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WO2016155367A1 - 换热器及具有其的多联机系统 - Google Patents

换热器及具有其的多联机系统 Download PDF

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Publication number
WO2016155367A1
WO2016155367A1 PCT/CN2015/098131 CN2015098131W WO2016155367A1 WO 2016155367 A1 WO2016155367 A1 WO 2016155367A1 CN 2015098131 W CN2015098131 W CN 2015098131W WO 2016155367 A1 WO2016155367 A1 WO 2016155367A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
pipe
refrigerant
inlet
tube
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2015/098131
Other languages
English (en)
French (fr)
Inventor
杨国忠
罗彬�
谭志军
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
Original Assignee
Midea Group Co Ltd
GD Midea Heating and Ventilating Equipment Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Midea Group Co Ltd, GD Midea Heating and Ventilating Equipment Co Ltd filed Critical Midea Group Co Ltd
Priority to EP15887317.4A priority Critical patent/EP3279599A4/en
Priority to BR112017002057A priority patent/BR112017002057A2/pt
Priority to US15/501,957 priority patent/US20180010857A1/en
Publication of WO2016155367A1 publication Critical patent/WO2016155367A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F25B39/028—Evaporators having distributing means
    • 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
    • F25B39/00—Evaporators; Condensers
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0263—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry or cross-section of header box
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/029—Other particular headers or end plates with increasing or decreasing cross-section, e.g. having conical shape

Definitions

  • the present invention relates to the field of heat exchanger equipment, and more particularly to a heat exchanger and a multi-connection system having the heat exchanger.
  • the multi-connection system in the related art is composed of an outdoor unit, an indoor unit, and a refrigerant flow between indoor and outdoor, and is divided into three types according to the number of refrigerant pipes between the outdoor unit and the refrigerant flow direction switching device (that is, three refrigerant pipes are used). And two controls (ie, two refrigerant pipes), of which the two control outdoor units have relatively complicated refrigerant systems, but they are concerned because of relatively simple construction and low cost.
  • the outdoor unit heat exchanger must be designed such that the refrigerant flow direction is fixed, that is, the refrigerant flow direction is independent of cooling or heating.
  • the flute tube is usually used instead of the conventional heat pump. Capillary design, which tends to cause two-phase refrigerant bias flow when the outdoor mechanism is hot, resulting in low system heating performance.
  • the present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention proposes a heat exchanger that is capable of better dispensing two-phase refrigerant without splitting the capillary.
  • the present invention also proposes a multi-connection system having the above heat exchanger.
  • a heat exchanger includes: a shunt tube including a body, an inlet, and a plurality of split ports, the inlet being disposed at a bottom of the body, the plurality of split ports being at the body
  • the lengthwise direction is distributed on the side wall of the body, and in the direction from bottom to top, the body comprises a plurality of sections of tubes, and the flow area of the tubes located downstream of each of the adjacent sections of the tubes a flow area smaller than the pipe body located upstream, the height of each pipe body is not more than 0.5 m, the number N of the pipe bodies is 2 ⁇ N ⁇ 3; the header, the header and the shunt
  • the tubes are connected by a plurality of heat exchange tubes, and the plurality of heat exchange tubes are spaced apart in the up and down direction, and the header tubes have an outlet for discharging the refrigerant.
  • the heat exchanger of the embodiment of the invention it is possible to better distribute the two-phase refrigerant without the split capillary.
  • the body is configured such that the flow rate of the liquid refrigerant flowing through the variable diameter of each adjacent two-stage pipe body is substantially equal to the flow rate of the liquid refrigerant of the inlet.
  • the flow rate of the liquid refrigerant at the variable diameter of each adjacent two-stage pipe body and the flow rate of the liquid refrigerant of the inlet are both in the range of 0.4 to 0.6 m/s.
  • the header is formed as a straight tube.
  • the heat exchange tube is a flat tube.
  • the present invention also proposes a multi-line system comprising the heat exchanger described above.
  • FIG. 1 is a schematic view of a heat exchanger according to an embodiment of the present invention.
  • FIG. 2 is a schematic view of a heat exchanger in accordance with another embodiment of the present invention.
  • a shunt tube 1 a body 11; a first tube body 111; a second tube body 112; a third tube body 113;
  • 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.
  • a heat exchanger 100 in accordance with an embodiment of the present invention will now be described with reference to Figures 1-2, wherein the heat exchanger 100 can be utilized in a refrigeration unit such as a single chiller, a chiller or a multi-line system.
  • a heat exchanger 100 As shown in FIG. 1 and FIG. 2, a heat exchanger 100 according to an embodiment of the present invention includes a shunt tube 1 and a heat exchange tube (not shown in the figure). Shown) and header 2.
  • the shunt tube 1 includes a body 11, an inlet 12, and a plurality of split ports (not shown), the inlet 12 is disposed at the bottom of the body 11, and the plurality of split ports are at the length of the body 11. The upper portion is distributed on the side wall of the body 11.
  • the collecting tube 2 and the shunt tube 1 are connected by a plurality of heat exchange tubes, and the plurality of heat exchange tubes are spaced apart in the up and down direction, and the collecting tube 2 has an outlet 21 for discharging the refrigerant, as shown in FIGS. 1 and 2,
  • the refrigerant enters the heat exchange tube from the branch pipe 1 through a plurality of split ports, and the refrigerant exotherms or absorbs heat in the heat exchange tubes, and the refrigerant that has passed through the heat release or heat absorption finally enters the header tube 2 and enters the other flow paths through the outlet 21.
  • the refrigerant flows from the bottom inlet 12 of the body 11 from the bottom to the top through each of the split ports, and the refrigerant passing through each of the split ports passes through the heat transfer tubes and enters the header 2.
  • the body 11 In the direction from bottom to top, the body 11 includes a plurality of sections of tubes, and the flow area of the tubes located downstream of each adjacent two sections is smaller than the flow area of the tubes located upstream, and the number N of the tubes is 2 ⁇ N ⁇ 3, that is, the number of tubes is two or three.
  • the body 11 includes a first tube body 111 and a second tube body 112, the inlet 12 is disposed on the first tube body 111, and the second tube body 112 is cross-sectioned.
  • the area is smaller than the cross-sectional area of the first pipe body 111, in other words, the flow area of the second pipe body 112 is smaller than the flow area of the first pipe body 111, so that the refrigerant first enters the first pipe body 111 from the inlet 12 at a certain speed.
  • the refrigerant in the first pipe body 111 flows from the bottom to the top.
  • the body 11 may also include a first tube body 111, a second tube body 112, and a third tube body 113.
  • the flow area of the second pipe body 112 is smaller than the flow area of the first pipe body 111
  • the flow area of the third pipe body 113 is smaller than the flow area of the second pipe body 112.
  • the same principle is adopted.
  • the length and the flow area of the first pipe body 111, the second pipe body 112 and the third pipe body 113 are arranged, so that the refrigerant can flow through the split port of the top of the body 11, so that the corresponding corresponding to the third pipe body 113 can be effectively improved.
  • the utilization rate of the heat exchange tubes thereby effectively improving the working efficiency of the heat exchanger 100.
  • each of the tubes is not more than 0.5 m, so that the refrigerant can be further circulated to reach the top portion of the body 11, thereby effectively improving the working efficiency of the upper portion of the heat exchanger 100.
  • the flow area of the tubes located downstream of each adjacent two stages is smaller than the flow area of the tubes located upstream, thereby Increasing the flow rate of the liquid refrigerant when the refrigerant flows through the variable diameter of each two-stage pipe body, and the purpose of accelerating on the way to ensure the upper portion of the shunt pipe 1
  • the domain is also capable of obtaining sufficient liquid refrigerant to ensure efficient use of the heat exchanger 100, so that the heat exchanger 100 can better distribute the two-phase refrigerant without the split capillary.
  • the body 11 is configured such that the flow rate of the liquid refrigerant flowing through the variable diameter of each adjacent two-stage pipe body is substantially equal to the flow rate of the liquid refrigerant of the inlet 12, that is, the pipe body of each adjacent two stages
  • the difference in flow area is designed to increase the flow rate of the liquid refrigerant flowing through the variable path to a flow rate substantially equal to the liquid refrigerant at the inlet. Therefore, the effect of accelerating the liquid refrigerant on the way is further ensured, and the speed of the liquid refrigerant entering from the upstream pipe body to the downstream pipe body is not significantly reduced, so that the liquid refrigerant can enter the heat exchange pipe in the upper region of the heat exchanger 100. The working efficiency of the heat exchanger 100 is further effectively improved.
  • the flow rate of the liquid refrigerant at the variable diameter of each adjacent two-stage pipe body and the flow rate of the liquid refrigerant of the inlet 12 are both in the range of 0.4 to 0.6 m/s, so that the flow rate of the liquid refrigerant is controlled to be constant.
  • the liquid refrigerant can be efficiently passed through the split port into the heat exchange tube, thereby improving the working efficiency of the entire heat exchanger 100.
  • the header 2 is formed as a straight tube.
  • the refrigerant flowing out of the heat exchange tube enters the header 2, and the refrigerant flows from the top to the bottom in the header 2.
  • the header 2 By constructing the header 2 as a straight tube, the circulation of the refrigerant can be facilitated, thereby improving the heat exchanger 100. Work efficiency.
  • the heat exchange tube is a flat tube, so that the heat exchange area between the refrigerant and the air can be increased, so that the refrigerant absorbs heat or exotherms better, thereby effectively improving the working efficiency of the heat exchanger 100.
  • fins may be arranged between each adjacent two heat exchange tubes in the up and down direction to increase the heat exchange area between the heat exchanger 100 and the air, and further improve the heat exchange effect of the heat exchanger 100.
  • the present invention also proposes a multi-line system comprising the heat exchanger 100 described above.
  • the first feature "on” or “under” the second feature may be a direct contact of the first and second features, or the first and second features may be indirectly through an intermediate medium, unless otherwise explicitly stated and defined. contact.
  • the first feature "above”, “above” and “above” the second feature may be that the first feature is directly above or above the second feature, or merely that the first feature level is higher than the second feature.
  • the first feature “below”, “below” and “below” the second feature may be that the first feature is directly below or obliquely below the second feature, or merely that the first feature level is less than the second feature.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

提供一种换热器（100）及具有其的多联机系统。换热器（100）包括分流管（1）和集流管（2）。分流管（1）包括本体（11），入口（12）和多个分流口。入口（12）设在本体（11）的底部，多个分流口在本体（11）的长度方向上分布在本体（11）的侧壁上。在从下到上的方向上，本体（11）包括多段管体，每相邻两段的管体中位于下游的管体的流通面积小于位于上游的管体的流通面积，每段管体的高度不大于0.5m，管体的数目N为2≤N≤3。集流管（2）和分流管（1）之间通过多个换热管连通，多个换热管在上下方向上间隔分布，集流管（2）具有排出冷媒的出口（21）。

Description

换热器及具有其的多联机系统 技术领域
本发明涉及换热器设备领域，尤其涉及一种换热器及具有该换热器的多联机系统。
背景技术
相关技术中的多联机系统由室外机、室内机以及室内外间的冷媒流向切换装置组成，按照室外机与冷媒流向切换装置之间冷媒配管根数不同又分为三管制(即冷媒配管为三根)和两管制(即冷媒配管为两根)，其中两管制室外机虽然冷媒回路相对复杂，但由于施工相对简单且成本较低备受关注。
对于两管制多联机系统，室外机换热器须设计为冷媒流向固定，即冷媒流向与制冷或制热无关，为了减小室外机制冷时的冷媒流动阻力通常用笛形管代替传统热泵机的毛细管设计，这往往会造成室外机制热时的两相冷媒偏流，导致系统制热性能低下。
发明内容
本发明旨在至少解决现有技术中存在的技术问题之一。为此，本发明提出一种换热器，所述换热器能够在没有分流毛细管的情况下较好地分配两相冷媒。
本发明还提出了一种具有上述换热器的多联机系统。
根据本发明实施例的换热器，包括：分流管，所述分流管包括本体、入口和多个分流口，所述入口设在所述本体的底部，所述多个分流口在所述本体的长度方向上分布在所述本体的侧壁上，在从下到上的方向上，所述本体包括多段管体，每相邻两段的所述管体中位于下游的管体的流通面积小于位于上游的管体的流通面积，每段所述管体的高度不大于0.5m，所述管体的数目N为2≤N≤3；集流管，所述集流管和所述分流管之间通过多个换热管连通，所述多个换热管在上下方向上间隔分布，所述集流管具有排出冷媒的出口。
根据本发明实施例的换热器，能够在没有分流毛细管的情况下较好地分配两相冷媒。
具体地，所述本体被构造成使得流过每相邻两段管体的变径处的液态冷媒的流速大体等于所述入口的液态冷媒的流速。
进一步地，每相邻两段管体的变径处的液态冷媒的流速和所述入口的液态冷媒的流速的取值范围均为0.4～0.6m/s。
具体地，所述集流管形成为直管。
具体地，所述换热管为扁管。
此外，本发明还提出了一种多联机系统，其包括上述的换热器。
附图说明
图1是根据本发明一个实施例的换热器的示意图；
图2是根据本发明另一个实施例的换热器的示意图。
附图标记：
换热器100；
分流管1；本体11；第一管体111；第二管体112；第三管体113；
入口12；
集流管2；出口21。
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。
在本发明的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”“内”、“外”、“顺时针”、“逆时针”、“轴向”、“径向”、“周向”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。
下面参照图1-图2描述根据本发明实施例的换热器100，其中换热器100可以应用在制冷装置例如单冷机、冷暖机或多联机系统中。
如图1和图2所示，根据本发明实施例的换热器100，包括分流管1、换热管(图中未 示出)和集流管2。
具体地，如图1所示，分流管1包括本体11、入口12和多个分流口(图中未示出)，入口12设在本体11的底部，多个分流口在本体11的长度方向上分布在本体11的侧壁上。
集流管2和分流管1之间通过多个换热管连通，多个换热管在上下方向上间隔分布，集流管2具有排出冷媒的出口21，参考图1和图2所示，冷媒从分流管1通过多个分流口进入换热管，冷媒在换热管里进行放热或吸热，经过放热或吸热的冷媒最后进入集流管2通过出口21进入其他流路。
也就是说，冷媒会从本体11的底部入口12从下向上的流经每个分流口，通过每个分流口的冷媒会经过换热管进入集流管2。
在从下到上的方向上，本体11包括多段管体，每相邻两段的管体中位于下游的管体的流通面积小于位于上游的管体的流通面积，管体的数目N为2≤N≤3，也就是说，管体的数量为两个或三个。
参考图1所示，例如在本发明的一个实施例中，本体11包括第一管体111和第二管体112，入口12设在第一管体111上，第二管体112的横截面积小于第一管体111的横截面积，换言之，第二管体112的流通面积小于第一管体111的流通面积，这样，冷媒会以一定的速度先从入口12进入第一管体111，第一管体111内的冷媒由下向上流动，经过分流口时，一部分冷媒会通过分流口经过换热管进入集流管2，第一管体111中的液态冷媒向上流动的过程中会越来越少，冷媒的速度也有降低的趋势，接着冷媒进入第二管体112，由于第二管体112的流通面积比第一管体111的流通面积小，从而起到了一定加速冷媒的趋势，从而保证了冷媒在第二管体112内的速度不会明显降低，进而保证了第二管体112中也能有足够的冷媒通过分流口流入换热管，有效地提高了换热器100的工作效率。
当然，本发明不限于此，如图2所示，在本发明的另一个实施例中，本体11也可以包括第一管体111、第二管体112和第三管体113，入口12设在第一管体111上，第二管体112的流通面积小于第一管体111的流通面积，第三管体113的流通面积小于第二管体112的流通面积，相同的原理，通过合理的设置第一管体111、第二管体112和第三管体113长度和流通面积，可以使得冷媒可以流经本体11的顶部的分流口，从而可有效地提高第三管体113对应的换热管的利用率，进而有效地提高换热器100的工作效率。
每段管体的高度不大于0.5m，这样，可进一步确保冷媒可以流通达到本体11的顶部区域，从而有效提高换热器100上部区域的工作效率。
根据本发明实施例的换热器100，通过使得本体11具有多个管体，每相邻两段的管体中位于下游的管体的流通面积小于位于上游的管体的流通面积，从而可以在冷媒流经每两段管体的变径处的时候提高液态冷媒的流速，起到途中加速的目的，保证分流管1上部区 域也能够得到足够的液态冷媒，保证换热器100得到高效利用，从而换热器100能够在没有分流毛细管的情况下较好地分配两相冷媒。
具体地，本体11被构造成使得流过每相邻两段管体的变径处的液态冷媒的流速大体等于入口12的液态冷媒的流速，也就是说，将每相邻两段的管体的流通面积的差值设计成可将流经该变径处的液态冷媒的流速提高至大体等于入口处的液态冷媒流速。从而进一步保证对液态冷媒起到途中加速的作用，保证从上游管体进入到下游管体的液态冷媒速度不会明显降低，进而使得液态冷媒可进入换热器100的上部区域的换热管，进一步有效地提高换热器100的工作效率。
具体地，每相邻两段管体的变径处的液态冷媒的流速和入口12的液态冷媒的流速的取值范围均为0.4～0.6m/s，这样，将液态冷媒的流速控制在一定的范围内，可有效地将液态冷媒大致平均的通过分流口进入换热管内，从而提高整个换热器100的工作效率。
参考图1和图2所示的示例，集流管2形成为直管。从换热管流出的冷媒进入集流管2，冷媒在集流管2内从上向下流通，通过将集流管2构造为直管，可以有利于冷媒的流通，从而提高换热器100的工作效率。
在本发明的一个示例中，换热管为扁管，这样，可以增加冷媒与空气的换热面积，从而使得冷媒更好地吸热或放热，进而有效地提高换热器100的工作效率。同时在上下方向每相邻的两个换热管之间可以设有翅片，以增加整个换热器100与空气的换热面积，进一步提高换热器100的换热效果。
此外，本发明还提出了一种多联机系统，其包括上述的换热器100。
在本发明中，除非另有明确的规定和限定，第一特征在第二特征“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
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 (6)

  1. 一种换热器，其特征在于，包括：
    分流管，所述分流管包括本体、入口和多个分流口，所述入口设在所述本体的底部，所述多个分流口在所述本体的长度方向上分布在所述本体的侧壁上，在从下到上的方向上，所述本体包括多段管体，每相邻两段的所述管体中位于下游的管体的流通面积小于位于上游的管体的流通面积，每段所述管体的高度不大于0.5m，所述管体的数目N为2≤N≤3；
    集流管，所述集流管和所述分流管之间通过多个换热管连通，所述多个换热管在上下方向上间隔分布，所述集流管具有排出冷媒的出口。
  2. 根据权利要求1所述的换热器，其特征在于，所述本体被构造成使得流过每相邻两段管体的变径处的液态冷媒的流速大体等于所述入口的液态冷媒的流速。
  3. 根据权利要求2所述的换热器，其特征在于，每相邻两段管体的变径处的液态冷媒的流速和所述入口的液态冷媒的流速的取值范围均为0.4～0.6m/s。
  4. 根据权利要求1-3中任一项所述的换热器，其特征在于，所述集流管形成为直管。
  5. 根据权利要求1-4中任一项所述的换热器，其特征在于，所述换热管为扁管。
  6. 一种多联机系统，其特征在于，包括根据权利要求1-5中任一项所述的换热器。
PCT/CN2015/098131 2015-03-31 2015-12-21 换热器及具有其的多联机系统 Ceased WO2016155367A1 (zh)

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