-third parameter value. For example, the twenty-third parameter value may be 45 °,43 °, or 41 °. A specific one of the parameters is selected as appropriate in consideration of the specific design.

The smaller the included angle θ, the more small the included angle θ will cause that the condensed water on the second windward side 2122 cannot be smoothly dropped from the bump E, and the smaller the included angle θ, the larger the size of the first side in the width direction of the machine body 10 will be, and further the width of the machine body 10 will become larger. In order to ensure that condensed water drops from the bump E, the volume of the body 10 is reduced, and the included angle θ is set to be not smaller than the twenty-fourth parameter value. For example, the twenty-fourth parameter value may be 15 °,17 °, or 19 °. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In some embodiments of the present application, the second windward surface 2122 forms an angle θ with the horizontal plane where the bump E is located. Theta is more than or equal to 15 degrees and less than 45 degrees.

In this embodiment, the included angle θ is set within a reasonable range, so that the condensed water on the second windward side 2122 can be collected and dripped at the bump E smoothly, thereby reducing the negative influence of the condensation on the air intake volume of the bump E near the air outlet 103 of the air conditioner, and avoiding increasing the volume of the machine body 10.

In some embodiments of the present application, the connection between the first windward surface 2121 and the second windward surface 2122 forms an obtuse angle ψ which opens towards the cross-flow fan 31. And ψ is less than or equal to 150 degrees.

In this embodiment, the obtuse angle ψ is set to be 150 ° or less, so that the first stage heat exchanger 212 is largely attached to the cross-flow fan 31, and heat exchange efficiency is improved.

The angle value of ψ cannot be too large, which would cause the size of the first heat exchanger 212 to be large in the width direction of the machine body 10, resulting in an increase in the width of the machine body 10, and it cannot be ensured that condensed water on the first windward side 2121 and the second windward side 2122 gathers at the bump E. To reduce the volume of the body 10, the obtuse angle ψ is set to be not smaller than the twenty-fifth parameter value. For example, the twenty-fifth parameter value may be 150 °,145 °, or 140 °. A specific one of the parameters is selected as appropriate in consideration of the specific design.

The angle value of ψ cannot be too small, and if so, the height of the first-stage heat exchanger 212 will be too high, and the first-stage heat exchanger 212 cannot be attached to the cross-flow fan 31, so that the height of the machine body 10 will be increased, and the heat exchange efficiency of the first-stage heat exchanger 212 will be affected. To reduce the volume of body 10, to meet a narrower depth, ψ is set at an obtuse angle.

Referring to fig. 34, the indoor heat exchanger 21 may include three heat exchangers, namely a first heat exchanger 212, a second heat exchanger 213, and a third heat exchanger 214. The first section heat exchanger 212, the second section heat exchanger 213 and the third section heat exchanger 214 are sequentially connected from bottom to top and then have an open semi-package structure.

An air channel 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 that is disposed toward the cross-flow fan 31. That is, the front volute tongue 3851 is the windward side of the volute tongue 385.

Wherein, a clearance is provided between the front volute tongue 3851 and the cross-flow fan 31. It should be noted that, the gap between the through-flow fan 31 and the front volute tongue 3851 in the through-flow duct in the machine body 10 is an important design parameter that affects the air volume and sound quality.

The cross flow fan 31 is not a rigid body, and referring to fig. 14, the cross flow fan 31 is extended in the longitudinal direction of the machine body 10, that is, when both ends of the cross flow fan 31 are fixed horizontally, the cross flow fan 31 is in a concave shape under the action of gravity, and the deformation is more remarkable as the cross flow fan 31 is longer. When the cross-flow fan 31 is located above the front volute tongue 3851, the deformation of the cross-flow fan 31 directly affects the gap between the cross-flow fan 31 and the front volute tongue 3851, thereby affecting the overall air volume and the sound quality of the air duct.

In the related art, the clearance between the cross flow fan 31 and the front tongue 3851 in the ducted air conditioner is set, and the deflection of the cross flow fan 31 is not considered. When the cross-flow fan 31 is partially located above the front volute tongue 3851, deformation of the cross-flow fan 31 can directly affect the gap between the cross-flow fan 31 and the front volute tongue 3851, which not only can deteriorate the sound quality of the noise air conditioner, but also can increase the risk of the front volute tongue 3851 colliding with the cross-flow fan 31 during transportation, and affect the user experience.

In order to solve the above-mentioned problems, in some embodiments of the present application, the clearance between the front volute tongue 3851 and the cross-flow fan 31 is reasonably set considering the flexural deformation of the cross-flow fan 31 along the length direction of the machine body 10.

Referring to fig. 34, a minimum gap between the front volute tongue 3851 and the cross-flow fan 31 is defined as δ3, and a diameter of an outer edge of the cross-flow fan 31 is defined as D. The minimum gap δ3 is set to be 0.03D or more in consideration of various dimensions of the cross-flow fan 31. Delta 3 is less than or equal to 0.06D.

It should be noted that, in a reasonable design range, the air volume of the through-flow air duct increases as the gap between the through-flow fan 31 and the front volute tongue 3851 decreases.

The minimum gap δ3 cannot be too large, and an excessive amount may cause a drop in the air volume. In order not to deteriorate the air volume performance, the minimum gap 63 is set to be not more than the twenty-sixth parameter value. For example, the twenty-sixth parameter value may be 0.06D,0.058D, or 0.056D. A specific one of the parameters is selected as appropriate in consideration of the specific design.

The minimum gap δ3 cannot be too small, which may cause the airflow of the cross-flow fan 31 to impact the front volute tongue 3851 to be aggravated, so that serious whistling sounds are generated, and in a more serious case, the cross-flow fan 31 may shake to directly collide with the front volute tongue 3851 during transportation. In order to ensure a good sound quality and to ensure that the cross-flow fan 31 does not collide with the front volute tongue 3851 during transportation, the minimum clearance δ3 is set to be not smaller than the twenty-seventh parameter value. For example, the twenty-seventh parameter value may be 0.03d,0.032D, or 0.034D. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In the air duct machine provided by the embodiment, the minimum gap delta 3 between the cross flow fan 31 and the front volute tongue 3851 is set to be delta 3 not less than 0.03D and delta 3 not more than 0.06D in consideration of the deflection deformation of the cross flow fan 31. The minimum gap delta 3 is set in a reasonable range, so that serious air leakage and air volume attenuation caused by overlarge distance between the cross-flow fan 31 and the front volute tongue 3851 are avoided, meanwhile, high noise value caused by overlarge distance between the cross-flow fan 31 and the front volute tongue 3851 is avoided, the working efficiency of the cross-flow fan 31 is effectively improved, and noise is reduced.

In some embodiments of the present application, the minimum gap between the front volute tongue 3851 and the cross-flow fan 31 is defined as δ3, and the diameter of the outer edge of the cross-flow fan 31 is defined as D. Wherein, the minimum gap delta 3 is set to be 0.03 D.ltoreq.delta 3.ltoreq.0.06D in consideration of various sizes of the cross flow fan 31.

In this embodiment, the minimum gap δ3 between the cross-flow fan 31 and the front volute tongue 3851 is adjusted by comprehensively considering the flow efficiency, the air volume and the noise of the air flow near the front volute tongue 3851 and the length dimension of the cross-flow fan 31, and the minimum gap δ3 is set to any value of 0.03d to 0.06d, so that the sound quality of the air duct machine is improved without reducing the air volume performance. The problem that the air conditioner noise level is increased and the sound quality is bad due to the fact that the too small minimum gap increases the collision risk with the front volute tongue 3851 in the running process of the cross-flow fan 31 and on the other hand, the interaction between the airflow excited by the cross-flow fan 31 and the surface of the front volute tongue 3851 is enhanced, and the problem that the air quantity is reduced due to the too large minimum gap is also avoided.

In some embodiments of the present application, the vertical distance between the end of the front volute tongue 3851 near the air intake 102 and the cross-flow fan 31 is the minimum gap δ3. The vertical distance between the end of the front volute tongue 3851 near the air conditioner air inlet 102 and the cross-flow fan 31 is set to be the minimum distance delta 3, so that the wind resistance performance of the air duct in the machine body 10 is guaranteed to be optimal.

When the fans are located above the air duct front volute tongue 3851, 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 may be matched according to the lengths of different cross-flow fans 31.

Specifically, when the length of the cross flow fan 31 does not exceed 800mm, the minimum gap δ3 may be set to δ3.gtoreq.0.03D. Delta 3 is less than or equal to 0.045D.

It can be understood that when the cross-flow fan 31 is extended along the length direction of the machine body 10, the cross-flow fan 31 is concave under the action of gravity. The length of the cross flow fan 31 is defined as L7, and the concave deformation thereof is relatively small when L7 is 800mm or less.

When L7 is less than or equal to 800mm, the minimum gap delta 3 cannot be too large, and the too large gap can cause serious air leakage and air quantity reduction. In order to ensure the air volume performance, when L2 is less than or equal to 800mm, the minimum clearance delta 3 is set to be not more than a twenty eighth parameter value. For example, the twenty-eighth parameter value may be 0.045D,0.042D, or 0.040D. A specific one of the parameters is selected as appropriate in consideration of the specific design.

When L7 is less than or equal to 800mm, the minimum clearance delta 3 cannot be too small, the noise value is too high due to the too small clearance, and the risk of collision between the cross-flow fan 31 and the front volute tongue 3851 exists. In order to improve the sound quality of the ducted air machine, to improve the working efficiency of the cross flow fan 31, to reduce noise, the minimum gap δ3 is set to be not smaller than the twenty-ninth parameter value. For example, the twenty-ninth parameter value may be 0.03d,0.032D, or 0.034D. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In some embodiments of the application, 0.03 D.ltoreq.δ3.ltoreq.0.045D when L7. Ltoreq.800 mm. In the present 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 800mm or less, the deformation amount thereof is relatively small. The minimum gap delta 3 between the cross flow fan 31 and the front volute tongue 3851 in the length dimension range is set in a relatively small dimension range, so that the length L7 of the cross flow fan 31 is less than or equal to 800mm, and the cross flow fan has higher air quantity and better sound quality.

In some embodiments of the present application, when the length of the cross flow fan 31 exceeds 800mm, the minimum gap δ3 may be set to δ3>0.045d. Delta 3 is less than or equal to 0.06D.

Specifically, when the cross-flow fan 31 is extended along the longitudinal direction of the machine body 10, the cross-flow fan 31 as a whole may exhibit a concave shape under the action of its own gravity, which defines the length of the cross-flow fan 31 as L7, and when L7>800mm, the concave deformation is relatively large.

When L7 is more than 800mm, the minimum clearance delta 3 cannot be too large, and the too large clearance can cause serious air leakage and air quantity reduction. In order to secure the air volume performance, the minimum gap δ3 is set to be not more than the thirty-th parameter value. For example, the thirty-first parameter value may be 0.06D,0.058D, or 0.056D. A specific one of the parameters is selected as appropriate in consideration of the specific design.

When L7>800mm, the minimum gap δ3 cannot be too small, and when the cross-flow fan 31 is deformed, the minimum gap δ3 is smaller, which results in a higher noise value, and at the same time, there is a risk of collision between the cross-flow fan 31 and the front volute tongue 3851. In order to improve the sound quality of the ducted air machine, to improve the working efficiency of the cross flow fan 31, to reduce noise, the minimum gap δ3 is set to be not smaller than the thirty-first parameter value. For example, the thirty-first parameter value may be 0.046D,0.048D, or 0.049D. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In some embodiments of the application, 0.045D < δ3.ltoreq.0.06D when L7>800 mm. In the present embodiment, considering the deformation of the cross flow fan 31 corresponding to the length, when the length L7 of the cross flow fan 31 is >800mm, the deformation amount thereof is relatively large. The minimum gap delta 3 between the cross flow fan 31 and the front volute tongue 3851 in this length dimension range is set in a relatively large dimension range, so that the length L7 of the cross flow fan 31 is >800mm, with higher air volume and better sound quality.

In some embodiments of the present application, the maximum clearance 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 delta is more than or equal to 0.02D. Delta is less than or equal to 0.04D.

The Δδ cannot be too small, and if it is too small, the maximum gap δ4 is too small, and if it is too small, the eddy noise generated by the airflow will be significantly increased. In order to improve the sound quality level of the ductwork, the difference delta is set to be not smaller than the thirty-second parameter value. For example, the thirty-second parameter value may be 0.02D,0.023D, or 0.025D. A specific one of the parameters is selected as appropriate in consideration of the specific design.

If Δδ is too large, the maximum gap δ4 is too large, and if the maximum gap δ4 is too large, the return air tends to increase at a low rotation speed of the cross flow fan 31, resulting in serious loss and leakage of the air guide flow, and a decrease in the air output. In order to reduce the air leakage and improve the air output, the difference delta is set to be not more than the thirty-third parameter value. For example, the thirty-third parameter value may be 0.04D,0.038D, or 0.055D. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In some embodiments of the present application, the maximum clearance 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, delta is more than or equal to 0.02D and less than or equal to 0.04D.

In the embodiment, delta is set within any value between 0.02D and 0.04D, so that the wind resistance of the air duct machine is improved. The problems of serious air guide flow loss and leakage caused by overlarge maximum gap delta 4 are effectively avoided, and meanwhile, the problem of obvious increase of vortex noise generated by air flow caused by overlarge gap delta 4 can be avoided.

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

In this embodiment, a gap is formed between the front volute tongue 3851 and the outer contour of the cross-flow fan 31 to form an air flow channel for return air. The maximum gap delta 4 is arranged at the channel inlet of the air flow channel of the front volute tongue 3851 for enabling air flow to flow smoothly, preventing noise from being formed by obstruction at the channel inlet, effectively improving the working efficiency of the cross-flow fan 31 and reducing noise.

In some embodiments of the present application, the front volute tongue 3851 has an end point A1 on the contour line of the cross-section of the through-flow wind wheel. Wherein A1 is the outline of the front volute tongue 3851 near the air inlet 102 of the air conditioner.

On the cross section of the cross-flow wind wheel, an endpoint An is arranged on the contour line of the front volute tongue 3851. Wherein An is An end point of the front volute tongue 3851 near the air outlet 103.

Referring to fig. 35 to 37, the gap between the front volute tongue 3851 and the cross-flow fan 31 is gradually increased from the point A1 to the point An.

Specifically, the gap between the front volute tongue 3851 and the through-flow fan 31 is gradually increased from the point A1 to the point An, so that the airflow channel between the front volute tongue 3851 and the outer contour of the through-flow fan 31 gradually decreases along the airflow flowing direction to form a gradual channel, the eccentric vortex size inside the through-flow fan 31 is reduced, the gradual differentiation and the impact of the airflow are reduced, the change of the airflow driven by the through-flow fan 31 when the airflow returns to the inner side of the air channel from the side of the front volute tongue 3851 is adapted, the airflow returns to the inner side of the air channel smoothly, the disturbance to the operation of the through-flow fan 31 is reduced, the airflow stability of the through-flow fan 31 is ensured, especially when the resistance is increased, and the abnormal noise caused by the airflow fluctuation is avoided.

In some embodiments of the application, the volute tongue 385 may include a wind-guiding surface 3852. Referring to fig. 35, the air guiding surface 3852 faces toward and is close to the air conditioning outlet 103 relative to the front volute tongue 3851. The air guiding surface 3852 faces the air outlet 103 of the air conditioner, so as to achieve a linear guiding effect on air flow in the air duct, and further avoid the problem of air loss at the air outlet 103 in the working process of the air duct.

In some embodiments of the present application, the air guiding surface 3852 and the front volute tongue 3851 are connected in a circular arc transition to form the volute tongue 385.

By the arrangement, the gradual change channel between the front volute tongue 3851 and the outer contour of the cross-flow fan 31 can be smoother, so that air flow transition is more natural and smooth, and the purpose of further improving the air flow stability of the cross-flow fan 31 is achieved.

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

With continued reference to fig. 35, the indoor heat exchanger 21 may include three heat exchangers, a first heat exchanger 212, a second heat exchanger 213, and a third heat exchanger 214, respectively. The first section heat exchanger 212, the second section heat exchanger 213 and the third section heat exchanger 214 are sequentially connected from bottom to top and then have an open semi-package structure. The open end of the half-pack structure faces the cross-flow fan 31, and the closed end of the half-pack structure faces the air conditioner air inlet 102. The arrangement enables the air flow entering the machine body 10 from the air conditioner air inlet 102 to be almost completely blown to the indoor heat exchanger 21, increases the heat exchange area of the indoor heat exchanger 21, improves the heat exchange efficiency of the air pipe machine 100, and increases the heat exchange air quantity.

Referring to fig. 38, taking l7=1000 mm as an example, the air duct machine provided by the present application adopts different noise spectrums at the minimum gap δ3. In practical 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 delta 3 are tested at the fan rotation speed (strong gear) of 1300rpm, and the test environment and the test position are the same in the test process.

As can be seen from Table 1, when the minimum clearance delta 3 between the cross-flow fan 31 and the front volute tongue 3851 is smaller than 0.045D, the OA-Peak value is smaller than 15dB, and the sound quality is poor. The OA-Peak value represents the difference between the overall noise level of the air duct machine and the highest noise Peak value at each frequency, and the sound quality is poor when the value is <15dB, and good when the value is >15 dB. And when the minimum gap delta 3 is increased to more than 0.045D, the OA-Peak value is more than 19dB, and the sound quality is better. The main reason is that the larger the minimum gap delta 3 is, the weaker the impact of the air flow driven by the cross-flow fan 31 on the surface of the front volute tongue 3851 is, so that the noise peak corresponding to the different frequency (760 Hz or so) of the blade impact in the frequency spectrum is reduced.

As can be seen from fig. 38, the heterofrequency peak decreases from 28.2dB to 22.3dB as the minimum gap δ3 increases from 0.043Dmm to 0.051D. When the minimum gap δ3 is further increased to 0.059Dmm, the heterofrequency peak substantially disappears. And compared with Case1, the Case2 has obvious sound quality improvement, and the air quantity is reduced by only 1.6 percent, and basically remains unchanged. Case3 has improved sound quality compared with Case2, but the air volume is further reduced, so that the minimum gap delta 3 cannot be too large, and the air flow leakage is serious due to too large gap, so that the air volume is seriously affected.

TABLE 1

Scheme for the production of a semiconductor device	δ3(mm)	δ3/D	Air volume (m 3/h)	OA-Peak value (dB)
					Case1	4.8	0.043	1281	13.7
Case2	5.7	0.051	1261	19.0
					Case3	6.6	0.059	1236	19.5

In order to solve the problem that the whole cross-flow fan 31 deforms under the action of gravity, so that the sound quality of the noise air duct is deteriorated, and the risk that the front volute tongue 3851 collides with the fan in the transportation process is increased.

Referring to fig. 39, in other embodiments of the present application, the front volute tongue 3851 is integrally configured as a front volute tongue 3851 with downward concave middle opposite ends, so that the corresponding through-flow fan 31 is in a concave shape under the action of its own gravity, the gap between the through-flow fan 31 and the front volute tongue 3851 is controlled to be consistent along the length direction (spanwise direction) of the air duct, abnormal frequency multiplication noise caused by the reduction of the gap due to the deflection deformation of the through-flow fan 31 is avoided, and the through-flow fan 31 collides with the front volute tongue 3851, so that the sound quality level and the transportation reliability of the air duct are improved.

Specifically, referring to fig. 39, the front scroll 384 is provided in a curved line in a longitudinal section of the front scroll 384. And on the longitudinal section of the front volute 384, the front volute tongue curve (the contour line of the front volute tongue 3851) gradually recedes downward from both ends to the middle position. Referring to fig. 39, the red curve is the front volute tongue curve.

That is, in the longitudinal section of the front scroll 384, the front tongue 3851 is curved in an upwardly open arc shape so that it can match the cross flow fan 31 having a deflection in the longitudinal direction of the machine body 10.

In this embodiment, the flexibility degree of the front volute tongue 3851 is adjusted to ensure the consistency of the gap between the cross-flow fan 31 and the front volute tongue 3851 along the length direction (spanwise direction) of the machine body 10, thereby avoiding frequency doubling noise caused by the reduction of the gap between the front volute tongue 3851 of the fan due to the bending deformation of the fan, and improving the sound quality level and the transportation reliability of the air conditioner due to the collision between the fan and the front volute tongue 3851.

In this embodiment, on the longitudinal section of the front volute 384, the front volute tongue 3851 is set to a curve gradually recessed downward from the two ends to the middle position thereof, so that the shape of the front volute tongue 3851 can be determined according to the flexing form of the cross-flow fan 31 along the length direction of the machine body 10 in the state where the two ends support the horizontal placement, and the influence of the deformation of the cross-flow fan 31 on the gap between the cross-flow fan 31 and the front volute tongue 3851 is avoided, so as to achieve a better sound quality level and transportation reliability.

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

Referring to fig. 39, on a longitudinal section of the front volute 384, a line connecting both 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 3851.

Wherein, the concave amount gradually decreases from the middle position of the curve of the front volute tongue 3851 to the two ends thereof, namely, the concave amount continuously and smoothly decreases from the middle position to the two ends. That is, the amount of concavity between the middle of the curve of the front volute tongue 3851 and the line M is the maximum amount of concavity. The amount of concavity between the ends of the curve of the front volute tongue 3851 and the line M is 0.

In the air duct machine provided in this embodiment, on the longitudinal section of the front volute 384, the connecting lines of the two ends of the front volute 384 are disposed above the front volute 3851 curve, and the concave amount is provided between the connecting lines of the two ends of the front volute 3851 curve and the front volute 3851 curve, so that the shape of the front volute 3851 can be determined according to the deflection form of the cross-flow fan 31 along the length direction of the machine body 10 in the state that the two ends of the cross-flow fan 31 are supported horizontally, and the influence of the deformation of the cross-flow fan 31 on the gap between the cross-flow fan 31 and the front volute 3851 is avoided, so as to achieve a better sound quality level and transportation reliability.

In some embodiments of the present application, the line connecting the ends of the curve of the front scroll 384 extends in the horizontal direction in the longitudinal section of the front scroll 384, and this arrangement ensures that the front scroll 384 extends in the longitudinal direction of the machine body 10.

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

In some embodiments of the present application, the length of the cross-flow fan 31 is no greater than 800 mm. A is less than or equal to 0.4mm and less than or equal to 0.6mm.

Specifically, when the cross flow fan 31 is horizontally arranged along the longitudinal direction of the machine body 10, the cross flow fan 31 as a whole may be depressed by its own gravity. The length of the cross flow fan 31 is defined as L7, and when L7 is 800mm or less, the downward deflection thereof is relatively small.

When L7 is less than or equal to 800mm, the maximum concave amount a cannot be too large, and the too large gap between the cross-flow fan 31 and the front volute tongue 3851 can cause too large gap, so that air leakage is serious and the air quantity is reduced. In order to ensure the air volume performance, when L7 is less than or equal to 800mm, the maximum concave amount a is set to be not more than a thirty-fourth parameter value. For example, the thirty-fourth parameter value may be 0.6mm,0.58mm, or 0.56mm. A specific one of the parameters is selected as appropriate in consideration of the specific design.

When L7 is less than or equal to 800mm, the maximum concave amount a cannot be too small, and if too small, the uniformity of the spreading direction of the gap between the cross-flow fan 31 and the front volute tongue 3851 cannot be ensured, the deformation of the cross-flow fan 31 can directly affect the gap between the cross-flow fan 31 and the front volute tongue 3851, so that not only can the noise value be higher, but also the collision risk of the cross-flow fan 31 and the front volute tongue 3851 exists. In order to improve the sound quality of the ducted air machine, to improve the working efficiency of the cross flow fan 31 and to reduce noise, the maximum concave amount a is set to be not smaller than the thirty-fifth parameter value. For example, the thirty-fifth parameter value may be 0.4mm,0.42mm, or 0.44mm. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In some embodiments of the application, 0.4 mm.ltoreq.a.ltoreq.0.6 mm when L7. Ltoreq.800 mm.

In the present embodiment, the maximum concave amount a is appropriately set in consideration of the degree of deflection corresponding to the length of the cross flow fan 31. When the length L7 of the cross-flow fan 31 is less than or equal to 800mm, the deformation amount is relatively small, the maximum concave amount a is set in a relatively small size range, the spanwise consistency of the gap between the cross-flow fan 31 and the front volute tongue 3851 is ensured, and the length L7 of the cross-flow fan 31 is less than or equal to 800mm, so that the cross-flow fan 31 has higher air quantity and better sound quality.

In some embodiments of the present application, when the length of the cross flow fan 31 exceeds 800mm, 0.6mm < a, a.ltoreq.0.8 mm.

Specifically, when the cross flow fan 31 is horizontally arranged along the longitudinal direction of the machine body 10, the cross flow fan 31 as a whole may be depressed by its own gravity. When L7>800mm, its downward flexural deformation is relatively large.

When L7>800mm, the maximum concave amount a cannot be too large, and the excessive large can cause the too large gap between the cross-flow fan 31 and the front volute tongue 3851, so that the air leakage is serious and the air quantity is reduced. In order to secure the air volume performance, the maximum dishing amount a is set to be not more than the thirty-sixth parameter value at L7>800 mm. For example, the thirty-sixth parameter value may be 0.8mm,0.78mm, or 0.76mm. A specific one of the parameters is selected as appropriate in consideration of the specific design.

When L7>800mm, the maximum concave amount a cannot be too small, and too small can cause the deformation of the long cross-flow fan 31 to directly affect the gap between the cross-flow fan 31 and the front volute tongue 3851, which not only can cause a high noise value, but also can cause a risk of collision between the cross-flow fan 31 and the front volute tongue 3851. In order to improve the sound quality of the air duct machine and reduce the collision risk, the maximum concave amount a is set to be larger than a thirty-seventh parameter value. For example, the thirty-seventh parameter value may be 0.6mm,0.62mm, or 0.64mm. A specific one of the parameters is selected as appropriate in consideration of the specific design.

In some embodiments of the application, 0.6mm < a.ltoreq.0.8 mm when L7>800 mm.

In the present embodiment, the maximum concave amount a is appropriately set in consideration of the degree of deflection 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 amount thereof is relatively large, and the maximum concave amount a is set in a relatively large size range, so that the length L7 of the cross flow fan 31 is greater than 800mm, and the cross flow fan 31 has higher air quantity and better sound quality.

In the air duct machine provided in this embodiment, when the through-flow fan 31 is located above the front volute tongue 3851, the deflection degree of the front volute tongue 3851 can be adjusted according to the length of the through-flow fan 31, so as to ensure the uniformity of the expansion direction of the gap between the through-flow fan 31 and the front volute tongue 3851.

That is, the front volute tongue 3851 structure with different concave shapes can be matched according to the difference of the deflection deformation degree of the cross-flow fan 31 with different lengths along the length direction of the machine body 10, so as to avoid frequency doubling 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 deflection deformation of the cross-flow fan 31, thereby realizing better sound quality level and transportation reliability.

In some embodiments of the application, the curve of the front volute tongue 3851 includes, but is not limited to, a conic, a catenary curve, etc., in the longitudinal section of the front volute 384.

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

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, delta 1 is more than or equal to 0.03D. δ1 is less than or equal to 0.045D. Delta 2 is more than or equal to 0.06D. Delta 2 is less than or equal to 0.075D,

By setting the amount of concavity, the degree of deflection of the cross-flow fan 31 at different lengths need not be considered when setting the minimum distance between the front volute tongue 3851 and the cross-flow fan 31. Therefore, the range of the minimum distance δ1 between the front volute tongue 3851 and the cross-flow fan 31 is identical to the range of the minimum distance δ1 in the foregoing embodiments, and similarly, the maximum distance δ2 is identical to the range of the maximum distance δ2 in the foregoing embodiments, which is not described herein in detail.

It is understood that, in the present embodiment, the minimum distance δ1 is the distance between the two ends of the front volute tongue 3851 and the cross-flow fan 31. The minimum distance between the front volute tongue 3851 and the cross-flow fan 31 is the sum of δ1 and the corresponding amount of concavity in the cross-section of either front volute tongue 3851. Similarly, the maximum distance between the front volute tongue 3851 and the cross-flow fan 31 is the sum of δ2 and the corresponding amount of concavity in the cross-section of either front volute tongue 3851.

In some embodiments of the present application, the gap between the front volute tongue 3851 and the cross-flow fan 31 is gradually widened from one end thereof near the air intake 102 to the other end thereof.

Specifically, in 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 return air. The gap between the front volute tongue 3851 and the cross-flow fan 31 is gradually widened from one end of the front volute tongue 3851, which is close to the air inlet 102 of the air conditioner, to the other end of the front volute tongue, so that the maximum distance delta 2 is positioned at the channel inlet of the air flow channel, and the minimum distance delta 1 is smaller than the gap value of the channel inlet, so that the air flow circulation is smoother, the obstruction generated at the channel inlet of the air return of the front volute tongue 3851 is prevented, the working efficiency of the cross-flow fan 31 can be improved, and the noise is reduced.

It should be noted that, the air duct machine with the cross flow fan 31 has a narrower depth than the air duct machine with the centrifugal fan, and can widen the installation scene, so the air duct machine with the cross flow fan 31 can be installed in the suspended ceiling and at the beam position of the hanging point of the curtain in the living room.

In the related art, due to the limitation of the installation scene on the height dimension of the machine body 10, the height of the air duct machine needs to be compressed as much as possible, which results in the limited height H of the air inlet 102 of the air conditioner, and limits the air intake of the air duct machine.

In addition, in the related art, due to the requirement of the actual installation position, when the air duct machine is installed, referring to fig. 40, the horizontal distance L between the air conditioner air inlet 102 and the roof beam (or wall surface) needs to be 80 mm-120 mm, and a separation area is formed above the air conditioner air inlet, so that the air supply amount of the air duct machine is further reduced. Further, under the installation environment, the resistance of the air conditioner air inlet 102 of the air pipe machine is overlarge, the risk of wind resistance noise resistance of the whole machine is increased, the user experience is reduced, and the product competitiveness is reduced.

In order to increase the air intake of the ducted air machine, referring to fig. 41-47, in some embodiments of the present application, the ducted air machine 100 may include a lower air intake 109.

Referring to fig. 43, the lower air inlet 109 is formed on the bottom plate 105 along the length direction of the machine body 10. That is, the length direction of the lower air inlet 109 is the length direction of the machine body 10.

The lower air inlet 109 is communicated with the air conditioner air inlet 102, and under the action of the cross-flow fan 31, indoor air enters the machine body 10 through the air conditioner air inlet 102 and the lower air inlet 109, exchanges heat through the indoor heat exchanger 21, and is output to the indoor through the air conditioner air outlet 103.

Referring to fig. 41-46, the water tray 5 may include a first water tray 52. The first water pan 52 is located between the air conditioner air inlet 102 and the lower air inlet 109.

The drip tray 5 may include a second drip tray 53. Wherein, the lower air inlet 109 is located between the first water receiving tray 52 and the second water receiving tray 53.

Referring to fig. 45, in the width direction of the machine body 10, the first water pan 52 and the second water pan 53 have the avoiding portion 51 therebetween, the avoiding portion 51 is provided corresponding to the lower air inlet 109, and the lower air inlet 109 communicates with the air conditioner air inlet 102 through the avoiding portion 51.

In this embodiment, the lower air inlet 109 is disposed on the bottom plate 105, and cooperates with the air conditioner air inlet 102 located at the rear side of the machine body 10 to realize air intake of the dual air inlets.

The air duct machine provided in this embodiment is applicable to an installation environment with a smaller horizontal distance between the air conditioner air inlet 102 and a wall (a roof beam or a cross beam), meets the requirements of actual installation positions, and can further widen the installation scene. By arranging the lower air inlet 109, not only the air supply quantity of the air pipe machine is increased, but also the air inlet resistance of the air pipe machine is reduced, and the wind resistance performance of the air channel is improved.

In other embodiments, referring to fig. 41, the water pan 5 is disposed below the indoor heat exchanger 21, and the lower air inlet 109 is directly penetrating through the bottom of the machine body 10, so as to communicate with the air conditioner air inlet 102. The lower air inlet 109 divides the water tray 5 into a first water tray 52 and a second water tray 53. In this embodiment, the water receiving tray 5 is integrally provided. Under the action of the cross-flow fan 31, indoor air enters the machine body 10 through the air conditioner air inlet 102 and the lower air inlet 109, exchanges heat through the indoor heat exchanger 21, and is output to the indoor through the air conditioner air outlet 103.

In some embodiments of the present application, the indoor heat exchanger 21 may comprise a three-stage heat exchanger.

Referring to fig. 44 and 45, the three heat exchangers are a first heat exchanger 212, a second heat exchanger 213, and a third heat exchanger 214, respectively. The first section heat exchanger 212, the second section heat exchanger 213 and the third section heat exchanger 214 are sequentially connected from bottom to top and then have an open semi-package structure. The open end of the half-pack structure faces the cross-flow fan 31, and the closed end of the half-pack structure faces the air conditioner air inlet 102.

The cross flow fan 31 is partially arranged in the half-package structure of the indoor heat exchanger 21, so that the original separation of the cross flow fan 31 and the indoor heat exchanger 21 is changed into the overlapping arrangement of 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 volumes of the cross flow fan 31 and the indoor heat exchanger 21 are unchanged.

The second heat exchanger 213 has a first connection end, and the first connection end is connected to the third heat exchanger 214.

In some embodiments of the present application, the first water pan 52 is located between the air conditioner inlet 102 and the lower inlet 109 in the cross section of the cross-flow fan 31.

Referring to fig. 44, in 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 the point C along the vertical direction falls into the first water receiving disc 52 and is used for receiving condensed water dropped at the joint of the third section heat exchanger 214 and the second section heat exchanger 213.

That is, the projection of the point C downward in the vertical direction falls within the projection range of the first water pan 52 downward in the vertical direction, so that the first water pan 52 is located below the point C.

Specifically, when the air pipe machine is operated in the cooling mode, there is a greater risk of dripping of condensed water droplets at the junction of the third-stage heat exchanger 214 and the second-stage heat exchanger 213. The first water pan 52 is arranged below the point C, so that water drops at the point C can drop in the first water pan 52, and the water drops are prevented from falling through the lower air inlet 109 to influence user experience.

In some embodiments of the present application, the projection of the first stage heat exchanger 212 downward in the vertical direction falls completely into the second drip tray 53.

Referring to fig. 44, on the cross section of the cross-flow fan 31, the first heat exchanger 212 is disposed obliquely from top to bottom toward the air-conditioning outlet 103, so that the air-duct machine operates in the cooling mode, and the condensed water on the indoor heat exchanger 21 flows into the second water receiving tray 53 from the end of the first heat exchanger 212 near the air-conditioning outlet 103.

In some embodiments of the present application, a downward projection of the connection between the first stage heat exchanger 212 and the second stage heat exchanger 213 in the vertical direction falls completely into the second water receiving tray 53, so as to receive condensed water dropping on the connection between the first stage heat exchanger 212 and the second stage heat exchanger 213, and avoid water drops at the connection from falling through the lower air inlet 109, which affects user experience.

In some embodiments of the application, the first stage heat exchanger 212 has a second connection end that is connected to the second stage heat exchanger 213.

Referring to FIG. 45, on the cross section of the cross-flow fan 31, the end point of the second connection end far from the cross-flow fan 31 is the point F, and the distance between the point F and the second water receiving tray 53 is H5, wherein H5 is equal to or greater than 20mm. In this embodiment, by setting the distance H5 between the point F and the second water receiving disc 53 to be not smaller than 20mm, it is ensured that sufficient air intake flows to the first-stage heat exchanger 212, and the air intake of the first-stage heat exchanger 212 is improved.

The distance H5 between the point F and the second water pan 53 cannot be too small, and too small results in a smaller intake air volume for the first stage heat exchanger 212. To ensure the intake air quantity of the first stage heat exchanger 212, the distance H5 is set to be not smaller than the thirty-eighth parameter value. For example, the thirty-eighth parameter value may be 21mm,22mm, or 23mm. A specific one of the parameters is selected as appropriate in consideration of the specific design.

The larger the distance H5 between the point F and the second water receiving tray 53, the larger the intake air volume of the first-stage heat exchanger 212. The thickness dimension of the body 10 may limit the distance H5 between the point F and the second water receiving tray 53 from being excessively large, thereby avoiding an increase in the volume of the body 10. Therefore, the maximum value of the distance H5 may be set according to the actual needs of the size of the machine body 10.

In some embodiments of the present application, the first baffle 531 is provided on the second drip tray 53.

Referring to fig. 44 and 47, the first baffle 531 is disposed on the second water pan 53, and a flow path through which the air flow flows is formed between one end of the first baffle 531 and the second heat exchanger 213. The distance H6 between the first baffle 531 and the second heat exchanger 213 is set to be greater than the distance H5 between the point F and the second water pan 53, so that the inlet area of the flow passage is large, ensuring that sufficient airflow flows through the first heat exchanger 212.

In some embodiments of the 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, so that the distance H6 is prevented from becoming a bottleneck for limiting the air intake of the first stage heat exchanger 212.

In some embodiments of the present application, the first water receiving tray 52 and the second water receiving tray 53 are respectively located at two sides of the lower air inlet 109.

The second water receiving tray 53 is provided with a first baffle 531 near the lower air inlet. The first water pan 52 is provided with a second baffle 521 adjacent to the lower air inlet 109. The side of the first water receiving tray 52 away from the first baffle 531 is provided with a flange 522. Wherein, the top end of the first baffle 531 is located on the same horizontal plane with the top end of the second baffle 521 and the top end of the flange 522.

Two ends of the first baffle 531 are respectively connected with two ends of the second baffle 521 through two third baffles, and the two third baffles, the second baffle 521 and the first baffle 531 enclose to form the avoiding part 51.

In this embodiment, the top ends of the first baffle 531, the second baffle 521 and the flange 522 are disposed on the same horizontal plane, so as to ensure the normal water storage function of the second water receiving tray 53 and the first water receiving tray 52.

Referring to fig. 46, in the present embodiment, the distance between the top end of the first baffle 531 and the bottom plate 105 is H9, the distance between the top end of the second baffle 521 and the bottom plate 105 is H10, and the distance between the top end of the flange 522 and the bottom plate 105 is H11, where h11=h9=h10.

In some embodiments of the present application, the first water receiving tray 52 and the second water receiving tray 53 are disposed in communication through the communication portion 54.

Specifically, referring to fig. 47, the communicating portions 54 are located at both ends in the length direction of the lower air intake 109, and the communicating portions 54 are disposed obliquely downward from the direction of the first water pan 52 to the second water pan 53. By disposing the communication portion 54 so as to be inclined, the condensed water in the first water-receiving tray 52 flows into the second water-receiving tray 53 through the communication portion 54, and merges with the condensed water in the second water-receiving tray 53. Wherein, the water outlet is arranged on the second water receiving disc 53, which is convenient for discharging condensed water.

It should be noted that the above embodiments are merely for illustrating the technical solution of the present utility model and not for limiting the same, and although the present utility model has been described in detail with reference to the above embodiments, it should be understood by those skilled in the art that the technical solution described in the above embodiments may be modified or some or all of the technical features may be equivalently replaced, and these modifications or substitutions do not make the essence of the corresponding technical solution deviate from the scope of the technical solution of the embodiments of the present utility model.

The foregoing description, for purposes of explanation, has been presented in conjunction with specific embodiments. The illustrative discussions above are not intended to be exhaustive or to limit the embodiments to the precise forms disclosed above. Many modifications and variations are possible in light of the above teaching. The embodiments were chosen and described in order to best explain the principles and the practical application, to thereby enable others skilled in the art to best utilize the embodiments and various embodiments with various modifications as are suited to the particular use contemplated.

Claims

1. An air duct machine, comprising:

2. An air duct machine, comprising:

the machine body is provided with an air conditioner air inlet and an air conditioner air outlet at two ends in the width direction, and the horizontal distance between the air conditioner air inlet and a wall is 80-120 mm;

the water receiving disc is arranged below the indoor heat exchanger;

3. The ducted air conditioner according to claim 1 or 2, wherein the indoor heat exchanger comprises a first section heat exchanger, a second section heat exchanger and a third section heat exchanger, the first section heat exchanger, the second section heat exchanger and the third section heat exchanger are sequentially connected from bottom to top to form a half-package structure, and an opening of the half-package structure faces the through-flow fan.

4. The ducted air conditioner according to claim 3, wherein the second heat exchanger has a first connection end connected with the third heat exchanger, and the first water receiving tray is located between the air conditioner air inlet and the lower air inlet on the cross section of the through-flow fan, an end point of the first connection end far away from the through-flow fan is a point C, and a projection of the point C in a vertical direction falls into the first water receiving tray.

5. The ducted air conditioner of claim 3, wherein the projection of the first section heat exchanger downward in the vertical direction and the projection of the connection of the first section heat exchanger and the second section heat exchanger downward in the vertical direction fall entirely into the second water tray.

6. The air duct machine according to claim 5, wherein the first heat exchanger is provided with a second connecting end connected with the second heat exchanger, the first heat exchanger is obliquely arranged from top to bottom towards an air outlet of the air conditioner on the cross section of the through-flow fan, an endpoint of the second connecting end far away from the through-flow fan is an F point, and the distance between the F point and the second water receiving disc is H5, wherein H5 is more than or equal to 20mm.

7. The ducted air conditioner of claim 6, wherein the second water pan is provided with a first baffle, and the distance between the first baffle and the second heat exchanger is H6, and H6> H5.

8. The ducted air machine of claim 7, wherein the difference between the distance H6 and the distance H5 is c, c >5mm.

9. The ducted air conditioner according to claim 1 or 2, wherein the first water receiving tray and the second water receiving tray are respectively located at two sides of the lower air inlet, a first baffle plate close to the lower air inlet is arranged on the second water receiving tray, a second baffle plate close to the lower air inlet is arranged on the first water receiving tray, a flange is arranged on one side, away from the first baffle plate, of the first water receiving tray, and the top end of the first baffle plate, the top end of the second baffle plate and the top end of the flange are located on the same horizontal plane.

10. The ducted air conditioner according to claim 1 or 2, characterized in that the first water pan and the second water pan are communicated and arranged through a communicating portion, the communicating portion is located at two ends of the lower air inlet in the length direction, and the communicating portion is obliquely arranged downwards from the first water pan to the second water pan.