WO2020019828A1 - 一种微通道蒸发器及一种空调系统 - Google Patents

一种微通道蒸发器及一种空调系统 Download PDF

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Publication number
WO2020019828A1
WO2020019828A1 PCT/CN2019/086578 CN2019086578W WO2020019828A1 WO 2020019828 A1 WO2020019828 A1 WO 2020019828A1 CN 2019086578 W CN2019086578 W CN 2019086578W WO 2020019828 A1 WO2020019828 A1 WO 2020019828A1
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Prior art keywords
flat tube
micro
channel evaporator
shaped body
groups
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PCT/CN2019/086578
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English (en)
French (fr)
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王瑞鑫
梁东旭
赵义逢
姚晋芳
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维谛技术有限公司
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Publication of WO2020019828A1 publication Critical patent/WO2020019828A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/05—Cost reduction

Definitions

  • the invention relates to the technical field of refrigeration, in particular to a micro-channel evaporator and an air conditioning system.
  • Inter-column air conditioners are mostly used in modular machine rooms. Refrigeration is mainly carried out by means of direct compression and vapor expansion.
  • the refrigerant circulates in a closed pipeline formed by the sequential connection of the compressor, condenser, throttling element and evaporator.
  • the specific process is :
  • the refrigerant is compressed into high-temperature and high-pressure gas by the compressor and enters the condenser. It is condensed and released into a low-temperature and high-pressure liquid in the condenser, and then throttled into a low-temperature and low-pressure liquid by the throttling element.
  • the returned refrigerant gas is returned to the compressor to complete a cycle.
  • the evaporator of the inter-row air conditioner usually uses a more traditional copper tube finned evaporator.
  • the structure of the existing copper tube finned evaporator includes heat exchange copper tube 01 and fins covering the outer surface of the heat exchange copper tube.
  • the evaporator will Setting multiple rows of heat exchange copper tubes 01 will increase production costs on the one hand, and densely arranged heat exchange copper tubes 01 will increase wind resistance and affect the heat exchange efficiency of the air conditioning unit.
  • Embodiments of the present invention provide a micro-channel evaporator and an air conditioning system to reduce production costs and improve refrigeration energy efficiency.
  • An embodiment of the present invention provides a micro-channel evaporator, including:
  • each piece of flat tube groups located at different positions in the air conditioning system, each piece of flat tube groups includes a liquid inlet header and a liquid outlet header, and is connected to the liquid inlet header and the liquid outlet header.
  • a set of flat tubes in between, a distribution tube is inserted into the liquid inlet header, and the distribution tube is provided with a plurality of through holes in the axial direction;
  • a distributor including a liquid inlet and a liquid outlet corresponding to each piece of flat tube group;
  • the inner diameter of the capillary tube of the flat tube group located at a position with a large air volume is larger than the inner diameter of the capillary tube of the flat tube group located at a position with a small air volume.
  • the capillary length of the flat tube group located at a position with a large air volume is smaller than the capillary length of the flat tube group located at a position with a small air volume.
  • the distribution density of the through holes on the distribution pipe located in the area with a larger air volume is smaller than the distribution density of the through holes on the distribution pipe located in the area with a small air volume.
  • the number of the flat tube groups is two, and the two flat tube groups are arranged in a V-shaped body, and the opening of the V-shaped body forms an air outlet of the micro-channel evaporator.
  • the number of the flat tube group is four pieces, and each of the two flat tube groups has a first V-shaped body setting and a second V-shaped body setting, and the second V-shaped body is stacked on the Above the first V-shaped body, the opening of the first V-shaped body and the opening of the second V-shaped body form an air outlet of the micro-channel evaporator.
  • the number of the water trays is two, which are respectively a water tray and a drain tray, and the water tray is located between the second V-shaped body and the first V-shaped body, so The drain pan is located at the bottom of the first V-shaped body.
  • the liquid refrigerant after the liquid refrigerant enters the distributor, it is sent to different flat tube groups through the capillaries connected to the respective liquid outlets of the distributor. Due to the difference in the air volume of each flat tube group, Different flat tube groups, by designing the corresponding capillaries to different sizes, can control the refrigerant flow that actually enters the flat tube group, so that on the one hand, the refrigerant in the flat tube group located at a location with a large air volume is guaranteed The flow can meet its heat exchange requirements, and on the other hand, it avoids waste of excessive refrigerant in the flat tube group located at a location with a small air volume. Compared with the copper tube fin evaporator in the prior art, the present invention The micro-channel evaporator provided by the embodiment not only has low production cost, but also greatly improves refrigeration energy efficiency.
  • An embodiment of the present invention further provides an air-conditioning system, including a compressor, a condenser, a throttling element, and a micro-channel evaporator according to any one of the foregoing technical schemes, which are sequentially connected through a pipeline to form a closed cycle.
  • the throttling element is connected to the liquid inlet of the distributor of the micro-channel evaporator, and the compressor is connected to the liquid outlet header of the micro-channel evaporator.
  • the air conditioning system has high cooling energy efficiency.
  • the throttle element is an electronic expansion valve; or the throttle element is a thermal expansion valve.
  • FIG. 1 is a schematic structural diagram of a copper tube finned evaporator in the prior art
  • FIG. 2 is a schematic structural diagram of a micro-channel evaporator according to an embodiment of the present invention.
  • embodiments of the present invention provide a micro-channel evaporator and an air conditioning system.
  • the following further describes the present invention in detail with examples.
  • the micro-channel evaporator provided by the embodiment of the present invention includes:
  • each flat tube group 10 located at different positions in the air conditioning system, each flat tube group 10 includes a liquid inlet header 11 and a liquid outlet header 12 and is connected to the liquid inlet header 11 and the liquid outlet A set of flat tubes 13 between the flow tubes 12, a distribution tube 14 is inserted into the liquid inlet header 11, and the distribution tube 14 is provided with a plurality of through holes (not shown) in the axial direction;
  • the distributor 20 includes a liquid inlet 21 and a liquid outlet 22 corresponding to each piece of the flat tube group 10;
  • a water pan 40 is located at the bottom of at least two flat tube groups 10;
  • the capillary tubes 30 corresponding to different flat tube groups 10 are selected to have different sizes according to the air volume at different positions of the flat tube groups 10.
  • the liquid refrigerant enters the distribution pipe 14 through the capillary 30, and is sprayed into the liquid collection header 11 through a through hole formed in the distribution tube 14, and then the liquid collection header 11 passes through the flat tube 13
  • the hot air from outside passes through the flat tube 13 of the micro-channel evaporator and the The liquid refrigerant undergoes heat exchange, and condensed water is formed on the surface of the flat tube 13.
  • the condensed water flows down the surface of the flat tube 13 under the force of gravity and is collected in a water pan 40 below the flat tube group 10.
  • the air duct formed between the fan and the air outlet of the micro-channel evaporator will inevitably be obstructed by pipes or other structural components, which will lead to different flat tube groups.
  • the air volume at the location will be different.
  • the refrigerant flow rate assigned to each flat tube group 10 is the same, not only will the refrigerant flow in the flat tube group 10 located at the position with a larger air volume fail to meet its replacement. Heat demand will also cause excessive refrigerant in the flat tube group 10 located at a location with a small air volume to cause waste, thereby affecting refrigeration energy efficiency.
  • the liquid refrigerant enters the distributor 20 and is sent to different flat tube groups 10 through the capillary tubes 30 connected to the liquid outlets 22 of the distributor 20. Due to the air volume of each flat tube group 10, Therefore, for different flat tube groups 10, by designing the corresponding capillary tubes 30 to different sizes, the refrigerant flow that actually enters the flat tube groups 10 can be controlled.
  • the refrigerant flow in the flat tube group 10 at the location can meet its heat exchange requirements, and on the other hand, it avoids waste of excessive refrigerant in the flat tube group 10 at a location with a small air volume, compared with the prior art. Copper tube fin evaporator, the micro-channel evaporator provided by the embodiment of the present invention not only has lower production cost, but also greatly improves refrigeration energy efficiency.
  • the number of flat tube groups is not limited. In a preferred embodiment of the present invention, the number of flat tube groups is two, and the two flat tube groups are arranged in a V-shaped body, and the openings of the V-shaped body form a microchannel evaporator.
  • the air outlet adopts the solution of this embodiment, which can reduce the height of the evaporator of the air conditioner between the rows, which is beneficial to the discharge of the condensed water.
  • the number of the flat tube groups 10 is four, and each of the two flat tube groups 10 is provided with a first V-shaped body 15 and a second V-shaped body 16, and the second V-shaped body 16 is stacked. It is placed on the first V-shaped body 15, and the opening of the first V-shaped body 15 and the opening of the second V-shaped body 16 form the air outlet of the micro-channel evaporator.
  • this solution can The height of the evaporators between the rows of air conditioners is further reduced, and the heat exchange area of the evaporators is significantly increased, thereby improving the heat exchange effect.
  • a water pan 40 can be provided below the first V-shaped body 15, so that the condensed water generated by the heat exchange between the first V-shaped body 15 and the second V-shaped body 16 can be under the action of gravity. Converge in the water pan 40.
  • the number of water pans 40 is two, which are a water pan 41 and a water pan 42, respectively. Between the V-shaped body 16 and the first V-shaped body 15, the drain pan 42 is located at the bottom of the first V-shaped body 15.
  • the amount of water passing through the capillary 30 is related to its inner diameter and length.
  • the larger the inner diameter and / or the length of the capillary 30 The shorter, the smaller the resistance, the more refrigerant flow through the capillary 30. Therefore, in the embodiment of the present invention, the flow rate of the refrigerant distributed to each flat tube group can be adjusted by changing the inner diameter and length of the capillary tube corresponding to different flat tube groups.
  • the inner diameter of the capillary tube 30 of the flat tube group 10 at a position with a large air volume is larger than the inner diameter of the capillary tube 30 of the flat tube group 10 at a position with a small air volume; in another specific embodiment
  • the length of the capillary tube 30 of the flat tube group 10 located at a position with a large air volume is smaller than the length of the capillary tube 30 of the flat tube group 10 located at a position with a small air volume.
  • the refrigerant flow rate can be adjusted by changing only one of the parameters of the inner diameter or the length of the capillary 30 during the specific setting. Of course, the two parameters can also be adjusted at the same time. The present invention does not limit this.
  • the adjusted refrigerant flow can meet the heat exchange requirements without causing waste. It should be noted that the specific size of the capillary tube 30 needs to be designed by the air volume in the air-conditioning system in which the flat tube group 10 is located, and is not repeated here.
  • the air volume at different locations of the flat tube group 10 is different, so the refrigerant flow rate of the flat tubes 13 in different regions of the flat tube group 10 also needs to be adjusted.
  • the distribution density of the through-holes on the distribution pipe 14 affects the refrigerant flow rate sent from the header 11 to the flat pipe 13, which is specifically expressed as the distribution density of the through-holes on the sub-spray pipe 14. The smaller the refrigerant flow from the header tube 11 to the flat tube 13 in the region with a larger air volume, the greater the flow rate of the refrigerant.
  • the distribution density of the through-holes on the piping 14 is smaller than the distribution density of the through-holes on the distribution pipe 14 located in the area with a small air volume, so that the flat tubes 13 in the area with a large air volume of the flat tube group 10 can be distributed to more Refrigerant to ensure heat exchange effect.
  • An embodiment of the present invention further provides an air conditioning system, which includes a compressor, a condenser, a throttling element 50 and a micro-channel evaporator according to any one of the foregoing technical solutions, which are sequentially connected through a pipeline to form a closed cycle, wherein the throttling element 50 is connected to the liquid inlet 21 of the distributor 20 of the micro-channel evaporator, and the compressor is connected to the liquid outlet header 12 of the micro-channel evaporator.
  • the throttle element 50 may be an electronic expansion valve or a thermal expansion valve. The invention does not limit this.
  • the air conditioning system has high cooling energy efficiency.

Abstract

一种微通道蒸发器及一种空调系统，以降低生产成本并且提升制冷能效。微通道蒸发器包括：位于空调系统中风量不同的位置的至少两片扁管组（10），每片扁管组（10）包括进液集流管（11）和出液集流管（12）以及连接于进液集流管（11）和出液集流管（12）之间的一组扁管（10），进液集流管（11）内插设有分配管（14），分配管（14）沿轴向设有若干通孔，分配器（20）包括进液口（21）以及与每片扁管组（10）对应的出液口（22），与至少两片扁管组（10）分别对应的毛细管（30），每根毛细管（30）用于将与其对应的扁管组（10）的分配管（14）与出液口（22）连接，水盘（40）位于至少两片扁管组（10）的底部，其中，对应不同扁管组（10）的毛细管（30）根据扁管组（10）所处位置的风量大小不同而选择不同尺寸。

Description

一种微通道蒸发器及一种空调系统
本申请要求于2018年7月26日提交中国专利局、申请号为201810836723.3、发明名称为“一种微通道蒸发器及一种空调系统”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本发明涉及制冷技术领域，特别是涉及一种微通道蒸发器及一种空调系统。
背景技术
列间空调多应用于模块化机房中，主要通过蒸汽压缩直接膨胀的方式进行制冷，制冷剂在压缩机、冷凝器、节流元件和蒸发器顺序连接形成的封闭管路中循环，具体过程为：冷媒通过压缩机被压缩成高温高压气体后进入冷凝器，在冷凝器内冷凝放热成低温高压液体，再经过节流元件节流成低温低压液体，然后进入蒸发器进行蒸发换热，蒸发后的制冷剂气体回到压缩机中完成一次循环。其中，列间空调的蒸发器通常使用较为传统的铜管翅片式蒸发器。
如图1所示，现有的铜管翅片式蒸发器的结构包括换热铜管01和包覆于换热铜管外表面的翅片，为了达到较大的换热量，蒸发器会设置多排换热铜管01，这样一方面会增加生产成本，另一方面，排布较为密集的换热铜管01也会增加风阻，影响空调机组的换热效率。
发明内容
本发明实施例提供了一种微通道蒸发器及一种空调系统，以降低生产成本，并且提升制冷能效。
本发明实施例提供了一种微通道蒸发器，包括：
位于空调系统中风量不同的位置的至少两片扁管组，每片所述扁管组包括进液集流管和出液集流管以及连接于进液集流管和出液集流管之间的一组扁管，所述进液集流管内插设有分配管，所述分配管沿轴向开设 有若干个通孔；
分配器，包括进液口以及与每片扁管组对应的出液口；
与所述至少两片扁管组分别对应的毛细管，每根所述毛细管用于将与其对应的扁管组的分配管与所述出液口连接；
水盘，位于所述至少两片扁管组的底部；
其中，对应不同扁管组的毛细管根据扁管组所处位置的风量大小不同而选择不同尺寸。
在一个具体的实施方式中，位于风量较大的位置处的扁管组的毛细管内径大于位于风量较小的位置处的扁管组的毛细管内径。
在一个具体的实施方式中，位于风量较大的位置处的扁管组的毛细管长度小于位于风量较小的位置处的扁管组的毛细管长度。
在一个具体的实施方式中，对于每片扁管组，位于风量较大的区域内的分配管上通孔的分布密度小于位于风量较小的区域内的分配管上通孔的分布密度。
在一个具体的实施方式中，所述扁管组的数量为两片，且所述两片扁管组呈V形体设置，所述V形体的开口形成所述微通道蒸发器的出风口。
在一个具体的实施方式中，所述扁管组的数量为四片，每两片扁管组分别呈第一V形体设置与第二V形体设置，且所述第二V形体叠置于所述第一V形体之上，所述第一V形体的开口与所述第二V形体的开口形成所述微通道蒸发器的出风口。
在一个具体的实施方式中，所述水盘的数量为两个，分别为中水盘和下水盘，所述中水盘位于所述第二V形体与所述第一V形体之间，所述下水盘位于所述第一V形体底部。
在本发明实施例中，液态冷媒进入分配器后经过与分配器的各个出液口连接的毛细管送入不同的扁管组，由于各片扁管组所处位置的风量的不同的，因此针对不同的扁管组，通过将与其对应的毛细管设计为不同的尺寸，就可以控制实际进入扁管组内的冷媒流量，这样一方面保证了位于风量较大的位置处的扁管组内的冷媒流量能够满足其换热需求，另一方面又避免了位于风量较小的位置处的扁管组内的冷媒过多造成浪费，相比现有技术中的铜管翅片式蒸发器，本发明实施例提供的微通道蒸发器不仅生 产成本较低，而且制冷能效也大大提升。
本发明实施例还提供了一种空调系统，包括通过管路顺序连接形成封闭循环的压缩机、冷凝器、节流元件以及如前述任一技术方案所述的微通道蒸发器，其中，所述节流元件与所述微通道蒸发器的分配器的进液口连接，所述压缩机与所述微通道蒸发器的出液集流管连接。该空调系统具有较高的制冷能效。
在一个具体的实施方式中，所述节流元件为电子膨胀阀；或者，所述节流元件为热力膨胀阀。
附图说明
图1为现有技术中的铜管翅片式蒸发器的结构示意图；
图2为本发明实施例微通道蒸发器的结构示意图。
附图标记：
现有技术部分：
01-换热铜管
本发明实施例部分：
10-扁管组    11-进液集流管    12-出液集流管    13-扁管
14-分配管    20-分配器    21-进液口    22-出液口
30-毛细管    40-水盘    15-第一V形体    16-第二V形体
41-中水盘    42-下水盘    50-节流元件
具体实施方式
为了降低生产成本，并且提升制冷能效，本发明实施例提供了一种微通道蒸发器及一种空调系统。为使本发明的目的、技术方案和优点更加清楚，以下举实施例对本发明作进一步详细说明。
如图2所示，本发明实施例提供的微通道蒸发器，包括：
位于空调系统中风量不同的位置的至少两片扁管组10，每片扁管组10包括进液集流管11和出液集流管12以及连接于进液集流管11和出液集流管12之间的一组扁管13，进液集流管11内插设有分配管14，分配 管14沿轴向开设有若干个通孔(图中未示出)；
分配器20，包括进液口21以及与每片扁管组10对应的出液口22；
与至少两片扁管组10分别对应的毛细管30，每根毛细管30用于将与其对应的扁管组10的分配管14与出液口22连接；
水盘40，位于至少两片扁管组10的底部；
其中，对应不同扁管组10的毛细管30根据扁管组10所处位置的风量大小不同而选择不同尺寸。
微通道蒸发器在工作时，液态冷媒经过毛细管30进入分配管14，由分配管14上开设的通孔喷入进液集流管11内，再然后由进液集流管11经过扁管13流至出液集流管12；与此同时，在位于微通道蒸发器的出风口前侧的风机的吸力作用下，外界热空气经过微通道蒸发器的扁管13并与扁管13内的液态冷媒发生热交换，在扁管13的表面形成冷凝水，冷凝水在重力所用下沿扁管13的表面流下，汇集在扁管组10下方的水盘40内。然而，由于空调机柜的内部结构较为紧凑，风机与微通道蒸发器的出风口之间形成的风道上不可避免地会被管路或者其它结构件所阻碍，这样就会导致不同扁管组10所在的位置的风量会有所差异，此时如果分配至每片扁管组10的冷媒流量是相同的，不仅会导致位于风量较大的位置处的扁管组10内的冷媒流量无法满足其换热需求，也会使得位于风量较小的位置处的扁管组10内冷媒过多造成浪费，从而影响制冷能效。
在本发明实施例中，液态冷媒进入分配器20后经过与分配器20的各个出液口22连接的毛细管30送入不同的扁管组10，由于各片扁管组10所处位置的风量的不同的，因此针对不同的扁管组10，通过将与其对应的毛细管30设计为不同的尺寸，就可以控制实际进入扁管组10内的冷媒流量，这样一方面保证了位于风量较大的位置处的扁管组10内的冷媒流量能够满足其换热需求，另一方面又避免了位于风量较小的位置处的扁管组10内的冷媒过多造成浪费，相比现有技术中的铜管翅片式蒸发器，本发明实施例提供的微通道蒸发器不仅生产成本较低，而且制冷能效也大大提升。
其中，扁管组的数量不限，在本发明的一个优选实施例中，扁管组的数量为两片，且两片扁管组呈V形体设置，V形体的开口形成微通道蒸发器的出风口，采用该实施例方案，可以降低列间空调蒸发器的高度，有利于冷凝水的排出。
更优的，如图1所示，扁管组10的数量为四片，每两片扁管组10分别呈第一V形体15设置与第二V形体16设置，且第二V形体16叠置于第一V形体15之上，第一V形体15的开口与第二V形体16的开口形成微通道蒸发器的出风口，相比现有技术中的整片式蒸发器，该方案可以进一步降低列间空调蒸发器的高度，并且明显增加了蒸发器的换热面积，从而提高换热效果。
上述实施例中的微通道蒸发器，可以在第一V形体15的下方设置一个水盘40，这样第一V形体15和第二V形体16热交换所产生的冷凝水均可在重力作用下汇聚到该水盘40内。为了使冷凝水更加便于排出，在本发明的优选实施例中，如图1所示，水盘40的数量为两个，分别为中水盘41和下水盘42，中水盘41位于第二V形体16与第一V形体15之间，下水盘42位于第一V形体15底部。
通过毛细管30的水量与其内径和长度有关，毛细管30的内径越小和/或长度越长，阻力越大，通过毛细管30的冷媒流量就越少；反之，毛细管30的内径越大和/或长度越短，阻力越小，通过毛细管30的冷媒流量就越多。因此，在本发明实施例中，可通过改变对应不同扁管组的毛细管内径和长度来调节分配至各个扁管组的冷媒流量。在一个具体的实施方式中，位于风量较大的位置处的扁管组10的毛细管30内径大于位于风量较小的位置处的扁管组10的毛细管30内径；在另一具体的实施方式中，位于风量较大的位置处的扁管组10的毛细管30长度小于位于风量较小的位置处的扁管组10的毛细管30长度。可以理解的，具体设置时，可以通过只改变毛细管30内径或者长度的其中一个参数来调节冷媒流量，当然也可以同时改变两个参数进行调节，本发明对此不做限制，只要保证经毛细管30调节后的冷媒流量能够在满足换热需求的同时又不会造成浪费即可。需要说明的是，毛细管30的具体尺寸需要扁管组10所处的空调系统中的风量进行设计，此处不作赘述。
对于每片扁管组10，实际上扁管组10的不同区域所处的位置的风量也是不同的，因此也需要对扁管组10的不同区域扁管13的制冷剂流量进行调节。在实现本发明的过程中，发明人发现，分配管14上通孔的分布密度影响由集流管11送入扁管13的冷媒流量，具体表现为，分喷管14上通孔的分布密度越小，由集流管11送入风量较大区域扁管13的冷媒流量就越多，因此，在本发明实施例中，针对每片扁管组10，位于风量较大的区域内的分配管14上通孔的分布密度小于位于风量较小的区域 内的分配管14上通孔的分布密度，这样就能使扁管组10的风量较大的区域的扁管13能够分配到更多的冷媒，保证换热效果。
本发明实施例还提供了一种空调系统，包括通过管路顺序连接形成封闭循环的压缩机、冷凝器、节流元件50以及如前述任一技术方案的微通道蒸发器，其中，节流元件50与微通道蒸发器的分配器20的进液口21连接，压缩机与微通道蒸发器的出液集流管12连接，其中，节流元件50具体可以为电子膨胀阀或者热力膨胀阀，本发明对此不做限制。该空调系统具有较高的制冷能效。
显然，本领域的技术人员可以对本发明进行各种改动和变型而不脱离本发明的精神和范围。这样，倘若本发明的这些修改和变型属于本发明权利要求及其等同技术的范围之内，则本发明也意图包含这些改动和变型在内。

Claims (9)

  1. 一种微通道蒸发器，其特征在于，包括：
    位于空调系统中风量不同的位置的至少两片扁管组，每片所述扁管组包括进液集流管和出液集流管以及连接于进液集流管和出液集流管之间的一组扁管，所述进液集流管内插设有分配管，所述分配管沿轴向开设有若干个通孔；
    分配器，包括进液口以及与每片扁管组对应的出液口；
    与所述至少两片扁管组分别对应的毛细管，每根所述毛细管用于将与其对应的扁管组的分配管与所述出液口连接；
    水盘，位于所述至少两片扁管组的底部；
    其中，对应不同扁管组的毛细管根据扁管组所处位置的风量大小不同而选择不同尺寸。
  2. 如权利要求1所述的微通道蒸发器，其特征在于，位于风量较大的位置处的扁管组的毛细管内径大于位于风量较小的位置处的扁管组的毛细管内径。
  3. 如权利要求1所述的微通道蒸发器，其特征在于，位于风量较大的位置处的扁管组的毛细管长度小于位于风量较小的位置处的扁管组的毛细管长度。
  4. 如权利要求1所述的微通道蒸发器，其特征在于，对于每片扁管组，位于风量较大的区域内的分配管上通孔的分布密度小于位于风量较小的区域内的分配管上通孔的分布密度。
  5. 如权利要求1所述的微通道蒸发器，其特征在于，所述扁管组的数量为两片，且所述两片扁管组呈V形体设置，所述V形体的开口形成 所述微通道蒸发器的出风口。
  6. 如权利要求1所述的微通道蒸发器，其特征在于，所述扁管组的数量为四片，每两片扁管组分别呈第一V形体设置与第二V形体设置，且所述第二V形体叠置于所述第一V形体之上，所述第一V形体的开口与所述第二V形体的开口形成所述微通道蒸发器的出风口。
  7. 如权利要求6所述的微通道蒸发器，其特征在于，所述水盘的数量为两个，分别为中水盘和下水盘，所述中水盘位于所述第二V形体与所述第一V形体之间，所述下水盘位于所述第一V形体底部。
  8. 一种空调系统，其特征在于，包括通过管路顺序连接形成封闭循环的压缩机、冷凝器、节流元件以及如权利要求1～7任一项所述的微通道蒸发器，其中，所述节流元件与所述微通道蒸发器的分配器的进液口连接，所述压缩机与所述微通道蒸发器的出液集流管连接。
  9. 如权利要求8所述的空调系统，其特征在于，所述节流元件为电子膨胀阀；或者，所述节流元件为热力膨胀阀。
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Publication number Priority date Publication date Assignee Title
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Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101031754A (zh) * 2005-08-08 2007-09-05 三菱电机株式会社 空调机及空调机的制造方法
CN102278908A (zh) * 2011-09-16 2011-12-14 四川长虹空调有限公司 微通道换热器
WO2014032488A1 (zh) * 2012-08-30 2014-03-06 Yu Shaoming 一种微通道热交换器
CN103913019A (zh) * 2014-01-18 2014-07-09 胡洁 一种用于制冷系统的高性能微通道换热器
CN204362491U (zh) * 2015-01-14 2015-05-27 北京雅驿欣科技有限公司 机柜主体及列间空调
CN204593813U (zh) * 2015-01-14 2015-08-26 深圳市艾特网能有限公司 列间空调用换热器及列间空调
CN105190202A (zh) * 2013-05-08 2015-12-23 三菱电机株式会社 热交换器和制冷循环装置
DE102015110845A1 (de) * 2014-07-11 2016-01-14 Hangzhou Sanhua Research Institute Co., Ltd. Kühlsystem und dessen Wärmeaustauscher
CN206496415U (zh) * 2016-12-29 2017-09-15 艾尔维尔(上海)机房设备有限公司 一种新型换热器结构的列间空调
CN208688035U (zh) * 2018-07-26 2019-04-02 维谛技术有限公司 一种微通道蒸发器及一种空调系统

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101031754A (zh) * 2005-08-08 2007-09-05 三菱电机株式会社 空调机及空调机的制造方法
CN102278908A (zh) * 2011-09-16 2011-12-14 四川长虹空调有限公司 微通道换热器
WO2014032488A1 (zh) * 2012-08-30 2014-03-06 Yu Shaoming 一种微通道热交换器
CN105190202A (zh) * 2013-05-08 2015-12-23 三菱电机株式会社 热交换器和制冷循环装置
CN103913019A (zh) * 2014-01-18 2014-07-09 胡洁 一种用于制冷系统的高性能微通道换热器
DE102015110845A1 (de) * 2014-07-11 2016-01-14 Hangzhou Sanhua Research Institute Co., Ltd. Kühlsystem und dessen Wärmeaustauscher
CN204362491U (zh) * 2015-01-14 2015-05-27 北京雅驿欣科技有限公司 机柜主体及列间空调
CN204593813U (zh) * 2015-01-14 2015-08-26 深圳市艾特网能有限公司 列间空调用换热器及列间空调
CN206496415U (zh) * 2016-12-29 2017-09-15 艾尔维尔(上海)机房设备有限公司 一种新型换热器结构的列间空调
CN208688035U (zh) * 2018-07-26 2019-04-02 维谛技术有限公司 一种微通道蒸发器及一种空调系统

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