WO2024087274A1 - Heat exchanger and air conditioner - Google Patents

Abstract

A heat exchanger (2) and an air conditioner. The heat exchanger (2) comprises: a heat exchange tube (21) and a plurality of heat sinks. The heat exchange tube (21) passes through a plurality of heat sinks arranged in sequence; the heat exchanger (2) comprises a first heat exchange section (22); the extension trajectory of the first heat exchange section (22) in the arrangement direction of the heat sinks is a first extension trajectory; the first extension trajectory is an arc section; tangent lines at two end points of the first extension trajectory are respectively a first tangent line and a second tangent line; and an included angle between the first tangent line and the second tangent line ranges from 60° to 110°.

Description

Heat exchanger and air conditioner

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is based on the Chinese patent application with application number 202211305462.5 and application date October 24, 2022, and claims the priority of the Chinese patent application. The entire content of the Chinese patent application is hereby introduced into this application as a reference.

Technical Field

The present application relates to the technical field of air conditioning equipment, and in particular to a heat exchanger and an air conditioner.

Background technique

In the related art, in order to increase the heat exchange area of the heat exchanger and to make the heat exchanger fit closely with other parts in the whole machine, at least part of the heat exchanger is bent into an arc. However, the bent part of the heat exchanger has problems of large air flow resistance and low air intake efficiency, and also causes the problem of increased noise. Therefore, there is room for improvement.

Summary of the invention

The present application aims to solve at least one of the technical problems existing in the prior art. To this end, one purpose of the present application is to propose a heat exchanger, by optimizing and improving the curved portion (i.e., the first heat exchange section) of the heat exchanger, so that the angle range between the tangents of the extension trajectory of the curved portion at its two end points is set to 60° to 110°, the width of the narrowest part of the airflow channel of the first heat exchange section can be increased, and when the airflow passes through the heat exchanger, the resistance to the airflow can be reduced, the air intake efficiency can be improved, the noise can be reduced, and it is also beneficial to increase the air output; in addition, since the heat exchanger includes a curved portion, the overall structure of the heat exchanger is compact, the heat exchange area is large, and the heat exchange efficiency is high.

The present application also proposes an air conditioner having the above heat exchanger.

According to the first aspect of the present application, the heat exchanger includes: a heat exchange tube and a plurality of heat sinks, the heat exchange tube is passed through the plurality of heat sinks arranged in sequence, and an air flow channel is defined between adjacent heat sinks, the heat exchanger includes a first heat exchange section, an extension trajectory of the first heat exchange section in the arrangement direction of the heat sinks is a first extension trajectory, the first extension trajectory is an arc segment, the tangents at the two endpoints of the first extension trajectory are respectively a first tangent and a second tangent, and the angle between the first tangent and the second tangent ranges from 60° to 110°.

According to the heat exchanger of the embodiment of the present application, by optimizing and improving the curved portion of the heat exchanger (i.e., the first heat exchange section), the angle range between the tangents of the extension trajectory of the curved portion at its two end points is set to 60° to 110°, which can increase the width of the narrowest part of the airflow channel of the first heat exchange section. When the airflow passes through the heat exchanger, the resistance to the airflow can be reduced, the air intake efficiency can be improved, the noise can be reduced, and at the same time, it is beneficial to increase the air output. In addition, since the heat exchanger includes the curved portion, the overall structure of the heat exchanger is compact, the heat exchange area is large, and the heat exchange efficiency is high.

According to some embodiments of the present application, the angle between the first tangent line and the second tangent line is 80°.

According to some embodiments of the present application, the heat exchanger further includes a second heat exchange section and a third heat exchange section, the second heat exchange section and the third heat exchange section are respectively connected to opposite ends of the first heat exchange section along the arrangement direction of the heat sink, and the extension tracks of the second heat exchange section and the third heat exchange section in the arrangement direction of the heat sink are respectively the second extension track and the third extension track;

Wherein, the second extension trajectory and the third extension trajectory are both straight line segments, the second extension trajectory is collinear with the first tangent line, and the third extension trajectory is collinear with the second tangent line.

According to some embodiments of the present application, the first heat exchange section, the second heat exchange section, and the third heat exchange section are integrally formed.

An air conditioner according to an embodiment of the second aspect of the present application includes: a casing having an air inlet and an air outlet; an air duct assembly disposed in the casing and including a fan; a heat exchanger assembly disposed in the casing and located on the upstream side of the air duct assembly, the heat exchanger assembly including a heat exchanger according to the embodiment of the first aspect of the present application.

According to the air conditioner of the embodiment of the present application, by setting the above-mentioned heat exchanger, by optimizing and improving the curved portion of the heat exchanger (i.e., the first heat exchange section), the angle range between the tangents of the extension trajectory of the curved portion at its two end points is set to 60°~110°, which can increase the width of the narrowest part of the air flow channel of the first heat exchange section. When the air flow passes through the heat exchanger, the resistance of the air flow can be reduced, the air intake efficiency is improved, the noise is reduced, and it is also beneficial to increase the air output. In addition, since the heat exchanger includes a curved portion, the overall structure of the heat exchanger is compact, the heat exchange area is large, and the heat exchange efficiency is high.

According to some embodiments of the present application, the heat exchanger assembly includes an electric auxiliary heating component, which is located between the heat exchanger and the wind wheel of the fan, and the minimum distance between the electric auxiliary heating component and the wind wheel is not less than 15 mm.

According to some embodiments of the present application, the air duct assembly includes an air duct volute, the wind wheel of the fan is arranged in the air duct volute, the wind wheel is a cross-flow wind wheel, the air duct volute includes a first volute and a second volute arranged opposite to each other, at least part of the wind wheel is located between the first volute and the second volute, the first volute includes a first volute body and a first volute tongue, the first volute tongue is connected to one end of the first volute body adjacent to the air inlet, the second volute includes a second volute body and a second volute tongue, the second volute tongue is connected to one end of the second volute body adjacent to the air inlet, and at least the part of the first volute body opposite to the wind wheel extends in an involute shape in the flow direction of the airflow.

According to some embodiments of the present application, the minimum distance between the first volute tongue and the outer peripheral contour of the wind wheel is B ₁ , the minimum distance between the second volute tongue and the outer peripheral contour of the wind wheel is E ₁ , the diameter of the wind wheel is D, the value range of B ₁ is 0.04D to 0.06D and/or the value range of E ₁ is 0.04D to 0.06D.

According to some embodiments of the present application, the minimum spacing between the first volute tongue and the outer peripheral contour of the wind wheel is B ₁ , the rotation axis of the wind wheel extends along the first direction, at least part of the air inlet and the air outlet are located on opposite sides of the casing along the second direction, a first straight line is drawn through the center of the wind wheel along the radial direction of the wind wheel and along the third direction, and the spacing between the outer peripheral contour of the wind wheel and the first volute body in the direction where the first straight line is located is B ₃ , and the value range of B ₃ is 2.5B ₁ to 4.5B ₁ , wherein the first direction, the second direction and the third direction are perpendicular to each other.

According to some embodiments of the present application, the value of B ₃ is 3.75B ₁ .

According to some embodiments of the present application, the straight line where the minimum spacing _B1 between the first volute tongue and the outer peripheral contour of the wind wheel is located is the second straight line, the angle between the first straight line and the second straight line is γ, a third straight line is drawn through the center of the wind wheel along the radial direction of the wind wheel, the third straight line is located between the first straight line and the second straight line and the angle between the third straight line and the second straight line is γ/2, the spacing between the outer peripheral contour of the wind wheel and the first volute body in the direction where the third straight line is located is _B2 , and the value range of _B2 is _1.5B1 to _3.5B1 .

According to some embodiments of the present application, the value of B ₂ is 2.3B ₁ .

According to some embodiments of the present application, the second volute body and the second volute tongue are transitionally connected via a fillet portion, the minimum spacing between the fillet portion and the inner wall surface of the first volute body is B ₄ , the diameter of the wind wheel is D, and the value range of B ₄ is 0.45D to 0.75D.

According to some embodiments of the present application, the value of B ₄ is 0.62D.

According to some embodiments of the present application, the second volute body and the second volute tongue are transitionally connected via a fillet portion, and the radius of the fillet portion is in the range of 2 to 8 mm.

According to some embodiments of the present application, the radius of the rounded corner is 6 mm.

According to some embodiments of the present application, the rotation axis of the wind wheel extends along a first direction, at least a portion of the air inlet and the air outlet are located on opposite sides of the casing along a second direction, and the second volute body includes an air guide portion, and an angle range between the air guide portion and the third direction is 35° to 75°, wherein the first direction, the second direction and the third direction are perpendicular to each other.

According to some embodiments of the present application, the angle between the wind guide portion and the third direction is 51°.

According to some optional embodiments of the present application, there is one wind wheel and the air duct assembly is a single cross-flow air duct structure.

Additional aspects and advantages of the present application will be given in part in the description below, and in part will become apparent from the description below, or will be learned through the practice of the present application.

BRIEF DESCRIPTION OF THE DRAWINGS

The above and/or additional aspects and advantages of the present application will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

FIG1 is a cross-sectional schematic diagram of an indoor unit of an air conditioner according to some embodiments of the present application;

FIG. 2 is a schematic cross-sectional view of a portion of the air conditioner indoor unit in FIG. 1 .

Reference numerals:

100. Air conditioner indoor unit;

10. housing; 11. air inlet; 12. air outlet; 13. air guide assembly; 131. first louver; 132. second louver; 14. first straight line; 15. second straight line; 16. third straight line;

20. Heat exchanger assembly; 2. Heat exchanger; 21. Heat exchange tube; 22. First heat exchange section; 23. Second heat exchange section; 24. Third heat exchange section; 3. Electrical auxiliary component; 31. Electrical auxiliary heating element;

30. Air duct assembly; 4. Fan; 41. Wind wheel; 5. Air duct volute; 51. First volute; 511. First volute body; 512. First volute tongue; 52. Second volute; 521. Second volute body; 522. Second volute tongue; 523. Air guide portion; 524. Rounded corner portion.

Detailed ways

The embodiments of the present application are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present application, and cannot be understood as limiting the present application.

The heat exchanger 2 according to an embodiment of the present application is described below with reference to FIGS. 1-2 .

1-2 , the heat exchanger 2 according to the first embodiment of the present application includes a heat exchange tube 21 and a plurality of heat sinks.

The heat exchange tube 21 is passed through a plurality of heat sinks arranged in sequence. The heat sinks can extend in a first direction. The plurality of heat sinks are arranged at intervals. An airflow channel is defined between adjacent heat sinks. The airflow channel can provide a space for airflow flow and guide the airflow. At the same time, the air can exchange heat with the heat exchanger 2 in the airflow channel. The heat exchanger 2 includes a first heat exchange section 22. The extension track of the first heat exchange section 22 in the arrangement direction of the heat sinks is a first extension track. The first extension track is an arc segment. The center of curvature of the first extension track is located on the downstream side of the heat exchange tube 21. The tangents at the two end points of the first extension track are the first tangent and the second tangent, respectively. For example, the first extension track includes a first end point and a second end point. The tangent at the first end point of the first extension track is the first tangent, and the tangent at the second end point of the first extension track is the second tangent. The value range of the angle α between the first tangent and the second tangent is 60° to 110°. For example, the angle α between the first tangent and the second tangent can be 60°, 70°, 80°, 90°, 100°, 110°, etc.

The heat exchanger 2 is bent to form the first heat exchange section 22. Compared with the unbent state, the width of the airflow channel of the bent first heat exchange section 22 on the side away from the center of curvature becomes larger, and the width of the airflow channel on the side close to the center of curvature becomes smaller. When the airflow passes through the narrowest part of the airflow channel, it will encounter greater resistance and generate greater noise, thereby increasing overall energy consumption, while also reducing the airflow flow and lowering the overall air intake efficiency.

When the angle α between the first tangent and the second tangent is too small, the width of the narrowest part of the airflow channel of the first heat exchange section 22 will be small. When the airflow passes through the heat exchanger 2, the airflow encounters large resistance, which increases the overall energy consumption, reduces the overall air intake efficiency, reduces the air volume, and easily generates excessive noise; when the angle α between the first tangent and the second tangent is too large, when the heat exchanger 2 is assembled on the whole machine, the size of the whole machine in the third direction (for example, refer to the e3 direction in the attached figure) will be large, occupying more indoor space, and not conducive to the arrangement of other structures in the whole machine. Therefore, when the angle α between the first tangent and the second tangent is in the range of 60° to 110°, the resistance of the airflow can be reduced, thereby reducing energy consumption, increasing the overall air intake efficiency, and reducing noise. At the same time, it can ensure that the overall structure is more compact, the heat exchange area is larger, and the heat exchange efficiency is higher.

According to the heat exchanger 2 of the embodiment of the present application, by optimizing and improving the curved portion (i.e., the first heat exchange section 22) of the heat exchanger 2, the angle range between the tangents of the extension trajectory of the curved portion at its two end points is set to 60° to 110°, which can increase the width of the narrowest part of the airflow channel of the first heat exchange section 22. When the airflow passes through the heat exchanger 2, the resistance to the airflow can be reduced, the air intake efficiency can be improved, the noise can be reduced, and it is also beneficial to increase the air output. In addition, since the heat exchanger 2 includes the curved portion, the overall structure of the heat exchanger 2 is compact, the heat exchange area is large, and the heat exchange efficiency is high.

According to some embodiments of the present application, referring to FIG. 1-FIG. 2, the angle α between the first tangent line and the second tangent line is 80°, which can better reduce the resistance of the airflow, thereby better reducing energy consumption, increasing the overall air intake efficiency, and reducing noise. At the same time, it can ensure that the overall structure is more compact, the heat exchange area is larger, and the heat exchange efficiency is higher.

According to some embodiments of the present application, with reference to FIGS. 1-2, the heat exchanger 2 further includes a second heat exchange section 23 and a third heat exchange section 24, which are respectively connected to opposite ends of the first heat exchange section 22 along the arrangement direction of the heat sinks, for example, the second heat exchange section 23 is connected to one side of the first end of the first heat exchange section 22, and the third heat exchange section 24 is connected to one side of the second end of the first heat exchange section 22. By connecting the second heat exchange section 23 and the third heat exchange section 24 to opposite ends of the first heat exchange section 22, the heat exchange area between the air and the heat exchanger 2 can be increased, and the heat exchange efficiency of the heat exchanger 2 for the passing airflow can be improved. The extension track of the second heat exchange section 23 in the arrangement direction of the heat sinks is the second extension track, and the extension track of the third heat exchange section 24 in the arrangement direction of the heat sinks is the third extension track.

Among them, the second extension trajectory and the third extension trajectory are both straight line segments, the second extension trajectory is collinear with the first tangent, and the third extension trajectory is collinear with the second tangent, that is, the second heat exchange section 23 extends along the first tangent direction at the first end point of the first heat exchange section 22, and the third heat exchange section 24 extends along the second tangent direction at the second end point of the first heat exchange section 22.

The second heat exchange section 23 and the third heat exchange section 24 are both straight sections, and the air flow speed of the second heat exchange section 23 and the third heat exchange section 24 is greater than the air flow speed of the first heat exchange section 22. Compared with the air flow speed of the curved part of the traditional heat exchanger 2, the air flow speed of the first heat exchange section 22 of the heat exchanger 2 of the present application is relatively large, so that the difference in air flow speed between the various heat exchange sections of the heat exchanger 2 is relatively small, so that the air flow speed distribution of the entire heat exchanger 2 along the arrangement direction of the heat sink is more balanced, reducing the overall noise, and at the same time, it can also improve the heat exchange efficiency and air intake efficiency of the heat exchanger 2.

According to some embodiments of the present application, referring to Fig. 1-Fig. 2, the first heat exchange section 22, the second heat exchange section 23 and the third heat exchange section 24 are integrally formed, which can reduce the processing steps of the heat exchanger 2. For example, the semi-finished product of the heat exchanger 2 can be bent to form an integral heat exchanger 2, the bent portion is the first heat exchange section 22, and the straight portions at both ends of the bent portion are the second heat exchange section 23 and the third heat exchange section 24 respectively.

The heat exchanger 2 according to an embodiment of the present application is described below with reference to FIGS. 1-2. The heat exchanger 2 includes a heat exchange tube 21 and a plurality of heat sinks, the heat sinks can extend along a first direction, the plurality of heat sinks are arranged at intervals, and an air flow channel is defined between adjacent heat sinks. The heat exchanger 2 includes a first heat exchange section 22, a second heat exchange section 23, and a third heat exchange section 24. The first heat exchange section 22, the second heat exchange section 23, and the third heat exchange section 24 are integrally formed.

The first heat exchange section 22 is a curved portion of the heat exchanger 2. The extension track of the first heat exchange section 22 in the arrangement direction of the heat sink is the first extension track. The first extension track includes a first end point and a second end point. The tangent at the first end point of the first extension track is the first tangent, and the tangent at the second end point of the first extension track is the second tangent. The angle α between the first tangent and the second tangent is 80°, which can reduce the resistance of the airflow passing through the first heat exchange section 22, thereby reducing energy consumption, increasing the overall air intake efficiency, and reducing noise. At the same time, it can ensure that the overall structure is more compact, the heat exchange area is larger, and the heat exchange efficiency is higher.

The second heat exchange section 23 and the third heat exchange section 24 are both linear, and the second heat exchange section 23 and the third heat exchange section 24 are respectively connected to the opposite ends of the first heat exchange section 22, the second heat exchange section 23 extends along the first tangent direction at the first end point of the first heat exchange section 22, and the third heat exchange section 24 extends along the second tangent direction at the second end point of the first heat exchange section 22.

When the heat exchanger 2 is working, the temperature of the heat exchange tube 21 changes, and the temperature of the heat sink changes with the temperature of the heat exchange tube 21. When the air passes through the heat exchanger 2 through the air flow channel, the air can exchange heat with the heat exchanger 2 in the air flow channel, thereby changing the temperature of the air flow and achieving the heat exchange effect of the heat exchanger 2 on the air.

The air conditioner according to the second embodiment of the present application, referring to FIGS. 1-2 , includes: a casing 10 , an air duct assembly 30 and a heat exchanger assembly 20 .

The housing 10 has an air inlet 11 and an air outlet 12. The air duct assembly 30 is arranged in the housing 10. The air duct assembly 30 includes a fan 4. The fan 4 can drive the air from the air inlet 11 to the air outlet 12, and has a guiding effect on the airflow. The heat exchanger assembly 20 is arranged in the housing 10 and is located on the upstream side of the air duct assembly 30. The heat exchanger assembly 20 includes a heat exchanger 2 according to the embodiment of the first aspect of the present application. The heat exchanger assembly 20 can change the temperature of the airflow passing through. The heat exchanger assembly 20 is located on the upstream side of the air duct assembly 30, so that the airflow after heat exchange can enter the room under the drive of the air duct assembly 30, thereby changing the indoor temperature.

For example, the air conditioner may be a split floor-standing air conditioner, which includes an air conditioner indoor unit 100 and an air conditioner outdoor unit, wherein the air conditioner indoor unit 100 includes the above-mentioned casing 10, air duct assembly 30 and heat exchanger assembly 20.

Specifically, the housing 10 is provided with an air inlet 11 and an air outlet 12 on opposite sides along the second direction (for example, referring to the e2 direction in the accompanying drawings). The air duct assembly 30 may include a fan 4 and an air duct volute 5, the fan 4 includes a wind wheel 41, and the rotation axis of the wind wheel 41 may extend along the first direction. The air duct volute 5 includes a first volute 51 and a second volute 52 arranged relatively spaced apart along the third direction, and at least a portion of the wind wheel 41 is located between the first volute 51 and the second volute 52. An air duct is defined in the air duct volute 5, and the portion of the air duct located on the downstream side of the wind wheel 41 is an air outlet duct, and the air outlet duct is provided with an air guide assembly 13, and the air guide assembly 13 can adjust the overall air outlet direction, and the air guide assembly 13 includes a first louver 131 and a second louver 132, the first louver 131 is located on a side close to the wind wheel 41 along the second direction, and the second louver 132 is located on a side close to the air outlet 12 along the second direction. The first louver 131 and the second louver 132 may be multiple, and the multiple first louvers 131 are arranged at intervals along the first direction, and the rotation axis of the first louver 131 extends along the third direction and the first louver 131 can swing around its own axis in the first direction. Multiple second louvers 132 are arranged at intervals along the third direction, and the rotation axis of the second louver 132 extends along the first direction and the second louver 132 can swing around its own axis in the third direction. The heat exchanger assembly 20 may include a heat exchanger 2 and an electric auxiliary heating component. The heat exchanger 2 is close to the inlet side of the housing 10 and is located on the upstream side of the air duct assembly 30. The electric auxiliary heating component is located between the heat exchanger 2 and the wind wheel 41.

Driven by the air duct assembly 30, air can enter the casing 10 from the air inlet 11, and the air entering the casing 10 exchanges heat with the heat exchanger assembly 20. The air after heat exchange can leave the casing 10 from the air outlet 12 and enter the room, thereby realizing the air conditioner's function of regulating the indoor temperature.

According to the air conditioner of the embodiment of the present application, by optimizing and improving the curved portion of the heat exchanger 2 (i.e., the first heat exchange section 22), the angle range between the tangents of the extension trajectory of the curved portion at its two end points is set to 60° to 110°, which can increase the width of the narrowest part of the air flow channel of the first heat exchange section 22. When the air flow passes through the heat exchanger 2, the resistance to the air flow can be reduced, the air intake efficiency can be improved, the noise can be reduced, and at the same time, it is beneficial to increase the air output; in addition, since the heat exchanger 2 includes the curved portion, the overall structure of the heat exchanger 2 is compact, the heat exchange area is large, and the heat exchange efficiency is high.

According to some embodiments of the present application, with reference to FIG. 1-FIG. 2, the heat exchanger assembly 20 includes an electric auxiliary heating component, which can electrically assist in heating the airflow. The electric auxiliary heating component is located between the heat exchanger 2 and the wind wheel 41 of the fan 4. The airflow after heat exchange in the heat exchanger 2 can flow through the electric auxiliary heating component and exchange heat with the electric auxiliary heating component, thereby further changing the temperature of the airflow. The minimum spacing between the electric auxiliary heating component and the wind wheel 41 is not less than 15 mm. When the minimum spacing between the electric auxiliary heating component and the wind wheel 41 is too small, when the airflow flows between the electric auxiliary heating component and the wind wheel 41, eddy currents are easily generated, thereby generating abnormal sounds. Therefore, when the minimum spacing between the electric auxiliary heating component and the wind wheel 41 is not less than 15 mm, the airflow between the electric auxiliary heating component and the wind wheel 41 can be better prevented from generating abnormal sounds. For example, the electric auxiliary heating component can be a thermistor.

For example, in a specific embodiment of the present application, the heat exchanger 2 of the heat exchanger assembly 20 includes a first heat exchange section 22, a second heat exchange section 23 and a third heat exchange section 24. The distance between the wind wheel 41 and the second heat exchange section 23 is smaller than the distance between the wind wheel 41 and the first heat exchange section 22, and the distance between the wind wheel 41 and the second heat exchange section 23 is smaller than the distance between the wind wheel 41 and the third heat exchange section 24. The heat exchanger assembly 20 includes an electric auxiliary heating component 31, and at least part of the electric auxiliary heating component is arranged between the third heat exchange section 24 and the wind wheel 41. Specifically, the electric auxiliary heating component includes two electric auxiliary heating components 31, one of which is located between the first heat exchange section 22 and the wind wheel 41, and the other is located between the third heat exchange section 24 and the wind wheel 41, so that the structure can be more compact.

According to some embodiments of the present application, with reference to FIG. 1-FIG. 2, the air duct assembly 30 includes an air duct volute 5, which can change the direction of the internal airflow, reduce the loss of air volume, and reduce noise. The wind wheel 41 of the fan 4 is arranged in the air duct volute 5, and the rotation axis of the wind wheel 41 can be perpendicular to the arrangement direction of the heat sink. The wind wheel 41 is a cross-flow wind wheel 41, which has the advantages of uniform air discharge, no turbulence, and a long air flow distance. The air duct volute 5 includes a first volute 51 and a second volute 52 arranged opposite to each other, and at least a part of the wind wheel 41 is located between the first volute 51 and the second volute 52. For example, part of the wind wheel 41 can be located between the first volute 51 and the second volute 52, or the whole of the wind wheel 41 can be located between the first volute 51 and the second volute 52.

The first volute 51 includes a first volute body 511 and a first volute tongue 512. The first volute tongue 512 is connected to one end of the first volute body 511 adjacent to the air inlet 11. The first volute tongue 512 can reduce the overall air volume loss and improve the ventilation efficiency of the wind wheel 41. The second volute 52 includes a second volute body 52 and a second volute tongue 522. The second volute tongue 522 is connected to one end of the second volute body 521 adjacent to the air inlet 11. The second volute tongue 522 can reduce the overall air volume loss and improve the ventilation efficiency of the wind wheel 41. At least the portion of the first volute body 511 opposite to the wind wheel 41 extends in an involute in the flow direction of the airflow. The air volume between the first volute body 511 and the wind wheel 41 can be increased to reduce noise.

According to some embodiments of the present application, with reference to FIG1 , the minimum spacing between the first volute tongue 512 and the outer peripheral contour of the wind rotor 41 is B ₁ , the minimum spacing between the second volute tongue 522 and the outer peripheral contour of the wind rotor 41 is E ₁ , the diameter of the wind rotor 41 is D, the value range of B ₁ is 0.04D to 0.06D, and the value range of E ₁ is 0.04D to 0.06D. For example, the minimum spacing B ₁ between the first volute tongue 512 and the outer peripheral contour of the wind rotor 41 can be 0.04D, 0.05D, 0.06D, etc.

When the minimum spacing _B1 between the first volute tongue 512 and the outer periphery of the wind wheel 41 is too small, when the wind wheel 41 is working, the first volute tongue 512 is easy to collide with the outer periphery of the wind wheel 41 under the action of air pressure, thereby affecting the overall normal operation. At the same time, the eddy noise generated by the airflow will be significantly increased; when the minimum spacing _B1 between the first volute tongue 512 and the outer periphery of the wind wheel 41 is too large, the airflow will easily cause an increase in return air at a low speed of the wind wheel 41, thereby increasing the overall air volume loss and reducing the ventilation efficiency of the wind wheel 41. Therefore, when the value range of the minimum spacing _B1 between the first volute tongue 512 and the outer periphery of the wind wheel 41 is 0.04D to 0.06D, the collision between the first volute tongue 512 and the outer periphery of the wind wheel 41 can be avoided, the noise can be reduced, and the overall air volume loss can be reduced, and the ventilation efficiency of the wind wheel 41 can be improved.

According to some embodiments of the present application, referring to Fig. 1, the minimum spacing between the first volute tongue 512 and the outer peripheral contour of the wind rotor 41 is _B1 , the minimum spacing between the second volute tongue 522 and the outer peripheral contour of the wind rotor 41 is _E1 , the diameter of the wind rotor 41 is D, and the value range of _E1 is 0.04D to 0.06D. For example, the minimum spacing _E1 between the second volute tongue 522 and the outer peripheral contour of the wind rotor 41 can be 0.04D, 0.05D, 0.06D, etc.

When the minimum spacing _E1 between the second volute tongue 522 and the outer periphery of the wind wheel 41 is too small, when the wind wheel 41 is working, the second volute tongue 522 is easy to collide with the outer periphery of the wind wheel 41 under the action of air pressure, thereby affecting the overall normal operation. At the same time, the vortex noise generated by the airflow will be significantly increased; when the minimum spacing _E1 between the second volute tongue 522 and the outer periphery of the wind wheel 41 is too large, the airflow is easy to cause an increase in return air at a low speed of the wind wheel 41, thereby increasing the overall air volume loss and reducing the ventilation efficiency of the wind wheel 41. Therefore, when the value range of the minimum spacing _E1 between the second volute tongue 522 and the outer periphery of the wind wheel 41 is 0.04D to 0.06D, the second volute tongue 522 can be prevented from colliding with the outer periphery of the wind wheel 41, reducing noise, and at the same time reducing the overall air volume loss and improving the ventilation efficiency of the wind wheel 41.

According to some embodiments of the present application, referring to FIG. 1 , the minimum spacing between the first volute tongue 512 and the outer peripheral contour of the wind wheel 41 is B ₁ , the minimum spacing between the second volute tongue 522 and the outer peripheral contour of the wind wheel 41 is E ₁ , the diameter of the wind wheel 41 is D, the value range of B ₁ is 0.04D to 0.06D, and the value range of E ₁ is 0.04D to 0.06D. The first volute tongue 512 and the second volute tongue 522 can be prevented from colliding with the outer peripheral contour of the wind wheel 41, thereby reducing the overall noise, and at the same time can reduce the overall air volume loss, thereby improving the ventilation efficiency of the wind wheel 41.

In some optional embodiments of the present application, the maximum value of the minimum distance _E1 between the second volute tongue 522 and the outer peripheral contour of the wind wheel 41 is not greater than the minimum distance _B1 between the first volute tongue 512 and the outer peripheral contour of the wind wheel 41, which can reduce airflow leakage at the second volute tongue 522 and improve air duct performance.

According to some embodiments of the present application, with reference to FIG. 1 , the minimum spacing between the first volute tongue 512 and the outer periphery of the wind wheel 41 is B ₁ . The rotation axis of the wind wheel 41 extends along the first direction, and at least part of the air inlet 11 and the air outlet 12 are located on opposite sides of the housing 10 along the second direction, so that the distance between the air inlet 11 and the air outlet 12 can be shortened, thereby reducing the overall air volume loss. Driven by the wind wheel 41, air can flow into the air inlet 11 for heat exchange and then flow out of the air outlet 12, thereby achieving temperature regulation of the surrounding environment. A first straight line 14 is drawn through the center of the wind wheel 41 along the radial direction of the wind wheel 41 and along the third direction, and the spacing between the outer periphery of the wind wheel 41 and the first volute body 511 in the direction of the first straight line 14 is B ₃ . For example, the intersection of the first straight line 14 and the outer periphery of the wind wheel 41 is point A, the intersection of the first straight line 14 and the inner wall surface of the first volute body 511 is point F, and the length of the line between point A and point F is B ₃ . The value range of _B3 is _2.5B1-4.5B1 , for example, the distance _B3 between the outer peripheral contour of the wind wheel 41 and the first volute body 511 in the direction where the first straight line 14 is located can be _2.5B1 , _2.75B1 , _3B1 , _3.25B1 , _3.5B1 , _3.75B1 , _4B1 , _4.25B1 , _4.5B1 , etc. The first direction, the second direction and _the third direction are perpendicular to each other, for example, the first direction can be perpendicular to the second direction, the second direction can be perpendicular to the third direction, and the first direction can be perpendicular to the third direction.

When the distance _B3 between the outer periphery of the wind wheel 41 and the first volute body 511 in the direction of the first straight line 14 is too small, the airflow between the first volute body 511 and the wind wheel 41 will be reduced, and surging will easily occur, generating more noise; when the distance _B3 between the outer periphery of the wind wheel 41 and the first volute body 511 in the direction of the first straight line 14 is too large, the overall size will be larger and occupy more space. Therefore, when the value range of the distance _B3 between the outer periphery of the wind wheel 41 and the first volute body 511 in the direction of the first straight line 14 is _2.5B1 to _4.5B1 , the airflow between the first volute body 511 and the wind wheel 41 can be increased, the noise can be reduced, and the overall size can be reduced.

According to some embodiments of the present application, referring to FIG. 1 , the value of B ₃ is 3.75B ₁ , which can increase the airflow between the first volute body 511 and the wind wheel 41, avoid surge, reduce noise, and better reduce the overall size and overall occupied space.

According to some embodiments of the present application, with reference to FIG. 2 , the straight line where the minimum spacing B ₁ between the first volute tongue 512 and the outer peripheral contour of the wind rotor 41 is located is the second straight line 15. For example, the second straight line 15 is drawn through the center of the wind rotor 41 along the radial direction of the wind rotor 41 and along the third direction, the intersection point of the second straight line 15 and the inner wall surface of the first volute tongue 512 is point G, the intersection point of the second straight line 15 and the outer peripheral contour of the wind rotor 41 is point H, and the length of the line connecting point G and point H is the minimum spacing B ₁ between the first volute tongue 512 and the outer peripheral contour of the wind rotor 41. The angle between the first straight line 14 and the second straight line 15 is γ, and the third straight line 16 is drawn through the center of the wind rotor 41 along the radial direction of the wind rotor 41. The third straight line 16 is located between the first straight line 14 and the second straight line 15, and the angle between the third straight line 16 and the second straight line 15 is γ/2, and the angle between the third straight line 16 and the first straight line 14 is also γ/2. The spacing between the outer peripheral contour of the wind rotor 41 and the first volute body 511 in the direction where the third straight line 16 is located is B ₂ . For example, the intersection of the third straight line 16 and the outer peripheral contour of the wind rotor 41 is point J, the intersection of the third straight line 16 and the inner wall surface of the first volute body 511 is point K, and the length of the line between point J and point K is B ₂ . The value range of B ₂ is 1.5B ₁ to 3.5B ₁ . For example, the spacing B ₂ between the outer peripheral contour of the wind rotor 41 and the first volute body 511 in the direction where the third straight line is located can be 1.5B ₁ , 1.9B ₁ , 2.3B ₁ , 2.7B ₁ , 3.1B ₁ , 3.5B ₁ , etc.

When the distance _B2 between the outer periphery of the wind wheel 41 and the first volute body 511 in the direction of the third straight line 16 is too small, the airflow between the first volute body 511 and the wind wheel 41 will be reduced, and surging will easily occur, generating more noise; when the distance B2 between the outer periphery of the wind wheel 41 and the first volute body 511 in the direction of the third straight line 16 is too large, the overall size will be larger and occupy more space. Therefore, when the value range of the distance _B2 between the outer periphery of the wind wheel 41 and the first volute body ₅₁₁ in the direction of the third straight line 16 is _1.5B1 to _3.5B1 , the airflow between the first volute body 511 and the wind wheel 41 can be increased, the noise can be reduced, and the overall size can be reduced.

According to some embodiments of the present application, referring to FIG. 2 , the value of B ₂ is 2.3B ₁ , which can increase the airflow between the first volute body 511 and the wind wheel 41 , avoid surge, reduce noise, and better reduce the overall size and overall occupied space.

According to some embodiments of the present application, referring to FIG. 1-FIG. 2, the second volute body 521 and the second volute tongue 522 are transitionally connected through the fillet 524, which can make the transition between the second volute body 521 and the second volute tongue 522 smoother, the airflow transition more naturally and smoothly, and improve the stability of the airflow near the fillet 524. The minimum spacing between the fillet 524 and the inner wall surface of the first volute body 511 is _B4 , the diameter of the wind wheel 41 is D, and the value range of _B4 is 0.45D-0.75D. For example, the minimum spacing _B4 between the fillet 524 and the inner wall surface of the first volute body 511 can be 0.45D, 0.5D, 0.55D, 0.6D, 0.62D, 0.65D, 0.7D, 0.75D, etc.

When the minimum spacing _B4 between the fillet 524 and the inner wall of the first volute body 511 is too small, the air volume of the whole machine will be small, and because the wind speed near the outlet is high, surging will occur and noise will be generated; when the minimum spacing _B4 between the fillet 524 and the inner wall of the first volute body 511 is too large, the wind speed near the outlet will be unstable. Therefore, when the minimum spacing _B4 between the fillet 524 and the inner wall of the first volute body 511 is in the range of 0.45D-0.75D, the overall air volume can be increased, the noise can be reduced, and the wind speed near the outlet can be optimized, so that the wind speed is more stable.

According to some embodiments of the present application, referring to FIG. 1-FIG . 2 , the value of B ₄ is 0.62D, which can increase the overall air volume and reduce noise, and at the same time can better optimize the nearby air outlet speed, thereby making the air outlet speed more stable.

According to some embodiments of the present application, referring to FIG. 1-FIG. 2, the second volute body 521 and the second volute tongue 522 are transitionally connected through the fillet 524, which can make the transition between the second volute body 521 and the second volute tongue 522 smoother, the airflow transition is more natural and smooth, and the stability of the airflow near the fillet 524 is improved. The radius of the fillet 524 ranges from 2 to 8 mm. For example, the radius of the fillet 524 can be 2 mm, 3 mm, 4 mm, 5 mm, 6 mm, 7 mm, 8 mm, etc.

When the radius of the fillet 524 is too small, the airflow stability near the fillet 524 is poor and noise is easily generated; when the radius of the fillet 524 is too large, the overall size will be larger and occupy more space. Therefore, when the radius of the fillet 524 is in the range of 2 to 8 mm, the airflow transition can be more natural and smooth, the stability of the airflow near the fillet 524 can be improved, and the overall size can be reduced.

According to some embodiments of the present application, referring to FIG. 1-FIG . 2 , the radius of the rounded corner 524 is 6 mm, which can make the airflow transition more natural and smooth, improve the stability of the airflow near the rounded corner 524 , and at the same time better reduce the overall size and reduce the overall occupied space.

According to some embodiments of the present application, with reference to FIGS. 1-2, the rotation axis of the wind wheel 41 extends along the first direction, and at least part of the air inlet 11 and the air outlet 12 are located on opposite sides of the housing 10 along the second direction, so that the distance between the air inlet 11 and the air outlet 12 can be shortened, thereby reducing the overall air volume loss. Driven by the wind wheel 41, air can flow into the air inlet 11 for heat exchange and then flow out of the air outlet 12, thereby achieving temperature regulation of the surrounding environment. The second volute body 521 includes an air guide 523, which can guide the outlet air flow. The value range of the angle β between the air guide 523 and the third direction is 35° to 75°, for example, the value of the angle β between the air guide 523 and the third direction can be 35°, 45°, 51°, 55°, 65°, 75°, etc. The first direction, the second direction and the third direction are perpendicular to each other, for example, the first direction can be perpendicular to the second direction, the second direction can be perpendicular to the third direction, and the first direction can be perpendicular to the third direction.

When the angle β between the air guide 523 and the third direction is too small, the overall wind speed will be reduced, resulting in a small air volume, and reducing the overall temperature regulation efficiency of the room; when the angle β between the air guide 523 and the third direction is too large, the wind speed will be high, and surging is likely to occur, thereby generating a large noise. Therefore, when the angle β between the air guide 523 and the third direction is in the range of 35° to 75°, the overall wind speed can be increased, the air volume can be increased, and the noise can be reduced.

According to some embodiments of the present application, referring to FIG. 1-FIG 2 , the angle β between the air guide portion 523 and the third direction is 51°, which can increase the overall wind speed, increase the air volume, and achieve a better noise reduction effect.

According to some embodiments of the present application, referring to FIG. 1-FIG. 2, there is one wind wheel 41, and the air duct component is a single cross-flow air duct structure. Driven by the wind wheel 41, air can flow in from the air inlet 11 for heat exchange and then flow out from the air outlet 12, thereby achieving temperature regulation of the surrounding environment. The air duct assembly 30 is a single cross-flow air duct structure, which has the advantages of large air volume and low noise compared to other structures.

The following describes an air conditioner according to an embodiment of the present application with reference to FIGS. 1-2 . In this embodiment, the first direction is the up-down direction, the second direction is the front-back direction, and the third direction is the left-right direction.

1-2 , in this embodiment, the air conditioner may be a split floor-standing air conditioner, which includes an air conditioner indoor unit 100 and an air conditioner outdoor unit, wherein the air conditioner indoor unit 100 includes a housing 10 , an air duct assembly 30 and a heat exchanger assembly 20 .

The housing 10 is formed with an air inlet 11 and an air outlet 12, at least part of the air inlet 11 and the air outlet 12 are located on opposite sides of the housing 10 along the front-rear direction, and an air duct assembly 30 and a heat exchanger assembly 20 are arranged in the housing 10. The air duct assembly 30 includes a fan 4 and an air duct volute 5, a wind wheel 41 of the fan 4 is arranged in the air duct volute 5, the rotation axis of the wind wheel 41 extends in the up-down direction, the diameter of the wind wheel 41 is D, and the wind wheel 41 is a crossflow wind wheel 41.

An air duct is defined in the air duct volute 5, and the part of the air duct located on the downstream side of the wind wheel 41 is the air outlet duct, and the air outlet duct is provided with an air guide assembly 13, and the air guide assembly 13 includes a first louver 131 and a second louver 132, the first louver 131 is located on the side close to the wind wheel 41 in the front-to-back direction, and the second louver 132 is located on the side close to the air outlet 12 in the front-to-back direction. There can be multiple first louvers 131 and second louvers 132, and multiple first louvers 131 are arranged at intervals in the up-down direction, and the rotation axis of the first louver 131 extends in the left-right direction, and the first louver 131 can swing up and down around its own axis. Multiple second louvers 132 are arranged at intervals in the left-to-right direction, and the rotation axis of the second louver 132 extends in the up-to-down direction, and the second louver 132 can swing left and right around its own axis.

The air duct volute 5 comprises a first volute 51 and a second volute 52 which are arranged at a relative interval in the left-right direction, and at least a part of the wind wheel 41 is located between the first volute 51 and the second volute 52. The first volute 51 comprises a first volute body 511 and a first volute tongue 512, and the first volute tongue 512 is connected to one end of the first volute body 511 adjacent to the air inlet 11, and the minimum spacing between the first volute tongue 512 and the outer peripheral contour of the wind wheel 41 is B ₁ , and the value range of B ₁ is 0.04D to 0.06D. The part of the first volute body 511 opposite to the wind wheel 41 extends in an involute in the flow direction of the airflow, and a first straight line 14 is drawn along the radial direction of the wind wheel 41 and in the left-right direction through the center of the wind wheel 41, and the spacing between the outer peripheral contour of the first volute body 511 and the wind wheel 41 in the direction where the first straight line 14 is located is B ₃ , and the value of B ₃ is 3.75B ₁ . The straight line where the minimum spacing _B1 between the first volute tongue 512 and the outer peripheral contour of the wind wheel 41 is located is the second straight line 15, the angle between the first straight line 14 and the second straight line 15 is γ, and a third straight line 16 is drawn along the radial direction of the wind wheel 41 through the center of the wind wheel 41. The third straight line 16 is located between the first straight line 14 and the second straight line 15, and the angle between the third straight line 16 and the second straight line 15 is γ/2. The angle between the third straight line 16 and the first straight line 14 is also γ/2. The spacing between the outer peripheral contour of the wind wheel 41 and the first volute body 511 in the direction where the third straight line 16 is located is _B2 , and _B3 is _2.3B1 .

The second volute 52 includes a second volute body 521 and a second volute tongue 522, and the second volute body 521 includes an air guide portion 523. The second volute tongue 522 is connected to one end of the second volute body 521 adjacent to the air outlet 12, and the minimum spacing between the second volute tongue 522 and the outer peripheral contour of the wind wheel 41 is _E1 , and the value range of _E1 is 0.04D to 0.06D, and the maximum value of E1 is not greater than _B1 . The second volute body 521 and the second volute tongue 522 are transitionally connected by a fillet portion 524, and the radius of the fillet portion 524 is 6mm. The minimum spacing between the fillet portion 524 and the inner wall surface of the first volute body 511 is _B4 , and _B4 is 0.62D. The angle β between the air guide portion 523 of the second volute body 521 and the right side direction is 51°.

The heat exchanger assembly 20 is located on the upstream side of the air duct assembly 30. The heat exchanger assembly 20 includes a heat exchanger 2 and an electric auxiliary heating component. The heat exchanger 2 includes a heat exchange tube 21 and a plurality of heat sinks. The heat exchange tube 21 is passed through a plurality of heat sinks arranged in sequence. Each heat sink can extend in the up and down directions. The plurality of heat sinks are arranged at intervals, and an air flow channel is defined between adjacent heat sinks. The heat exchanger 2 can be divided into a first heat exchange section 22, a second heat exchange section 23 and a third heat exchange section 24. The second heat exchange section 23 is located at the rear side of the wind wheel 41, and the third heat exchange section 24 is located at the right side of the wind wheel 41. The first heat exchange section 22 is connected between the second heat exchange section 23 and the third heat exchange section 24. The distance between the wind wheel 41 and the second heat exchange section 23 is smaller than the distance between the wind wheel 41 and the first heat exchange section 22, and the distance between the wind wheel 41 and the second heat exchange section 23 is smaller than the distance between the wind wheel 41 and the third heat exchange section 24.

The extension trajectory of the first heat exchange section 22 in the arrangement direction of the heat sink is a first extension trajectory, which is an arc segment. The tangents at the two end points of the first extension trajectory are respectively the first tangent and the second tangent, and the angle α between the first tangent and the second tangent is 80°.

The second heat exchange section 23 and the third heat exchange section 24 are respectively connected to the opposite ends of the first heat exchange section 22 along the arrangement direction of the heat sinks. The extension trajectory of the second heat exchange section 23 in the arrangement direction of the heat sinks is the second extension trajectory, and the extension trajectory of the third heat exchange section 24 in the arrangement direction of the heat sinks is the third extension trajectory. Both the second extension trajectory and the third extension trajectory are straight line segments. The second extension trajectory is collinear with the first tangent, and the third extension trajectory is collinear with the second tangent.

The electric auxiliary heating component is located between the heat exchanger 2 and the wind wheel 41 of the fan 4, and the minimum spacing between the electric auxiliary heating component and the wind wheel 41 is not less than 15 mm. The electric auxiliary heating component includes two electric auxiliary heating parts 31, one of which is located between the first heat exchange section 22 and the wind wheel 41, and the other is located between the third heat exchange section 24 and the wind wheel 41.

When the air conditioner needs to work, the heat exchanger assembly 20 and the fan 4 start to start, the temperature of the heat exchange tube 21, the heat sink and the electric auxiliary heating component in the heat exchanger 2 changes, the fan wheel 41 of the fan 4 starts to rotate, and the air enters the casing 10 from the air inlet 11 driven by the fan wheel 41. The air entering the casing 10 exchanges heat with the heat exchanger 2. The air after heat exchange exchanges heat again through the electric auxiliary heating component. Finally, the air with changed temperature can leave the casing 10 from the air outlet 12 and enter the room, thereby realizing the air conditioner's function of regulating the indoor temperature.

In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present application.

In the description of the present application, “plurality” means two or more.

In the description of the present application, “above”, “over” and “above” a first feature to a second feature includes the first feature being directly above and obliquely above the second feature, or simply means that the first feature is horizontally higher than the second feature.

In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials, or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

Although the embodiments of the present application have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present application, and that the scope of the present application is defined by the claims and their equivalents.

Claims (19)

1. A heat exchanger, wherein the heat exchanger comprises a heat exchange tube and a plurality of heat sinks, the heat exchange tube is passed through the plurality of heat sinks arranged in sequence, the heat exchanger comprises a first heat exchange section, an extension trajectory of the first heat exchange section in the arrangement direction of the heat sinks is a first extension trajectory, the first extension trajectory is an arc segment, the tangents at the two end points of the first extension trajectory are respectively a first tangent and a second tangent, and the angle between the first tangent and the second tangent ranges from 60° to 110°.
2. The heat exchanger according to claim 1, wherein the angle between the first tangent line and the second tangent line is 80°.
3. The heat exchanger according to claim 1 or 2, wherein the heat exchanger further comprises a second heat exchange section and a third heat exchange section, the second heat exchange section and the third heat exchange section are respectively connected to opposite ends of the first heat exchange section along the arrangement direction of the heat sink, and the extension tracks of the second heat exchange section and the third heat exchange section in the arrangement direction of the heat sink are respectively the second extension track and the third extension track;

   The second extension trajectory and the third extension trajectory are both straight line segments, the second extension trajectory is collinear with the first tangent line, and the third extension trajectory is collinear with the second tangent line.
4. The heat exchanger according to claim 3, wherein the first heat exchange section, the second heat exchange section and the third heat exchange section are integrally formed.
5. An air conditioner, comprising:

   a housing having an air inlet and an air outlet;

   An air duct assembly is disposed in the housing and includes a fan;

   A heat exchanger assembly is disposed in the casing and located on the upstream side of the air duct assembly, and the heat exchanger assembly includes a heat exchanger according to any one of claims 1-4.
6. The air conditioner according to claim 5, wherein the heat exchanger assembly comprises an electric auxiliary heating component, the electric auxiliary heating component is located between the heat exchanger and the wind wheel of the fan, and the minimum spacing between the electric auxiliary heating component and the wind wheel is not less than 15 mm.
7. The air conditioner according to claim 5, wherein the air duct assembly includes an air duct volute, the wind wheel of the fan is arranged in the air duct volute, the wind wheel is a cross-flow wind wheel, the air duct volute includes a first volute and a second volute arranged opposite to each other, at least a part of the wind wheel is located between the first volute and the second volute, the first volute includes a first volute body and a first volute tongue, the first volute tongue is connected to one end of the first volute body adjacent to the air inlet, the second volute includes a second volute body and a second volute tongue, the second volute tongue is connected to one end of the second volute body adjacent to the air inlet, and at least the part of the first volute body opposite to the wind wheel extends in an involute in the flow direction of the airflow.
8. The air conditioner according to claim 7, wherein the minimum distance between the first volute tongue and the outer peripheral contour of the wind wheel is _B1 , the minimum distance between the second volute tongue and the outer peripheral contour of the wind wheel is _E1 , the diameter of the wind wheel is D, the value range of _B1 is 0.04D to 0.06D and/or the value range of _E1 is 0.04D to 0.06D.
9. The air conditioner according to claim 7, wherein the minimum spacing between the first volute tongue and the outer peripheral contour of the wind wheel is B ₁ , the rotation axis of the wind wheel extends along the first direction, at least part of the air inlet and the air outlet are located on opposite sides of the casing along the second direction, a first straight line is drawn through the center of the wind wheel along the radial direction of the wind wheel and along the third direction, and the spacing between the outer peripheral contour of the wind wheel and the first volute body in the direction where the first straight line is located is B ₃ , and the value range of B ₃ is 2.5B ₁ to 4.5B ₁ , wherein the first direction, the second direction and the third direction are perpendicular to each other.
10. The air conditioner according to claim 9, wherein the value of B ₃ is 3.75B ₁ .
11. The air conditioner according to claim 9, wherein the straight line where the minimum spacing _B1 between the first volute tongue and the outer peripheral contour of the wind wheel is located is the second straight line, the angle between the first straight line and the second straight line is γ, a third straight line is drawn along the radial direction of the wind wheel through the center of the wind wheel, the third straight line is located between the first straight line and the second straight line, and the angle between the third straight line and the second straight line is γ/2, the spacing between the outer peripheral contour of the wind wheel and the first volute body in the direction where the third straight line is located is _B2 , and the value range of _B2 is _1.5B1 to _3.5B1 .
12. The air conditioner according to claim 11, wherein the value of B ₂ is 2.3B ₁ .
13. The air conditioner according to claim 7, wherein the second volute body and the second volute tongue are transitionally connected via a fillet portion, the minimum spacing between the fillet portion and the inner wall surface of the first volute body is _B4 , the diameter of the wind wheel is D, and the value range of _B4 is 0.45D to 0.75D.
14. The air conditioner according to claim 13, wherein the value of _B4 is 0.62D.
15. The air conditioner according to claim 7, wherein the second volute body and the second volute tongue are transitionally connected via a fillet portion, and the radius of the fillet portion is in the range of 2 to 8 mm.
16. The air conditioner according to claim 15, wherein the radius of the fillet portion is 6 mm.
17. The air conditioner according to claim 7, wherein the rotation axis of the wind wheel extends along a first direction, at least a portion of the air inlet and the air outlet are located on opposite sides of the casing along a second direction, the second volute body includes an air guide portion, and an angle between the air guide portion and a third direction ranges from 35° to 75°, wherein the first direction, the second direction and the third direction are perpendicular to each other.
18. The air conditioner according to claim 17, wherein the angle between the air guide portion and the third direction is 51°.
19. The air conditioner according to any one of claims 5-18, wherein the fan has one wind wheel and the air duct assembly is a single cross-flow air duct structure.

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