CN112240723A

CN112240723A - Heat exchange fin and air duct type air conditioner

Info

Publication number: CN112240723A
Application number: CN202010486868.2A
Authority: CN
Inventors: 罗彬�; 周柏松; 李运志
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: 2021-01-19
Anticipated expiration: 2040-06-01
Also published as: CN112240723B

Abstract

The invention discloses a heat exchange fin and an air duct type air conditioning device, wherein the heat exchange fin comprises a first side contour line and a second side contour line which are spaced from each other, the second side contour line is arranged in a bending way towards the first side contour line, the first side contour line is arranged in a bending way away from the second side contour line, and at least part of area of at least one of the first side contour line and the second side contour line is a continuous section in a single-arch cycloid. By the mode, the condensed water on the heat exchange fins can slide downwards at the highest speed, the problem that the condensed water on the existing heat exchange fins is not smoothly or slowly discharged is solved, and the heat exchange effect of the heat exchanger is improved. And because the cycloid is the curve profile, can increase the area of contact of heat transfer fin and air current in limited space, and then promote the heat transfer effect.

Description

Heat exchange fin and air duct type air conditioner

Technical Field

The invention relates to the technical field of air conditioners, in particular to a heat exchange fin and an air pipe type air conditioner device.

Background

The air pipe type air conditioner (called air pipe machine for short) is one kind of indoor unit of air conditioner, because its installation mode is concealed, it is easy to implement the aesthetic property of home decoration, and occupies a place in the domestic air conditioner market.

At present, in a duct type air conditioner, 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.

Therefore, the optimization of the heat exchange fins is an important factor for improving the overall performance of the air conditioner.

Disclosure of Invention

The invention provides a heat exchange fin and an air conditioner, which aim to improve the drainage performance and the heat exchange performance of the heat exchange fin by optimizing the outline line type of the heat exchange fin.

In order to solve the technical problems, the invention adopts a technical scheme that: a heat exchange fin is provided. The heat exchange fins comprise a first side contour line and a second side contour line which are spaced from each other, the second side contour line is arranged in a bending mode towards the first side contour line, the first side contour line is arranged in a bending mode towards the direction departing from the second side contour line, and at least part of area of at least one of the first side contour line and the second side contour line is a continuous section in a single-arch cycloid.

By the mode, the condensed water on the heat exchange fins can slide downwards at the highest speed, the problem that the condensed water on the existing heat exchange fins is not smoothly or slowly discharged is solved, and the heat exchange effect of the heat exchanger is improved. And because the cycloid is the curve profile, can increase the area of contact of heat transfer fin and air current in limited space, and then promote the heat transfer effect.

Drawings

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

FIG. 1 is a schematic cross-sectional view of an air duct type air conditioning apparatus 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;

FIG. 3 is a side view of a heat exchanger fin according to another embodiment of the present invention;

FIG. 4 is a side view of a heat exchanger fin according to yet another embodiment of the present invention.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within 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 is used for forming a receiving cavity 11, and the heat exchanger 30 is disposed in the receiving cavity 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.

By comparing the angle setting manner (β 1 is 7 degrees, β 2 is 22 degrees) of the present embodiment with the angle setting manner (β 1 is 5 degrees, β 2 is 19 degrees) of the comparative example, it is found that the difference of the change of the wind speed of the comparative example is significantly larger in the process of the transition from one end to the other end of the wind speed passing through the heat exchanging fin 31, and therefore, the wind speed uniformity of the present embodiment is significantly better than that of the comparative example.

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.

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.

It should be further noted that the two optimized solutions described above 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 sickle-shaped heat exchange fins 31 shown in fig. 1 and 2, and can also be V-shaped, straight-bar-shaped, crescent-shaped, C-shaped, U-shaped, and the like heat exchange fins 31.

Referring to fig. 2, a detailed description will be given of a specific shape of the heat exchange fin 31 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 first side contour line 311 serves as a windward side contour line, and the second side contour line 312 serves as a leeward side contour line. In other embodiments, the second side contour 312 may be used as the windward side contour and the first side contour 311 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. Further, when there is a chamfer 317 at the connection of

end contours

314 and 315 to first side contour 311 and/or second side contour 312, the contour lines at chamfer 317 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 first side contour line 311 and the second side contour line 312 are curved toward the direction close to the fan 20, so that the heat exchange fin 31 is arranged in a sickle shape.

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 comdenstion water is down flowed along heat transfer fin 31 under the effect of gravity, and the comdenstion water is more in heat transfer fin 31's the latter half accumulation, and the comdenstion water of adhesion on heat transfer fin 31 not only can lead to the windage of heat transfer fin 31's the latter half to be greater than the windage of the top, and then leads to heat transfer fin 31's heat transfer inhomogeneous, and the comdenstion water also can reduce heat transfer fin 31's heat transfer performance moreover.

At present, V-shaped heat exchange fins or straight-bar-shaped heat exchange fins are usually adopted in an air pipe type air conditioning device, when the V-shaped heat exchange fins are adopted, extra parts such as sealing baffles and sealing cotton need to be added in the middle of a heat exchanger, and therefore condensate water on the V-shaped heat exchange fins is prevented from being discharged smoothly, and the heat exchange effect is influenced. When adopting straight bar heat transfer fin, because tuber pipe air conditioner device's fuselage space restriction, in order to improve heat transfer effect, then the broad that straight bar heat transfer fin's fin width needs to set up, and the inclination of straight bar heat transfer fin needs the great that sets up, but so set up can lead to the comdenstion water on the heat transfer fin to get rid of more slowly.

Therefore, in the present embodiment, in order to make the water discharge of the heat exchanging fin 31 smoother, at least a partial region of at least one of the first side contour line 311 and the second side contour line 312 may be provided as a continuous section in a single-arch cycloid.

The cycloid is the locus of a fixed point P on the circumference when a rolling circle rolls on a fixed straight line l 4. When the rolling circle rolls for a circle, the track drawn by the fixed point P on the rolling circle is an arch cycloid. The cycloids have an arch height of 2a (i.e., the diameter of a circle) and an arch width of 2 pi a (i.e., the circumference of a circle).

According to the steepest curve principle, the time for a mass point between two points to slide down along a cycloid is shortest under the action of gravity. Therefore, by the mode, the condensed water on the heat exchange fins 31 can slide down at the fastest speed, the problem that the condensed water in the existing heat exchange fins 31 is not smoothly or slowly discharged is solved, and the heat exchange effect of the heat exchanger 30 is improved. And because the cycloid is the curve profile, can increase the area of contact of heat transfer fin 31 and air current in limited space, and then promote the heat transfer effect.

Alternatively, in a specific embodiment, the first side contour line 311 and the second side contour line 312 may be continuous segments on a single-arch cycloid, so as to maximize the ratio of the continuous segments on the first side contour line 311 and the second side contour line 312, and to improve the drainage performance of the heat exchange fin 31.

Alternatively, in another embodiment, as shown in FIG. 3, the first side contour 311 may further include straight line segments S1-S2, arc segments S2-S3, and straight line segments S3-S4, which are sequentially connected in a direction from the upper end portion to the lower end portion. It is noted that references to "connected in series" in this application include direct connections or connections that transition through other lines.

Through the mode, the straight line segments S1-S2 and the straight line segments S3-S4 are arranged on the two sides of the arc segments S2-S3 respectively, so that the included angle between the tail end of the heat exchange fin 31 and the direction D1 can be increased, and the air outlet smoothness in the end portion area of the heat exchange fin 31 is further improved.

Further, in the embodiment, the arc sections S2-S3 may be directly connected with the straight sections S1-S2 and S3-S4, and tangent to the straight sections S1-S2 and S3-S4 at the connecting point, so that the continuity of the first side contour line 311 can be ensured, and the punching and cutting are facilitated.

Further, in the present embodiment, the second side contour line 312 may further include straight line segments S1'-S2', arc segments S2'-S3', and straight line segments S3'-S4' that are sequentially connected in a direction from the upper end portion to the lower end portion.

In the present embodiment, as shown in fig. 2, the first side contour line 311 and the second side contour line 312 are further arranged to be in translational coincidence. Specifically, when the second side contour line 312 is translated toward the first side contour line 311 along the direction D4, the translation curve 312' formed by the second side contour line 312 coincides with at least a partial region of the first side contour line 311. In one embodiment, the length of the overlapped portion of the translation curve 312' and the first side contour 311 accounts for greater than or equal to 90% of the total length of the second side contour 312. The heat exchange fins 31 are generally formed by punching and cutting a sheet, so that the utilization rate of materials can be maximized, the materials are saved, and the production cost is reduced.

Further, end

contours

314, 315 comprise straight line segments parallel to direction D4. Direction D4 is generally oriented along the length of the sheet material during the stamping process, in such a manner that the partial areas of

end contours

314, 315 are flush with the edges of the sheet material to further reduce scrap.

Optionally, in a specific embodiment, a chamfer 317 is formed between each of the two opposite ends of the second side contour line 312 and the corresponding side

end contour lines

314 and 315, so that the heat exchanging fins 31 are not prone to being chipped at the position of the corner, thereby affecting the heat exchanging effect, and avoiding scratches during the assembling process of the heat exchanger 30.

Alternatively, in a specific embodiment, the included angle α 1 between the direction D4 and the connecting line of the end points of the two ends of the continuous section may be set to 85 to 95 degrees, so that the fin widths of the heat exchange fins 31 are substantially equal in the direction from the upper end portions to the lower end portions of the heat exchange fins 31, so as to facilitate the arrangement of the heat exchange tubes 32.

In the present application, a reference point is selected on the second side contour line 312, the normal (perpendicular to the tangent line) of the reference point intersects the first side contour line 311, and forms an intersection point, and the straight-line distance between the reference point and the intersection point is the fin width at the reference point, such as W1, W2, and the like shown in fig. 2. 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.

Optionally, in a specific embodiment, an included angle between the direction D4 and a connecting line of two end points of the continuous segment may be set to be 90 degrees, and the direction D4 may be set to be parallel to the extending direction of the end contour line, so that the fin widths of the heat exchange fins 31 are equal everywhere, which not only facilitates the uniform arrangement of the heat exchange tubes 32, but also ensures that no waste material is generated when the fins are continuously punched.

In conjunction with the above description, as shown in fig. 2, the single-arch cycloid includes the upper half portion and the lower half portion which are axisymmetrically arranged along the preset symmetry axis l 3. In the upper half part, the distance between the cycloid and the fixed line l4 is gradually increased, and the included angle of the tangent of the cycloid relative to the symmetrical axis l3 is gradually increased. In the lower half, the distance between the cycloid and the fixed line l4 gradually decreases, and the angle of the tangent of the cycloid with respect to the axis of symmetry l3 gradually decreases.

Alternatively, in a specific embodiment, the continuous segments on the first side contour line 311 and the second side contour line 312 may be arranged on the lower half portion of the cycloid so that the included angle between the tangent of the first side contour line 311 and the second side contour line 312 and the symmetry axis l3 becomes gradually smaller in the direction from the upper end portion to the lower end portion of the heat exchange fin 31 so as to accelerate the condensed water.

Herein, the symmetry axis l3 in the present application is a straight line passing through the fixed point P on the rolling circle and perpendicular to the fixed straight line l4 when the rolling circle rolls for a half circle. In the present embodiment, the symmetry axis l3 may be disposed along the direction D1. In other embodiments, the axis of symmetry l3 may be disposed obliquely with respect to the direction D1, and the angle between the axis of symmetry l3 and the direction D1 is less than or equal to 10 degrees.

Under the condition that the overall height H1 of the heat exchange fin 31 is the same, the included angle α 2 between the connecting line of the end points of the two continuous sections on the second side contour line 312 and the symmetry axis l3 determines the depth of the heat exchange fin 31 along the direction D1, i.e., the overall width H2 of the heat exchange fin 31. If the included angle α 2 between the connecting line of the two end points of the continuous segment on the second side contour line 312 and the symmetry axis l3 is too large, the depth of the heat exchange fin 31 is relatively small, and further the area of the main surface of the heat exchange fin 31 is relatively small, and the overall heat exchange performance of the heat exchange fin 31 is deteriorated. If the included angle α 2 between the connecting line of the end points of the two ends of the continuous segment on the second side contour line 312 and the symmetry axis l3 is too small, the smoothness of the airflow at the end of the heat exchange fin 31 is insufficient, resulting in poor heat exchange performance at the end of the heat exchange fin 31. When the symmetry axis L3 of the heat exchanging fin 31 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 symmetry axis L3 of the heat exchanging fin 31 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.

Therefore, in one embodiment, the angle α 2 between the symmetry axis l3 and the connecting line of the two end points of the continuous segment may be set to 60-65 degrees, and the ratio of the straight-line distance between the projections of the two end points of the continuous segment on the symmetry axis l3 to the diameter of the rolling circle for forming the single-arch cycloid is 0.54-0.66.

In this way, the depth of the heat exchange fin 31 in the direction D1 can be ensured, and the heat exchange performance of the tip of the heat exchange fin 31 can be ensured.

Further, in an embodiment, the ratio of the translation distance D3 from the second side contour line 312 to the first side contour line 311 to the rounded diameter D5 may be set to be 0.19-0.24, so that the heat exchange performance of the end of the heat exchange fin 31 can be ensured by ensuring a reasonable aspect ratio of the heat exchange fin 31.

Referring to fig. 4, fig. 4 further shows tube holes 316 on the basis of the heat exchange fin 31 shown in fig. 2 so that the heat exchange tubes 32 can be inserted into the heat exchange fin 31.

As shown in fig. 4, the tube holes 316 of the heat exchanging fin 31 are arranged in a row. Specifically, in the present embodiment, each row of pipe holes 316 is arranged at intervals along an arrangement curve formed by translating the first side contour 311 or the second side contour 312 along the direction D4, and a ratio of a shortest distance from a center of each pipe hole 316 in each row of pipe holes 316 to the corresponding arrangement curve to a radius of each pipe hole 316 is less than or equal to 1.5.

Further, the sum of the shortest distances from the centers of the pipe holes 316 in each row of pipe holes 316 to the corresponding arrangement curve is smaller than the sum of the shortest distances from the centers of the pipe holes 316 in each row of pipe holes 316 to other translation curves formed after the first side contour 311 or the second side contour 312 is translated.

Further, the tube holes 316 of different rows are arranged at intervals along an arrangement line formed in parallel with the line l3 on which the peak width of the heat exchange fin 31 is located.

In this way, the direction of each row of tube holes 316 is approximately the same as the direction of the first side contour line 311 or the second side contour line 312, so that the surface space of the heat exchange fins 31 is fully utilized, and the overall heat exchange performance of the heat exchanger 30 is improved. In other embodiments, the apertures 316 may be arranged in other ways.

Further, in this embodiment, the fin width is set to K × n × D, where n1 is the number of rows of tube holes 316 on the heat exchange fin, D is the tube hole row spacing, and K is a variation coefficient, and the value range is 0.8-1.2.

The tube hole row spacing D is defined as the distance between the tube hole 316 closest to the

end contour

314 or 315 in the row of tube holes 316 close to the first side contour 311, and the line drawn through the center E3 of the tube hole 316 and the extension line of the first side contour 311 and the second side contour 312 or both is the normal line of the intersection point E4 with respect to the intersection points E4 and E5. When the number of rows of the pipe holes 316 is 2 or more (2 rows shown in fig. 4), the straight line further intersects the arrangement curve of the pipe holes 316 in the adjacent row or the extension line of the arrangement curve at the intersection point E6. At this time, the tube hole row pitch D is a linear distance between the tube hole center E3 of the tube hole 316 and the intersection point E6, which is selected. When the number of rows of the tube holes 316 is 1, the tube hole row spacing D is a linear distance between the intersection points E4 and E5. In this way, it is ensured that each heat exchange tube 32 inserted into the tube hole 316 can exhibit an optimal heat exchange performance.

Optionally, in one embodiment, the ratio of the radius of the tube holes 316 to the tube hole row spacing D is 0.23-0.29, thereby further ensuring that each heat exchange tube 32 exhibits optimal heat exchange performance.

Wherein the center of the tube bore 316 closest to end

contours

314, 315 has a shortest distance D4 of 0.25 xd to 0.75 xd from the center of

end contours

314, 315 to the center of

end contours

314, 315, where D is the tube bore row spacing described above.

Further, in the present embodiment, the shortest distance D4 from the center of tube hole 316 closest to end

profiles

314, 315 is set to 0.4-0.6 of tube hole row spacing D. Through the mode, the heat exchange performance of the heat exchange tube 32 inserted into the tube hole 316 closest to the

end contour lines

314 and 315 can be brought into full play, and the heat exchange tube 32 can be prevented from being gouged in the assembling process.

The above description is only an embodiment of the present invention, and not intended to limit the scope of the present invention, and all modifications of equivalent structures and equivalent processes performed by the present specification and drawings, or directly or indirectly applied to other related technical fields, are included in the scope of the present invention.

Claims

1. The utility model provides a heat transfer fin, its characterized in that, heat transfer fin includes spaced first side contour line and second side contour line each other, second side contour line is towards the crooked setting of the direction of first side contour line, first side contour line deviates from the crooked setting of the direction of second side contour line, at least partial region of at least one in first side contour line and the second side contour line is the continuous section in the single-arch cycloid.

2. The heat exchange fin according to claim 1, wherein the second side contour line is at least partially coincident with the first side contour line after being translated, and the length of the coincident portion of the second side contour line and the first side contour line is not less than 90% of the length of the second side contour line.

3. The heat exchange fin according to claim 2, wherein the included angle between the translation direction and the line connecting the end points of the two ends of the continuous section is 85-95 degrees.

4. The heat exchange fin according to claim 2, wherein the single arcuate cycloid comprises an upper half and a lower half disposed in axial symmetry along a predetermined axis of symmetry, wherein the continuous section is located on the lower half.

5. The heat exchange fin according to claim 2, wherein the included angle between the symmetry axis and the line connecting the two end points of the continuous section is 60-65 degrees, and the ratio of the straight-line distance between the projections of the two end points of the continuous section on the symmetry axis to the diameter of the rolling circle for forming the single-arch cycloid is 0.54-0.66.

6. The heat exchange fin according to claim 5, wherein the ratio of the translation distance from the second side contour to the first side contour to the diameter of the round is 0.19-0.24.

7. An air duct type air conditioning device, which is characterized by comprising a shell, a fan assembly and the heat exchange fin as claimed in any one of claims 1 to 6, wherein the shell is used for forming a containing cavity; the heat exchange fins are arranged in the accommodating cavity; the fan assembly comprises a volute and a fan arranged in the volute, airflow generated by the fan flows into the accommodating cavity through an air outlet of the volute, the fan and the heat exchange fins are arranged at intervals along a first direction, and a first side contour line and a second side contour line are respectively bent towards a direction close to the fan.

8. The air duct type air conditioning device according to claim 7, wherein the volute comprises a first pressure expansion plate and a second pressure expansion plate, the first pressure expansion plate and the second pressure expansion plate are arranged at intervals along a second direction perpendicular to the first direction and parallel to the heat exchange fins so as to guide the air flow generated by the fan to flow into the accommodating cavity through the air outlet of the volute;

in the direction from the fan to the heat exchange fins, the first pressure expansion plate is inclined towards the second pressure expansion plate, and the second pressure expansion plate is inclined towards the direction departing from the first pressure expansion plate; on a reference cross section formed by a plane where the main surfaces of the heat exchange fins are located, an included angle between the first pressure expansion plate and the first direction is 6-9 degrees, and an included angle between the second pressure expansion plate and the first direction is 20-24 degrees.

9. The air duct type air conditioner according to claim 8, wherein the air duct type air conditioner satisfies the following formula:

L2＝ξ×(L1+L3×tgθ)；

wherein, theta is the contained angle between first diffuser plate and the second diffuser plate, tg is tangent trigonometric function, and L1 is the air outlet of spiral case is followed the height of second direction, and L2 is the heat transfer fin is followed the height of second direction, and L3 is the heat transfer fin is close to the tip of the air outlet of spiral case with the air outlet of spiral case is followed the distance of first direction, and xi is the preset coefficient of 1.3-1.6.

10. The air duct type air conditioning apparatus according to claim 8, wherein the first direction is a horizontal direction, the second direction is a vertical direction, the first diffuser plate is located at an upper end of the second diffuser plate, the single-arch cycloid includes an upper half portion and a lower half portion that are axisymmetrically arranged along a predetermined axis of symmetry, wherein the continuous section is located on the lower half portion, and an angle between the axis of symmetry and the first direction is less than or equal to 10 degrees.