CN213066335U

CN213066335U - Air duct type air conditioner

Info

Publication number: CN213066335U
Application number: CN202020977867.3U
Authority: CN
Inventors: 周柏松; 吴淋; 李运志; 吴多德; 韦福权; 罗彬�
Original assignee: Midea Group Co Ltd; GD Midea Heating and Ventilating Equipment Co Ltd
Current assignee: Midea Group Co Ltd; GD Midea Heating and Ventilating Equipment Co Ltd; Guangdong Midea HVAC Equipment Co Ltd
Priority date: 2020-06-01
Filing date: 2020-06-01
Publication date: 2021-04-27
Anticipated expiration: 2030-06-01

Abstract

The utility model discloses an air duct type air conditioning device. The air pipe type air conditioning device comprises a heat exchanger, wherein the heat exchanger comprises a plurality of heat exchange fins, heat exchange pipes and plastic side plates, and the plurality of heat exchange fins are arranged at intervals; the heat exchange tube comprises linear tube sections which are arranged on the plurality of heat exchange fins in a penetrating mode and U-shaped tube sections which are connected to the adjacent tail ends of different linear tube sections; the plastic side plate is provided with a slot for receiving the U-shaped pipe section, wherein the slot is set to be capable of adapting to at least two different arrangement modes of the U-shaped pipe section. When the arrangement mode of the U-shaped pipe sections is changed, the heat exchange pipe can be supported by the same plastic side plate, so that the universality of the plastic side plate is improved, and the mass production of the plastic side plate is facilitated to reduce the production cost.

Description

Air duct type air conditioner

Technical Field

The utility model relates to an air conditioning technology field, concretely relates to tuber pipe formula air conditioning equipment.

Background

At present, in an air conditioning device, a heat exchanger based on heat exchange fins is mostly adopted to realize a heat exchange function. Particularly, the heat exchange tubes are arranged on the plurality of heat exchange fins at intervals in a penetrating mode, the heat exchange tubes serve as flow channels of heat exchange media, gaps among the heat exchange fins serve as airflow channels, and airflow generated by the fan exchanges heat with the heat exchange media in the flowing process of the airflow channels.

The non-welding end of the U-shaped heat exchange tube on the heat exchanger is usually provided with a plastic side plate to utilize the clamping groove arranged on the plastic side plate to support the heat exchange tube, the plastic side plate is usually arranged into an integral structure to improve the fixed assembly efficiency of the heat exchange tube, but when the insertion tube mode of the heat exchange tube is changed, the clamping groove on the plastic side plate can be adjusted therewith, so that the universality of the plastic side plate is not high.

SUMMERY OF THE UTILITY MODEL

The utility model provides an air duct type air conditioning device to promote the commonality of plastic sideboard.

In order to solve the technical problem, the utility model discloses a technical scheme be: the air pipe type air conditioning device comprises a heat exchanger, wherein the heat exchanger comprises a plurality of heat exchange fins, heat exchange pipes and plastic side plates, and the plurality of heat exchange fins are arranged at intervals; the heat exchange tube comprises linear tube sections which are arranged on the plurality of heat exchange fins in a penetrating mode and U-shaped tube sections which are connected to the adjacent tail ends of different linear tube sections; the plastic side plate is provided with a slot for receiving the U-shaped pipe section, wherein the slot is set to be capable of adapting to at least two different arrangement modes of the U-shaped pipe section.

In this way, set the slot to two kinds of at least different arrangement modes that can adapt to the U-shaped pipeline section for when the arrangement mode of U-shaped pipeline section changes, can utilize same plastic sideboard to support the heat transfer pipe, with the commonality that promotes the plastic sideboard, and then the large-scale production of the plastic sideboard of being convenient for is with reduction in production cost.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings used in the description of the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained without inventive work, wherein:

fig. 1 is a schematic cross-sectional view of an air duct type air conditioner according to an embodiment of the present invention;

fig. 2 is a side view of a heat exchanger fin according to an embodiment of the present invention;

FIGS. 3 and 4 are graphs showing a flow velocity distribution of an air duct type air conditioner using a diffuser plate arrangement according to an embodiment of the present invention and a comparison of the flow velocity distribution of a comparative example;

fig. 5 is a schematic perspective view of a heat exchanger and an auxiliary fitting mechanism according to an embodiment of the present invention;

fig. 6 is a side view of a sheet metal sideboard in accordance with an embodiment of the present invention;

FIG. 7 is a schematic perspective view of the sheet metal edge panel of FIG. 6;

FIG. 8 is a schematic cross-sectional view of the sheet metal side panel of FIG. 7;

fig. 9 is a schematic perspective view of a plastic side plate according to an embodiment of the present invention;

FIG. 10 is a schematic perspective view of the plastic sideplate of FIG. 9 in cooperation with one arrangement of U-shaped pipe sections;

FIG. 11 is a schematic perspective view of the plastic sideplate of FIG. 9 in cooperation with an alternative arrangement of U-shaped pipe sections;

figure 12 is a partial cross-sectional view of the plastic sideplate of figure 9 mated to the U-shaped pipe section.

Detailed Description

The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.

Reference herein to "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment can be included in at least one embodiment of the application. The appearances of the phrase 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 explicitly and implicitly understood by one skilled in the art that the embodiments described herein can be combined with other embodiments.

Referring to fig. 1 and 2, fig. 1 is a schematic cross-sectional view of an air duct type air conditioner according to an embodiment of the present invention, and fig. 2 is a side view of a heat exchange fin according to an embodiment of the present invention. As shown in fig. 1, the air duct type air conditioner of the present embodiment mainly includes a casing 10, a fan assembly 20, and a heat exchanger 30. The housing 10 forms a receiving chamber 11, and the heat exchanger 30 is disposed in the receiving chamber 11. In the present embodiment, the heat exchanger 30 includes a plurality of heat exchange fins 31 arranged at intervals from each other and heat exchange tubes 32 penetrating the heat exchange fins 31. Since the section shown in fig. 1 is a reference section formed by a plane of the main surfaces of the heat exchange fins 31, only one heat exchange fin 31 is shown in fig. 1, and the remaining heat exchange fins 31 are arranged at intervals from the heat exchange fins 31 shown in fig. 1 in a direction perpendicular to the paper surface on which fig. 1 is drawn. The heat exchange fin 31 is generally formed by press molding from a sheet material, and the main surfaces of the heat exchange fin 31 are two side surfaces which are spaced from each other in the thickness direction of the heat exchange fin 31 and have the largest surface area.

The fan assembly 20 includes a volute 21 and a fan 22 disposed in the volute 21, and an air flow generated by the fan 20 flows into the accommodating chamber 11 through an air outlet 211 of the volute 21 under the action of the volute 21 and is blown and swept on the heat exchanger 30. The heat exchange medium flowing in the heat exchange tube 32 exchanges heat with the air flow flowing through the heat exchanger 30 through the heat exchange tube 32 and the heat exchange fins 31, and then cools or heats the air flow flowing through the heat exchanger 30 as required. The airflow after heat exchange by the heat exchanger 30 further flows out through the air outlet 101 of the housing 10.

The present application further optimizes the following aspects based on the overall structure of the air duct type air conditioner described above:

1. volute air outlet angle

In the present embodiment, the fan 22 and the heat exchanging fin 31 are arranged at a distance in the direction D1. The scroll casing 21 includes a first pressure expanding plate 212 and a second pressure expanding plate 213, and the first pressure expanding plate 212 and the second pressure expanding plate 213 are arranged at intervals in the direction D2. The direction D2 is perpendicular to the direction D1 and parallel to the major surfaces of the heat exchanger fins 31. Further, in the direction from the fan 22 to the heat exchange fins 31, the first diffuser plate 212 is inclined toward the second diffuser plate 213, and the second diffuser plate 213 is inclined away from the first diffuser plate 212.

It is noted that, in the normal installation and use state of the air duct type air conditioner of the present application, the direction D1 is generally a horizontal direction, the direction D2 is generally a vertical direction (i.e., a gravity direction), and the first diffuser plate 212 is located on the upper side of the second diffuser plate 213. The relative positional relationships of "up", "down", "front", "back" and the like mentioned in the present application are also the relative positional relationships of the air duct type air conditioning device in the normal installation and use states.

The first pressure expanding plate 212 and the second pressure expanding plate 213 are used for guiding the airflow generated by the fan 22 to flow into the accommodating chamber 11 through the air outlet 211 of the scroll casing 21, and converting the speed energy of the airflow into pressure energy through the shape change of the flow passage between the first pressure expanding plate 212 and the second pressure expanding plate 213, thereby increasing the pressure of the airflow at the air outlet 211. Therefore, the angle parameters of the first and second

pressure expanding plates

212 and 213 directly affect the uniformity of the flow velocity distribution of the air flow passing through the heat exchange fins 31.

Therefore, in the present embodiment, in order to obtain a better uniformity of the flow velocity distribution, the included angle β 1 between the first diffuser plate 212 and the direction D1 is set to 6 to 9 degrees, and the included angle β 2 between the second diffuser plate 213 and the direction D1 is set to 20 to 24 degrees, on the reference cross section formed by the plane of the main surfaces of the heat exchanging fins 31. In one embodiment, the included angle β 1 is set to 6-8 degrees and β 2 is set to 21-23 degrees. It is noted that, unless otherwise indicated, all numerical ranges recited herein are intended to be inclusive.

Further reference is made to the flow rate profiles of the present example and the comparative example shown in fig. 3 and 4. Fig. 3 and 4 are flow velocity distribution diagrams of the air flow generated by the fan 22 after passing through the same heat exchanger 30 shown in fig. 1 when the included angles β 1 and β 2 between the first pressure expansion plate 212 and the second pressure expansion plate 213 and the direction D1 are different. Wherein the Y-axis in the figure represents the wind speed, the X-axis represents different sampling points on the leeward side contour line (the first side contour line 311 in fig. 2) of the heat exchange fin 31 from the middle region to the end region, and the different lines represent different sampling points from one end to the other end of the heat exchanger 30 in the interval direction of the heat exchange fin 31.

Further, fig. 3 adopts the angle setting manner of the present embodiment, specifically, the included angle β 1 is 7 degrees, and the included angle β 2 is 22 degrees. Fig. 4 adopts other angle setting modes, specifically, the included angle β 1 is 5 degrees, and the included angle β 2 is 19 degrees. From the comparison between fig. 3 and fig. 4, it can be found that the difference of the wind speed variation in the transition process from the middle area to the end area of the wind speed flowing through the heat exchanging fin 31 of fig. 4 is significantly larger than that of fig. 3, so that the flow velocity uniformity of the air flow in the angle setting mode of the embodiment is significantly higher than that in other angle setting modes.

It is to be noted that, when the first pressure expanding plate 212 or the second pressure expanding plate 213 is a flat plate or a main body portion is a flat plate, the included angles β 1 and β 2 with the direction D1 are the included angles between the extension lines of the straight line segments formed on the above-mentioned reference cross sections of the flat plate portions of the first pressure expanding plate 212 or the second pressure expanding plate 213 and the direction D1. When the first pressure expanding plate 212 or the second pressure expanding plate 213 is an arc-shaped plate or a main body part thereof is an arc-shaped plate, the included angles β 1 and β 2 between the first pressure expanding plate 212 or the second pressure expanding plate 213 and the direction D1 are the included angles between the connecting line of the two ends of the overall line formed on the reference cross section and the direction D1.

Further, when the ratio of the length of the straight line segment corresponding to the flat plate in the entire line formed on the reference cross section of the first pressure expanding plate 212 or the second pressure expanding plate 213 to the total length of the entire line is greater than or equal to 60%, the main portion of the first pressure expanding plate 212 or the second pressure expanding plate 213 is considered to be the flat plate, and when the ratio of the length of the straight line segment corresponding to the flat plate to the total length of the entire line is less than 60%, the main portion of the first pressure expanding plate 212 or the second pressure expanding plate 213 is considered to be the arc plate.

Referring to fig. 1, the air flow exiting through the outlet 211 of the volute 21 is mainly divided into three flow velocity zones before reaching the heat exchanger 30: zone A, zone B and zone C. The area A is a direct blowing main flow area, the area B is a main flow diffusion and diffusion area, and the area C is a dynamic pressure conversion static pressure and inherent static pressure diffusion area. The flow rate of the area A is larger than that of the area B, and the flow rate of the area C is small.

With further reference to FIG. 2, the heat exchanger fin 31 has a first side contour 311 and a second side contour 312 spaced from each other. Wherein, second side contour line 312 sets up in heat transfer fin 31 towards fan 22 one side, as windward side contour line, and first side contour line 311 sets up in heat transfer fin 31 and deviates from fan 22 one side, as leeward side contour line.

As shown in fig. 1, in the present embodiment, the extension line of the first diffuser plate 212 intersects the second side contour line 312 to form an intersection point E1, the extension line of the second diffuser plate 213 intersects the second side contour line 312 to form an intersection point E2, the intersection point E1 has a vertical distance D1 to a reference line L1 passing through the uppermost end of the heat exchanging fin 31 and being parallel to the direction D1, the intersection point E2 has a vertical distance D2 to a reference line 12 passing through the lowermost end of the heat exchanging fin 31 and being parallel to the direction D1, and the ratio of the sum of the vertical distance D1 and the vertical distance D2, D1+ D2, and the height L2 of the heat exchanging fin 31 in the direction D2 is 0.26-0.35. Referring to the above description, when the first or second

pressure expanding plate

212 or 213 is a flat plate or a main body portion is a flat plate, an extension thereof is an extension of a straight line segment formed on the above-described reference section by the flat plate portion of the first or second

pressure expanding plate

212 or 213. When the first pressure expanding plate 212 or the second pressure expanding plate 213 is an arc-shaped plate or a main body part is an arc-shaped plate, the extension line thereof is the extension line of the connection line of the two ends of the integral line formed on the reference cross section by the first pressure expanding plate 212 or the second pressure expanding plate 213.

Through the mode, the direct-blowing main flow area A and the main flow diffusion extension area B can simultaneously cover the heat exchange fins 31, so that the heat exchange of the heat exchange fins 31 is more uniform.

Further, since the slow diffusion of the air flow to both sides is similar when the air flow flows in the closed passage, the vertical distance d1 and the vertical distance d2 can be set to be approximately equal. Specifically, the ratio of the vertical distance D1 to the height L2 of the heat exchange fins 31 along the direction D2 is set to 0.13-0.175, and the ratio of the vertical distance D2 to the height L2 of the heat exchange fins 31 along the direction D2 is set to 0.13-0.175, so that the main flow diffusion and diffusion areas B on both sides of the direct blowing main flow area a can cover the heat exchange fins 31, and the heat exchange uniformity of the heat exchange fins 31 is further improved.

Further, in this embodiment, the second side contour line 312 is curved toward the first side contour line 311, the first side contour line 311 is curved away from the second side contour line 312, and a ratio of a linear distance D3 between projections of the intersection point E1 and the intersection point E2 on the reference line L1 or L2 to a width L4 of the heat exchange fin along the direction D1 is less than or equal to 0.2, so that the main flow diffusion regions B on both sides of the direct blowing main flow region a can more completely cover the heat exchange fin 31.

2. Size of the whole machine

Referring to fig. 1, in the duct type air conditioner, if the heat exchanger 30 is too close to the air outlet 211 of the scroll casing 21, the direct blowing area of the air flow is small, the local flow velocity passing through the heat exchanger 30 is large, the heat exchange is insufficient, and the noise is large. If the heat exchanger 30 is too far away from the air outlet 211 of the volute casing 21, the air flow enters the relatively large space of the accommodating chamber 11 from the relatively small space of the volute casing 21, and the air flows may collide with each other in the accommodating chamber 11, resulting in a large local loss. Meanwhile, the size of the whole machine is increased, the integrated design of an air conditioner and a home is not facilitated, and the cost is high.

Therefore, in the present embodiment, in order to achieve a balance between the heat exchange performance and the overall size, the air duct type air conditioning apparatus is further arranged to satisfy the following formula on the reference cross section formed by the plane of the main surfaces of the heat exchange fins 31:

L2＝ξ×(L1+L3×tgθ)；

wherein θ is an included angle between the first pressure expanding plate 212 and the second pressure expanding plate 213, tg is a tangent trigonometric function, L1 is a height of the air outlet 211 of the scroll casing 21 along the direction D2, L2 is a height of the heat exchanging fin 31 along the direction D2, L3 is a distance between an end of the heat exchanging fin 31 close to the air outlet 211 and the air outlet 211 along the direction D1, and ξ is a preset coefficient of 1.3-1.6.

In conjunction with the above description, for different plate shapes, the angles between the first pressure expanding plate 212 and the second pressure expanding plate 213 and the direction D1 are defined by the extension lines and/or the two end connecting lines of the first pressure expanding plate 212 and the second pressure expanding plate 213. Therefore, in the present embodiment, the angle θ between the first pressure expanding plate 212 and the second pressure expanding plate 213 refers to the angle between the above-described extension lines and/or both end connecting lines of the first pressure expanding plate 212 and the second pressure expanding plate 213. Specifically, the included angle θ between the first pressure expanding plate 212 and the second pressure expanding plate 213 is the difference between the included angle β 1 between the first pressure expanding plate 212 and the direction D1 and the included angle β 2 between the second pressure expanding plate 213 and the direction D1, that is, θ ═ β 2 — β 1. The height L1 of the air outlet 211 of the scroll casing 21 along the direction D2 specifically refers to the distance between two opposite side edges of the air outlet 211 of the scroll casing 21 along the direction D2.

Through the mode, the heat exchange performance of the air pipe type air conditioning device and the size of the whole air pipe type air conditioning device can be effectively balanced. Under the same air quantity, the airflow flowing through the heat exchanger 30 is more uniform, and the heat exchange effect is better and the noise is lower. Under the same noise, the air pipe type air conditioning device can have larger air quantity, and air conditioning in larger space is met. Meanwhile, the air duct type air conditioning device has a smaller volume and meets the wider requirement of home air conditioning integration.

Optionally, in a specific embodiment, the included angle θ between the first pressure-expanding plate 212 and the second pressure-expanding plate 213 is set to 10 to 20 degrees, so as to optimize the coverage area of the directly-blown main flow area a on the heat exchange fins 31.

Optionally, in a specific embodiment, the ratio between L1 and L2 is set to 0.4 to 0.6, and ξ is set to 1.4 to 1.5, so as to improve the air outlet smoothness at the upper and lower ends of the air duct type air conditioning device, and improve the heat exchange effect at the tail end of the heat exchange fin 31.

Alternatively, in a specific embodiment, the height L2 of the heat exchange fin 31 along the direction D2 is 190mm, the height L1 of the air outlet 211 of the scroll casing 21 along the direction D2 is set to 80-100mm, and the distance L3 between the end of the heat exchange fin 31 close to the air outlet 211 and the air outlet 211 along the direction D1 is further calculated according to the above formula, thereby achieving the balance between the heat exchange performance and the size of the whole machine.

3. Condensate water interference

Further in connection with fig. 2, the fin width of the heat exchange fin 31 is gradually reduced in a direction from the middle region to the end region of the heat exchange fin 31. The heat exchange fin 31 has a straight line l3 where the peak width is located. In the present embodiment, the straight line l3 along which the peak width is located is disposed along the direction D1. In other embodiments, the line l3 along which the peak width is located may be inclined with respect to the direction D1 and the angle between the two is less than or equal to 10 degrees. The heat exchanger fins 31 further have an overall height H1 and an overall width H2. When the straight line L3 along which the peak width of the heat exchanging fin 31 is located is arranged along the direction D1, the height L2 of the heat exchanging fin 31 along the direction D2 is the overall height H1 of the heat exchanging fin 31, and the width L4 of the heat exchanging fin 31 along the direction D1 is the overall width H2 of the heat exchanging fin 31. When the straight line L3 on which the peak width of the heat exchanging fin 31 is located forms an included angle with the direction D1, the height L2 of the heat exchanging fin 31 along the direction D2 and the width along the direction D1 are projections of the overall height H1 and the overall width H2 of the heat exchanging fin 31 in the directions D2 and D1, and can be obtained by calculation according to a trigonometric function.

In the process of refrigerating the air duct type air conditioner, when the air flow passes through the surfaces of the heat exchange fins 31, water vapor in the air flow is condensed when meeting cold, and condensed water is generated. The condensed water flows down along the heat exchange fins 31 under the action of gravity, and the condensed water is accumulated more on the lower half portions of the heat exchange fins 31, so that the wind resistance of the lower half portions of the heat exchange fins 31 is larger than that of the upper half portions, and the heat exchange of the heat exchange fins 31 is uneven.

Therefore, in order to improve the uniformity of heat exchange between the lower half and the upper half of the heat exchange fin 31, on the reference cross section formed by the plane of the main surface of the heat exchange fin 31, the intersection point E3 formed by the bisector l4 of the included angle θ between the first pressure spreading plate 212 and the second pressure spreading plate 213 and the straight line l3 of the peak width of the heat exchange fin 31 is set to be located on the side of the heat exchange fin 31 close to the fan 22, and the intersection point E4 formed by the bisector l3 and the second side contour line 312 of the heat exchange fin 31 is located below the straight line l3 of the peak width.

Because the two sides of the angular bisector l3 of the included angle between the first pressure expansion plate 212 and the second pressure expansion plate 213 correspond to the maximum flow velocity region of the air flow, the lower half portion of the heat exchange fin 31 can be purged by the air flow with a higher speed in the above manner to overcome the wind resistance of the condensed water, and further the heat exchange effect of the whole heat exchange fin 31 is more uniform. In addition, because there is certain weight along direction D2 in the air current direction of the lower half of sweeping heat exchange fin 31, can provide extra acceleration force for the comdenstion water on the basis of gravity, and then accelerate the flow of comdenstion water.

Optionally, in a specific embodiment, the ratio of the vertical distance d4 from the intersection point E4 to the straight line l3 where the peak width is located to the overall height H1 of the heat exchange fin 31 is set to be 0.02 to 0.06, so as to avoid the reverse non-uniformity of the heat exchange performance of the lower half and the upper half of the heat exchange fin 31 caused by the excessive flow speed of the air flow sweeping the lower half of the heat exchange fin 31.

Optionally, in a specific embodiment, an included angle β 3 between the bisector l4 and the straight line l3 of the peak width is set to 10 to 16 degrees, so as to achieve the balance between the heat exchange performance and the acceleration of the condensed water.

OptionallyIn one embodiment, based on the above setting range of the included angle β 3, the linear distance d5 between the intersection point E5 and the intersection point E3 formed by the straight line l3 where the peak width is located and the second side contour 312 and the peak width W are further determined_maxThe ratio of (A) is set to 0.45-0.61.

Further with reference to fig. 2, optionally, in a specific embodiment, the second side contour line 312 includes arc segments S1'-S2', S1'-S5', arc segments S2'-S3', S5'-S6' and straight segments S3'-S4', S6'-S7' connected in sequence in a direction from the middle region to the end region on both sides of the straight line l3 where the arc segments S2'-S3', S5'-S6' have a radius of curvature larger than the arc segments S1'-S2', S1'-S5', and the intersection point E4 is located on the arc segments S1'-S5' below the straight line l3 where the peak width is located. Through any one or combination of the two modes, the maximum flow velocity areas on the two sides of the angular bisector l4 can be fully acted on the middle area of the heat exchange fin 31, and the heat exchange effect is improved.

It is noted that the peak width W of the heat exchange fins 31 mentioned above_maxThe line l3 along which the peak width is located, the overall height H1, the overall width H2, and other shape characterizing parameters of the heat exchanging fin 31 mentioned later are described in detail below with reference to fig. 2.

4. Air outlet collector angle of heat exchanger

As shown in fig. 1, the air duct type air conditioning device of the present embodiment further includes a first manifold plate 41 and a second manifold plate 51, and the first manifold plate 41 and the second manifold plate 51 are respectively disposed above and below the heat exchanging fins 31 in the direction D2.

In the present embodiment, the second bus plate 51 is formed by a portion of the water collector 50 near the air outlet 101 of the housing 10. In other embodiments, the second manifold plate 51 may be provided as a separate element from the drip tray 50. The first manifold plate 41 and the second manifold plate 51 are configured to converge the air flow passing through the heat exchange fins 31, and guide the air flow to the air outlet 101 of the housing 10. In the air duct type air conditioner of the present embodiment, the space between the first and

second bus plates

41 and 51 and the first side contour line 311 determines the air-out smoothness and the flow-converging effect of the heat exchanger 30.

Therefore, in order to achieve a balance between the air-out smoothness and the flow-joining effect, on a reference cross section formed by a plane of the main surface of the heat exchanging fin 31, the perpendicular bisector of the peak width Wmax of the heat exchanging fin 31 forms an intersection point E6 and an intersection point E7 with the first side profile line 311, and further forms an intersection point E8 and an intersection point E9 with the first bus plate 41 and the second bus plate 51, respectively.

The included angle beta 4 between the tangent of the intersection point E6 and the tangent of the adjacent intersection point E8 is 27-37 degrees, and the included angle beta 5 between the tangent of the intersection point E7 and the tangent of the adjacent intersection point E9 is 36-46 degrees.

In this way, the size of the convergence angle of the air outlet side of the heat exchanger 30 defined by the first collecting plate 41 and the second collecting plate 51 is moderate, so that air outlet of the heat exchanger 30 is smooth, the heat exchange effect of the tail end of the heat exchange fin 31 is further improved, and a better convergence effect is achieved. In addition, further through the difference setting of contained angle beta 4 and contained angle beta 5 to the contained angle beta 3 of cooperation above-mentioned description, can further ensure the balance of the air-out smoothness degree of heat transfer fin 31 upper half and the latter half.

Alternatively, in one embodiment, the intersection point E6 and the intersection point E7 have a linear distance d6, which is the sum of the perpendicular distances from the intersection point E6 and the intersection point E7 to the line l3 along which the peak width is located, and the ratio of the linear distance d6 to the overall height H1 of the heat exchange fin 31 is 0.46-0.56.

Alternatively, in one embodiment, the second side contour line 312 is curved toward the first side contour line 311, the first side contour line 311 is curved away from the second side contour line 312, the ratio between the linear distance d7 of the intersection point E8 and the upper end point of the first side contour line 311 along the linear l3 of the peak width and the peak width Wmax is 0.92-1.13, and the ratio between the linear distance d8 of the intersection point E9 and the lower end point of the first side contour line 311 along the linear l3 of the peak width and the peak width Wmax is 0.93-1.14. Further, the straight distance d7 and the straight distance d8 may be set approximately equal, for example, the ratio of the straight distance d7 and the straight distance d8 may be set to 0.9-1.1.

Further with reference to fig. 2, optionally, in a specific embodiment, the first side contour line 311 includes, on both sides of the straight line l3 where the peak width is located, arc segments S1-S2, S1-S5, arc segments S2-S3, S5-S6, and straight line segments S3-S4, S6-S7, which are sequentially connected in the direction from the middle region to the end regions, respectively, wherein the radius of curvature of the arc segments S2-S3, S5-S6 is greater than the radius of curvature of the arc segments S1-S2, S1-S5. The intersection point E6 and the intersection point E7 are located on arc segments S2-S3, S5-S6.

Through one or the combination of the three modes, a sufficient space can be ensured between the first bus plate 41 and the first side contour line 311, and the air outlet smoothness of the heat exchanger 30 can be further ensured.

Optionally, in a specific embodiment, a ratio of a sum of the included angle β 4 and the included angle β 5 to the opening angle α 1 of the first side contour line 311 is 0.58 to 0.79, so that the heat exchange fin 31 has a sufficient depth along the direction D1 while ensuring the air outlet smoothness of the heat exchanger 30, and the heat exchange efficiency of the heat exchange fin 31 is improved.

Further, water tray 50 includes two

water receiving tanks

53 and 54 separated by a platform portion 52. The heat exchange fins 31 are supported on the bearing platform part 52, the projection of the lower end point of the first side contour line 311 along the direction D2 falls into the water receiving tank 53, the projection of the lower end point of the second side contour line 312 along the direction D2 falls into the water receiving tank 54, and the

water receiving tanks

53 and 54 are used for respectively receiving the condensed water falling along the first side contour line 311 and the second side contour line 312. Since the first side contour line 311 is located on the leeward side than the second side contour line 312, more condensate water is collected along the first side contour line 311. Therefore, in one embodiment, along direction D1, the width of catch basin 53 is greater than the width of catch basin 54. In this way, excessive accumulation of condensed water in the water receiving tank 53 can be avoided, and the condensed water in the water receiving tank 53 is prevented from being blown out by the airflow.

It should be further noted that the above-described four optimized solutions for the overall structure of the air duct type air conditioner can be used alone or in combination, and the heat exchange fins 31 used are not limited to the crescent heat exchange fins shown in fig. 1 and 2, and can also be V-shaped or straight-bar heat exchange fins.

Referring to fig. 2, a detailed description will be given of a specific shape of the crescent-shaped heat exchange fin shown in fig. 1 and 2.

In the present embodiment, the heat exchange fin 31 shown in fig. 1 and 2 includes a first side contour 311, a second side contour 312, and two

end contours

314 and 315.

In the present application, the contour line refers to a combination of two or more contour lines having a predetermined line type for defining the outline of the heat exchange fin 31. The first side contour line 311 and the second side contour line 312 refer to two contour lines that are spaced apart in the incoming wind direction D3 when the heat exchanging fin 31 is in operation. One of the first side contour line 311 and the second side contour line 312 serves as a windward side contour line, and the other serves as a leeward side contour line. Further, the windward side contour line refers to the side contour line on the side facing the wind direction D3 of the first side contour line 311 and the second side contour line 312, and the leeward side contour line refers to the side contour line on the side facing away from the wind direction D3 of the first side contour line 311 and the second side contour line 312. In the present embodiment, the second side contour line 312 serves as a windward side contour line, and the first side contour line 311 serves as a leeward side contour line. In other embodiments, the first side contour 311 may be used as the windward side contour and the second side contour 312 may be used as the leeward side contour.

End contour lines

314 and 315 refer to contour lines for connecting adjacent ends of the first side contour line 311 and the second side contour line 312. It should be noted that, when the edge of the heat exchange fin 31 is notched due to the process or installation, the contour line of the notch should be understood as being formed by the transition of the contour lines on both sides of the notch. Furthermore, when there is a corner cut at the junction of

end contours

314 and 315 with first side contour 311 and/or second side contour 312, the contour lines at the corner cut should be considered part of

end contours

314 and 315.

In this embodiment, the second side contour line 312 is curved toward the first side contour line 311, the first side contour line 311 is curved away from the second side contour line 312, and the fin width of the heat exchange fin 31 gradually decreases in the direction from the central region of the heat exchange fin 31 to the end regions on both sides of the central region, so that the heat exchange fin 31 is integrally disposed in a moon shape. Generally, the wind field formed by the airflow includes a high flow velocity region in the middle and low flow velocity regions on both sides of the high flow velocity region. The fin width of the heat exchange fin 31 is set to be gradually reduced in the direction from the middle area of the heat exchange fin 31 to the end areas on the two sides of the middle area, so that the high flow velocity area corresponds to the middle area with large fin width, the low flow velocity area corresponds to the end area with small fin width, the heat exchange of the middle area and the end area of the heat exchange fin 31 is more uniform, and the overall heat exchange performance is improved.

It should be noted that the descriptions of "gradually decreasing" and "gradually increasing" mentioned in the present application refer to the overall variation trend, which may be continuous variation or stepwise variation. For example, the above-mentioned "fin width gradually decreases" may include a partial fin width constant region, i.e., stepwise decrease.

In the present application, a reference point is selected on the first side contour 311, the normal (perpendicular to the tangent) of the reference point intersects the second side contour 312 to form an intersection, and the linear distance between the reference point and the intersection is the fin width at the reference point, such as W shown in FIG. 2_maxAnd the like. It should be noted that, when the line type of the contour line where the reference point is located is a straight line, the normal line of the reference point is the perpendicular line of the straight line.

Further, the length of the line connecting the reference point and the intersection point where the width of the fin is maximum is the peak width W_maxThe straight line where the line connecting the reference point and the intersection point is located is the straight line l3 where the peak width is located. It is noted that when the first side contour 311 and the second side contour 312 have a curved shape, the line l3 where the peak width is located is generally a straight line connecting the vertices of the first side contour 311 and the second side contour 312. When the fin is provided with a plurality of connecting lines with the largest width, the straight line where the connecting line in the middle is located is selected as the straight line l3 where the peak width is located.

5. Auxiliary matching mechanism

The present application will further optimize the secondary engagement mechanism of the heat exchanger 30 in conjunction with fig. 5-12.

In this embodiment, the two ends of the heat exchanger 30 are respectively provided with a metal plate side plate 60 and a plastic side plate 70, and are specifically arranged outside the heat exchange fins 31 at the outermost ends of the heat exchanger 30 along the direction perpendicular to the main surfaces of the heat exchange fins 31, so as to fix the heat exchanger 30 on the casing 10 of the air duct type air conditioning device through the metal plate side plate 60 and the plastic side plate 70.

Alternatively, in one embodiment, the heat exchange tube 32 includes linear tube segments 326 passing through the plurality of heat exchange fins 31 and U-shaped tube segments 327 connected to adjacent ends of the different linear tube segments 326. Wherein the linear tube section 326 is used for supporting and fixing a plurality of heat exchange fins 31, and the U-shaped tube section 327 is connected to the adjacent ends of the linear tube section 326 to facilitate the backflow of the heat exchange medium.

Further, the heat exchanger 30 has a welded end and a non-welded end, wherein the U-shaped pipe 327 and the linear pipe 326 are integrally formed at the non-welded end, the U-shaped pipe 327 and the linear pipe 326 are connected at the welded end in a welding manner, the plastic side plate 70 is disposed at the non-welded end, and the metal plate side plate 60 is disposed at the welded end.

5.1. Side plate support

Referring to fig. 5-8, the sheet metal edge plate 60 is secured to the housing 10 by an edge plate bracket 80. Sheet metal sideboard 60 includes sheet metal sideboard main part 62, and sideboard support 80 includes backup pad 82, and backup pad 82 sets up with sheet metal sideboard 60 coincide to lock each other through locking mechanical system 90.

Optionally, in a specific embodiment, the sheet metal edge plate body 62 is substantially the same as the heat exchange fins 31 in shape, and the sheet metal edge plate body 62 is stacked with the heat exchange fins 31 in a direction perpendicular to the main surfaces of the heat exchange fins 31 and located at the outermost side of the heat exchange fins 31. The sheet metal side plate main body 62 is provided with avoidance holes 64 coaxial with the tube holes 316 at positions corresponding to the tube holes 316 of the heat exchange fins 31, and the heat exchange tubes 32 penetrate through the avoidance holes 64 and the tube holes 316 to fix the plurality of heat exchange fins 31 and the sheet metal side plate main body 62. The support plate 82 is overlapped with the sheet metal side plate main body 62 in the direction perpendicular to the main surface of the heat exchange fin 31, and the support plate 82 and the sheet metal side plate main body 62 are assembled and fixed through the locking mechanism 90.

Specifically, in one embodiment, the first fixing hole 84 may be provided in the support plate 82, the second fixing hole 66 may be provided in the sheet metal edge plate main body 62, the first fixing hole 84 and the second fixing hole 66 may be overlapped, and the locking mechanism 90 may be a fastener inserted into the first fixing hole 84 and the second fixing hole 66. The locking mechanism 90 may be, for example, a bolt and a nut that are engaged with each other to fix the support plate 82 and the sheet metal side plate main body 62 by a screw fixing structure. Alternatively, the locking mechanism 90 may be a rivet to fix the support plate 82 and the sheet metal blank side plate main body 62 by caulking.

In other embodiments, the support plate 82 and the sheet metal side plate main body 62 may be fixedly connected by clamping or other methods, and the embodiment of the present application is not particularly limited.

In order to ensure the connection strength and the connection stability of the support plate 82 and the sheet metal side plate main body 62, the number of the locking mechanisms 90 is generally three or more, and the locking mechanisms 90 in a large number may make the installation and the removal inconvenient and may affect the installation efficiency of the heat exchanger 30. Moreover, when the heat exchange tube 32 inserted into the heat exchange fin 31 is deformed, the locking mechanism 90 interferes with the operation space of the repair tool, and it is inconvenient to repair the heat exchange tube 32.

Therefore, in the present embodiment, the side plate bracket 80 further includes a sunken platform 86 disposed on the support plate 82, and the sheet metal side plate 60 further includes a lug 68 disposed on the sheet metal side plate body 62, wherein when the support plate 82 and the sheet metal side plate body 62 are stacked, the lug 68 is inserted into the sunken platform 86.

Specifically, when fixing sideboard bracket 80 and panel beating sideboard 60, can insert heavy platform 86 with lug 68 earlier, fix a position backup pad 82 and panel beating sideboard main part 62 for first fixed orifices 84 on the backup pad 82 and the second fixed orifices 66 on the panel beating sideboard main part 62 overlap, then adopt locking mechanical system 90 to insert and place in first fixed orifices 84 and second fixed orifices 66, with backup pad 82 and panel beating sideboard main part 62 fixed connection. In this way, the number of the locking mechanisms 90 can be reduced, so that the assembly efficiency of the heat exchanger 30 can be improved, and the interference of repair tools can be avoided, thereby facilitating the maintenance of the heat exchange pipe 32.

In other embodiments, the platform 86 and the lug 68 may be replaced by other types of first and second locking positions, which only need to ensure that when the supporting plate 82 is disposed in superposition with the sheet metal edge plate main body 62, one of the first and second locking positions is locked into the other, and then cooperates with the locking mechanism 90 to achieve relative fixing of the sheet metal edge plate 60 and the edge plate bracket 80.

Optionally, in a specific embodiment, the sinking platform 86 is recessed toward a side of the supporting plate 82 close to the sheet metal sideboard main body 62, the sinking platform 86 has a notch 862, the notch 862 is located on a side edge of the supporting plate 82 close to the sheet metal sideboard main body 62, the lug 68 is located on a side edge of the sheet metal sideboard main body 62 close to the supporting plate 82, and when the supporting plate 82 and the sheet metal sideboard main body 62 are overlapped, the lug 68 can be inserted into the sinking platform 86 along the notch 862. Locking mechanism 90 is fixed in the one side of backup pad 82 towards heat transfer fin 31 with panel beating sideboard main part 62, and lug 68 butt on the panel beating sideboard main part 62 deviates from one side of heat transfer fin 31 in backup pad 82, and then can form limiting displacement respectively in the relative both sides of backup pad 82 to fix backup pad 82.

It can be understood that, in another specific embodiment, the lug 68 and the sinking platform 86 may be arranged in reverse, that is, the lug 68 is arranged on one side edge of the supporting plate 82 facing the sheet metal side plate body 62, the sinking platform 86 is arranged on the sheet metal side plate body 62 and is recessed towards one side of the sheet metal side plate body 62 close to the supporting plate 82, wherein the fixing manner of the lug 68 and the sinking platform 86 may refer to the description of the above embodiment, and will not be described again here.

Alternatively, in one embodiment, the number of locking mechanisms 90 may be two, with two locking mechanisms 90 connecting opposite ends of the sheet metal blank body 62 and the support plate 82. The number of the counter sink 86 and the lug 68 which are matched with each other can be one, and the counter sink 86 and the lug 68 are respectively arranged in the middle areas of the support plate 82 and the sheet metal side plate body 62, so that the support plate 82 and the sheet metal side plate body 62 are stressed uniformly.

Or, in another specific embodiment, the number of the locking mechanisms 90 may be one, the number of the counter sink 86 and the number of the lug 68 which are matched with each other may be two, and the two counter sink sinks 86 and the two lugs 68 which are matched with each other are respectively arranged at two opposite ends of the sheet metal side plate main body 62 and the support plate 82, which may also simplify the installation complexity of the heat exchanger 30 and improve the production efficiency.

Alternatively, in other specific embodiments, the number and the arrangement positions of the locking mechanism 90 and the counter sink 86 and the lug 68 which are matched with each other may be reasonably set according to the shapes and the sizes of the support plate 82 and the sheet metal side plate main body 62 to fix the support plate 82 and the sheet metal side plate main body 62, which is not particularly limited in the present application.

Alternatively, in a specific embodiment, when the heat exchanging fin 31 has a moon-shaped profile, the edge of the supporting plate 82 close to the sheet metal side plate main body 62 may be configured to match the profile of the side contour line of the heat exchanging fin 31, so as to avoid the heat exchanging tube 32 passing through the heat exchanging fin 31. At this time, the lug 68 may be provided corresponding to the central region of the heat exchange fin 31, and the shape of the lug 68 may be provided in a triangular shape so as to be adapted to the shape of the edge of the support plate 82.

Or, in a specific embodiment, when the heat exchanging fin 31 is disposed in a V shape or a straight strip shape, the lug 68 in other shapes may be further disposed specifically according to the shape of the edge of the supporting plate 82, which is not specifically limited in the embodiment of the present invention.

Optionally, in a specific embodiment, both the side plate bracket 80 and the sheet metal side plate 60 may be made of metal or alloy by stamping, so as to improve the structural strength of the side plate bracket 80 and the sheet metal side plate 60 and improve the production efficiency of the heat exchanger 30. The sheet metal edge plates 60 can be replaced by other types of edge plates made of other heat-resistant materials.

Further, in a specific embodiment, the lug 68 and the sheet metal side plate body 62 are coplanar and equal in thickness, and the recessed depth of the counter sink 86 relative to the support plate 82 is equal to the thickness of the sheet metal side plate body 62 and the lug 68, so as to simplify the manufacturing process of the sheet metal side plate body 62, improve the manufacturing efficiency of the sheet metal side plate body 62, and make the surface of the lug 68 away from the support plate 82 flush with the surface of the support plate 82, so as to facilitate the installation of the heat exchanger 30.

Further, in order to improve the stability of the side plate bracket 80 and the sheet metal side plate 60, the overlapping area of the side plate bracket 80 and the sheet metal side plate 60 can be increased to support the support plate 82 in an auxiliary manner.

For example, the sheet metal edge plate body 62 and the edge region of the support plate 82 between the locking mechanism 90 and the platform 86 and the lug 68 may be at least partially overlapped to support the edge of the support plate 82, so as to improve the stability of the support plate 82 on the one hand and avoid the deformation of the edge of the support plate 82 under the action of external force on the other hand.

Alternatively, in one embodiment, one side edge of the support plate 82 adjacent the sheet metal blank body 62 is disposed in a wave-like curve such that the heat exchange tubes 32 adjacent the support plate 82 are located in the valley regions of the wave-like curve and the peak regions of the wave-like curve are embedded between adjacent heat exchange tubes 32. Therefore, on one hand, the overlapping area of the sheet metal side plate main body 62 and the supporting plate 82 can be increased as much as possible, on the other hand, the supporting plate 82 can be used for carrying out auxiliary supporting on the heat exchange tube 32, and the phenomenon that the assembly is influenced due to deformation or deflection of the heat exchange tube 32 is avoided.

Further, in a specific embodiment, the sideboard bracket 80 further comprises a fixing flange 88, the fixing flange 88 is disposed at the other side edge of the supporting plate 82 departing from the sheet metal sideboard main body 62, and is turned over relative to the supporting plate 82, and the fixing flange 88 is used for fixing the sideboard bracket 80 to the housing 10 of the air duct type air conditioner.

5.2. Plastic side plate

At present, when fixing the heat exchanger 30 in the air duct type air conditioner, a slot 72 is usually formed on the plastic side plate 70 corresponding to each U-shaped tube 327, and the heat exchange tube 32 is supported by inserting the U-shaped tube 327 into the slot 72, so as to prevent the heat exchange tube 32 from deforming. When the connection mode (i.e., the arrangement mode of the U-shaped pipe section 327) between the U-shaped pipe section 327 and the linear pipe section 326 is changed, different slots 72 are required to be adapted to the U-shaped pipe section 327, so that different plastic side plates 70 need to be manufactured according to different arrangement modes of the U-shaped pipe section 327, and the universality of the plastic side plates 70 is not high.

Therefore, as shown in fig. 9-11, in the present embodiment, the insertion slot 72 is configured to be capable of adapting to at least two different arrangement manners of the U-shaped pipe section 327, so that when the arrangement manner of the U-shaped pipe section 327 changes, the heat exchanging pipe 32 can be supported by using the same plastic side plate 70, so as to improve the versatility of the plastic side plate 70, and further facilitate mass production of the plastic side plate 70 to reduce the production cost.

Further, in order to avoid the heat exchange tube 32 from being separated from the plastic side plate 70, in one embodiment, a fastening portion 74 may be disposed in the slot 72 to fasten the U-shaped tube 327 after the U-shaped tube 327 is inserted into the slot 72, so as to fasten and fix the U-shaped tube 327.

The number of the buckling parts 74 in the slots 72 capable of being matched with the U-shaped pipe sections 327 in different arrangement modes can be at least two, each buckling part 74 corresponds to different arrangement modes, and then the U-shaped pipe sections 327 are arranged in a corresponding arrangement mode and are inserted into the slots 72 to be clamped and fixed to the U-shaped pipe sections 327. Thus, when the arrangement of the heat exchange tube 32 is changed, at least one of the locking portions 74 disposed in the slot 72 can be locked with the heat exchange tube 32 to prevent the plastic side plate 70 from separating from the heat exchange tube 32.

Optionally, in one embodiment, the slot 72 is configured to simultaneously receive at least two U-shaped tube sections 327, and the at least two U-shaped tube sections 327 have at least two different arrangements, wherein the at least two U-shaped tube sections 327 have different spacing directions in the different arrangements.

For example, in one embodiment, at least two U-shaped tube segments 327 may be received in at least some of the slots 72 at the same time, and the at least two U-shaped tube segments 327 have two different arrangements, namely a first arrangement and a second arrangement.

Specifically, in the embodiment shown in fig. 10, the number of the heat exchange tubes 32 in the same slot 72 is two, and the two U-shaped tube sections 327 are arranged at intervals along the direction D11. In the embodiment shown in fig. 11, the number of the heat exchange tubes 32 in the same slot 72 is two, and the two U-shaped tube sections 327 are arranged at intervals along the direction D12, wherein the direction D11 and the direction D12 are perpendicular to each other.

Alternatively, in a specific embodiment, the direction D11 may be set as the wind inlet direction of the heat exchanger 30, and the direction D12 may be set perpendicular to the wind inlet direction of the heat exchanger 30.

Alternatively, in another specific embodiment, the direction D11 and the direction D12 may be arranged to intersect with each other. Alternatively, in another embodiment, at least two U-shaped tube sections 327 may be provided in three or more arrangements, and more arrangements may be realized by changing the inclination angle between the spacing direction of the U-shaped tube sections 327 and the direction D11 in each arrangement.

Alternatively, in one embodiment, the slot 72 is disposed in a parallelogram in a cross-section perpendicular to the insertion direction of the U-shaped tube section 327 relative to the slot 72, the direction D11 is the direction of spacing between two opposite sides of the parallelogram, and the direction D12 is the direction of spacing between the other two opposite sides of the parallelogram. In this way, when the U-shaped tube section 327 is inserted into the slot 72 in different arrangement modes, the side walls of the slot 72 can be tightly attached to the heat exchange tube 32, so as to improve the supporting effect of the heat exchange tube 32 and prevent the heat exchange tube 32 from deforming.

Further, in one embodiment, the plastic side panel 70 may include a plastic side panel body 76 and a slot side panel 78 integrally formed with the plastic side panel body 76, the slot side panel 78 enclosing the slot 72. In this way, on one hand, the contact area between the slot 72 and the heat exchange tube 32 can be increased by extending the height of the slot side plate 78, so as to enhance the abutting action force on the heat exchange tube 32, and on the other hand, the thickness of the plastic side plate main body 76 can be reduced, so that the material consumption is reduced, and the cost is reduced.

Optionally, in an embodiment, an elastic cantilever 71 is further formed on the slot side plate 78, the fastening portion 74 is disposed on the elastic cantilever 71, and in the process that the heat exchange tube 32 is inserted into the slot 72, the elastic cantilever 71 is driven to deform by the abutting acting force of the heat exchange tube 32 on the fastening portion 74, so that the heat exchange tube 32 enters the slot 72, and after the heat exchange tube 32 enters the slot 72, the elastic restoring force of the elastic cantilever 71 drives the fastening portion 74 to restore to be fastened with the heat exchange tube 32.

In one embodiment, the slot side plate 78 is provided with a first notch 73 along the insertion direction of the U-shaped pipe section 327 relative to the slot 72, and a second notch 75 is further provided on the slot side plate 78 or the plastic side plate body 76 along the circumferential direction of the slot side plate 78, and the first notch 73 is communicated with the second notch 75, so that the slot side plate 78 forms the elastic cantilever 71.

Alternatively, the first notch 73 may be disposed at a position adjacent to the latching portion 74 along the circumferential direction of the slot side plate 78 to extend the moment arm at the position of the latching portion 74 as much as possible, so that the heat exchange tube 32 is deformed against the elastic cantilever 71.

The above only is the embodiment of the present invention, not limiting the patent scope of the present invention, all the equivalent structures or equivalent processes that are used in the specification and the attached drawings or directly or indirectly applied to other related technical fields are included in the patent protection scope of the present invention.

Claims

1. An air duct type air conditioning apparatus, characterized in that the air duct type air conditioning apparatus includes a heat exchanger, the heat exchanger includes:

a plurality of heat exchange fins arranged at intervals from one another;

the heat exchange tube comprises linear tube sections penetrating the heat exchange fins and U-shaped tube sections connected to the adjacent tail ends of different linear tube sections;

the plastic side plate is provided with a slot, the slot is used for receiving the U-shaped pipe section, and the slot is set to be capable of adapting to at least two different arrangement modes of the U-shaped pipe section.

2. The air duct type air conditioning device according to claim 1, wherein the plastic side plate is further provided with at least two buckling parts corresponding to the slots, each buckling part corresponds to a different arrangement manner, and the U-shaped pipe sections are arranged in a corresponding arrangement manner and are clamped and fixed after being inserted into the slots.

3. The air duct type air conditioner according to claim 2, wherein the slot is configured to receive at least two of the U-shaped duct sections simultaneously, the at least two U-shaped duct sections having at least two different arrangements, wherein the at least two U-shaped duct sections are spaced differently in different directions of arrangement.

4. The air duct type air conditioner according to claim 2, wherein the at least two U-shaped pipe sections have at least a first arrangement in which the at least two U-shaped pipe sections are spaced apart in a first direction and a second arrangement in which the at least two U-shaped pipe sections are spaced apart in a second direction, the first direction and the second direction being perpendicular to or crossing each other.

5. The air duct type air conditioner according to claim 4, wherein the slot is provided in a parallelogram shape in a cross section perpendicular to an insertion direction of the U-shaped pipe section with respect to the slot, the first direction is a direction of spacing between two opposite sides of the parallelogram, and the second direction is a direction of spacing between the other two opposite sides of the parallelogram.

6. The air duct type air conditioning device according to claim 2, wherein the plastic side plate comprises a plastic side plate body and a slot side plate integrally formed with the plastic side plate body, the slot side plate is enclosed into the slot, the slot side plate further forms a flexible cantilever, and the locking portion is disposed on the flexible cantilever.

7. The air duct type air conditioner as claimed in claim 6, wherein the slot side plate is provided with a first cut along an insertion direction of the U-shaped pipe section with respect to the slot, and a second cut is further provided on the slot side plate or the plastic side plate body along a circumferential direction of the slot side plate, the first cut and the second cut communicating with each other, so that the slot side plate forms the elastic cantilever.

8. The air duct type air conditioning device according to claim 1, wherein the heat exchanger has a welded end and a non-welded end, the U-shaped duct section and the linear duct section are integrally formed at the non-welded end, the U-shaped duct section and the linear duct section are connected at the welded end by welding, the plastic side plate is disposed at the non-welded end, the heat exchanger further includes a sheet metal side plate disposed at the welded end, the air duct type air conditioning device further includes a side plate bracket, the side plate bracket includes a support plate and a first locking position disposed on the support plate, the sheet metal side plate includes a sheet metal side plate main body and a second locking position disposed on the sheet metal side plate main body, when the support plate and the sheet metal side plate main body are stacked, one of the first locking position and the second locking position is locked into the other, and then realize with the locking mechanism cooperation the panel beating sideboard with the relative fixation of sideboard support.

9. The air duct type air conditioning device according to claim 1, further comprising a housing and a fan assembly, wherein the housing is configured to form an accommodating cavity, the heat exchanger is disposed in the accommodating cavity, the heat exchanger includes a heat exchange fin, the fan assembly includes a volute and a fan disposed in the volute, the fan and the heat exchange fin are disposed at intervals along a third direction, the volute includes a first pressure expansion plate and a second pressure expansion plate, and the first pressure expansion plate and the second pressure expansion plate are disposed at intervals along a fourth direction perpendicular to the third direction and parallel to a main surface of the heat exchange fin, so as to guide an air flow generated by the fan to flow into the accommodating cavity through an air outlet of the volute;

the first pressure expansion plate inclines towards the direction towards the second pressure expansion plate in the direction from the fan to the heat exchange fins, the second pressure expansion plate inclines towards the direction away from the first pressure expansion plate, on a reference section formed by the planes of the main surfaces of the heat exchange fins, the included angle between the first pressure expansion plate and the third direction is 6-9 degrees, and the included angle between the second pressure expansion plate and the third direction is 20-24 degrees.

10. The air duct type air conditioner according to claim 9, wherein the air conditioner satisfies the following formula:

L2＝ξ×(L1+L3×tgθ)；

the spiral case comprises a first pressure expansion plate, a second pressure expansion plate, a heat exchange fin, a third pressure expansion plate, a fourth pressure expansion plate, a third pressure expansion plate and a fourth pressure expansion plate, wherein theta is an included angle between the first pressure expansion plate and the second pressure expansion plate, tg is a tangent trigonometric function, L1 is the height of the air outlet of the spiral case in the fourth direction, L2 is the height of the heat exchange fin in the fourth direction, L3 is the distance between the end part of the heat exchange fin.

11. The air duct type air conditioning device according to claim 9, wherein the heat exchange fins include a first side contour line and a second side contour line that are arranged at an interval from each other, the first side contour line is a leeward side contour line, the second side contour line is a windward side contour line, the fin width of the heat exchange fins is gradually reduced in a direction from a middle area to an end area of the heat exchange fins, a first intersection point formed by a bisector of an included angle between the first diffuser plate and the second diffuser plate and a straight line where a peak width of the heat exchange fins is located on one side of the heat exchange fins close to the fan, and a second intersection point formed by the bisector and the second contour line is located below the straight line where the peak width is located.