CN113758359A - Heat exchange fin, heat exchanger and air conditioning device - Google Patents

Heat exchange fin, heat exchanger and air conditioning device Download PDF

Info

Publication number
CN113758359A
CN113758359A CN202010486871.4A CN202010486871A CN113758359A CN 113758359 A CN113758359 A CN 113758359A CN 202010486871 A CN202010486871 A CN 202010486871A CN 113758359 A CN113758359 A CN 113758359A
Authority
CN
China
Prior art keywords
heat exchange
fin
side contour
exchange fin
contour line
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202010486871.4A
Other languages
Chinese (zh)
Inventor
周柏松
罗彬�
李丰
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Midea Group Co Ltd
GD Midea Heating and Ventilating Equipment Co Ltd
Guangdong Midea HVAC Equipment Co Ltd
Original Assignee
Midea Group Co Ltd
GD Midea Heating and Ventilating Equipment Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Midea Group Co Ltd, GD Midea Heating and Ventilating Equipment Co Ltd filed Critical Midea Group Co Ltd
Priority to CN202010486871.4A priority Critical patent/CN113758359A/en
Publication of CN113758359A publication Critical patent/CN113758359A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/032—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by heat exchangers
    • F24F1/0325—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

The invention discloses a heat exchange fin, a heat exchanger and an air conditioning device. The heat exchange fin includes a first side contour and a second side contour spaced apart from each other. The first side contour line comprises a first reference point and a second reference point, the vertical distance from the first reference point to a straight line where the peak width of the heat exchange fin is located is 25% of the overall height of the heat exchange fin, the ratio of the fin width at the first reference point to the peak width of the heat exchange fin is 0.64-0.96, the vertical distance from the second reference point to a straight line where the peak width of the heat exchange fin is located is 45% of the overall height of the heat exchange fin, the ratio of the fin width at the second reference point to the peak width of the heat exchange fin is 0.54-0.80, and the fin width at the second reference point is smaller than the fin width at the first reference point. Through the mode, the heat exchange fins meet the requirement of matching of the flow velocity of the wind field, and meanwhile, the tail ends of the heat exchange fins can be guaranteed to have high heat exchange performance.

Description

Heat exchange fin, heat exchanger and air conditioning device
Technical Field
The invention relates to the technical field of air conditioners, in particular to a heat exchange fin, a heat exchanger and an air conditioning device.
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.
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, a heat exchanger and an air conditioning device, which aim to improve the heat exchange performance of the heat exchange fin by optimizing the fin width change rule of the heat exchange fin.
In order to solve the technical problems, the invention adopts a technical scheme that: the utility model provides a heat exchange fin, this heat exchange fin include first side contour line and second side contour line, and first side contour line and second side contour line are spaced each other. The second side profile line is arranged in a bending mode towards the direction of the first side profile line, the first side profile line is arranged in a bending mode towards the direction deviating from the second side profile line, and the width of the heat exchange fins gradually decreases from the middle area of the heat exchange fins to the end areas of the two sides of the middle area. The first side contour line comprises a first reference point and a second reference point, the vertical distance from the first reference point to a straight line where the peak width of the heat exchange fin is located is 25% of the overall height of the heat exchange fin, and the ratio of the fin width at the first reference point to the peak width of the heat exchange fin is 0.64-0.96. The vertical distance from the second reference point to a straight line where the peak width of the heat exchange fin is located is 45% of the overall height of the heat exchange fin, the ratio of the fin width at the second reference point to the peak width of the heat exchange fin is 0.54-0.80, and the fin width at the second reference point is smaller than the fin width at the first reference point.
In such a way, the width change rule of the heat exchange fins is optimized, so that the heat exchange fins meet the requirement of matching of the flow velocity of the wind field and the tail ends of the heat exchange fins have high heat exchange performance.
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;
FIGS. 3a and 3b are graphs comparing a flow velocity distribution of an air duct type air conditioner using a diffuser plate arrangement according to an embodiment of the present invention with a flow velocity distribution of a comparative example;
FIGS. 4a and 4b are graphs comparing a flow velocity distribution of a ducted air conditioner using heat exchange fins according to an embodiment of the present invention with a flow velocity distribution of a comparative example;
FIG. 5 is a side view of a heat exchanger fin according to another embodiment of the present invention;
FIG. 6 is a side view of a heat exchanger fin according to another embodiment of the present invention;
FIG. 7 is a perspective view of a portion of a heat exchanger fin according to an embodiment of the present invention;
FIG. 8 is an enlarged partial schematic view of FIG. 6;
FIG. 9 is a perspective view of a portion of a heat exchanger fin according to another embodiment of the present invention;
FIG. 10 is a partial top view of another embodiment according to the present invention;
FIG. 11 is a cross-sectional schematic view of a heat exchanger according to an embodiment of the present invention;
FIG. 12 is a cross-sectional schematic view of a heat exchanger according to another embodiment of the invention;
fig. 13 is a schematic perspective view of a heat exchanger and an auxiliary fitting mechanism according to an embodiment of the present invention;
FIG. 14 is a side view of a sheet metal edge panel according to one embodiment of the present invention;
FIG. 15 is a schematic perspective view of the sheet metal edge panel of FIG. 14;
FIG. 16 is a schematic cross-sectional view of the sheet metal blank of FIG. 15;
FIG. 17 is a perspective view of a plastic side panel according to an embodiment of the present invention;
FIG. 18 is a schematic perspective view of the plastic sideplate of FIG. 17 in cooperation with one arrangement of U-shaped pipe sections;
FIG. 19 is a schematic perspective view of the plastic sideplate of FIG. 17 in cooperation with an alternative arrangement of U-shaped pipe sections;
figure 20 is a partial cross-sectional view of the plastic sideplate of figure 17 mated to the U-shaped pipe section.
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 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 velocity profiles of the present example and the comparative example shown in figures 3a and 3 b. Fig. 3a and 3b 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. 3a 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. 3b shows other angle configurations, specifically, the included angle β 1 is 5 degrees, and the included angle β 2 is 19 degrees. From the comparison between fig. 3a and fig. 3b, it can be seen that the wind speed flowing through the heat exchanging fins 31 in fig. 3b is significantly different from that in fig. 3a in the transition process from the middle region to the end region, and therefore the flow velocity uniformity of the air flow in the angular setting of the embodiment is significantly higher than that in other angular settings.
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.
Optionally, in an 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 is further determinedmaxThe 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 abovemaxThe 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. 2maxW1, W2, etc. 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 WmaxThe 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. Is worthy of noteIt is to be noted that, when the first side contour line 311 and the second side contour line 312 have curved shapes, the straight line l3 where the peak width is located is generally a straight line where a line connecting the vertices of the first side contour line 311 and the second side contour line 312 is located. 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.
In this embodiment, the first side contour 311 and the second side contour 312 are further configured to be translationally coincident. Specifically, when the first side contour line 311 is shifted by the peak width W from the straight line l3 where the peak width is located toward the second side contour line 312maxThen, the translation curve 311' formed by the first side contour line 311 coincides with at least a partial region of the second side contour line 312. In one embodiment, the length of the overlapped portion of the translation curve 311' and the second side contour line 312 accounts for 90% or more of the total length of the first side contour line 311. The heat exchange fins 31 are generally formed by punching and cutting a sheet material, so that waste materials in the processing process can be reduced, and the production cost is reduced.
Further, the end contour lines 314, 315 comprise straight line segments parallel to the line l3 along which the peak width of the heat exchanger fin 31 is located. The line l3 along which the peak width lies is generally arranged along the length of the sheet during the stamping process, in such a way that the partial regions of the end contour 314, 315 are flush with the edge of the sheet, in order to further reduce scrap.
As shown in fig. 2, the shape characterizing parameters of the heat exchanging fin 31 further include the overall height, the overall width and the opening angle of the side profile. The overall height refers to a projected dimension H1 of the heat exchanging fin 31 on a reference plane P1 perpendicular to a line l3 on which the peak width is located and perpendicular to the main surface of the heat exchanging fin 31. The overall width refers to the projected dimension H2 of the heat exchanger fin 31 on a reference plane P2 that is perpendicular to the major surfaces of the heat exchanger fin and that is a line l3 where the peak width is parallel. The side contour line forms an intersection with a straight line l3 of the peak width, and the opening angle of the side contour line is an angle between a connecting line connecting both ends of the side contour line and the intersection, and for example, in fig. 2, the opening angle of the first side contour line 311 is α 1.
The present application will further optimize the heat exchange fins 31 based on the overall shape of the heat exchange fins 31 described above with reference to the following drawings:
1. side profile flare angle
At overall height H1 and peak width WmaxIn the same case, the opening angle α 1 of the first side contour 311 determines the depth of the heat exchanging fin 31 along the straight line l3 where the peak width is located, i.e., the overall width H2 of the heat exchanging fin 31. If the opening angle α 1 of the first side contour line 311 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 opening angle α 1 of the first side contour line 311 is too small, the smoothness of the air flow at the end of the heat exchange fin 31 is insufficient, resulting in deterioration of the heat exchange performance at the end of the heat exchange fin 31.
In order to achieve a balance between the overall heat exchange performance and the smoothness of the end air flow, in the present embodiment, the opening angle α 1 of the first side profile 311 is set to 80 to 135 degrees. Optionally, in a specific embodiment, the opening angle α 1 of the first side contour 311 is further set to 95-120 degrees. In another embodiment, the opening angle α 1 of the first side contour 311 is further set to 100-. Through the mode, the heat exchange fin 31 can have the largest heat exchange area in the minimum space, and the smoothness of the airflow at the tail end can be ensured.
Further, the first side contour 311 has an end tangent angle. Specifically, the end tangent included angle is an included angle α 2 between tangents of two end points of the first side contour line 311. Specifically in fig. 2, the included angle is the tangent of the endpoints S4 and S7. It should be noted that when the end point is located on a straight line segment, the tangent line is the extension of the straight line segment. At overall height H1 and peak width WmaxSimilarly, in the case that the first side contour line 311 and the second side contour line 312 are overlapped in a translation manner, the included angle α 2 of the tangent line at the end of the first side contour line 311 determines the fin width at the end of the heat exchanging fin 31. If the included angle α 2 of the tangent line at the end of the first side contour line 311 is too large, the fin width at the end of the heat exchange fin 31 is relatively large, and the effect of matching with the flow velocity of the wind field cannot be realized, if the included angle α 2 of the tangent line at the end of the first side contour line is too large, the first side contour line at the end of the heat exchange fin 31 at the end of the heat exchange fin cannot realize the effect of matching with the flow velocity of the wind field, and if the included angle α 2 of the tangent line at the end of the first side contour line at the end of the heat exchange fin is too large, the first side contour line at the end of the heat exchange fin 31 at the end of the first side contour line at the end of the wind fieldIf the included angle α 2 of the tangent line at the end of the contour line 311 is too small, the fin width at the end of the heat exchange fin 31 is relatively small, which results in poor heat exchange performance at the end of the heat exchange fin 31.
Therefore, in the present embodiment, the included angle α 2 of the end tangent of the first side contour 311 is further set to be 60-120 degrees, and the included angle α 2 of the end tangent of the first side contour 311 is smaller than the opening angle α 1 of the first side contour 311. Further, the ratio of the included angle α 2 of the end tangent of the first side contour 311 to the opening angle α 1 may be set to 0.7-0.85. By the mode, the width of the fin at the tail end of the first side contour line 311 can meet the requirement of matching of the flow velocity of the wind field, and higher heat exchange performance can be guaranteed.
Further, the first side contour line 311 is set to be located in a region defined by a connecting line of the vertex S8 of the end tangent included angle α 2 and both end points S4, S7 of the first side contour line 311 and a connecting line of the vertex S1 of the opening angle α 1 and both end points S4, S7 of the first side contour line 311, and an included angle between the tangent of the first side contour line 311 and a straight line l3 on which the peak width of the heat exchanging fin 31 is located gradually decreases in a direction from the middle region to the end region. The specific line type of the first side contour line 311 may be formed by one or more combinations of an arc line, a straight line segment, an elliptic curve, a circular arc line, a spline curve, a cycloid segment, and the like, and the number of each line may be one or more. In this way, the first side contour line 311 can have a reasonable bending shape, and a reasonable fin width variation rule can be obtained when the first side contour line and the second side contour line 312 are overlapped in a translation mode along the straight line l3 where the peak width is located. It is noted that the first side contour 311 is located within the region including the case where the first side contour 311 coincides with the edge of the region. For example, in FIG. 2, the straight line segments S3-S4, S6-S7 of the first side contour 311 and the connecting lines of the end points S4, S7 and the vertex S8 coincide.
2. Law of fin width variation
As described above, the fin width of the heat exchange fin 31 gradually decreases in the direction from the middle region of the heat exchange fin 31 to the end regions on both sides of the middle region, and then cooperates with the high flow velocity region and the low flow velocity region of the airflow wind field to improve the overall heat exchange performance of the heat exchange fin 31. However, if the width of the heat exchange fins 31 is too small in the direction from the middle region to the end region, the effect of matching the flow velocity of the wind field cannot be achieved. If the variation range of the fin width of the heat exchange fin 31 is too large, the fin width of the tail end of the heat exchange fin 31 is relatively small, resulting in deterioration of the heat exchange performance of the tail end of the heat exchange fin 31.
Therefore, in the present embodiment, the rule of variation in fin width of the heat exchange fin 31 in the direction from the middle region to the end region is further optimized. Specifically, the first side contour 311 has a reference point E11 and a reference point E12, a vertical distance from the reference point E11 to a straight line l3 along which the peak width of the heat exchanging fin 31 is located is 25% of the overall height H1 of the heat exchanging fin 31, and a vertical distance from the reference point E12 to a straight line l3 along which the peak width of the heat exchanging fin 31 is located is 45% of the overall height H1 of the heat exchanging fin 31. Fin width W1 at reference point E11 and peak width W of heat exchanger fin 31maxIs 0.64-0.96, the fin width W2 at reference point E12 and the peak width W of the heat exchanger fin 31maxIs 0.54-0.80 and the fin width W2 at reference point E12 is less than the fin width W1 at reference point E11.
Alternatively, in one embodiment, the fin width W1 at reference point E11 and the peak width W of the heat exchanger fin 31maxIs 0.75-0.85, the fin width W2 at reference point E12 and the peak width W of the heat exchanger fin 31maxThe ratio of (A) to (B) is 0.60-0.70.
Optionally, in a particular embodiment, the ratio of fin width W2 at reference point E12 to fin width W1 at reference point E11 is 0.70-0.90.
Optionally, in a specific embodiment, the first side contour 311 has a reference point E13, and the vertical distance from the reference point E13 to the straight line l3 of the peak width of the heat exchanging fin 31 is 35% of the overall height H1 of the heat exchanging fin 31. Fin width W3 at reference point E13 and peak width W of heat exchanger fin 31maxIs 0.60-0.89, and the fin width W3 at reference point E13 is less than at reference point E11And is greater than fin width W2 at reference point E12.
Optionally, in a particular embodiment, a ratio of fin width W3 at reference point E13 to fin width W1 at reference point E11 is 0.85-0.95 and a ratio of fin width W2 at reference point E12 to fin width W3 at reference point E13 is 0.85-0.95.
By the mode, the fin width change rule of the heat exchange fins 31 can meet the requirement of wind field flow velocity matching, and the tail ends of the heat exchange fins 31 can have high heat exchange performance.
Alternatively, in one embodiment, the peak width W of the heat exchanger fins 31maxThe perpendicular bisector of (a) forms an intersection point E6 and an intersection point E7 with the first side contour line 311, respectively, and the straight line distance d6 of the intersection point E6 and the intersection point E7, i.e., the sum of the vertical distances from the intersection point E6 and the intersection point E7 to the straight line l3 where the peak width is located. The ratio of the linear distance d6 to the overall height H1 of the heat exchanger fin 31 is 0.46-0.56. The smoothness of the airflow at the ends of the heat exchange fins 31 can be ensured in the above manner.
3. Contour line type
Referring to fig. 2, the first side contour line 311 is formed by a linear combination of at least two arcs and at least one straight line sequentially connected in a direction from the middle region to the end region of the heat exchange fin 31 on both sides of the straight line l3 where the peak width of the heat exchange fin 31 is located. Wherein the radii of curvature of the at least two arc segments increase gradually in a direction from the middle region to the end regions.
Specifically, in the present embodiment, the upper half portion of the first side contour 311 on the upper side of the straight line l3 where the peak width is located includes the curved sections S1-S2, the curved sections S2-S3, and the straight line sections S3-S4 which are connected in order in the direction from the middle region to the end region. The lower half of the first side contour 311, which is located on the lower side of the line l3 where the peak width is located, includes the curved sections S1-S5, the curved sections S5-S6, and the straight line sections S6-S7, which are connected in order in the direction from the middle region to the end region. The curvature radius of the arc sections S2-S3 is larger than that of the arc sections S1-S2, and the curvature radius of the arc sections S5-S6 is larger than that of the arc sections S1-S5. It is noted that references to "connected in series" in this application include direct connections or connections that transition through other lines.
Through the manner, the first side contour line 311 has a large bending degree through the sequential connection of the arc sections S1-S2 and the arc sections S2-S3 and the sequential connection of the arc sections S1-S5 and the arc sections S5-S6, the depth of the heat exchange fin 31 along the straight line l3 with the peak width is ensured, and meanwhile, the included angle alpha 2 of the tangent line at the tail end of the first side contour line 311 is not too small through the straight line sections S3-S4 and the straight line sections S6-S7, so that the heat exchange performance of the tail end of the heat exchange fin 31 is ensured.
Further, in the present embodiment, the arc sections S1-S2, the arc sections S2-S3 and the straight line sections S3-S4 on the upper side of the straight line l3 where the peak width is located are axisymmetrically arranged with the arc sections S1-S5, the arc sections S5-S6 and the straight line sections S6-S7 on the lower side of the straight line l3 where the peak width is located, with the straight line l3 where the peak width is located as a symmetry axis. In other embodiments, an asymmetric arrangement may also be employed. Further, in other embodiments, the number of arc segments and straight line segments may be varied as desired and is not limited to the number shown in FIG. 2.
In the present embodiment, the included angle between the tangent of the arc segments S1-S2 and S2-S3, the arc segments S1-S5 and the arc segments S2-S4 and the straight line l3 of the peak width is gradually reduced in the direction from the middle region to the end region, thereby ensuring that the first side contour line 311 is bent away from the second side contour line 312 while facilitating drainage of the condensed water.
Further, the ratio of the curvature radius of the arc sections S1-S2 to the curvature radius of the arc sections S2-S3, the ratio of the curvature radius of the arc sections S1-S5 to the curvature radius of the arc sections S5-S6 are 0.24-0.29, the ratio of the arc length of the arc sections S1-S2 to the arc length of the arc sections S2-S3, and the ratio of the arc length of the arc sections S1-S5 to the arc length of the arc sections S5-S6 are 1.1-1.35, and further the depth of the heat exchange fin 31 and the included angle alpha 2 of the tangent at the tail end are optimized.
Further, the arc sections S1-S2, S2-S3, S1-S5 and S5-S6 are arcs, and the arc sections S1-S2 and S1-S5 are directly connected and arranged in a common circle so as to facilitate the arrangement of pipe holes.
Further, arc segments S2-S3 are directly connected with arc segments S1-S2 and straight line segments S3-S4 and are tangent to arc segments S1-S2 and straight line segments S3-S4 at the connecting point, arc segments S5-S6 are directly connected with arc segments S1-S5 and straight line segments S6-S7 and are tangent to arc segments S1-S5 and straight line segments S6-S7 at the connecting point. Through the mode, the continuity of the first side contour line 311 can be ensured, and the stamping and cutting are facilitated.
Further, the upper half portion of the second side contour line 312 on the upper side of the straight line l3 where the peak width is located includes an arc section S1'-S2', an arc section S2'-S3', and a straight line section S3'-S4' which are connected in order in the direction from the middle region to the end region. The lower half of the second side contour line 312 located on the lower side of the straight line l3 where the peak width is located includes an arc section S1'-S5', an arc section S5'-S6', and a straight line section S6'-S7' which are connected in order in the direction from the middle region to the end region.
After the first side contour line 311 is translated along the straight line l3 where the peak width is located, the arc sections S1-S2, S2-S3, S1-S5, and S5-S6 of the first side contour line 311 can respectively overlap with the arc sections S1' -S2', S2' -S3', S1' -S5', and S5' -S6' on the second side contour line 312, and the straight line sections S3-S4, and S6-S7 ' on the first side contour line can respectively overlap with the straight line sections S3' -S4', and S6' -S7' on the second side contour line at least partially, so that the utilization rate of materials is maximized, the materials are saved, and the production cost is reduced.
Optionally, in a specific embodiment, the straight line segments S3'-S4' and S6'-S7' on the second side contour line respectively form a chamfer with the end contour line of the corresponding side, so that the heat exchanging fin 31 is not prone to being chipped at the position of the corner, the heat exchanging effect is affected, and scratches can be avoided during the assembling process of the heat exchanger 30.
Further, in the present embodiment, the reference point E11 is located on the arc sections S2-S3 of the first side contour line 311, the reference point E12 is located on the straight line sections S3-S4 of the first side contour line 311, the reference point E13 is located on the straight line sections S3-S4 of the first side contour line 311, the intersection point of the straight line of the fin width at the reference point E11 and the second side contour line 312 is located on the arc sections S1'-S2' of the second side contour line 312, the intersection point of the straight line of the fin width at the reference point E12 and the second side contour line is located on the straight line sections S3'-S4' of the second side contour line 312, and the intersection point of the straight line of the fin width at the reference point E13 and the second side contour line 312 is located on the arc sections S2'-S3' of the second side contour line 312. By the mode, the fin width change rule of the heat exchange fin 31 meets the requirement, and meanwhile, the depth of the heat exchange fin 31 on the straight line l3 where the peak width is located is ensured.
Further, in the present embodiment, the peak width W of the heat exchange fin 31maxThe intersection point E6 and the intersection point E7 formed by the perpendicular bisector and the first side contour line 311 are respectively located at the arc sections S2-S3 and S5-S6 of the first side contour line 311, thereby ensuring the smoothness of the airflow at the tail end of the heat exchange fin 31.
Further reference is made to the flow velocity profiles of the present example and the comparative example shown in fig. 4a and 4 b. Fig. 4a and 4b are flow velocity distribution diagrams after the heat exchanger 30 is away from the side of the fan 22 when the heat exchange fin 31 of the present embodiment and the heat exchange fin of the comparative example are employed, respectively. Wherein, fig. 4a adopts the heat exchange fin 31 of this embodiment, fig. 4b adopts the comparative heat exchange fin of three-arc type, which includes three-segment arcs connected in sequence in the direction from the middle region to the end region respectively on both sides of the straight line where the peak width is located, and the curvature radius of the arcs becomes larger gradually. Therefore, the opening angle, the tail end tangent included angle and the tail end fin width of the leeward side profile of the heat exchange fin are respectively smaller than those of the embodiment. From the comparison result of fig. 4a and fig. 4b, it can be found that the area of the heat exchange fin 31 of the present embodiment in the low wind speed region located in the middle region on the side away from the fan 22 is significantly smaller than that of the heat exchange fin of the comparative example, the uniformity of the flow velocity is significantly improved, and the heat exchange performance is significantly improved.
4. Pipe hole arrangement
Referring to fig. 5, fig. 5 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. 5, 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 line 311 or the second side contour line 312 along the straight line l3 where the peak width is located, and a ratio of a shortest distance from the center of each pipe hole 316 in each row of pipe holes 316 to the corresponding arrangement curve to a radius of the 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.
In the present embodiment, the number of rows of the tube holes 316 in the middle region is greater than the number of rows of the tube holes 316 in the end regions in the direction of the interval between the first side contour 311 and the second side contour 312. Specifically, in fig. 5, the number of rows of the tube holes 316 in the middle region is three, and the number of rows of the tube holes 316 in the end regions is two. In other embodiments, the number of rows of the tube holes 316 in the middle region may be four, and the number of rows of the tube holes 316 in the end regions may be two, or the number of rows of the tube holes 316 in the middle region may be three, and the number of rows of the tube holes 316 in the end regions may be one, and the number of rows of the tube holes 316 in the middle region and the number of rows of the tube holes 316 in the end regions are not specifically limited in this application.
Further, in the present embodiment, the height H3 of the central region where the number of rows of tube holes 316 is relatively high is set to 25% to 50% of the overall height H1 of the heat exchanging fin 31.
As shown in fig. 5, the boundary between the middle region and the end region is formed by connecting the centers of the pipe holes 316 of the middle region and the pipe holes 316 of the end region that are adjacent to each other in a row of pipe holes 316 near the first side contour line 311. Parallel lines parallel to a straight line l3 where the peak width is located are further made along the midpoint of the connecting line of the centers of the pipe holes, and two parallel lines l5 and l6 are further obtained on two sides of the straight line l3 where the peak width is located. The parallel lines l5 and l6 are the dividing lines between the central region and the end regions. The parallel lines l5 and l6 are spaced apart by a distance H3 in a direction perpendicular to the line l3 along which the peak width lies, which is the height of the middle region.
Through the mode, the number of rows of the pipe holes 361 in the middle area is set to be larger than that of the pipe holes 361 in the end area, the height H3 of the middle area and the overall height H1 of the heat exchange fins 31 are set in a reasonable range, and the heat exchange fins 31 can be better matched with a high flow velocity area and a low flow velocity area of a wind field, so that a better heat exchange effect is achieved.
Alternatively, in one embodiment, the height H3 of the central region may be set to 30% -45% of the overall height H1 of the heat exchanger fins 31.
Further with reference to FIG. 2, optionally, in one embodiment, the ratio of the height H3 of the central region to the linear distance d6 of the intersection E6 and the intersection E7 is set to 0.60-0.80, and the ratio of the linear distance d6 of the intersection E6 and the intersection E7 to the overall height H1 of the heat exchanger fin 31 is 0.46-0.56. Through the mode, better heat exchange effect can be realized while the smoothness of the air flow of the heat exchange fins 31 is ensured.
Further, the intersection points E18, E19 of the parallel lines l5 and l6 serving as the boundary lines of the middle region and the end region with the first side contour lines 311 and the intersection points E20, E21 of the second side contour lines 312 are located on the arc segments S2-S3, S5-S6 of the first side contour lines 311 and the arc segments S2'-S3', S5'-S6' of the second side contour lines 312, respectively, and the intersection points E18 of the parallel lines l5 and l6 with the first side contour lines 31 are located on the side of the straight line l3 on which the reference point E11 and the intersection point E6 are located near the peak width. Therefore, the fin area corresponding to the arc sections S1-S2 with relatively large curvature is fully utilized as the middle area of the heat exchange fin 31, and the middle area is ensured to have enough fin width.
Further, in the present embodiment, the fin width of the central region is set to K1 × n1 × D, and the fin width of the end region is set to K2 × n2 × D. Wherein n1 and n2 are the number of rows of pipe holes 316 in the middle area and the end area respectively, D is the distance between the rows of the pipe holes at the tail end, and K1 and K2 are variation coefficients with the value range of 0.8-1.2.
The terminal 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 closest to the first side contour 311 and the second side contour 312, and the line drawn through the center E14 of the tube hole 316 and the line drawn from the extension of the first side contour 311 and the second side contour 312 or both is the normal line at the intersection point E15 with respect to the intersection points E15 and E16. When the number of rows of the pipe holes 316 in the end region is 2 or more (2 rows shown in fig. 5), 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 E17. At this time, the distal tube hole row pitch D is a linear distance between the tube hole center E14 of the selected tube hole 316 and the intersection point E17. When the number of rows of tube holes 316 in the end region is 1, the distance D between the rows of terminal tube holes is the linear distance between the intersection points E15 and E16. 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 terminal 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 contour 314, 315 has a shortest distance H4 from the center of end contour 314, 315 to end contour 314, 315 of 0.25 xd to 0.75 xd, where D is the above-described terminal tube bore row spacing.
Further, in this embodiment, the shortest distance H4 from the center of the tube hole 316 closest to the end contour 314, 315 is set to 0.4-0.6 of the end 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.
5. Surface structure
Referring to fig. 6, fig. 6 further shows various surface structures on the basis of the heat exchange fin 31 shown in fig. 5, and the surface structure of the heat exchange fin 31 is optimized in the following aspects:
5.1. heat transfer enhancement structure
As shown in fig. 6, in the present embodiment, the heat exchange fin 31 is provided with a plurality of heat transfer enhancing structures, specifically, a plurality of bridge piece sets 317, each bridge piece set 317 includes at least one bridge piece 3171, and each bridge piece 3171 has a specific shape as shown in fig. 7, and includes two side walls 3171a disposed in a bent manner relative to the heat exchange fin 31 and opposite to each other, and a top wall 3171b bridging the two side walls 3171 a. Each of the bridge pieces 3171 serves as a heat transfer enhancing unit. The main function of the bridge piece set 317 is to destroy the flow boundary layer, improve the heat transfer coefficient of the air side of the heat exchange fin 31, and further realize heat transfer enhancement.
As described above, the fin width of the heat exchange fin 31 of the present embodiment becomes gradually smaller in the direction from the central region of the heat exchange fin 31 to the end regions on both sides of the central region, and further the number of rows of the tube holes 316 in the central region is larger than the number of rows of the tube holes 316 in the end regions. When the heat exchange fins 31 are combined with the heat exchange tubes 32 to form the heat exchanger 30, the heat exchange capacity of the middle regions of the heat exchange fins 31 is greater than that of the end regions of the heat exchange fins 31.
Therefore, in this embodiment, the heat transfer enhancing capability of the bridge plate set 317 in the end region is set to be greater than the heat transfer enhancing capability of the bridge plate set 317 in the middle region, so as to improve the heat exchange uniformity of the middle region and the end region of the heat exchange fin 31, and further improve the overall heat exchange performance of the heat exchanger 30.
Specifically, the heat transfer enhancing capacity of the bridge piece set 317 is related to the number, height, width and other parameters of the arrangement of the bridge pieces 3171 per unit area, so that the heat transfer enhancing capacity of the bridge piece set 317 in the end region can be greater than that of the bridge piece set 317 in the middle region by differentiating one or more of the above parameters of the bridge pieces 3171 in the middle region and the end regions.
Alternatively, the number of the arrangement of the bridge pieces 3171 per unit area in the end region is set to be greater than the number of the arrangement of the bridge pieces 3171 per unit area in the middle region, so that the heat transfer enhancing capability of the bridge piece group 317 in the end region is greater than that of the bridge piece group 317 in the middle region. In the present application, the number of arrangement per unit area refers to a ratio of the number of the bridge pieces 3171 in the middle region or the end regions to the area of the middle region or the end regions.
For example, as shown in FIG. 6, the number of bridge pieces 3171 in at least some of the bridge piece sets 317 in the end regions is set greater than the number of bridge pieces 3171 in at least some of the bridge piece sets 317 in the middle regions, thereby providing a greater heat transfer enhancement capability for the bridge piece sets 317 in the end regions than for the bridge piece sets 317 in the middle regions. Specifically, in fig. 6, the number of the bridge pieces 3171 in the bridge piece group 317 in the end region is three or four, and the number of the bridge pieces 3171 in the bridge piece group 317 disposed in the middle region is two or three. Of course, in other embodiments, the number of the bridge pieces 3171 in the bridge piece set 317 may be set according to practical situations, and the application is not limited in particular.
Further, in the present embodiment, the second side contour line 312 is taken as the windward side contour line, and the first side contour line 311 is taken as the leeward side contour line. The air current is at the in-process of following the transmission of second side outline line 312 to first side outline line 311, and the velocity of flow constantly descends to constantly carry out the heat transfer with heat transfer fin 31, lead to the difference in temperature between air current and the heat transfer fin 31 to diminish gradually, and then make heat transfer fin 31 be less than the heat transfer ability in the region that is close to second side outline line 312 in the heat transfer ability of the region that is close to first side outline line 311. Therefore, the heat transfer enhancing capability of the bridge piece set 317 near the second side contour line 312 can be further set to be smaller than that of the bridge piece set 317 near the first side contour line 311, so as to improve the uniformity of heat exchange between the first side contour line 311 and the second side contour line 312 of the heat exchange fin 31. Specifically, the number of bridge pieces 3171 in at least a portion of the set of bridge pieces 317 adjacent to the first side contour 311 may be set greater than the number of bridge pieces 3171 in at least a portion of the set of bridge pieces 317 adjacent to the second side contour 312. For example, in fig. 6, in the central region of the heat exchange fin 31, the number of the bridges 3171 in the bridge group 317 adjacent to the second side contour line 312 is two, and the number of the bridges 3171 in the bridge group 317 adjacent to the first side contour line 311 is three. Of course, in other embodiments, the second side contour 312 may be used as the leeward side contour, and the first side contour 311 may be used as the windward side contour. At this time, the specific arrangement of the bridge piece set 317 also needs to be adjusted accordingly.
Further, during the cooling process, when the airflow passes through the surfaces of the heat exchange fins 31, the water vapor in the airflow may be condensed when meeting the cold, and condensed water is generated. The condensed water flows down along the heat exchange fins 31 by gravity, and the amount of water gradually increases in the flow direction. Therefore, in this embodiment, the drainage capacity of the bridge set 317 in the lower end region can be further set to be greater than the drainage capacity of the bridge set 317 in the upper end region, so as to reduce the drainage difficulty of the lower end of the heat exchange fin 31, so that the drainage is smoother, and the heat exchange effect of the lower end of the heat exchange fin 31 is further improved.
Specifically, the drainage capacity of the bridge piece group 317 is also related to various parameters such as the number of arranged bridge pieces 3171 per unit area, the height, and the width, and therefore, the drainage capacity of the bridge piece group 317 in the lower end region can be made larger than the drainage capacity of the bridge piece group 317 in the upper end region by differentiating one or more of the above parameters of the bridge pieces 3171 in the upper end region and the lower end region.
Alternatively, the number of arrangement per unit area of the bridge pieces 3171 in the lower end region is set smaller than the number of arrangement per unit area of the bridge pieces 3171 in the upper end region, so that the drainage capacity of the bridge piece group 317 in the lower end region is greater than that of the bridge piece group 317 in the upper end region.
For example, as shown in fig. 6, the number of the bridge pieces 3171 in at least a part of the bridge piece group 317 in the lower end region is set smaller than the number of the bridge pieces 3171 in at least a part of the bridge piece group 317 in the upper end region, so that the drainage capacity of the bridge piece group 317 in the lower end region is greater than that of the bridge piece group 317 in the upper end region. Specifically, in fig. 6, the number of the bridge pieces 3171 in the bridge piece group 317 in the upper end portion region is four, and the number of the bridge pieces 3171 in the bridge piece group 317 in the lower end portion region is three. Of course, in other embodiments, the number of the bridge pieces 3171 in the bridge piece set 317 may be set according to practical situations, and the application is not limited in particular. In other embodiments, the set of fins 317 may be replaced by other heat transfer enhancing structures, such as vortex generators, louvers, and other various other raised structures relative to the heat exchange fins 31, as described below.
5.2. Heat insulation structure
In this embodiment, the number of rows of the tube holes 316 on the heat exchange fin 31 is at least two, specifically, the central area is 3 rows, and the end area is 2 rows.
The heat exchanging fin 31 is further provided with a plurality of rows of heat insulating structures 318, 319 in rows, and each row of heat insulating structures 318, 319 is arranged between two adjacent rows of tube holes 316. The primary function of the row thermal spacers 318, 319 is to prevent cross-talk between heat exchange tubes 32 inserted into adjacent two rows of tube holes 316.
As described above, the fin width of the heat exchange fin 31 of the present embodiment becomes gradually smaller in the direction from the central region of the heat exchange fin 31 to the end regions on both sides of the central region, and further the number of rows of the tube holes 316 in the central region is larger than the number of rows of the tube holes 316 in the end regions. When the heat exchange fin 31 is combined with the heat exchange tube 32 to form the heat exchanger 30, the wind resistance of the middle region of the heat exchange fin 31 is greater than that of the end regions of the heat exchange fin 31.
Therefore, in the present embodiment, setting the wind resistance of the row thermal insulation structure 318 in the middle area to be smaller than the wind resistance of the row thermal insulation structure 319 in the end area can balance the wind resistance in the middle area and the wind resistance in the end area, and improve the overall heat exchange performance of the heat exchange fin 31.
Specifically, the windage of the row thermal structures 318, 319 is primarily related to the height, width, etc. of the row thermal structures 318, 319, and thus the windage of the row thermal structures 318 in the middle region may be made less than the windage of the row thermal structures 319 in the end regions by adjusting one or more of the above parameters.
For example, the height of the row spacing thermal structures 318 in the central region may be set to be less than the height of the row spacing thermal structures 319 in the end regions, and/or the width of the row spacing thermal structures 318 in the central region may be set to be less than the width of the row spacing thermal structures 319 in the end regions.
In this embodiment, the row spacing thermal structures 318 in the middle region are slits and the row spacing thermal structures 319 in the end regions are louvers, the specific configuration of which is shown in FIG. 7. The louver is a strip-shaped area which is mainly formed by cutting the heat exchange fins 31 and is turned over relative to the heat exchange fins 31.
Further, since 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 middle region is curved to a greater extent and has a slope varying in a reverse direction, so that the flow rate of the condensed water in the middle region is relatively slow, and the flow rate of the condensed water in the middle region can be increased by setting the heat insulating structure 318 in the middle region as a slit. Furthermore, by providing the row spacing thermal structures 319 in the end regions as louvers, an additional turbulating effect may be provided, thereby enhancing heat transfer in the end regions.
In other embodiments, the row spacing thermal structures 318, 319 in the middle and end regions may both be provided as louvers, or both as slits, and the embodiments of the present application are not particularly limited.
Further, in order to improve the smoothness of water drainage, the water drainage capacity of the thermal structure 319 at the lower end region may be set to be greater than the water drainage capacity of the thermal structure 319 at the upper end region, so that water drainage is smoother, and the heat exchange effect of the lower end region of the heat exchange fin 31 may be improved.
Specifically, since the height and width of the row spacing thermal structures 319 may affect the drainage capacity, in the present embodiment, the height of the row spacing thermal structures 319 in the lower end region is set to be smaller than the height of the row spacing thermal structures 319 in the upper end region, and/or the width of the row spacing thermal structures 319 in the lower end region is set to be smaller than the width of the row spacing thermal structures 319 in the upper end region, to enhance the drainage capacity in the lower end region.
Further, as described above, in the present embodiment, the second side contour line 312 is taken as the windward side contour line, and the first side contour line 311 is taken as the leeward side contour line. The heat exchange fins 31 have a heat exchange capacity in the region near the first side contour 311 lower than that in the region near the second side contour 312. Therefore, the row pitch of the row spaced thermal structures 318 or 319 is set to gradually increase in the direction from the second side contour line 312 to the first side contour line 311. In this way, the heat exchange efficiency of the heat exchange tube 32 near the leeward side can be enhanced.
In the present application, when the number of rows of the tube holes 316 in the heat exchange fin 31 is two in the direction from the second side contour 312 to the first side contour 311, the row pitch of the row spacing thermal structure 318 or 319 refers to the spacing distance between the row spacing thermal structure 318 or 319 and the adjacent first side contour 311 and second side contour 312. When the number of rows of tube holes 316 in the heat exchange fin 31 is at least three, the row pitch of the row spacing thermal structure 318 or 319 further includes the spacing distance between two adjacent rows of the row spacing thermal structure 318 or 319.
For example, as shown in fig. 6, in the present embodiment, in the middle area of the heat exchanging fin 31, the number of rows of the tube holes 316 is three, and the row pitch of the row spacing thermal structures 318 includes a distance d9 between the row spacing thermal structures 318 close to the second side contour line 312 and the second side contour line 312, a spacing distance d10 between the two rows of row spacing thermal structures 318, and a spacing distance d11 between the row spacing thermal structures 318 close to the first side contour line 311 and the first side contour line 312, respectively, wherein d9< d10< d 11. In the end regions of the heat exchanger fins 31, the rows of tube holes 316 are in two rows, and the row pitch of the row spacing thermal structures 319 includes a spacing distance d12 between the row spacing thermal structures 319 and the second side contour 312 and a distance d13 between the row spacing thermal structures 319 and the first side contour 311, respectively, wherein d12< d 13. Further, the second side contour line 312 is taken as a leeward side contour line, and the first side contour line 311 is taken as a windward side contour line. At this point, the row spacing of the row spacer thermal structures 318 or 319 would need to be adjusted accordingly.
Further, as shown in fig. 6, the heat exchange fin 31 is further provided with a row internal insulation structure 320, and the row internal insulation structure 320 is arranged between two tube holes 316 which are located at the middle region and the end region and adjacent to each other in the row of tube holes 316 close to the second side contour 312. By arranging the inner heat-insulating discharge structure 320 at the junction of the middle region and the end region, mutual heat transfer between the adjacent heat exchange tubes 32 of the middle region and the end region can be avoided, and the overall heat exchange performance of the heat exchanger 30 can be improved.
5.3. End reinforcing rib
Further, as shown in fig. 6, the heat exchange fin 31 is provided with an end reinforcing rib 321, and the end reinforcing rib 321 is arranged between the tube hole 316 close to the end contour 314 or 315 and the end contour 314 or 315, so as to enhance the strength of the end of the heat exchange fin 31 and avoid the occurrence of curling.
Further, in the present embodiment, the end reinforcing ribs 321 are arranged in an elongated shape, and the length direction of the end reinforcing ribs 321 is arranged in the radial direction of the pipe hole 316 near the end contour 314 or 315 and directed to the point of the end contour 314 or 315 where the distance from the center of the pipe hole 316 near the end contour 314 or 315 is the largest.
Specifically, in the present embodiment, the pore 316 closest to end contour 314 or 315 is the pore 316 adjacent to end contour 314 or 315 and second side contour 312, and the point at which the distance from the pore 316 is the greatest is the corner cut between end contour 314 or 315 and second side contour 312. The elongated end ribs 321 extend in a direction along a line connecting the center of the tube hole 316 and the cut angle to reinforce the strength of the end portion located farthest from the tube hole 316.
The end reinforcing ribs 321 may be integrally formed with the heat exchange fin 31, and the end reinforcing ribs 321 may be formed on the surface of the heat exchange fin 31 by stamping, so as to simplify the connection manner of the end reinforcing ribs 321.
Optionally, the protruding direction of the end reinforcing rib 321 relative to the heat exchange fin 31 may be the same as the protruding direction of the heat transfer enhancing structure and the heat insulating structure relative to the heat exchange fin 31, so as to improve the production efficiency of the heat exchange fin through one-step punch forming.
Further, in one embodiment, the end reinforcing ribs 321 have a width of 0.3 to 1.5mm and a length of 2mm to 10 mm. In other specific embodiments, the width of the end reinforcing rib 321 may be 0.3mm, 0.5mm, 0.8mm, 1mm, 1.25mm, 1.5mm, etc., and the length may be 2mm, 2.5mm, 3mm, 3.5mm, 4mm, 4.5mm, 5mm, 5.5mm, 6mm, 6.5mm, 7mm, 7.5mm, 8mm, 8.5mm, 9mm, 9.5mm, 10mm, etc., and the end reinforcing rib may be flexibly set according to the distance between the tube hole 316 and the end contour lines 314 and 315 and the thickness of the heat exchange fin 31, which is not particularly limited in the present application.
5.4. Vortex generator
As further shown in fig. 6-10, the heat exchange fin 31 is further provided with a vortex generator, and the vortex generator is configured to enable an airflow flowing from the windward side of the heat exchange tube 32 to form a vortex under the action of the vortex generator, so as to reduce the area of the wake area on the leeward side of the heat exchange tube 32.
Specifically, as the air flows through the heat exchange tubes 32, separation occurs on the leeward side of the heat exchange tubes 32, forming a larger wake zone, which has poor heat transfer properties.
Therefore, in the present embodiment, one or at least two vortex generators may be symmetrically disposed on the periphery of the heat exchange tube 32 along the air flowing direction, so as to suppress the separation of air on the leeward side of the heat exchange tube 32, reduce the area of the wake region, and improve the heat transfer performance on the leeward side of the heat exchange tube 32, thereby improving the overall heat transfer performance of the heat exchanger 30.
Alternatively, in a specific embodiment, the vortex generator is a convex hull 322 integrally formed with the heat exchanging fin 31 and protruding relative to the heat exchanging fin 31, and the specific shape of the convex hull 322 is as shown in fig. 7-8. When the airflow flows through the surface of the convex hull 322, horseshoe-shaped vortex, transverse vortex, longitudinal vortex, mixed vortex and even complex secondary vortex are formed, so that the local nussel number (Nu) at the downstream of the convex hull 322 is strengthened, and the heat exchange of the downstream heat exchange fin 31 is strengthened. The presence of the convex hulls 322 improves the degree of synergy of velocity and temperature gradient, so that under the same Reynolds number, the heat exchange fins 31 with the convex hulls 322 have a synergy angle lower than that of the flat sheets without the convex hulls 322 and a heat exchange coefficient higher than that of the flat sheets, so as to improve the heat transfer performance of the leeward side of the heat exchange tubes 32, thereby improving the overall heat transfer performance of the heat exchanger 30.
Optionally, in a specific embodiment, the convex hull 322 may be formed by stamping, and the protruding direction of the convex hull 322 relative to the surface of the heat exchange fin 31 may be set to be the same as the protruding direction of the heat transfer enhancing structure, the heat insulation structure, and the end reinforcing ribs 320 relative to the surface of the heat exchange fin 31, so as to form the above structure on the heat exchange fin 31 at the same time by one-time stamping forming, thereby greatly simplifying the production process of the heat exchange fin 31 and improving the production efficiency of the heat exchange fin 31.
Alternatively, in a specific embodiment, the protruding direction of the convex hull 322 with respect to the surface of the heat exchange fin 31 may be set to be different from the protruding direction of the above structure.
Optionally, in a specific embodiment, a part of the convex hulls 322 may be arranged to protrude towards one side of the heat exchange fin 31, and another part of the convex hulls 322 may be arranged to protrude towards the other side of the heat exchange fin 31, so that the heat exchange enhancement effects at two sides of the heat exchange fin 31 are the same.
Optionally, in a specific embodiment, the convex hulls 322 may also be formed on the surface of the heat exchange fin 31 by using other production process manners, which are not specifically limited in this application.
Further, when the convex hull 322 is disposed on the windward side of the heat exchange tube 32, the improvement of the heat exchange enhancement effect of the convex hull 322 on the heat exchange fins 31 is significantly weaker than that on the leeward side of the heat exchange tube 32, and the pressure drop level on the windward side is larger than that on the leeward side. Therefore, in the present embodiment, as shown in fig. 8, the convex hull 322 is disposed on the leeward side of the heat exchange tube 32. Moreover, the convex hull 322 is further disposed in a fan-shaped area which takes the center of the pipe hole 316 as a vertex and faces the leeward side of the heat exchange pipe 32, and two side edges of the fan-shaped area and the wind inlet direction D4 of the heat exchange pipe 32 form an included angle of 45 degrees respectively, so as to improve the heat exchange effect of the leeward side of the heat exchange pipe 32 and improve the overall heat exchange performance of the heat exchanger 30.
Specifically, in an embodiment, the wind inlet direction D4 of the heat exchange tube 32 may be a horizontal direction, and the fan-shaped area is an area on the upper and lower sides forming an angle of 45 degrees with the horizontal direction. In other embodiments, the wind direction D4 of the heat exchange tube 32 may also be inclined from the horizontal direction.
Further, in an embodiment, when the heat exchange pipe 32 is a circular pipe, the ratio of the distance between the convex hull 322 and the heat exchange pipe 32 to the diameter of the heat exchange pipe 32 may be set to 0.3-1.0.
Further, the convex hull 322 is one of the heat transfer enhancing structures, when the fluid flows through the convex hull 322, horseshoe-shaped vortices are formed in the front half part of the convex hull 322, and transverse vortices are formed in the rear half part of the convex hull 322, so that the convex hull 322 generates a large shape resistance while increasing the heat exchange, and the pressure drop of the fluid is increased. Therefore, in specific use, the number of the convex hulls 322 arranged on the periphery of each heat exchange pipe 32 can be one or more than two. At this time, all the convex hulls 322 on the periphery of each heat exchange tube 32 can be used as a heat transfer enhancing structure, and each convex hull 322 can be used as a heat transfer enhancing unit, and the differentiation arrangement is performed with reference to the above description. For example, the number, height, etc. of the convex hulls 322 arranged on the heat exchange fins 31 in unit area are set differently to achieve the above-described effects of uniform heat exchange and accelerating the flow of the condensed water.
Alternatively, in a specific embodiment, the number of the convex hulls 322 at the rear side of each heat exchange tube 32 may be set to 2 to 6, and the height of the convex hulls 322 may be set to 0.8 to 1.2 mm.
Further, since the heat transfer coefficient of the convex hull 322 is also related to the shape of the convex hull 322, the heat transfer coefficient of the convex hull 322 can be further improved by changing the shape of the convex hull 322.
Alternatively, in one embodiment, the projection of the convex hull 322 on the heat exchanging fin 31 is provided in an elliptical shape, a rectangular shape, or a raceway shape. That is, the projection of the convex hull 322 on the heat exchanging fin 31 has a major axis direction D5 and a minor axis direction D6 perpendicular to the major axis direction D5, and the major axis dimension D14 of the projection of the convex hull 322 in the major axis direction D5 is larger than the minor axis dimension D15 in the minor axis direction D6.
At this point, the heat transfer coefficient and drag coefficient of the convex hull 322 are related to the ratio of the major axis dimension d14 and the minor axis dimension d15 of the convex hull 322. As the major axis dimension d14 of the convex hull 322 increases, the resistance to flow and the knoop number (Nu) decreases, and the velocity becomes less synergistic with the temperature gradient. The opposite is true when the minor axis dimension d15 is increased. This is because an increase in the major axis dimension d14 of the convex hull 322 causes the shape of the convex hull 322 to more closely approximate the streamlined drag reducing shape, with less turbulence resulting in reduced heat transfer and drag, and an increase in the minor axis dimension d15 resulting in the opposite effect.
Thus, in one embodiment, the ratio of the major axis dimension d14 to the minor axis dimension d15 of the convex hull 322 may be set between 1.2 and 1.6 to optimize the heat transfer coefficient and drag coefficient of the convex hull 322.
Further, the angle between the long axis direction D5 of the convex hull 322 and the wind inlet direction D4 is large, which results in a significant increase in flow resistance and a significant increase in airflow pressure drop. Therefore, in an embodiment, the included angle between the long axis direction D5 of the convex hull 322 and the wind inlet direction D4 of the heat exchange pipe 32 can be further set to be less than or equal to 10 degrees, so as to reduce the air flow resistance and reduce the air pressure drop.
For example, the long axis direction D5 of the convex hull 322 may be set to coincide with the incoming wind direction D4, i.e., the angle between the two is 0 degrees. Alternatively, the included angle between the major axis direction D5 and the wind direction D4 may be set to 1 degree, 2 degrees, 3 degrees, 4 degrees, 5 degrees, 6 degrees, 7 degrees, 8 degrees, 9 degrees, 10 degrees, or the like.
In addition, the shape of the convex hull 322 may also be set according to needs, for example, the projection of the convex hull 322 on the heat exchange fin 31 may be set to be a circle, a drop (large curvature radius near the windward side), a regular or irregular polygon, and the like, and the present application is not limited specifically.
Optionally, in a specific embodiment, the ratio of the long axis dimension d14 of the convex hull 322 to the diameter of the heat exchange tube 32 may be set to 0.2-0.6, so as to improve the turbulence effect of the convex hull 322 on the periphery of the heat exchange tube 32.
Further, since the number of the convex hulls 322 disposed at the periphery of each heat exchange tube 32 and the ratio of the long axis dimension d14 to the short axis dimension d15 of the convex hulls 322 can affect the heat transfer coefficient and the drag coefficient of the convex hulls 322, the number of the convex hulls 322 disposed at the periphery of the same heat exchange tube 32 and the ratio of the long axis dimension d14 to the short axis dimension d15 of the convex hulls 322 can be coupled to balance the heat transfer coefficient and the drag coefficient of the convex hulls 322. Specifically, the number of convex hulls 322 is set to be inversely related to the ratio of the major axis dimension d14 to the minor axis dimension d 15. That is, when the ratio of the major axis dimension d14 to the minor axis dimension d15 of the convex hull 322 is designed to be larger, the number of convex hulls 322 can be reduced appropriately; similarly, when the ratio of the major axis dimension d14 to the minor axis dimension d15 of the convex hull 322 is designed to be small, the number of convex hulls 322 can be increased appropriately.
Alternatively, in a specific embodiment, as shown in fig. 9-10, the vortex generator may also be a flap 323 integrally formed with the heat exchange fin 31 and folded over with respect to the heat exchange fin 31, the flap 323 having a specific shape as shown in fig. 9. The flap 323 serves to guide the air flow along the gap between the flap 323 and the heat exchange tube 32 toward the leeward side of the heat exchange tube 32, thereby forming a vortex.
Optionally, in a specific embodiment, the folded piece 323 may be formed by stamping, and the folding direction of the folded piece 323 relative to the surface of the heat exchange fin 31 may be set to be the same as the protruding direction of the heat transfer enhancing structure, the heat insulating structure, and the end reinforcing rib 320 relative to the surface of the heat exchange fin 31, so that the structures are formed at the same time by one-step stamping forming, thereby greatly simplifying the production process of the heat exchange fin 31 and improving the production efficiency of the heat exchange fin 31.
In a specific embodiment, the folding direction of the folding piece 323 relative to the surface of the heat exchange fin 31 can be set to be different from the protruding direction of other surface structures. Alternatively, other manufacturing methods may be adopted to form the folding pieces 323 on the surface of the heat exchanging fin 31, which is not limited in this application.
As shown in fig. 10, the flap 323 is connected to the heat exchange fin 31 by a connection line 324, and the connection line 324 is disposed around the tube hole 316 to guide air as the air flows through the heat exchange tube 32, suppress separation of air on the leeward side of the heat exchange tube 32, and reduce the area of a wake region.
Further, the higher the height of the flap 323, the greater the wind resistance provided by the flap 323. Therefore, the height of the flap 323 relative to the main surface of the heat exchange fin 31 can be set gradually larger in the direction from the windward side to the leeward side of the heat exchange tube 32 to reduce the wind resistance near the windward side while enhancing the turbulent flow effect of the flap 323.
Optionally, in one embodiment, the flap 323 is folded over an area defined by the connecting line 324 and a cut line 325 on a side of the connecting line 324 facing away from the tube aperture 316.
Specifically, as shown in fig. 10, the cut line 325 includes a first cut line 3251 and a second cut line 3252, wherein one end of the first cut line 3251 is connected to an end of the connection line 324 near the windward side of the heat exchange tube 32, the other end of the first cut line 3251 is connected to another end of the connection line 324 near the leeward side of the heat exchange tube 32 by the second cut line 3252, and the first cut line 3251 and the connection line 324 are separated from each other in a direction from the windward side to the leeward side of the heat exchange tube 32, so that the height of the flap 323 gradually increases in a direction from the windward side to the leeward side of the heat exchange tube 32 after the flap 323 is folded over the heat exchange fin 31.
In other embodiments, the shape of the flap 323 can also take other shapes, such as a triangle, a regular or irregular polygon, and the height of the flap 323 can also be set constant or have other variations.
Further, since the flap 323 disposed on the windward side of the heat exchange tube 32 may cause the pressure drop level on the windward side to be increased, in an embodiment, an angle α 3 between a connecting line between an end point of the connecting line 324 of the flap 323 and the heat exchange fin 31 near the windward side of the heat exchange tube 32 and the center of the tube hole 316 and the windward direction D7 of the heat exchange tube 32 may be set to be 90-110 degrees, so as to reduce the resistance of the windward side of the flap 323 and reduce the pressure drop level. Further, the included angle α 4 between the connecting line between the two end points of the connecting line 324 between the flap 323 and the heat exchange fin 31 and the center of the tube hole 316 can be set to 47-56 degrees.
Further, in an embodiment, the connecting line 324 between the folding piece 323 and the heat exchange fin 31 may be configured as an arc, the tube hole 316 is configured as a circular hole, and the circle center of the arc where the connecting line 324 is located coincides with the circle center of the tube hole 316, so that the folding piece 323 and the heat exchange tube 32 are approximately arranged at equal intervals, and further the turbulence effect of the folding piece 323 on the leeward side of the heat exchange tube 32 is improved.
Optionally, in a specific embodiment, the ratio of the radius R2 of the connecting line 324 between the flap 323 and the heat exchanging fin 31 to the radius R1 of the tube hole 316 is 1.19-1.34, so as to further enhance the turbulent flow effect.
6. Pipe diameter optimization
Referring to fig. 11-12, fig. 11-12 are schematic cross-sectional views of two variations of the heat exchanger 30 described above. The tube diameter of the heat exchange tube 32 is optimized in the following aspects with reference to fig. 11 to 12:
6.1 combination of different pipe diameters
Referring first to fig. 5, in the heat exchanger 30 described above, the cross-sectional shape of the heat exchange tube 32 and the cross-sectional shape of the tube hole 316 are both circular on a reference section formed by a plane of the main surface of the heat exchange fin 31, and the tube hole 316 provided on the heat exchange fin 31 has a substantially uniform tube diameter, so that the heat exchange tube 32 and the heat exchange fin 31 are more tightly connected to facilitate heat transfer.
Because the heat exchange medium in the heat exchange tube 32 can take place the phase transition when evaporating or condensing in the heat exchange tube 32, gaseous phase and liquid phase volume ratio can change gradually, and gaseous phase and liquid phase specific volume differ 20 ~ 30 times for the velocity of flow of heat exchange medium takes place great change in the heat exchange tube 32 of the same pipe diameter before and after the phase transition, and then influences heat transfer and the flow resistance of heat exchange medium in the heat exchange tube 32.
Therefore, in this embodiment, in order to better adapt to the specific volume change and the pressure change of the heat exchange medium during the evaporation or condensation process, it is ensured that the heat exchange medium can be in a state with a high heat exchange coefficient no matter in a liquid state, a two-phase state and a gas state, and the flow resistance can be effectively reduced, so as to improve the heat exchange capacity of the heat exchanger 30 and the energy efficiency of the air conditioner, the combination of the heat exchange tubes 32 with different tube diameters can be used, so that the heat exchange medium sequentially flows through the heat exchange tubes 32 with different tube diameters during the evaporation or condensation.
Because the heat exchange medium in the heat exchange tube 32 flows in the heat exchange tube 32, the heat exchange tube 32 near the windward side first contacts the airflow, the heat exchange medium gradually evaporates under the action of the airflow, and the volume continuously changes, in this embodiment, the aperture of at least part of the tube hole 316 near the leeward side contour line (first side contour line 311) may be larger than the aperture of at least part of the tube hole 316 near the windward side contour line (second side contour line 312). At this time, because the shape of the heat exchange tube 32 is consistent with the shape of the tube hole 316, the heat exchange tube 32 also generates corresponding changes to better adapt to the specific volume change and the pressure change of the heat exchange medium in the evaporation or condensation process, ensure that the heat exchange medium is in a state with high heat exchange coefficient no matter in a liquid state, a two-phase state and a gas state, and effectively reduce the flow resistance of the heat exchange medium, thereby improving the heat exchange capacity of the heat exchanger 30 and the energy efficiency of the air conditioner.
Specifically, as described above, the heat exchanging fin 31 has the first side contour 311 and the second side contour 312 spaced apart 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.
Alternatively, in one embodiment, the aperture of the tube hole 316 may be arranged to increase gradually in a direction from the windward side contour to the leeward side contour, i.e., in a direction from the second side contour 312 to the first side contour 311.
For example, in one embodiment, the apertures of the tube holes 316 disposed on the leeward side of the contour may be larger than the apertures of the tube holes 316 disposed on the windward side of the contour.
Specifically, as described above, at least two rows of tube holes 316 are arranged in rows in the heat exchange fin 31 in the direction along the interval between the windward side contour line and the leeward side contour line, each row of tube holes 316 is arranged at intervals along the arrangement curve formed by the first side contour line 311 or the second side contour line 312 after being translated along the line l3 where the peak width is located, and the tube holes 316 in different rows are arranged at intervals along the arrangement line formed in parallel with the line l3 where the peak width of the heat exchange fin 31 is located.
Therefore, in an embodiment, in the pipe holes 316 arranged along the same alignment line, the hole diameter of the pipe hole 316 may be gradually increased in a direction from the second side contour 312 to the first side contour 311.
For example, as shown in fig. 11, in the direction of the interval from the second side contour 312 to the first side contour 311, the number of rows of the tube holes 316 provided in the middle region is three, and the number of rows of the tube holes 316 provided in the end regions at both ends of the middle region is two. The aperture of the row of pipe holes 316 close to the second side contour line 312 is smaller than the aperture of the row of pipe holes 316 close to the first side contour line 311, and the aperture of the row of pipe holes 316 arranged between the two rows of pipe holes 316 may be smaller than or equal to the aperture of the row of pipe holes 316 close to the first side contour line 311, so as to implement the aperture change of the pipe holes 316.
Alternatively, in one embodiment, the aperture of the tube hole 316 may be set to 4-7 mm.
Further, the aperture of the array of pipe holes 316 near the second side contour 312 may be set to be 4mm to 5mm, and the aperture of the array of pipe holes 316 near the first side contour 311 may be set to be 6.35 mm to 7 mm.
Alternatively, in one embodiment, the hole center distance between adjacent tube holes 316 may be set to 12mm to 21 mm. The pitch between adjacent pipe holes 316 refers to a distance between pipe hole centers of two adjacent pipe holes 316. It is thus ensured that each heat exchange tube 32 inserted into the tube hole 316 can exhibit an optimum heat exchange performance. It will be appreciated that the center of the orifice 316 is the center of a circle when the orifice 316 is circular, and the center of the orifice 316 is the center of a geometric center when the orifice 316 is non-circular, such as elliptical or other shapes.
The hole center distances between the adjacent pipe holes 316 may be equal, the hole center distances between the adjacent pipe holes 316 may be different, or the hole center distances between the adjacent pipe holes 316 in a part of the area may be equal, and the hole center distances between the adjacent pipe holes 316 in a part of the area may be different.
Alternatively, in one embodiment, the center-to-center distance d16 of at least some adjacent pipe holes 316 in the row of pipe holes 316 near the second side contour 312 may be smaller than the center-to-center distance d17 of at least some adjacent pipe holes 316 in the row of pipe holes 316 near the first side contour 311 for accommodating larger-diameter heat exchange pipes 32, thereby ensuring that each heat exchange pipe 32 inserted into the pipe holes 316 can exert the best heat exchange performance.
For example, in one embodiment, at least some of the adjacent pipe apertures 316 in the row of pipe apertures 316 near one side of the second side contour 312 may be located at a center-to-center distance d16 of 12mm to 19mm, and the adjacent pipe apertures 316 in the row of pipe apertures 316 near the first side contour 311 may be located at a center-to-center distance d17 of 14mm to 21 mm.
Generally speaking, the wind field that the air current formed is including the high velocity of flow district that is located the middle part region and the low velocity of flow district that is located high velocity of flow district both sides, and the amount of wind in heat transfer fin 31 middle part region is greater than the regional amount of wind of tip, and heat transfer coefficient and the wind speed positive correlation of heat exchanger 30, the heat transfer effect of the heat exchange tube 32 in the middle part region is better, if the middle part region can make the heat transfer performance reduction of heat exchanger 30 air side with the regional pipe diameter that uses the size to equal of tip, and also can lead to the air-out temperature in middle part region and the tip region to differ great.
Further, as described above, the fin width of the heat exchange fin 31 becomes gradually smaller in the direction from the central region of the heat exchange fin 31 to the end regions on both sides of the central region, and therefore, in the present embodiment, in order to enhance the heat exchange performance of the heat exchanger 30, the aperture of at least part of the tube holes 316 of the central region may be set larger than the aperture of at least part of the tube holes 316 of the end regions. By the arrangement mode, the heat exchange tube 32 with a larger tube diameter can be further arranged in the middle area with a larger fin width so as to further increase the heat exchange area in the middle area, enhance the heat exchange performance of the heat exchanger 30, and simultaneously increase the flow resistance of air in the middle area, so that part of air flows to the end area with a small pressure difference; and in the low tip region of air flow velocity, use the heat exchange tube 32 of less pipe diameter, can reduce the flow resistance of air to maintain certain air flow velocity, make heat exchange tube 32 obtain abundant heat transfer, promote heat exchanger 30's whole heat transfer performance.
It is noted that the above-described variation in the aperture diameter of the orifice 316 between the first side contour 312 and the second side contour 312 and from the middle region to the end region may be used alone or in combination. Thus, alternatively, in one embodiment, the apertures 316 in the middle region may be set equal in diameter, the apertures 316 in the end regions may be set equal in diameter, and the apertures 316 in the middle region may be set greater in diameter than the apertures 316 in the end regions. Alternatively, in another embodiment, the apertures of the tube holes 316 may be arranged to decrease gradually in a direction from the middle region to the end regions.
Further, in an embodiment, among the pipe holes 316 arranged along the same alignment curve, the pipe holes 316 may be arranged such that the hole diameters thereof gradually decrease in a direction from the middle region to the end regions.
In summary, one or a combination of the two methods can ensure that the middle area has a large enough heat exchange area, and can effectively reduce the flow resistance of the heat exchange medium, thereby improving the heat exchange capacity of the heat exchanger 30.
6.2 tubular changes
In the heat exchanger 30 using the circular heat exchange tube 32, when the air current flows through the heat exchange tube 32, a heat exchange dead zone is easily generated on the leeward side of the circular heat exchange tube 32, and the heat exchange effect of the heat exchange fins 31 in the heat exchange dead zone is poor. Further, the narrow tube spacing between adjacent circular heat exchange tubes 32 results in increased ventilation resistance as the air flow passes through the narrow passages.
Therefore, as shown in fig. 12, in the present embodiment, the heat exchange tubes 32 are provided as flat tubes. Because the area of the heat transfer blind spot of the lee side of flat pipe is less, and the tube space between the adjacent flat pipes is great, can form great air current way, consequently, can reduce the heat transfer blind spot, reinforcing heat transfer effect to can reduce the flow resistance of air current.
Alternatively, in one embodiment, the tube hole 316 for passing the heat exchange tube 32 may have a major axis direction D8 and a minor axis direction D9, and the major axis dimension D18 of the tube hole 316 in the major axis direction D8 is greater than the minor axis dimension D19 in the minor axis direction D9. At this time, since the shape of the heat exchange pipe 32 is identical to the shape of the pipe hole 316, the heat exchange pipe 32 also needs to be changed accordingly.
Since the angle parameter between the long axis direction D8 and the wind entering direction D10 directly affects the area of the heat exchange dead zone on the leeward side of the heat exchange tube 32 and the flow resistance of air, in this embodiment, in order to reduce the area of the heat exchange dead zone on the leeward side of the heat exchange tube 32 and the flow resistance of air, the included angle between the long axis direction D8 and the wind entering direction D10 needs to be set reasonably.
Specifically, in the present embodiment, the long axis direction D8 of the tube hole 316 and the windward side contour line (the second side contour line 312) form an intersection, and by setting the included angle α 5 between the tangential direction of the intersection and the long axis direction D8 to be 70 to 110 degrees, the long axis direction D8 of the tube hole 316 and the windward direction D10 can be better matched, so as to reduce the area of the heat exchange dead zone on the leeward side of the heat exchange tube 32 and the flow resistance of air.
Further, since 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 an angle between a tangent of the second side contour line 312, i.e., the windward side contour line, and the straight line l3 of the peak width becomes gradually smaller in a direction from the middle region to the end region, an angle between the long axis direction D8 of the pipe hole 316 and the straight line l3 of the peak width may be set to gradually increase, thereby further better matching with the wind entering direction D10.
Further, the heat exchange tube 32 in the middle region has a good heat exchange effect and a large flow resistance of the heat exchange medium. Therefore, when the heat exchanger is used specifically, the setting modes of the long axis dimension d18 and/or the short axis dimension d19 of the flat tubes can be set differentially by referring to the above-described setting mode of the pipe diameter of the circular heat exchange tube 32, so that the above-described heat exchange effect is enhanced, and the flow resistance of the heat exchange medium in the heat exchange tube 32 is reduced. In the present embodiment, the distance between the centers of the adjacent pipe holes 316 specifically refers to the distance between the geometric centers of the adjacent heat exchange pipes 32.
Specifically, the heat exchange effect of the heat exchange tube 32 is mainly related to parameters such as the major axis dimension d18 and the minor axis dimension d19 of the heat exchange tube 32, so that the heat exchange effect of the heat exchange tube 32 in the middle region can be stronger than that of the heat exchange tube 32 in the end region by adjusting one or more of the above parameters.
For example, the major axis dimension d18 of at least some of the tube apertures 316 in the central region may be greater than the major axis dimension d18 of at least some of the tube apertures 316 in the end regions, and/or the minor axis dimension d19 of at least some of the tube apertures 316 in the central region may be greater than the minor axis dimension d19 of at least some of the tube apertures 316 in the end regions.
Further, the flow resistance of the heat exchange medium within the heat exchange tube 32 is primarily related to parameters such as the major axis dimension d18 and the minor axis dimension d19 of the heat exchange tube 32, and thus the flow resistance of the heat exchange medium within the heat exchange tube 32 can be reduced by adjusting one or more of the above parameters.
For example, the major axis dimension d18 of at least some of the tube apertures 316 near the leeward side contour may be greater than the major axis dimension d18 of at least some of the tube apertures 316 near the windward side contour, and/or the minor axis dimension d19 of at least some of the tube apertures 316 near the leeward side contour may be greater than the minor axis dimension d19 of at least some of the tube apertures 316 near the windward side contour.
In one embodiment, the arrangement of the orifices 316 follows the arrangement described above. That is, at least two rows of tube holes 316 are arranged on the heat exchange fin 31, the at least two rows of tube holes 316 are arranged at intervals along the interval direction of the second side contour line 312 and the first side contour line 311, each row of tube holes 316 are arranged at intervals along an arrangement curve formed by translating the second side contour line 312 or the first side contour line 311, and the tube holes 316 in different rows are further arranged at intervals along an arrangement straight line parallel to the straight line where the peak width of the heat exchange fin 31 is located. At this time, in the tube holes 316 arranged along the same alignment line, the major axis dimension d18 and/or the minor axis dimension d19 of the tube holes 316 gradually increase in the direction from the second side contour line 312 to the first side contour line 311, and in the tube holes 316 arranged along the same alignment curve, the major axis dimension d18 and/or the minor axis dimension d19 of the tube holes 316 gradually decrease in the direction from the middle region to the end regions.
Alternatively, in one embodiment, as shown in FIG. 12, the heat exchange tube 32 can be provided with a major dimension d18 of 5-12mm and the heat exchange tube 32 can be provided with a minor dimension d19 of 0.8-3 mm.
Alternatively, in one embodiment, the tube spacing between adjacent tube holes 316 may be set to 7mm to 16 mm. It is thus ensured that each heat exchange tube 32 inserted into the tube hole 316 can exhibit an optimum heat exchange performance.
Optionally, in a specific embodiment, a plurality of microchannels arranged at intervals along the long axis direction D8 may be further disposed inside the heat exchange tube 32 to further improve the heat exchange performance of the heat exchange tube 32.
It should be noted that the shape, fin width and arrangement of the tube holes 316 of the heat exchange fins 31 in fig. 11 and 12 can be set in various manners as described above, and will not be described in detail herein.
7. Auxiliary matching mechanism
The present application will further optimize the secondary engagement mechanism of the heat exchanger 30 in conjunction with fig. 13-20.
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.
7.1. Side plate support
Referring to fig. 13-16, 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.
Alternatively, in the specific embodiment, when the heat exchange fins 31 are arranged in a V shape or a straight shape, the lugs 68 in other shapes may also be arranged according to the shape of the edge of the support plate 82, and the embodiment of the present invention is not limited in particular.
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.
7.2. 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. 17 to 19, in the present embodiment, the insertion slot 72 is configured to be capable of adapting to at least two different arrangement modes of the U-shaped pipe section 327, so that when the arrangement mode 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. 18, 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. 19, 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 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 (12)

1. A heat exchange fin, comprising:
a first side contour line; and
the first side contour line and the second side contour line are spaced from each other, the second side contour line is arranged in a bending mode towards the first side contour line, and the first side contour line is arranged in a bending mode towards the direction deviating from the second side contour line;
wherein, heat transfer fin's fin width follow heat transfer fin's middle part is regional to the tip region's of the regional both sides in middle part orientation diminishes gradually, first side profile line includes:
the vertical distance from the first reference point to a straight line where the peak width of the heat exchange fin is located is 25% of the overall height of the heat exchange fin, and the ratio of the fin width at the first reference point to the peak width of the heat exchange fin is 0.64-0.96; and
and the vertical distance from the second reference point to a straight line where the peak width of the heat exchange fin is located is 45% of the overall height of the heat exchange fin, the ratio of the fin width at the second reference point to the peak width of the heat exchange fin is 0.54-0.80, and the fin width at the second reference point is smaller than the fin width at the first reference point.
2. The heat exchange fin according to claim 1, wherein the first side profile line has a third reference point, the vertical distance from the third reference point to a straight line where the peak width of the heat exchange fin is located is 35% of the overall height of the heat exchange fin, the ratio of the fin width at the third reference point to the peak width of the heat exchange fin is 0.60-0.89, and the fin width at the third reference point is smaller than the fin width at the first reference point and larger than the fin width at the second reference point.
3. The heat exchange fin according to claim 2,
the first side contour line is arranged on two sides of a straight line where the peak width of the heat exchange fin is located and respectively comprises:
a first arc segment;
a second arc segment; and
the first arc section, the second arc section and the first straight line section are sequentially connected in the direction from the middle area to the end area;
the second side contour lines respectively comprise the following two sides of the straight line where the peak width of the heat exchange fin is located:
a third arc segment;
a fourth arc segment; and
a second straight line segment, the third arc segment, the fourth arc segment and the second straight line segment are sequentially connected from the middle region to the end region,
when the first side contour line is translated along the straight line where the peak width is located, the first arc section and the second arc section can coincide with the third arc section and the fourth arc section respectively, the first straight line section and the second straight line section can coincide at least partially, the first reference point is located on the second arc section, the second reference point and the third reference point are located on the first straight line section, the intersection point of the straight line where the fin width at the first reference point is located and the second side contour line is located on the third arc section, the intersection point of the straight line where the fin width at the second reference point is located and the second side contour line is located on the second straight line section, and the intersection point of the straight line where the fin width at the third reference point is located and the second side contour line is located on the fourth arc section.
4. The heat exchange fin according to claim 3, wherein two intersection points formed by the perpendicular bisector of the peak width and the first side contour line are respectively located on the second arc section of the first side contour line, and the ratio of the linear distance of the two intersection points to the overall height of the heat exchange fin is 0.46-0.56.
5. The heat exchange fin according to claim 2, wherein the opening angle of the first side contour line is 95-120 degrees, and the ratio of the included angle of the end tangent of the first side contour line to the opening angle is 0.7-0.85.
6. The heat exchange fin according to claim 2, wherein the heat exchange fin is provided with tube holes in rows, the number of rows of the tube holes in the middle region is greater than the number of rows of the tube holes in the end regions in the direction of the interval between the first side contour line and the second side contour line, and the height of the middle region is 25% -50% of the overall height of the heat exchange fin.
7. The heat exchange fin of claim 6, wherein the fin width of the central region is K1 xn 1 xd, the fin width of the end regions is K2 xn 2 xd, n1 and n2 are the number of rows of tube holes in the central region and the end regions, respectively, D is the terminal tube hole row spacing of the heat exchange fin, and K1 and K2 are coefficients of variation ranging from 0.8 to 1.2.
8. The heat transfer fin of claim 6, further comprising a plurality of heat transfer enhancement structures disposed thereon, wherein the heat transfer enhancement structures in the end regions have a greater heat transfer enhancement capability than the heat transfer enhancement structures in the central region; the end region includes:
an upper end region located on an upper side of the middle region; and
a lower end region located below the middle region, wherein a drainage capacity of the heat transfer enhancement structure in the lower end region is greater than a drainage capacity of the heat transfer enhancement structure in the upper end region.
9. The heat exchange fin according to claim 6, wherein the number of rows of tube holes is at least two, the at least two rows of tube holes are arranged at intervals along the interval direction of the first side contour line and the second side contour line, wherein a plurality of rows of spaced thermal structures are further arranged on the heat exchange fin in rows, each row of spaced thermal structures is arranged between two adjacent rows of the tube holes, and wherein the wind resistance of the row spaced thermal structures in the middle area is smaller than that of the row spaced thermal structures in the end areas.
10. The heat exchange fin according to claim 6, further comprising a vortex generator disposed on the heat exchange fin, wherein the vortex generator is used for reducing the area of a wake region on the leeward side of the heat exchange tube inserted into the tube hole, and the vortex generator is a flap integrally formed with the heat exchange fin and folded over with respect to the heat exchange fin, or a convex hull integrally formed with the heat exchange fin and protruding with respect to the heat exchange fin.
11. A heat exchanger, characterized in that the heat exchanger comprises a heat exchange tube and a heat exchange fin as recited in any one of claims 1 to 10, the heat exchange tube being disposed through the heat exchange fin.
12. An air conditioning apparatus, characterized in that it comprises a heat exchanger according to claim 11.
CN202010486871.4A 2020-06-01 2020-06-01 Heat exchange fin, heat exchanger and air conditioning device Pending CN113758359A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202010486871.4A CN113758359A (en) 2020-06-01 2020-06-01 Heat exchange fin, heat exchanger and air conditioning device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202010486871.4A CN113758359A (en) 2020-06-01 2020-06-01 Heat exchange fin, heat exchanger and air conditioning device

Publications (1)

Publication Number Publication Date
CN113758359A true CN113758359A (en) 2021-12-07

Family

ID=78782269

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202010486871.4A Pending CN113758359A (en) 2020-06-01 2020-06-01 Heat exchange fin, heat exchanger and air conditioning device

Country Status (1)

Country Link
CN (1) CN113758359A (en)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107843030A (en) * 2017-11-22 2018-03-27 广东美的制冷设备有限公司 Indoor heat exchanger, indoor apparatus of air conditioner and air conditioner
CN110701942A (en) * 2019-10-23 2020-01-17 广东美的暖通设备有限公司 Heat exchanger fin, heat exchanger, indoor unit and air conditioner

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107843030A (en) * 2017-11-22 2018-03-27 广东美的制冷设备有限公司 Indoor heat exchanger, indoor apparatus of air conditioner and air conditioner
CN110701942A (en) * 2019-10-23 2020-01-17 广东美的暖通设备有限公司 Heat exchanger fin, heat exchanger, indoor unit and air conditioner

Similar Documents

Publication Publication Date Title
US6308527B1 (en) Refrigerant evaporator with condensed water drain structure
US20060237178A1 (en) Heat exchanger
US20070107890A1 (en) Heat exchanger and method for the production thereof
US20130068437A1 (en) Tube for Heat Exchanger, Heat Exchanger, and Method for Manufacturing Tube for Heat Exchanger
CN109813146B (en) Fin for heat exchanger, heat exchanger and air conditioner outdoor unit
WO2023246447A1 (en) Finned tube with pipe-fin bridge for airflow in zones
CN113758359A (en) Heat exchange fin, heat exchanger and air conditioning device
CN213120241U (en) Heat exchanger
CN213120240U (en) Heat exchanger
CN213066335U (en) Air duct type air conditioner
CN112240610B (en) Air duct type air conditioner
CN115790237A (en) Heat exchange fin structure, heat exchange tube and heat exchanger
CN213066336U (en) Air duct type air conditioner
CN113757809B (en) Air duct type air conditioner
CN210119132U (en) A fin, heat exchanger and air condensing units for heat exchanger
CN113757808B (en) Air duct type air conditioner
CN113757807B (en) Air duct type air conditioner
CN213811914U (en) Heat exchange fin, heat exchanger and air conditioning device
CN112240723B (en) Heat exchange fin and air duct type air conditioner
CN213811913U (en) Heat exchange fin, heat exchanger and air conditioning device
CN211925909U (en) Heat exchanger for air conditioner indoor unit and air conditioner indoor unit
CN106197095B (en) Heat exchanger
CN113758354A (en) Heat exchange fin, heat exchanger and air conditioning device
CN113758360A (en) Heat exchange fin, heat exchanger and air conditioning device
CN113758355A (en) Heat exchange fin, heat exchanger and air conditioning device

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination