CN113757807A - Air duct type air conditioner - Google Patents

Air duct type air conditioner Download PDF

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Publication number
CN113757807A
CN113757807A CN202010486368.9A CN202010486368A CN113757807A CN 113757807 A CN113757807 A CN 113757807A CN 202010486368 A CN202010486368 A CN 202010486368A CN 113757807 A CN113757807 A CN 113757807A
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China
Prior art keywords
heat exchange
fin
side contour
contour line
line
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Granted
Application number
CN202010486368.9A
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Chinese (zh)
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CN113757807B (en
Inventor
韦福权
罗彬�
周柏松
李兆辉
李丰
李运志
李跃飞
吴彦东
马丽华
吴淋
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
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Midea Group Co Ltd
GD Midea Heating and Ventilating Equipment Co Ltd
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Priority to CN202010486368.9A priority Critical patent/CN113757807B/en
Publication of CN113757807A publication Critical patent/CN113757807A/en
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Publication of CN113757807B publication Critical patent/CN113757807B/en
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    • 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Abstract

The invention discloses an air duct type air conditioning device which comprises a shell, heat exchange fins and a fan assembly. The casing forms an accommodation chamber, and heat transfer fin sets up in the accommodation intracavity, and fan and the heat transfer fin of fan subassembly set up along first direction interval. The first pressure expansion plate and the second pressure expansion plate of the volute are arranged at intervals along a second direction which is perpendicular to the first direction and parallel to the main surfaces of the heat exchange fins so as to guide airflow generated by the fan to flow into the accommodating cavity through the air outlet of the volute. In the direction from the fan to the heat exchange fins, the first pressure expansion plate inclines towards the direction towards the second pressure expansion plate, and the second pressure expansion plate inclines towards the direction deviating from the first pressure expansion plate. On a reference cross section formed by the plane of the main surface of the heat exchange fin, the included angle between the first pressure expansion plate and the first direction is 6-9 degrees, and the included angle between the second pressure expansion plate and the first direction is 20-24 degrees. By the mode, the uniformity of the flow velocity distribution of the air flow flowing through the heat exchange fins can be improved.

Description

Air duct type air conditioner
Technical Field
The invention relates to the technical field of air conditioners, in particular to an air duct type air conditioner device.
Background
The air pipe type air conditioner (called air pipe machine for short) is one kind of indoor unit of air conditioner, because its installation mode is concealed, it is easy to implement the aesthetic property of home decoration, and occupies a place in the domestic air conditioner market.
A ducted air conditioning unit generally includes a housing, a heat exchanger disposed within the housing, and a fan assembly. When the air pipe type air conditioning device operates, air flow generated by rotation of the fan assembly enters the shell, exchanges heat with the heat exchanger in the process of flowing through the heat exchanger, and finally flows out of the shell, so that temperature adjustment of an installation area is achieved.
At present, a fan assembly of the air duct type air conditioning device mainly adopts a volute design of a traditional fan, so that the uniformity of the flow velocity distribution of air flow flowing through a heat exchanger is poor, and the overall heat exchange performance of the air duct type air conditioning device is influenced.
Disclosure of Invention
The invention provides an air duct type air conditioning device, which aims to solve the technical problem that the uniformity of the flow velocity distribution of air flow flowing through a heat exchanger in the air duct type air conditioning device is poor.
In order to solve the technical problems, the invention adopts a technical scheme that: the utility model provides a tuber pipe air conditioning equipment, includes casing, heat transfer fin and fan subassembly. The shell is used for forming an accommodating cavity. The heat exchange fins are arranged in the accommodating cavity, the fan assembly comprises a volute and a fan arranged in the volute, and the fan and the heat exchange fins are arranged at intervals in a first direction. The volute comprises a first pressure expansion plate and a second pressure expansion plate, wherein the first pressure expansion plate and the second pressure expansion plate are arranged at intervals along a second direction perpendicular to the first direction and parallel to the main surfaces of the heat exchange fins so as to guide airflow generated by the fan to flow into the accommodating cavity through an air outlet of the volute. In the direction from the fan to the heat exchange fins, the first pressure expansion plate inclines towards the direction towards the second pressure expansion plate, and the second pressure expansion plate inclines towards the direction deviating from the first pressure expansion plate. On a reference cross section formed by the plane of the main surface of the heat exchange fin, the included angle between the first pressure expansion plate and the first direction is 6-9 degrees, and the included angle between the second pressure expansion plate and the first direction is 20-24 degrees.
Through the mode, the included angle of the first pressure expansion plate and the second pressure expansion plate relative to the interval direction of the fan and the heat exchange fins is optimized, and the uniformity of the flow velocity distribution of the air flow flowing through the heat exchange fins is improved.
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.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Reference herein to "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment can be included in at least one embodiment of the application. The appearances of the phrase in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments. It is explicitly and implicitly understood by one skilled in the art that the embodiments described herein can be combined with other embodiments.
Referring to fig. 1 and 2, fig. 1 is a schematic cross-sectional view of an air duct type air conditioner according to an embodiment of the present invention, and fig. 2 is a side view of a heat exchange fin according to an embodiment of the present invention. As shown in fig. 1, the air duct type air conditioner of the present embodiment mainly includes a casing 10, a fan assembly 20, and a heat exchanger 30. The housing 10 is used for forming a receiving cavity 11, and the heat exchanger 30 is disposed in the receiving cavity 11. In the present embodiment, the heat exchanger 30 includes a plurality of heat exchange fins 31 arranged at intervals from each other and heat exchange tubes 32 penetrating the heat exchange fins 31. Since the section shown in fig. 1 is a reference section formed by a plane of the main surfaces of the heat exchange fins 31, only one heat exchange fin 31 is shown in fig. 1, and the remaining heat exchange fins 31 are arranged at intervals from the heat exchange fins 31 shown in fig. 1 in a direction perpendicular to the paper surface on which fig. 1 is drawn. The heat exchange fin 31 is generally formed by press molding from a sheet material, and the main surfaces of the heat exchange fin 31 are two side surfaces which are spaced from each other in the thickness direction of the heat exchange fin 31 and have the largest surface area.
The fan assembly 20 includes a volute 21 and a fan 22 disposed in the volute 21, and an air flow generated by the fan 20 flows into the accommodating chamber 11 through an air outlet 211 of the volute 21 under the action of the volute 21 and is blown and swept on the heat exchanger 30. The heat exchange medium flowing in the heat exchange tube 32 exchanges heat with the air flow flowing through the heat exchanger 30 through the heat exchange tube 32 and the heat exchange fins 31, and then cools or heats the air flow flowing through the heat exchanger 30 as required. The airflow after heat exchange by the heat exchanger 30 further flows out through the air outlet 101 of the housing 10.
The present application further optimizes the following aspects based on the overall structure of the air duct type air conditioner described above:
1. volute air outlet angle
In the present embodiment, the fan 22 and the heat exchanging fin 31 are arranged at a distance in the direction D1. The scroll casing 21 includes a first pressure expanding plate 212 and a second pressure expanding plate 213, and the first pressure expanding plate 212 and the second pressure expanding plate 213 are arranged at intervals in the direction D2. The direction D2 is perpendicular to the direction D1 and parallel to the major surfaces of the heat exchanger fins 31. Further, in the direction from the fan 22 to the heat exchange fins 31, the first diffuser plate 212 is inclined toward the second diffuser plate 213, and the second diffuser plate 213 is inclined away from the first diffuser plate 212.
It is noted that, in the normal installation and use state of the air duct type air conditioner of the present application, the direction D1 is generally a horizontal direction, the direction D2 is generally a vertical direction (i.e., a gravity direction), and the first diffuser plate 212 is located on the upper side of the second diffuser plate 213. The relative positional relationships of "up", "down", "front", "back" and the like mentioned in the present application are also the relative positional relationships of the air duct type air conditioning device in the normal installation and use states.
The first pressure expanding plate 212 and the second pressure expanding plate 213 are used for guiding the airflow generated by the fan 22 to flow into the accommodating chamber 11 through the air outlet 211 of the scroll casing 21, and converting the speed energy of the airflow into pressure energy through the shape change of the flow passage between the first pressure expanding plate 212 and the second pressure expanding plate 213, thereby increasing the pressure of the airflow at the air outlet 211. Therefore, the angle parameters of the first and second pressure expanding plates 212 and 213 directly affect the uniformity of the flow velocity distribution of the air flow passing through the heat exchange fins 31.
Therefore, in the present embodiment, in order to obtain a better uniformity of the flow velocity distribution, the included angle β 1 between the first diffuser plate 212 and the direction D1 is set to 6 to 9 degrees, and the included angle β 2 between the second diffuser plate 213 and the direction D1 is set to 20 to 24 degrees, on the reference cross section formed by the plane of the main surfaces of the heat exchanging fins 31. In one embodiment, the included angle β 1 is set to 6-8 degrees and β 2 is set to 21-23 degrees. It is noted that, unless otherwise indicated, all numerical ranges recited herein are intended to be inclusive.
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 a specific implementationIn the embodiment, based on the above-mentioned setting range of the angle β 3, the linear distance d5 between the intersection E5 and the intersection E3 formed by the straight line l3 in which the peak width is located and the second side contour 312, and the peak width W are further set to be equal to each othermaxThe 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. It is noted that when the first side contour 311 and the second side contour 312 have a curved shape, the line l3 where the peak width is located is generally a straight line connecting the vertices of the first side contour 311 and the second side contour 312. When the fin is provided with a plurality of connecting lines with the largest width, the straight line where the connecting line in the middle is located is selected as the straight line l3 where the peak width is located.
In this embodiment, the first side contour 311 and the second side contour 312 are further configured to be translationally coincident. Specifically, the first side contour 311 is made flat along the line l3 where the peak width is located toward the second side contour 312Width W of shift peakmaxThen, 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 the area of the main surface of the heat exchange fin 31 is relatively largeSmaller, the overall heat exchange performance of the heat exchange fins 31 becomes worse. 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 wind field flow velocity cannot be realized, and if the included angle α 2 of the tangent line at the end of the first side contour line 311 is too small, the fin width at the end of the heat exchange fin 31 is relatively small, which results in the deterioration of the 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 fin width of the heat exchange fin 31 is further increased from the middle region to the end portionThe change rule in the direction of the area is 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 the fin width W1 at reference point E11 and greater than the 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.
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 (10)

1. An air duct type air conditioning apparatus, characterized by comprising:
the shell forms an accommodating cavity;
the heat exchange fins are arranged in the accommodating cavity;
the fan assembly comprises a volute and a fan arranged in the volute, the fan and the heat exchange fins are arranged at intervals along a first direction, the volute comprises a first pressure expansion plate and a second pressure expansion plate, the first pressure expansion plate and the second pressure expansion plate are arranged at intervals along a second direction which is perpendicular to the first direction and parallel to the main surfaces of the heat exchange fins so as to guide airflow generated by the fan to flow into the accommodating cavity through an air outlet of the volute, the first pressure expansion plate is inclined towards the second pressure expansion plate in the direction from the fan to the heat exchange fins, and the second pressure expansion plate is inclined towards the direction away from the first pressure expansion plate;
on a reference cross section formed by a plane where the main surfaces of the heat exchange fins are located, an included angle between the first pressure expansion plate and the first direction is 6-9 degrees, and an included angle between the second pressure expansion plate and the first direction is 20-24 degrees.
2. The air duct type air conditioning apparatus according to claim 1, wherein the first direction is a horizontal direction, the second direction is a vertical direction, and the first diffuser plate is located on an upper side of the second diffuser plate.
3. The air duct type air conditioner according to claim 1, wherein said heat exchanging fin includes a first side contour line and a second side contour line spaced apart from each other, wherein the first side contour line is taken as a leeward side contour line, the second side contour line is taken as a windward side contour line, the extension line of the first pressure expansion plate and the second side contour line intersect at a first intersection point, the extension line of the second pressure expansion plate and the second side contour line intersect at a second intersection point, the first intersection point has a first vertical distance to a first reference line passing through the uppermost ends of the heat exchange fins and parallel to the first direction, the second intersection point has a second perpendicular distance to a second reference line passing through the lowermost ends of the heat exchange fins and parallel to the first direction, the ratio of the sum of the first vertical distance and the second vertical distance to the height of the heat exchange fin along the second direction is 0.26-0.35.
4. The air duct type air conditioning unit according to claim 3, wherein a ratio of the first vertical distance to a height of the heat exchange fin in the second direction is 0.13 to 0.175, and a ratio of the second vertical distance to a height of the heat exchange fin in the second direction is 0.13 to 0.175.
5. The air duct type air conditioner according to claim 3, wherein the air duct type air conditioner satisfies the following formula:
L2＝ξ×(L1+L3×tgθ)；
wherein, theta is the contained angle between first diffuser plate and the second diffuser plate, tg is tangent trigonometric function, and L1 is the air outlet of spiral case is followed the height of second direction, and L2 is the heat transfer fin is followed the height of second direction, and L3 is the heat transfer fin is close to the tip of the air outlet of spiral case with the air outlet of spiral case is followed the distance of first direction, and xi is the preset coefficient of 1.3-1.6.
6. The air duct type air conditioning device according to claim 3, wherein the second side contour line is curved in a direction toward the first side contour line, the first side contour line is curved in a direction away from the second side contour line, and a ratio of a straight-line distance between projections of the first intersection point and the second intersection point on the first reference line or the second reference line to a width of the heat exchange fin in the first direction is less than or equal to 0.2.
7. The air duct type air conditioning device according to claim 6, wherein the fin width of the heat exchange fin is gradually reduced in a direction from the middle area to the end area of the heat exchange fin, a third intersection point formed by an angular bisector of an included angle between the first diffuser plate and the second diffuser plate and a straight line where the peak width of the heat exchanger fin is located on one side of the heat exchanger fin close to the fan, and a fourth intersection point formed by the angular bisector and a second side contour line of the heat exchange fin is located below the straight line where the peak width is located.
8. The air duct type air conditioning device according to claim 7, characterized in that a first reference point and a second reference point are provided on the first side contour line, a vertical distance from the first reference point to a straight line on which the peak width is located is 25% of the overall height of the heat exchange fin, a vertical distance from the second reference point to a straight line on which the peak width of the heat exchange fin is located is 45% of the overall height of the heat exchange fin, a ratio of the fin width at the first reference point to the peak width of the heat exchange fin is 0.64-0.96, a 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.
9. The air duct type air conditioning device according to claim 7, wherein the flare angle of the first side contour line is 80 to 135 degrees, the first side contour line comprises at least two arc sections and at least one straight line section which are sequentially connected in a direction from the middle region to the end region on both sides of a straight line where the peak width of the heat exchange fin is located, and the curvature radii of the at least two arc sections gradually increase in a direction from the middle region to the end region.
10. The ducted air conditioning unit according to claim 7, wherein the heat exchanging fins have pipe holes arranged in rows, the number of rows of the pipe holes in the middle region is greater than the number of rows of the pipe holes in the end regions in the direction of the interval between the first side contour line and the second side contour line, the ducted air conditioning unit further includes heat exchanging pipes, the heat exchanging pipes being inserted into the pipe holes;
the height of the middle area is 25% -50% of the overall height of the heat exchange fin, the fin width of the middle area is K1 xn 1 xd, the fin width of the end area is K2 xn 2 xd, n1 and n2 are the number of rows of the tube holes in the middle area and the end area respectively, D is the distance between rows of the tail end tube holes in the end area, and K1 and K2 are variation coefficients and range from 0.8 to 1.2.
CN202010486368.9A 2020-06-01 2020-06-01 Air duct type air conditioner Active CN113757807B (en)

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