WO2016074399A1 - 平行流换热器及具有其的空调器 - Google Patents

平行流换热器及具有其的空调器 Download PDF

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Publication number
WO2016074399A1
WO2016074399A1 PCT/CN2015/074393 CN2015074393W WO2016074399A1 WO 2016074399 A1 WO2016074399 A1 WO 2016074399A1 CN 2015074393 W CN2015074393 W CN 2015074393W WO 2016074399 A1 WO2016074399 A1 WO 2016074399A1
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Prior art keywords
heat exchanger
parallel flow
flat tube
flow heat
heat exchange
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PCT/CN2015/074393
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English (en)
French (fr)
Inventor
李丰
岑晓维
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广东美的制冷设备有限公司
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Publication of WO2016074399A1 publication Critical patent/WO2016074399A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular

Definitions

  • the present invention relates to the field of refrigeration equipment technology, and in particular to a parallel flow heat exchanger and an air conditioner having the same.
  • the parallel flow porous microchannel heat exchanger is an all-aluminum heat exchanger, which is widely used as a new type of heat exchanger for air conditioners.
  • air conditioners At present, whether it is automobile air conditioner or household air conditioner industry, most manufacturers use flat tubes of 16mm width and above, but parallel flow heat exchangers have higher cost, most of them are used for 2p and above models, and very small power machines are very It is difficult to have a cost advantage. With the current copper price, the traditional flat tube is difficult to replace the copper tube heat exchanger. The main performance is that although the parallel flow condenser is better than the copper tube heat exchanger, the cost is higher.
  • the present invention aims to solve at least one of the technical problems in the related art to some extent. To this end, the present invention proposes a parallel flow heat exchanger having the advantages of simple structure and high heat exchange efficiency.
  • the present invention also proposes an air conditioner having the parallel flow heat exchanger described above.
  • Two collecting pipes, the two collecting pipes are disposed at two ends of the flat pipe, and two ends of each of the heat exchange channels are respectively connected with the corresponding collecting pipes; and a plurality of heat dissipating fins a sheet, the plurality of heat dissipating fins being disposed between two adjacent flat tubes.
  • the material reduces the production cost, improves the heat exchange efficiency of the parallel flow heat exchanger, and makes the parallel flow heat exchanger suitable for the low-power air conditioner, thereby expanding the application range of the parallel flow heat exchanger.
  • each of the flat tubes has a height b and satisfies: 1.3 ⁇ b ⁇ 1.4 mm.
  • the inner circumferences of the two adjacent heat exchange channels The shortest distance between the walls is c and satisfies: 0.2 ⁇ c ⁇ 0.28 mm, and the side surface of the flat tube perpendicular to the height direction of the flat tube is a first side, the first side and the heat exchange passage
  • the shortest distance between the inner peripheral walls is d and satisfies: 0.23 ⁇ d ⁇ 0.31 mm, and the side surface of the flat tube perpendicular to the width direction of the flat tube is a second side, and the second side is replaced with the second side
  • the shortest distance between the inner peripheral walls of the hot aisle is e and satisfies: 0.2 ⁇ e ⁇ 0.7 mm.
  • the shortest distance between the inner peripheral walls of the two adjacent heat exchange passages is c, and the c satisfies: 0.23 ⁇ c ⁇ 0.25 mm.
  • a side surface of the flat tube perpendicular to a height direction of the flat tube is a first side, and between the first side surface and an inner peripheral wall of the heat exchange passage
  • the shortest distance is d, and the d satisfies: 0.26 ⁇ d ⁇ 0.28 mm.
  • a side surface of the flat tube perpendicular to a width direction of the flat tube is a second side, and between the second side surface and an inner peripheral wall of the heat exchange passage
  • the shortest distance is e, and the e satisfies: 0.4 ⁇ e ⁇ 0.5 mm.
  • the number of the heat exchange channels is N and satisfies: 8 ⁇ N ⁇ 10.
  • the header has an outer diameter of m and satisfies: 14 ⁇ m ⁇ 16 mm.
  • the collector has a wall thickness of n and satisfies: 1.0 ⁇ n ⁇ 1.2 mm.
  • the width of the heat dissipating fins is greater than or equal to the width of the flat tube.
  • the heat dissipating fin has a width f and satisfies: 10 ⁇ f ⁇ 11 mm.
  • an air conditioner comprising the parallel flow heat exchanger as described above is provided.
  • FIG. 1 is a schematic perspective view of a parallel flow heat exchanger according to an embodiment of the present invention
  • Figure 2 is a partial structural schematic view of the parallel flow heat exchanger of Figure 1;
  • Figure 3 is a plan view of the parallel flow heat exchanger of Figure 2;
  • Figure 4 is a plan view of the flat tube of Figure 3;
  • Figure 5 is a cross-sectional view of the header of Figure 1;
  • Figure 6 is a graph showing the outer diameter and heat exchange amount of the header of the parallel flow heat exchanger according to an embodiment of the present invention, wherein the X axis represents the outer diameter of the header (the outer diameter of the header) The unit of dimension is mm), and the Y axis in the figure indicates the heat exchange amount of the parallel flow heat exchanger (the unit of heat exchange amount is W);
  • Figure 7 is a graph of the outer diameter of the header and the charge of the refrigerant in the parallel flow heat exchanger according to an embodiment of the present invention, wherein the X axis represents the outer diameter of the header (the outer diameter of the header) The unit of size is mm), and the Y axis in the figure indicates the refrigerant charge of the parallel flow heat exchanger (the unit of refrigerant charge is g);
  • Figure 8 is a graph showing the width of the heat dissipating fins and the amount of refrigerant charge in the parallel flow heat exchanger according to an embodiment of the present invention, wherein the X axis indicates the width of the heat dissipating fins (the width of the fins is mm) In the figure, the Y axis represents the heat transfer amount of the parallel flow heat exchanger (the unit of heat exchange amount is W).
  • the collecting tube 120 and the heat dissipating fins 130 are identical to The collecting tube 120 and the heat dissipating fins 130.
  • a parallel flow heat exchanger 100 according to an embodiment of the present invention will be described in detail below with reference to the accompanying drawings.
  • a parallel flow heat exchanger 100 includes a plurality of flat tubes 110, two header tubes 120, and a plurality of heat dissipating fins 130.
  • a plurality of flat tubes 110 are spaced apart, and each of the flat tubes 110 is formed with a plurality of heat exchange channels 111 extending along the longitudinal direction of the flat tubes 110, and a plurality of heat exchange channels.
  • 111 is spaced apart along the width direction of the flat tube 110, and two collecting tubes 120 are disposed at two ends of the flat tube 110, and two ends of each heat exchange passage 111 are respectively connected with the corresponding collecting tube 120, and a plurality of heat dissipating fins 130 is disposed between two adjacent flat tubes 110.
  • a plurality of flat tubes 110 are spaced apart in the up and down direction (up and down direction as shown in FIG.
  • each flat tube 110 has a width direction of the flat tube 110 (eg, The front-rear direction shown in FIG. 1 is spaced apart, and each heat exchange passage 111 extends along the length direction of the flat tube 110, and the header 120 is disposed at both ends of the flat tube 110 extending in the longitudinal direction, and each heat exchange Both ends of the passage 111 are in communication with the corresponding header 120.
  • the header 120 on the left side communicates with the left end of the heat exchange passage 111
  • the header 120 on the right side communicates with the right end of the heat exchange passage 111.
  • the heat exchange efficiency of the parallel flow heat exchanger 100 can be improved, the structure of the parallel flow heat exchanger 100 can be simplified, the production materials can be saved, and the production cost can be reduced.
  • the parallel flow heat exchanger 100 can also be applied to a low-power air conditioner, thereby expanding the application range of the parallel flow heat exchanger 100.
  • each of the flat tubes 110 has a height b and satisfies: 1.3 ⁇ b ⁇ 1.4 mm. It has been experimentally verified that when the height of the flat tube 110 is 1.3 ⁇ b ⁇ 1.4 mm, the heat exchange efficiency of the parallel flow heat exchanger 100 is high. Considering that the number of heat exchange passages 111 on the flat tube 110 is also an important parameter affecting the heat exchange efficiency of the parallel flow heat exchanger 100, in a preferred example of the present invention, heat is exchanged on the same flat tube 110. The number of the channels 111 is N and satisfies: 8 ⁇ N ⁇ 10. Thereby, the heat exchange efficiency of the parallel flow heat exchanger 100 can be further improved.
  • the shortest distance between the inner peripheral walls of the adjacent two heat exchange passages 111 is c and satisfies: 0.2 ⁇ c ⁇ 0.28 mm
  • the side surface of the flat tube 110 perpendicular to the height direction of the flat tube 110 is the first side surface 112
  • the shortest distance between the first side surface 112 and the inner peripheral wall of the heat exchange passage 111 is d and satisfies: 0.23 ⁇ d ⁇ 0.31 mm
  • the side surface of the flat tube 110 perpendicular to the width direction of the flat tube 110 is the second side surface 113
  • the shortest distance between the second side surface 113 and the inner peripheral wall of the heat exchange passage 111 is e and satisfies: 0.2 ⁇ e ⁇ 0.7 Mm.
  • the "height direction” may refer to the up and down direction shown in FIG. 4
  • the "width direction” may refer to the front and rear direction shown in FIG.
  • the shortest distance c between the inner peripheral walls of the adjacent two heat exchange passages 111 on the flat tube 110, the first side surface 112 and the inner peripheral wall of the heat exchange passage 111 is a dimensional parameter of the flat tube 110, which has been proved by production practice to be 0.2 ⁇ c ⁇ 0.28 mm, 0.23 ⁇ d ⁇ When 0.31 mm and 0.2 ⁇ e ⁇ 0.7 mm, the flat tube 110 has a simple processing process, good structural strength, and low production cost.
  • the flat tube 110 In order to further simplify the processing of the flat tube 110, optimize the structural strength of the flat tube 110, and reduce the production cost of the flat tube 110, in a preferred example of the present invention, on the same flat tube 110, two adjacent ones are replaced.
  • the shortest distance between the inner peripheral walls of the hot runner 111 is 0.23 ⁇ c ⁇ 0.25 mm. It is verified by experiments that when 0.23 ⁇ c ⁇ 0.25mm, the flat tube 110 has a simpler processing process, better structural strength and lower production cost.
  • the first side 112 is replaced on the same flat tube 110.
  • the shortest distance between the inner peripheral walls of the hot runner 111 is 0.26 ⁇ d ⁇ 0.28 mm. It is verified by experiments that when 0.26 ⁇ d ⁇ 0.28mm, the flat tube 110 has a simpler processing process, better structural strength and lower production cost.
  • the second side 113 is replaced on the same flat tube 110.
  • the shortest distance between the inner peripheral walls of the hot runner 111 is 0.4 ⁇ e ⁇ 0.5 mm. It is verified by experiments that when 0.4 ⁇ e ⁇ 0.5mm, the processing technology of the flat tube 110 is simpler, the structural strength is better, and the production cost is lower.
  • the size of the header 120 is also an important parameter of the heat exchange efficiency and production cost of the parallel flow heat exchanger 100
  • the production cost of the parallel flow heat exchanger 100 is lowered.
  • the outer diameter of the header 120 is m and satisfies: 14 ⁇ m ⁇ 16 mm.
  • the wall thickness of the header 120 is n and satisfies: 1.0 ⁇ n ⁇ 1.2 mm.
  • the width of the heat dissipating fins 130 is greater than or equal to the width of the flat tube 110. Thereby, the heat exchange efficiency of the parallel flow heat exchanger 100 can be further improved.
  • the heat dissipating fins 130 have a width f and satisfy: 10 ⁇ f ⁇ 11 mm. Thereby, not only the heat exchange efficiency of the parallel flow heat exchanger 100 can be improved, but also the production materials can be further saved, and the production cost can be reduced.
  • the height b of the flat tube 110 is 1.3-1.4 mm
  • the number N of heat exchange passages 111 is 8-10.
  • the shortest distance c between the inner peripheral walls of the adjacent two heat exchange passages 111 is 0.2-0.28 mm
  • the shortest distance d between the first side surface 112 and the inner peripheral wall of the heat exchange passage 111 is 0.26-0.28 mm
  • the second The shortest distance e between the side surface 113 and the inner peripheral wall of the heat exchange passage 111 is 0.4-0.5 mm
  • the wall thickness n of the header 120 is 1.0-1.2 mm.
  • the 6 is a graph of the outer diameter of the header 120 and the heat exchange amount, in which the X axis represents the outer diameter of the header 120 (the outer diameter of the header 120 is in mm), and the Y axis represents parallel.
  • the amount of heat exchange of the flow heat exchanger 100 (the unit of heat exchange amount is W).
  • the heat exchange amount of the parallel flow heat exchanger 100 increases as the outer diameter of the header 120 increases; when the header 120 When the outer diameter m is 14-16 mm, the heat exchange amount of the parallel flow heat exchanger 100 is maintained within the range of 4500-4580 W; when the outer diameter of the header 120 is m16 mm, the heat exchange of the parallel flow heat exchanger 100 The amount is maintained at around 4550W;
  • the refrigerant charge amount of the parallel flow heat exchanger 100 (the unit of the refrigerant charge amount is g). As can be seen from the figure, the refrigerant charge amount of the parallel flow heat exchanger 100 is proportional to the outer diameter of the header 120. That is, the refrigerant charge amount increases as the outer diameter of the header 120 increases.
  • the heat exchange amount of the parallel flow heat exchanger 100 is maintained at 4550 W.
  • the outer diameter dimension of the header 120 has little effect on the heat exchange efficiency of the parallel flow heat exchanger 100.
  • the parallel heat exchanger 100 can ensure a large heat exchange amount and save production. Use materials to reduce production costs.
  • the 8 is a graph showing the width and heat exchange amount of the heat dissipating fin 130.
  • the X axis indicates the width of the heat dissipating fin 130 (the width of the heat dissipating fin 130 is in mm), and the Y axis indicates the parallel flow heat exchanger.
  • the heat exchange amount of 100 (the unit of heat exchange amount is W). As can be seen from the figure, when the width f of the heat dissipating fins 130 is 10-11 mm, the heat exchange amount of the parallel flow heat exchanger 100 is maintained at a relatively high range.
  • the parallel flow heat exchanger 100 has not only a simple structure, a low production cost, but also a high heat exchange efficiency.
  • An air conditioner according to an embodiment of the present invention includes the parallel flow heat exchanger 100 as described above.
  • the production material reduces the production cost and also improves the heat exchange efficiency of the parallel flow heat exchanger 100.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” or “second” may include at least one of the features, either explicitly or implicitly.
  • the meaning of "a plurality” is at least two, such as two, three, etc., unless specifically defined otherwise.
  • the terms “installation”, “connected”, “connected”, “fixed” and the like shall be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise. Or in one piece; it may be a mechanical connection, or it may be an electrical connection or a communication with each other; it may be directly connected or indirectly connected through an intermediate medium, and may be an internal connection of two elements or an interaction relationship between two elements. Unless otherwise expressly defined. For those skilled in the art, the specific meanings of the above terms in the present invention can be understood on a case-by-case basis.

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  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
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  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

一种平行流换热器(100)及具有其的空调器。该平行流换热器(100)包括：多根间隔开的扁管(110)，每根扁管(110)的宽度为a且a＝8mm，每根扁管(110)的高度为b且满足：1≤b≤2mm，每根扁管(110)内均设有多条沿扁管长度方向延伸的换热通道(111)，多条换热通道(111)沿扁管(110)的宽度方向间隔开；两根集流管(120)，每根换热通道(111)的两端分别与对应的集流管(120)连通；以及多个散热翅片(130)，多个散热翅片(130)设在相邻的两个扁管(110)之间。

Description

平行流换热器及具有其的空调器 技术领域
本发明涉及制冷设备技术领域，具体而言，特别涉及一种平行流换热器及具有其的空调器。
背景技术
中国是铝资源丰富，而铜资源缺乏的国家。空调能效标准逐年提升，势必会消耗大量的铜资源，造成铜价飞速上涨，铜资源紧缺的风险。因此铝代铜技术将成为今后空调换热器发展的必然趋势。
平行流多孔微通道换热器就是一种全铝换热器，它作为一种用于空调的新型换热器，越来越受到广泛的应用。目前国内外无论是汽车空调还是家用空调行业，各厂家大部分使用的是16mm宽及以上的扁管，但是平行流换热器成本较高，多数用于2p及以上机型，小功率机上很难有成本优势。以目前的铜价，传统规格扁管难以替代铜管换热器，其主要表现在，性能上虽然平行流冷凝器比铜管换热器好，但成本较高。
发明内容
本发明旨在至少在一定程度上解决相关技术中的技术问题之一。为此，本发明提出一种平行流换热器，所述平行流换热器具有结构简单、换热效率高的优点。
本发明还提出一种空调器，所述空调器具有上述平行流换热器。
根据本发明的一个方面提供了一种平行流换热器，包括：多根间隔开的扁管，每根所述扁管的宽度为a且a＝8mm，每根所述扁管的高度为b且满足：1≤b≤2mm，每根所述扁管内均形成多条沿所述扁管长度方向延伸的换热通道，多条所述换热通道沿所述扁管的宽度方向间隔开；两根集流管，所述两根集流管设在所述扁管的两端，每根所述换热通道的两端分别与对应的所述集流管连通；以及多个散热翅片，所述多个散热翅片设在相邻的两个扁管之间。
根据本发明的平行流换热器，通过将扁管构造成宽度为a＝8mm，高度为1≤b≤2mm的扁管，由此不但简化了平行流换热器的结构，减少了生产用料，降低了生产成本，还提高了平行流换热器的换热效率，使平行流换热器适用于小功率的空调器，进而扩大了平行流换热器的适用范围。
优选地，每根所述扁管的高度为b且满足：1.3≤b≤1.4mm。
根据本发明的一个实施例，在同一根所述扁管上，所述相邻的两条所述换热通道的内周 壁之间的最短距离为c且满足：0.2≤c≤0.28mm，所述扁管上垂直于所述扁管的高度方向的侧面为第一侧面，所述第一侧面与所述换热通道的内周壁之间的最短距离为d且满足：0.23≤d≤0.31mm，所述扁管上垂直于所述扁管的宽度方向的侧面为第二侧面，所述第二侧面与所述换热通道的内周壁之间的最短距离为e且满足：0.2≤e≤0.7mm。
优选地，在同一根所述扁管上，所述相邻的两条所述换热通道的内周壁之间的最短距离为c，所述c满足：0.23≤c≤0.25mm。
优选地，在同一根所述扁管上，所述扁管上垂直于所述扁管的高度方向的侧面为第一侧面，所述第一侧面与所述换热通道的内周壁之间的最短距离为d，所述d满足：0.26≤d≤0.28mm。
优选地，在同一根所述扁管上，所述扁管上垂直于所述扁管的宽度方向的侧面为第二侧面，所述第二侧面与所述换热通道的内周壁之间的最短距离为e，所述e满足：0.4≤e≤0.5mm。
在本发明的一个示例中，在同一根所述扁管上，所述换热通道的条数为N且满足：8≤N≤10。
在本发明的一个示例中，所述集流管的外径为m且满足：14≤m≤16mm。
优选地，所述集流管的壁厚为n且满足：1.0≤n≤1.2mm。
根据本发明的一些实施例，所述散热翅片的宽度大于等于所述扁管的宽度。
优选地，所述散热翅片的宽度为f且满足：10≤f≤11mm。
根据本发明的另一个方面提供了一种空调器，包括如上所述的平行流换热器。
根据本发明的空调器，通过将扁管构造成宽度为a＝8mm，高度为1≤b≤2mm的扁管，由此不但简化了平行流换热器的结构，减少了生产用料，降低了生产成本，还提高了平行流换热器的换热效率。
附图说明
图1是根据本发明的一个实施例的平行流换热器立体结构示意图；
图2是图1中的平行流换热器的局部结构示意图；
图3是图2中的平行流换热器的俯视图；
图4是图3中的扁管的俯视图；
图5是图1中的集流管的剖面图；
图6是根据本发明的一个实施例的平行流换热器的集流管的外径与换热量的曲线图，图中X轴表示集流管的外径尺寸(集流管的外径尺寸单位为mm)，图中Y轴表示平行流换热器的换热量(换热量的单位为W)；
图7是根据本发明的一个实施例的平行流换热器的集流管外径与冷媒充注量的曲线图，图中X轴表示集流管的外径尺寸(集流管的外径尺寸的单位为mm)，图中Y轴表示平行流换热器的冷媒充注量(冷媒充注量的单位为g)；
图8是根据本发明的一个实施例的平行流换热器的散热翅片的宽度与冷媒充注量的曲线图，图中X轴表示散热翅片的宽度(散热翅片的宽度单位为mm)，图中Y轴表示平行流换热器的换热量(换热量的单位为W)。
附图标记：
平行流换热器100，
扁管110，换热通道111，第一侧面112，第二侧面113，
集流管120，散热翅片130。
具体实施方式
下面详细描述本发明的实施例，所述实施例的示例在附图中示出。下面通过参考附图描述的实施例是示例性的，旨在用于解释本发明，而不能理解为对本发明的限制。
下面参照附图详细描述根据本发明实施例的平行流换热器100。
如图1-图8所示，根据本发明实施例的平行流换热器100，包括：多根扁管110、两根集流管120以及多个散热翅片130。
具体而言，如图1和图2所示，多根扁管110间隔开设置，每根扁管110内均形成多条沿扁管110长度方向延伸的换热通道111，多条换热通道111沿扁管110的宽度方向间隔开，两根集流管120设在扁管110的两端，每根换热通道111的两端分别与对应的集流管120连通，多个散热翅片130设在相邻的两个扁管110之间。如图1所示，多根扁管110沿上下方向(如图1所示的上下方向)间隔开，每根扁管110上的多条换热通道111沿该扁管110的宽度方向(如图1所示的前后方向)间隔开，每条换热通道111均沿扁管110的长度方向延伸，集流管120设在扁管110的沿长度方向延伸的两端，且每条换热通道111的两端与对应的集流管120连通。例如，如图1所示，位于左侧的集流管120与换热通道111的左端连通，位于右侧的集流管120与换热通道111的右端连通。
图3和图4所示，每根扁管110的宽度为a且a＝8mm，每根扁管110的高度为b且满足：1≤b≤2mm。由此，可提高平行流换热器100的换热效率，简化平行流换热器100的结构，节约生产用料，降低生产成本。同时也可以使平行流换热器100适用于小功率的空调器，进而扩大了平行流换热器100的适用范围。
根据本发明实施例的平行流换热器100，通过将扁管110构造成宽度为a＝8mm，高度为 1≤b≤2mm的扁管110，由此不但简化了平行流换热器100的结构，减少了生产用料，降低了生产成本，还提高了平行流换热器100的换热效率，使平行流换热器100适用于小功率的空调器，进而扩大了平行流换热器100的适用范围。
如图1-图5所示，根据本发明的一个实施例，每根扁管110的高度为b且满足：1.3≤b≤1.4mm。经实验验证，当扁管110的高度为1.3≤b≤1.4mm时，平行流换热器100的换热效率较高。考虑到扁管110上的换热通道111的条数也是影响平行流换热器100的换热效率的重要参数，在本发明的一个优选的示例中，在同一根扁管110上，换热通道111的条数为N且满足：8≤N≤10。由此，可以进一步提高平行流换热器100的换热效率。
如图4所示，在本发明的一个可选的示例中，在同一根扁管110上，相邻的两条换热通道111的内周壁之间的最短距离为c且满足：0.2≤c≤0.28mm，扁管110上垂直于扁管110的高度方向的侧面为第一侧面112，第一侧面112与换热通道111的内周壁之间的最短距离为d且满足：0.23≤d≤0.31mm，扁管110上垂直于扁管110的宽度方向的侧面为第二侧面113，第二侧面113与换热通道111的内周壁之间的最短距离为e且满足：0.2≤e≤0.7mm。这里的“高度方向”可以指图4中所示的上下方向，“宽度方向”可以指图4中所示的前后方向。
需要说明的是，在扁管110的制造过程中，扁管110上的相邻的两条换热通道111的内周壁之间的最短距离c、第一侧面112与换热通道111的内周壁之间的最短距离d以及第二侧面113与换热通道111的内周壁之间的最短距离e是扁管110的尺寸参数，经生产实践证明，当0.2≤c≤0.28mm、0.23≤d≤0.31mm、0.2≤e≤0.7mm时，扁管110的加工工艺简单、结构强度好、生产成本低。
为进一步简化扁管110的加工工艺、优化扁管110的结构强度、降低扁管110的生产成本，在本发明的一个优选的示例中，在同一根扁管110上，相邻的两条换热通道111的内周壁之间的最短距离为0.23≤c≤0.25mm。经实验验证，当0.23≤c≤0.25mm时，扁管110的加工工艺更简单、结构强度更优、生产成本更低。
为进一步简化扁管110的加工工艺、优化扁管110的结构强度、降低扁管110的生产成本，在本发明的一个优选的示例中，在同一根扁管110上，第一侧面112与换热通道111的内周壁之间的最短距离为0.26≤d≤0.28mm。经实验验证，当0.26≤d≤0.28mm时，扁管110的加工工艺更简单、结构强度更优、生产成本更低。
为进一步简化扁管110的加工工艺、优化扁管110的结构强度、降低扁管110的生产成本，在本发明的一个优选的示例中，在同一根扁管110上，第二侧面113与换热通道111的内周壁之间的最短距离为0.4≤e≤0.5mm。经实验验证，当0.4≤e≤0.5mm时，扁管110的加工工艺更简单、结构强度更优、生产成本更低。
考虑到集流管120的尺寸也是平行流换热器100的换热效率、生产成本的重要参数，为进一步提高平行流换热器100的换热效率，降低平行流换热器100的生产成本，在本发明的一个实施例中，如图5所示，集流管120的外径为m且满足：14≤m≤16mm。进一步地，在本发明的一个优选的示例中，集流管120的壁厚为n且满足：1.0≤n≤1.2mm。由此，可以进一步提高平行流换热器100的换热效率，降低平行流换热器100的生产成本。
为了使整个平行流换热器100的换热性能能够充分发挥，散热翅片130的宽度大于等于扁管110的宽度。由此，可以进一步提高平行流换热器100的换热效率。为节约生产用料、降低生产成本，在本发明的一个优选的示例中，散热翅片130的宽度为f且满足：10≤f≤11mm。由此，不但可以提高平行流换热器100的换热效率，还可以进一步节约生产用料，降低生产成本。
下面参照图1-图8，以具体数值对根据本发明实施例的平行流换热器100的进行说明。值得理解的是，下述数值只是示例性说明，而不是对本发明的具体限制。
如图1-图8所示，平行流换热器100的扁管110的宽度a＝8mm，扁管110的高度b为1.3-1.4mm，换热通道111的条数N为8-10，相邻的两条换热通道111的内周壁之间的最短距离c为0.2-0.28mm，第一侧面112与换热通道111的内周壁之间的最短距离d为0.26-0.28mm，第二侧面113与换热通道111的内周壁之间的最短距离e为0.4-0.5mm，集流管120的壁厚n为1.0-1.2mm。
图6为集流管120外径与换热量的曲线图，图中X轴表示集流管120的外径尺寸(集流管120的外径尺寸单位为mm)，图中Y轴表示平行流换热器100的换热量(换热量的单位为W)。由图可知，当集流管120的外径m为10-14mm时，平行流换热器100的换热量随着集流管120的外径的增大而增大；当集流管120的外径m为14-16mm时，平行流换热器100的换热量变维持在4500-4580W范围内；当集流管120的外径m＞16mm时，平行流换热器100的换热量维持在4550W左右；
图7为集流管120外径与冷媒充注量的曲线图，图中X轴表示集流管120的外径尺寸(集流管120的外径尺寸的单位为mm)，图中Y轴表示平行流换热器100的冷媒充注量(冷媒充注量的单位为g)。由图可知，平行流换热器100的冷媒充注量与集流管120的外径成正比。也就是说，冷媒充注量随着集流管120的外径的增大而增大。
结合图6和图7可知，当集流管120的外径m＞16mm时，虽然平行流换热器100的冷媒充注量较大，但是平行流换热器100的换热量维持在4550W左右，即当集流管120的外径m＞16mm时，集流管120的外径尺寸对平行流换热器100的换热效率影响较小。考虑到平行流换热器100的制造成本问题，当集流管120的外径m为14-16mm时，既可以保证平行流换热器100的具有较大的换热量，又可以节约生产用料，降低生产成本。
图8为散热翅片130的宽度与换热量的曲线图，图中X轴表示散热翅片130的宽度(散热翅片130的宽度单位为mm)，图中Y轴表示平行流换热器100的换热量(换热量的单位为W)。由图可知，当散热翅片130的宽度f为10-11mm时，平行流换热器100的换热量维持在一个较高的范围内。
由此可知，根据本发明实施例的平行流换热器100的不但具有简单的结构、较低的生产成本，还具有较高的换热效率。
根据本发明实施例的空调器，包括如上所述的平行流换热器100。
根据本发明实施例的空调器，通过将扁管110构造成宽度为a＝8mm，高度为1≤b≤2mm的扁管110，由此不但简化了平行流换热器100的结构，减少了生产用料，降低了生产成本，还提高了平行流换热器100的换热效率。
在本发明的描述中，需要理解的是，术语“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。在本发明的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
在本发明中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接或彼此可通讯；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系，除非另有明确的限定。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本发明中的具体含义。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本发明的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不必须针对的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任一个或多个实施例或示例中以合适的方式结合。此外，在不相互矛盾的情况下，本领域的技术人员可以将本说明书中描述的不同实施例或示例以及不同实施例或示例的特征进行结合和组合。
尽管上面已经示出和描述了本发明的实施例，可以理解的是，上述实施例是示例性的， 不能理解为对本发明的限制，本领域的普通技术人员在本发明的范围内可以对上述实施例进行变化、修改、替换和变型。

Claims (12)

  1. 一种平行流换热器，其特征在于，包括：
    多根间隔开的扁管，每根所述扁管的宽度为a且a＝8mm，每根所述扁管的高度为b且满足：1≤b≤2mm，每根所述扁管内均形成多条沿所述扁管长度方向延伸的换热通道，多条所述换热通道沿所述扁管的宽度方向间隔开；
    两根集流管，所述两根集流管设在所述扁管的两端，每根所述换热通道的两端分别与对应的所述集流管连通；以及
    多个散热翅片，所述多个散热翅片设在相邻的两个扁管之间。
  2. 根据权利要求1所述的平行流换热器，其特征在于，每根所述扁管的高度为b且满足：1.3≤b≤1.4mm。
  3. 根据权利要求1所述的平行流换热器，其特征在于，在同一根所述扁管上，所述相邻的两条所述换热通道的内周壁之间的最短距离为c且满足：0.2≤c≤0.28mm，所述扁管上垂直于所述扁管的高度方向的侧面为第一侧面，所述第一侧面与所述换热通道的内周壁之间的最短距离为d且满足：0.23≤d≤0.31mm，所述扁管上垂直于所述扁管的宽度方向的侧面为第二侧面，所述第二侧面与所述换热通道的内周壁之间的最短距离为e且满足：0.2≤e≤0.7mm。
  4. 根据权利要求3所述的平行流换热器，其特征在于，所述c满足：0.23≤c≤0.25mm。
  5. 根据权利要求3所述的平行流换热器，其特征在于，所述d满足：0.26≤d≤0.28mm。
  6. 根据权利要求3所述的平行流换热器，其特征在于，所述e满足：0.4≤e≤0.5mm。
  7. 根据权利要求1所述的平行流换热器，其特征在于，在同一根所述扁管上，所述换热通道的条数为N且满足：8≤N≤10。
  8. 根据权利要求1所述的平行流换热器，其特征在于，所述集流管的外径为m且满足：14≤m≤16mm。
  9. 根据权利要求8所述的平行流换热器，其特征在于，所述集流管的壁厚为n且满足：1.0≤n≤1.2mm。
  10. 根据权利要求1-9中任一项所述的平行流换热器，其特征在于，所述散热翅片的宽度大于等于所述扁管的宽度。
  11. 根据权利要求10所述的平行流换热器，其特征在于，所述散热翅片的宽度为f且满足：10≤f≤11mm。
  12. 一种空调器，其特征在于，包括根据权利要求1-11中任一项所述的平行流换热器。
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CN1981168A (zh) * 2004-07-05 2007-06-13 昭和电工株式会社 蒸发器
JP2009229025A (ja) * 2008-03-25 2009-10-08 Showa Denko Kk オイルクーラ
CN202915789U (zh) * 2012-08-26 2013-05-01 浙江富源制冷设备有限公司 一种微通道换热器扁管

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CN1981168A (zh) * 2004-07-05 2007-06-13 昭和电工株式会社 蒸发器
JP2009229025A (ja) * 2008-03-25 2009-10-08 Showa Denko Kk オイルクーラ
CN202915789U (zh) * 2012-08-26 2013-05-01 浙江富源制冷设备有限公司 一种微通道换热器扁管

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