WO2020143539A1 - 一种换热器和空调器 - Google Patents

一种换热器和空调器 Download PDF

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Publication number
WO2020143539A1
WO2020143539A1 PCT/CN2020/070181 CN2020070181W WO2020143539A1 WO 2020143539 A1 WO2020143539 A1 WO 2020143539A1 CN 2020070181 W CN2020070181 W CN 2020070181W WO 2020143539 A1 WO2020143539 A1 WO 2020143539A1
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WIPO (PCT)
Prior art keywords
bypass
heat exchange
tube
supercooling
heat exchanger
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PCT/CN2020/070181
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English (en)
French (fr)
Inventor
王飞
许文明
付裕
郭刚
张心怡
Original Assignee
青岛海尔空调器有限总公司
海尔智家股份有限公司
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Publication of WO2020143539A1 publication Critical patent/WO2020143539A1/zh

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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
    • 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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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

Definitions

  • the invention relates to the technical field of heat exchangers, in particular to a heat exchanger and an air conditioner.
  • a shunt tube or a shunt is usually used for the shunt design, but the conventional shunt method has no direction distinction. It passes through the same pipeline during cooling operation and heating operation. When the device is in cooling operation, it meets the cooling operation requirements through the supercooling pipeline, while in the heating operation, it still passes through the supercooling pipeline, which will increase the pressure loss of the system and reduce the heat exchange efficiency of the system.
  • Embodiments of the present invention provide a heat exchanger and an air conditioner to solve the problem of reduced heat exchange efficiency during heating operation of the heat exchanger.
  • a brief summary is given below. This summary section is not a general comment, nor is it to determine key/important constituent elements or to describe the scope of protection of these embodiments. Its sole purpose is to present some concepts in a simple form as a preface to the detailed description that follows.
  • a heat exchanger is provided.
  • the above heat exchanger includes a heat exchange tube group
  • the supercooling tube group is connected in series with the heat exchange tube group; and the supercooling tube group and the heat exchange tube group form a flow path with a double-row arrangement structure;
  • Supercooling bypass pipe the supercooling bypass pipe is connected in parallel with the first pipe section of the supercooling pipe group and the heat exchange pipe group;
  • a bypass bypass pipe which is connected in parallel with at least part of the first pipe section of the heat exchange tube group and at least part of the second pipe section except the first pipe section;
  • the supercooling check valve is provided on the supercooling bypass pipe, and the conduction direction of the supercooling check valve is limited to flow from the parallel node of the supercooling bypass pipe with the supercooling pipe group to the parallel node with the first pipe section;
  • the shunt check valve is arranged on the shunt bypass pipe, and the conduction direction of the shunt check valve is defined as flowing from the parallel node of the heat exchange tube group with the first pipe section to the parallel node with at least part of the pipe section of the second pipe section.
  • the number of heat exchange tubes in the first tube section of the heat exchange tube group in which the supercooling bypass tubes are connected in parallel is less than or equal to the number of heat exchange tubes in the supercooling tube group in which they are connected in parallel.
  • the number of heat exchange tubes in the first tube section of the heat exchange tube group in which the subcooling bypass tubes are connected in parallel is less than or equal to the number of heat exchange tubes in at least part of the tube sections of the second tube section in which the bypass bypass tubes are connected in parallel .
  • the number of heat exchange tubes of the subcooling tube group in which the subcooling bypass tubes are connected in parallel is greater than or equal to the number of heat exchange tubes in at least part of the tube sections of the second tube section connected in parallel with the bypass bypass tubes.
  • the number of supercooling bypass tubes is multiple, and multiple supercooling bypass tubes are connected in parallel.
  • the number of heat exchange tubes of the first tube section of the heat exchange tube group in which multiple subcooling bypass tubes are connected in parallel is the same or different.
  • the number of bypass bypass pipes is multiple, and multiple subcooling bypass pipes are connected in parallel.
  • the number of the heat exchange tubes of the second tube section of the heat exchange tube group in which the multiple bypass bypass tubes are connected in parallel is the same or different.
  • an air conditioner is provided.
  • the above air conditioner includes an indoor heat exchanger, an outdoor heat exchanger, a compressor and a refrigerant circulation flow path formed by connecting four-way valves; wherein, the outdoor heat exchanger is any of the optional embodiments described above In the heat exchanger, the heat exchange tube group of the heat exchanger communicates with the compressor, and the subcooling tube group communicates with the indoor heat exchanger.
  • another air conditioner is further provided.
  • the air conditioner includes an indoor heat exchanger, an outdoor heat exchanger, a compressor, and a refrigerant circulation flow path formed by connecting four-way valves; wherein, the indoor heat exchanger is any of the optional embodiments described above In the heat exchanger, the heat exchange tube group of the heat exchanger communicates with the compressor, and the subcooling tube group communicates with the indoor heat exchanger.
  • the technical solution provided by the embodiment of the present invention may include the following beneficial effects: when the heat exchanger is in heating operation, the heat exchanger is divided by a one-way valve, which can reduce the complexity of the system and reduce the overcooling during heating The pressure loss of the system caused by the pipe group improves the heat exchange efficiency of the system.
  • Fig. 1 is a schematic structural diagram of a heat exchanger according to an exemplary embodiment.
  • the terms "include”, “include” or any other variant thereof are intended to cover non-exclusive inclusion, so that a structure, device, or device that includes a series of elements includes not only those elements, but also others that are not explicitly listed Elements, or include elements inherent to such structures, devices, or equipment. Without further restrictions, the element defined by the sentence "including one" does not exclude that there are other identical elements in the structure, device or equipment that includes the element.
  • the embodiments in this document are described in a progressive manner. Each embodiment focuses on the differences from other embodiments. The same and similar parts between the embodiments can be referred to each other.
  • connection should be understood in a broad sense, for example, it may be a mechanical connection or an electrical connection, or it may be the communication between two elements, It may be directly connected or indirectly connected through an intermediary.
  • connection should be understood in a broad sense, for example, it may be a mechanical connection or an electrical connection, or it may be the communication between two elements, It may be directly connected or indirectly connected through an intermediary.
  • connection should be understood in a broad sense, for example, it may be a mechanical connection or an electrical connection, or it may be the communication between two elements, It may be directly connected or indirectly connected through an intermediary.
  • the term “plurality” means two or more.
  • A/B means: A or B.
  • a and/or B means: A or B, or A and B.
  • a heat exchanger including a heat exchange tube group 1, a supercooled tube group 2, a supercooled bypass tube 3, a bypass bypass tube 5, a supercooled check valve 4, a split flow Directional valve 6, in which the supercooling tube group 2 and the heat exchange tube group 1 are connected in series, and the supercooling tube group 2 and the heat exchange tube group 1 form a flow path of a double-row arrangement structure;
  • the supercooling bypass tube 3 is The subcooling pipe group 2 is connected in parallel with the first pipe section;
  • the bypass bypass pipe 5 is connected in parallel with at least part of the pipe sections of the first pipe section and the second pipe section;
  • the subcooling check valve 4 is provided on the subcooling bypass pipe 3;
  • the directional valve 6 is provided on the bypass bypass pipe 5;
  • the heat exchange pipe group 1 includes a first pipe section and a second pipe section.
  • the conduction direction of the supercooling one-way valve 4 is defined as that the parallel node of the supercooling bypass pipe 3 and the supercooling pipe group 2 flows to the parallel node of the supercooling bypass pipe 3 and the first pipe section;
  • the conducting direction of the shunt check valve 6 is defined as a parallel node of the heat exchange tube group 1 and the first tube section, and a parallel node of the heat exchange tube group 1 and at least part of the tube section of the second tube section.
  • the heat exchange tube group 1 includes a first tube section and a second tube section connected in series.
  • the first tube section may be the heat exchange tube group 1 connected to the supercooled tube group 2 and connected in parallel with the supercooled bypass tube 3
  • a section of the heat exchange tube group 1 the second tube section may be a portion of the heat exchange tube group 1 other than the first tube section, wherein the portion of the second tube section parallel to the bypass bypass pipe 5 is at least part of the second tube section,
  • the portion of the second pipe section except at least part of the second pipe section is other pipe sections of the second pipe section.
  • the parallel node of the supercooled tube group 2 and the supercooled bypass tube 3 may be the first node
  • the parallel node of the first tube segment and the bypass bypass tube 5 may be the second node
  • the parallel node of the tube 3 may be a third node
  • the parallel node of the shunt bypass tube 5 and at least part of the second tube section may be a fourth node.
  • the refrigerant circulates in the second tube section, the first tube section, and the subcooled tube group 2, and the refrigerant flow path is at least part of the tube section entering the second tube section from the fourth node, Flowing through the third node, to the first pipe section, through the second node, to the supercooling pipe group 2, because the supercooling check valve 4 and the split check valve 6 are check valves, so during cooling operation, cooling
  • the flow of refrigerant from the fourth node to the first node does not flow through the cold check valve 4 and the split check valve 6, that is, the flow of refrigerant from the fourth node to the first node does not flow through the cold bypass In the tube 3 and the bypass bypass tube 5, the refrigerant passes through the second tube section of the heat exchange tube group 1 to the first tube section, and then passes through the supercooled tube group 2, so that the refrigerant is recooled when passing through the supercooled tube group 2,
  • the refrigerant can be sufficiently cooled so that it
  • the refrigerant provided by the present invention is not limited, and may be a refrigerant.
  • the refrigerant flow path is a path.
  • the refrigerant enters at least part of the second pipe section, the refrigerant is in a gaseous state.
  • the refrigerant passes through the first tube section and the supercooling tube group 2 in turn, the state of the refrigerant gradually passes through the gas-liquid mixing, and passes through the supercooling tube group 2, and finally the refrigerant flowing out at the first node is guaranteed to be fully condensed into a liquid state.
  • Longer supercooling tube group 2 is necessary to ensure the cooling effect.
  • the heat exchanger added to subcooling tube group 2 has better cooling effect and more cooling effect than the heat exchanger passing only heat exchange tube group 1. Good, heat exchange efficiency is guaranteed.
  • the refrigerant circulates in the subcooling bypass pipe 3, the first pipe section, and the bypass bypass pipe 5.
  • the refrigerant flow path is from the first node to the subcooling bypass Tube 3, and shunt two channels at the first node, one to the supercooled tube group 2, the other to the supercooled bypass tube 3, and the refrigerant flowing to the supercooled bypass tube 3 flows to the third node, at point three Divide the two channels again, one to the first pipe section, at the second node, the refrigerant flowing through the cold pipe group 2 merges with the refrigerant flowing through the first pipe section, and flows to the bypass bypass pipe 5, at the third node The other way flows to at least part of the second pipe section.
  • the refrigerant flowing through the bypass bypass pipe 5 merges with the refrigerant flowing through at least part of the pipe section of the second pipe section and flows to other pipe sections of the second pipe section.
  • Forming a three-way shunt when the refrigerant in the gas-liquid mixed state enters from the first node, if there is no subcooling bypass pipe 3 provided with a supercooling check valve 4 and a shunt bypass with a shunt check valve 6 Tube 5, the resistance of the refrigerant is large, which will reduce the heat exchange efficiency and affect the heating effect.
  • the flow path from the first node through the supercooled tube group 2 to the second node may be the first flow path
  • the flow path from the first node through the supercooled bypass tube 3 to the third node may be the second flow path
  • the flow path from the second node through the bypass bypass 5 to the fourth node may be the third flow path
  • the path from the third node through the first pipe section to the second node may be the fourth flow path, from the first
  • the flow path from the three nodes to the fourth node through at least part of the second pipe section may be a fifth flow path.
  • the refrigerant provided by the present invention is not limited, and may be a refrigerant.
  • the refrigerant flow path is three paths, and one path is from the first node to the second through the supercooling tube group 2 Node, through the bypass bypass 5 to the fourth node; a path is the first node through the supercooled bypass 3 to the third node, through the first pipe section to the second node, after the bypass bypass 5 to the fourth node
  • the other path is that the first node passes through the supercooled bypass pipe 3 to the third node, and passes through at least part of the second pipe section to the fourth node.
  • the first path is the first flow path to the third flow path;
  • the second path is the second flow path to the fourth flow path to the third flow path;
  • the third path is the second flow path to the fifth flow path.
  • the heat exchanger is shunted by the one-way valve during the heating operation, which can reduce the complexity of the system and reduce the system pressure loss caused by the supercooling tube group 2 during heating , Thereby improving the heat exchange efficiency of the system.
  • the number of heat exchange tubes in the first tube section of the heat exchange tube group 1 in which the supercooling bypass tubes 3 are connected in parallel is less than or equal to the number of heat exchange tubes in the supercooling tube group 2 in parallel.
  • the refrigerant flow path is three paths, one path is from the first node through the supercooling tube group 2 to the second node, through the bypass bypass pipe 5 to the fourth node ; One path is the first node through the supercooled bypass pipe 3 to the third node, after the first pipe section to the second node, through the bypass bypass pipe 5 to the fourth node; the other path is the first node through the supercooled bypass Pass the pipe 3 to the third node and pass at least part of the pipe section of the second pipe section to the fourth node.
  • the first path is the first flow path to the third flow path; the second path is the second flow path to the fourth flow path to the third flow path; and the third path is the second flow path to the fifth flow path.
  • the number of heat exchange tubes in the first pipe section is greater than the number of heat exchange tubes in the supercooled pipe group 2
  • the flow pressure difference between the two ends of the first pipe section will be greater than that of the supercooled pipe group 2
  • the refrigerant is at the first node
  • the flow rate of refrigerant flowing to the first path will be greater than the flow rate of refrigerant flowing to the second path.
  • the role of the subcooling bypass pipe 3 will be greatly weakened, and the setting of the subcooling bypass pipe 3 will not be effective
  • the expected effect cannot allow refrigerant circulation to achieve multi-path diversion, and cannot well alleviate the resistance loss of the flow path. Therefore, when the number of heat exchange tubes in the first tube section of the heat exchange tube group 1 is less than or equal to the number of heat exchange tubes in the supercooled tube group 2, the multi-path can be better achieved when the heat exchanger is in heating operation Diversion reduces the greater resistance when the refrigerant enters the first node, reduces the resistance loss of the flow path, and improves the heating efficiency.
  • the heat exchanger is shunted by the one-way valve during the heating operation, which can reduce the complexity of the system and reduce the system pressure loss caused by the supercooling tube group 2 during heating , Thereby improving the heat exchange efficiency of the system.
  • the number of heat exchange tubes of the first tube section of the heat exchange tube group 1 in which the subcooling bypass tube 3 is connected in parallel is less than or equal to the heat exchange of at least part of the tube sections of the second tube section in which the bypass bypass tube 5 is connected in parallel The number of tubes.
  • the refrigerant flow path is three paths, one path is from the first node through the supercooling tube group 2 to the second node, through the bypass bypass pipe 5 to the fourth node ; One path is the first node through the supercooled bypass pipe 3 to the third node, after the first pipe section to the second node, through the bypass bypass pipe 5 to the fourth node; the other path is the first node through the supercooled bypass Pass the pipe 3 to the third node and pass at least part of the pipe section of the second pipe section to the fourth node.
  • the first path is the first flow path to the third flow path; the second path is the second flow path to the fourth flow path to the third flow path; and the third path is the second flow path to the fifth flow path.
  • the number of heat exchange tubes in the first tube section is greater than the number of heat exchange tubes in at least part of the tube sections of the second tube section, the flow pressure difference between the two ends of the first tube section will be greater than the flow pressure difference between at least part of the second tube section, then the refrigerant At the third node, the flow rate of refrigerant flowing to the fifth path will be greater than the flow rate of refrigerant flowing to the fourth path.
  • the role of the bypass bypass pipe 5 will be greatly weakened, and the setting of the bypass bypass pipe 5 will play a role. If the expected effect is not achieved, the circulation of refrigerant cannot be divided into multiple paths, and the resistance loss of the flow path cannot be well relieved. Therefore, when the number of heat exchange tubes in the first tube section of the heat exchange tube group 1 is less than or equal to the number of heat exchange tubes in at least part of the tube sections of the second tube section, the heat exchanger can be better realized during heating operation The multi-path diversion relieves the greater resistance when the refrigerant enters the first node, reduces the resistance loss of the flow path, and improves the heating efficiency.
  • the heat exchanger is shunted by the one-way valve during the heating operation, which can reduce the complexity of the system and reduce the system pressure loss caused by the supercooling tube group 2 during heating , Thereby improving the heat exchange efficiency of the system.
  • the number of heat exchange tubes of the supercooled tube group 2 in which the subcooling bypass tubes 3 are connected in parallel is greater than or equal to the number of heat exchange tubes in at least part of the tube sections of the second tube section in which the bypass bypass tubes 5 are connected in parallel.
  • the refrigerant flow path is three paths, one path is from the first node through the supercooling tube group 2 to the second node, through the bypass bypass pipe 5 to the fourth node ; One path is the first node through the supercooled bypass pipe 3 to the third node, after the first pipe section to the second node, through the bypass bypass pipe 5 to the fourth node; the other path is the first node through the supercooled bypass Pass the pipe 3 to the third node and pass at least part of the pipe section of the second pipe section to the fourth node.
  • the first path is the first flow path to the third flow path; the second path is the second flow path to the fourth flow path to the third flow path; and the third path is the second flow path to the fifth flow path.
  • the number of heat exchange tubes in at least part of the second tube section is greater than the number of heat exchange tubes in the subcooled tube group 2
  • the flow pressure difference between the two ends of the at least part of the second tube section will be greater than the flow pressure difference between the two ends of the subcooled tube group 2
  • the refrigerant flow at the first node, the flow rate of refrigerant flowing to the first path will be greater than the flow rate of refrigerant flowing to the third path, at this time, the role of the subcooling bypass pipe 3 will be greatly weakened, the subcooling bypass
  • the arrangement of the tube 3 does not play the expected role, the refrigerant can not be circulated to realize the multi-path diversion, and the flow path resistance loss cannot be alleviated well.
  • the multi-path splitting can be better achieved when the heat exchanger is in heating operation.
  • the greater resistance when the refrigerant enters the first node is alleviated, the flow path resistance loss is reduced, and the heating efficiency is improved.
  • the heat exchanger is shunted by the one-way valve during the heating operation, which can reduce the complexity of the system and reduce the system pressure loss caused by the supercooling tube group 2 during heating , Thereby improving the heat exchange efficiency of the system.
  • the number of the subcooling bypass tubes 3 is plural, and the plurality of subcooling bypass tubes 3 are connected in parallel.
  • the number of supercooling bypass tubes 3 is not limited, and may include first supercooling bypass tubes 3 and second supercooling bypass tubes 3, first supercooling bypass tubes 3 and second supercooling bypass
  • the through pipe 3 may be connected in parallel. Under the condition that the flow pressure difference between the two ends of the subcooling bypass pipe 3 is unchanged, the refrigerant entering the first node can play a better shunt effect.
  • the heat exchanger is shunted by the one-way valve during the heating operation, which can reduce the complexity of the system and reduce the system pressure loss caused by the supercooling tube group 2 during heating , Thereby improving the heat exchange efficiency of the system.
  • the number of the heat exchange tubes of the first tube section of the heat exchange tube group 1 in which multiple subcooling bypass tubes 3 are connected in parallel is the same or different.
  • the multiple supercooling bypass pipes 3 are connected in parallel, and the flow pressure of the two ends of the supercooling bypass pipes 3 remains unchanged, and the refrigerant entering the first node can be diverted.
  • the heat exchange tubes in the heat exchange tube group 1 can be connected in series. The more heat exchange tubes in series, the longer the refrigerant flow path, the greater the pressure resistance of the heat exchange tube group 1, and the greater the power loss. Large, the first tube section of the heat exchange tube group 1 belongs to the heat exchange tube group 1, the same reason, therefore, the number of heat exchange tubes of the first tube section of the heat exchange tube group 1 is parallel to the heat exchange of the supercooling bypass tube 3 The number of tube groups 1 may be the same.
  • the multiple supercooling bypass pipes 3 are connected in parallel, and the flow pressure of the two ends of the supercooling bypass pipes 3 remains unchanged, and the refrigerant entering the first node can be diverted.
  • the heat exchange tubes in the heat exchange tube group 1 can be connected in series. The more heat exchange tubes in series, the longer the refrigerant flow path, the greater the pressure resistance of the heat exchange tube group 1, and the greater the power loss. Large, the first tube section of the heat exchange tube group 1 belongs to the heat exchange tube group 1, the same reason, therefore, the number of heat exchange tubes of the first tube section of the heat exchange tube group 1 is parallel to the heat exchange of the supercooling bypass tube 3 The number of the tube group 1 may be different.
  • the heat exchanger is shunted by the one-way valve during the heating operation, which can reduce the complexity of the system and reduce the system pressure loss caused by the supercooling tube group 2 during heating , Thereby improving the heat exchange efficiency of the system.
  • the number of the bypass bypass tubes 5 is multiple, and the multiple subcooling bypass tubes 3 are connected in parallel.
  • the number of shunt bypass pipes 5 is not limited, and may include a first shunt bypass pipe and a second shunt bypass pipe, and the first shunt bypass pipe and the second shunt bypass pipe may be connected in parallel, Under the condition that the flow pressure difference between the two ends of the bypass bypass pipe 5 is unchanged, the refrigerant entering the third node can be better divided.
  • the heat exchanger is shunted by the one-way valve during the heating operation, which can reduce the complexity of the system and reduce the system pressure loss caused by the supercooling tube group 2 during heating , Thereby improving the heat exchange efficiency of the system.
  • the number of heat exchange tubes of the second tube section of the heat exchange tube group 1 in which the plurality of bypass bypass tubes 5 are connected in parallel is the same or different.
  • connection modes of the plurality of bypass bypass pipes 5 are parallel connections.
  • the refrigerant entering the third node can be diverted, and The heat exchange tubes in the heat exchange tube group 1 can be connected in series.
  • the greater the number of heat exchange tubes in series the longer the refrigerant flow path, the greater the pressure resistance of the heat exchange tube group 1, and the greater the power loss.
  • the second tube section of the heat exchange tube group 1 belongs to the heat exchange tube group 1, for the same reason, therefore, the number of heat exchange tubes of the second tube section of the heat exchange tube group 1 is parallel to the heat exchange tube group 1 of the bypass bypass tube 5 The number can be the same.
  • connection modes of the plurality of bypass bypass pipes 5 are parallel connections.
  • the refrigerant entering the third node can be diverted, and The heat exchange tubes in the heat exchange tube group 1 can be connected in series.
  • the greater the number of heat exchange tubes in series the longer the refrigerant flow path, the greater the pressure resistance of the heat exchange tube group 1, and the greater the power loss.
  • the second tube section of the heat exchange tube group 1 belongs to the heat exchange tube group 1, for the same reason, therefore, the number of heat exchange tubes of the second tube section of the heat exchange tube group 1 is parallel to the heat exchange tube group 1 of the bypass bypass tube 5 The number can be different.
  • the heat exchanger is shunted by the one-way valve during the heating operation, which can reduce the complexity of the system and reduce the system pressure loss caused by the supercooling tube group 2 during heating , Thereby improving the heat exchange efficiency of the system.
  • An embodiment of the present invention further provides an air conditioner, including an indoor heat exchanger, an outdoor heat exchanger, a compressor, and a refrigerant circulation flow path connected by a four-way valve; wherein, the outdoor heat exchanger is any optional implementation as described above
  • the heat exchange tube group 1 of the heat exchanger communicates with the compressor
  • the subcooling tube group 2 communicates with the indoor heat exchanger.
  • the outdoor heat exchanger of the air conditioner is installed in the outdoor unit of the air conditioner, and the volume of the outdoor unit of the air conditioner is more unrestricted.
  • the outdoor heat exchanger is the outdoor heat exchanger as described in any of the optional embodiments above, the supercooled side A plurality of subcooling bypass tubes 3 connected in parallel in the group of 3 pass tubes, and a plurality of bypass bypass tubes 5 can occupy more space and have higher heat exchange efficiency of the air conditioner.
  • the outdoor heat exchanger when the air conditioner is performing cooling operation, includes a heat exchange tube group 1, a subcooling tube group 2, a subcooling bypass tube 3, a bypass bypass tube 5, a supercooling check valve 4, a shunt One-way valve 6, in which the supercooling tube group 2 and the heat exchange tube group 1 are connected in series, and the supercooling tube group 2 and the heat exchange tube group 1 form a flow path of a double-row arrangement structure;
  • the supercooling bypass tube 3 It is connected in parallel with the supercooling tube group 2 and the first tube section;
  • the bypass bypass tube 5 is connected in parallel with at least part of the tube sections of the first tube section and the second tube section;
  • the subcooling check valve 4 is provided on the subcooling bypass tube 3;
  • the check valve 6 is provided on the bypass bypass pipe 5.
  • the refrigerant circulates in the second pipe section, the first pipe section, and the supercooled pipe group 2.
  • the refrigerant flow path is at least part of the pipe section that enters the second pipe section from the fourth node, flows through the third node, and reaches the first pipe section, flows through the From the second node to the supercooled pipe group 2, since the supercooled check valve 4 and the split check valve 6 are both check valves, during the cooling operation, the flow of refrigerant from the fourth node to the first node does not flow.
  • the refrigerant passes through the heat exchange tube group 1 The second pipe section to the first pipe section, and then through the supercooling tube group 2, so that the refrigerant is recooled when passing through the supercooling tube group 2, so that the refrigerant can be fully cooled, so that it will not evaporate too quickly, thereby improving the air conditioner The cooling effect of the whole system.
  • the flow path of the refrigerant in the outdoor heat exchanger is a path.
  • the refrigerant enters at least part of the second pipe section, the refrigerant is in a gaseous state, and the refrigerant passes through the first pipe section and the Cold pipe group 2, the state of the refrigerant gradually passes through the gas-liquid mixture, passes through the supercooled pipe group 2, and finally the refrigerant flowing out at the first node is guaranteed to be fully condensed into a liquid state.
  • a longer subcooled pipe group 2 is very necessary to ensure the cooling effect.
  • the outdoor heat exchanger added to the supercooling tube group 2 has better cooling effect, better cooling effect, and heat exchange efficiency. Guarantee, also improve the cooling work efficiency of the air-conditioning system.
  • the refrigerant in the outdoor heat exchanger circulates in the supercooling bypass pipe 3, the first pipe section, and the bypass bypass pipe 5, and the circulation path of the refrigerant enters from the first node.
  • the three nodes are divided into two channels, one to the first pipe section.
  • the refrigerant flowing through the cold pipe group 2 merges with the refrigerant flowing through the first pipe section, and flows to the bypass bypass pipe 5, at the third node.
  • the other way flows to at least part of the second pipe section.
  • the one way refrigerant flowing through the bypass bypass pipe 5 merges with the one way refrigerant flowing through at least part of the pipe section of the second pipe section and flows to other pipe sections of the second pipe section to form Three-way shunting, when the refrigerant in the gas-liquid mixed state enters from the first node, if there is no subcooling bypass pipe 3 provided with a supercooling check valve 4 and a shunt bypass pipe 5 provided with a shunt check valve 6, The greater resistance of the refrigerant will reduce the heat exchange efficiency and affect the heating effect of the air conditioner.
  • the flow path of the refrigerant in the outdoor heat exchanger is three paths, one path is from the first node through the supercooling tube group 2 to the second node, through the bypass bypass tube 5 To the fourth node; one path is that the first node passes through the supercooled bypass pipe 3 to the third node, passes the first pipe section to the second node, and passes through the bypass bypass pipe 5 to the fourth node; the other path is the first node Pass the supercooling bypass pipe 3 to the third node, and pass at least part of the pipe section of the second pipe section to the fourth node.
  • the first path is the first flow path to the third flow path; the second path is the second flow path to the fourth flow path to the third flow path; and the third path is the second flow path to the fifth flow path.
  • the multi-path shunt is used to alleviate the greater resistance when the refrigerant enters the first node, reduce the resistance loss of the flow path, and improve the heating efficiency of the air conditioner.
  • the number of heat exchange tubes in the first tube section is less than or equal to the number of heat exchange tubes in the subcooled tube group 2, and the flow pressure difference between the two ends of the first tube section will be smaller than the flow pressure difference between the two ends of the supercooled tube group 2, then At the first node, the flow rate of the refrigerant flowing to the first path will be smaller than the flow rate of the refrigerant flowing to the second path.
  • the setting of the subcooling bypass 3 achieves the desired effect, so that the refrigerant flow achieves multi-path Diversion, which can alleviate the resistance loss of the flow path and improve the heating efficiency.
  • the number of heat exchange tubes in the first pipe section is less than or equal to the number of heat exchange tubes in at least part of the pipe sections of the second pipe section, and the pressure difference between the two ends of the first pipe section will be less than that of at least part of the second pipe section If the pressure difference is different, the refrigerant flows at the third node, and the flow rate of the refrigerant flowing to the fifth path will be less than the flow rate of the refrigerant flowing to the fourth path.
  • bypass bypass pipe 5 will be greatly weakened, and the bypass bypass
  • the setting of the tube 5 does not play the expected role, and the setting of the refrigerant cannot achieve the expected effect, so that the refrigerant circulation realizes multi-path shunting, which can alleviate the resistance loss of the flow path and improve the heating efficiency.
  • the number of heat exchange tubes of the supercooled tube group 2 is greater than or equal to the number of heat exchange tubes of at least part of the tube sections of the second tube section, and the difference in flow pressure between the two ends of at least part of the tube sections of the second tube section will be smaller than that of the subcooled tube group 2
  • the supercooling bypass pipe 3 may be two first supercooling bypass pipes 3 and a second supercooling bypass pipe 3 connected in parallel, the first supercooling bypass pipe 3 and the second supercooling The bypass pipe 3 may be connected in parallel. Under the condition that the flow pressure difference between the two ends of the subcooling bypass pipe 3 is unchanged, the refrigerant entering the first node may be better diverted.
  • bypass bypass pipe 5 may be two first bypass bypass pipes and a second bypass bypass pipe connected in parallel, and the first bypass bypass pipe and the second bypass bypass pipe may be connected in parallel
  • the refrigerant entering the third node can play a better shunt effect.
  • the one-way valve is used to divide the outdoor heat exchanger, which can reduce the complexity of the system and reduce the system pressure loss caused by the supercooling tube group 2 during heating, thereby improving the system. Heat exchange efficiency.
  • An embodiment of the present invention further provides another air conditioner, including an indoor heat exchanger, an outdoor heat exchanger, a compressor and a four-way valve connected to form a refrigerant circulation flow path; wherein, the indoor heat exchanger is any optional as described above
  • the heat exchange tube group 1 of the heat exchanger communicates with the compressor, and the subcooling tube group 2 communicates with the indoor heat exchanger.
  • the air conditioner may further include a throttling device, which is not limited, the throttling device may be a capillary tube, the compressor of the air conditioner may be a fixed frequency compressor, and the capillary tube may be connected in parallel to the supercooling tube group 2 and the supercooling bypass tube 3 The end of the node away from the heat exchange tube group 1.
  • a throttling device may be a capillary tube
  • the compressor of the air conditioner may be a fixed frequency compressor
  • the capillary tube may be connected in parallel to the supercooling tube group 2 and the supercooling bypass tube 3 The end of the node away from the heat exchange tube group 1.
  • the air conditioner may further include a throttling device, which is not limited, the throttling device may be an electronic expansion valve, the compressor of the air conditioner may be an inverter compressor, and the electronic expansion valve may be connected to the subcooling tube group 2 and the subcooling bypass The end of the parallel node of the tube 3 away from the heat exchange tube group 1.
  • a throttling device may be an electronic expansion valve
  • the compressor of the air conditioner may be an inverter compressor
  • the electronic expansion valve may be connected to the subcooling tube group 2 and the subcooling bypass The end of the parallel node of the tube 3 away from the heat exchange tube group 1.
  • the indoor heat exchanger when the air conditioner is performing a cooling operation, includes a heat exchange tube group 1, a subcooling tube group 2, a subcooling bypass tube 3, a bypass bypass tube 5, a supercooling check valve 4, a diversion One-way valve 6, in which the supercooling tube group 2 and the heat exchange tube group 1 are connected in series, and the supercooling tube group 2 and the heat exchange tube group 1 form a flow path of a double-row arrangement structure;
  • the supercooling bypass tube 3 It is connected in parallel with the supercooling tube group 2 and the first tube section;
  • the bypass bypass tube 5 is connected in parallel with at least part of the tube sections of the first tube section and the second tube section;
  • the subcooling check valve 4 is provided on the subcooling bypass tube 3;
  • the check valve 6 is provided on the bypass bypass pipe 5.
  • the refrigerant circulates in the second pipe section, the first pipe section, and the supercooled pipe group 2.
  • the refrigerant flow path is at least part of the pipe section that enters the second pipe section from the fourth node, flows through the third node, and reaches the first pipe section, flows through the From the second node to the supercooled pipe group 2, since the supercooled check valve 4 and the split check valve 6 are both check valves, during the cooling operation, the flow of refrigerant from the fourth node to the first node does not flow.
  • the refrigerant passes through the heat exchange tube group 1 The second pipe section to the first pipe section, and then through the supercooling tube group 2, so that the refrigerant is recooled when passing through the supercooling tube group 2, so that the refrigerant can be fully cooled, so that it will not evaporate too quickly, thereby improving the air conditioner The cooling effect of the whole system.
  • the flow path of the refrigerant in the indoor heat exchanger is a path.
  • the refrigerant enters at least part of the second pipe section, the refrigerant is in a gaseous state, and the refrigerant passes through the first pipe section and the Cold pipe group 2, the state of the refrigerant gradually passes through the gas-liquid mixture, passes through the supercooled pipe group 2, and finally the refrigerant flowing out at the first node is guaranteed to be fully condensed into a liquid state.
  • a longer subcooled pipe group 2 is very necessary to ensure the cooling effect.
  • the indoor heat exchanger added to the supercooling tube group 2 has better cooling effect, better cooling effect, and heat exchange efficiency. Guarantee, also improve the cooling work efficiency of the air-conditioning system.
  • the throttling device may be provided at the end of the parallel node of the supercooling tube group 2 and the supercooling bypass tube 3 away from the heat exchange tube group 1, and connected to the supercooling tube group 2, the supercooling tube group 2 makes the refrigerant again For cooling, there is enough supercooling degree to control the refrigerant not to evaporate too fast before the throttling components, thereby improving the cooling efficiency of the air conditioner.
  • the refrigerant in the indoor heat exchanger circulates in the subcooling bypass pipe 3, the first pipe section, and the bypass bypass pipe 5, and the circulation path of the refrigerant enters from the first node.
  • the three nodes are divided into two channels, one to the first pipe section.
  • the refrigerant flowing through the cold pipe group 2 merges with the refrigerant flowing through the first pipe section, and flows to the bypass bypass pipe 5, at the third node.
  • the other way flows to at least part of the second pipe section.
  • the one way refrigerant flowing through the bypass bypass pipe 5 merges with the one way refrigerant flowing through at least part of the pipe section of the second pipe section and flows to other pipe sections of the second pipe section to form Three-way shunting, when the refrigerant in the gas-liquid mixed state enters from the first node, if there is no subcooling bypass pipe 3 provided with a supercooling check valve 4 and a shunt bypass pipe 5 provided with a shunt check valve 6, The greater resistance of the refrigerant will reduce the heat exchange efficiency and affect the heating effect of the air conditioner.
  • the flow path of the refrigerant in the indoor heat exchanger is three paths, one path is from the first node through the supercooling tube group 2 to the second node, and passes through the bypass bypass tube 5 To the fourth node; one path is that the first node passes through the supercooled bypass pipe 3 to the third node, passes the first pipe section to the second node, and passes through the bypass bypass pipe 5 to the fourth node; the other path is the first node Pass the supercooling bypass pipe 3 to the third node, and pass at least part of the pipe section of the second pipe section to the fourth node.
  • the first path is the first flow path to the third flow path;
  • the second path is the second flow path to the fourth flow path to the third flow path;
  • the third path is the second flow path to the fifth flow path.
  • the multi-path diversion reduces the greater resistance when the refrigerant enters the first node, reduces the resistance loss of the flow path, and improves the heating efficiency of the air conditioner.
  • the number of heat exchange tubes in the first tube section is less than or equal to the number of heat exchange tubes in the subcooled tube group 2, and the flow pressure difference between the two ends of the first tube section will be smaller than the flow pressure difference between the two ends of the supercooled tube group 2, then At the first node, the flow rate of the refrigerant flowing to the first path will be smaller than the flow rate of the refrigerant flowing to the second path.
  • the setting of the subcooling bypass 3 achieves the desired effect, so that the refrigerant flow achieves multi-path Diversion, which can alleviate the resistance loss of the flow path and improve the heating efficiency.
  • the number of heat exchange tubes in the first pipe section is less than or equal to the number of heat exchange tubes in at least part of the pipe sections of the second pipe section, and the pressure difference between the two ends of the first pipe section will be less than that of at least part of the second pipe section If the pressure difference is different, the refrigerant flows at the third node, and the flow rate of the refrigerant flowing to the fifth path will be less than the flow rate of the refrigerant flowing to the fourth path.
  • bypass bypass pipe 5 will be greatly weakened, and the bypass bypass
  • the setting of the tube 5 does not play the expected role, and the setting of the refrigerant cannot achieve the expected effect, so that the refrigerant circulation realizes multi-path shunting, which can alleviate the resistance loss of the flow path and improve the heating efficiency.
  • the number of heat exchange tubes of the supercooled tube group 2 is greater than or equal to the number of heat exchange tubes of at least part of the tube sections of the second tube section, and the difference in flow pressure between the two ends of at least part of the tube sections of the second tube section will be smaller than that of the subcooled tube group 2
  • the supercooling bypass pipe 3 may be two first supercooling bypass pipes 3 and a second supercooling bypass pipe 3 connected in parallel, the first supercooling bypass pipe 3 and the second supercooling The bypass pipe 3 may be connected in parallel. Under the condition that the flow pressure difference between the two ends of the subcooling bypass pipe 3 is unchanged, the refrigerant entering the first node may be better diverted.
  • bypass bypass pipe 5 may be two first bypass bypass pipes and a second bypass bypass pipe connected in parallel, and the first bypass bypass pipe and the second bypass bypass pipe may be connected in parallel
  • the refrigerant entering the third node can play a better diversion effect.
  • the check valve is used to shunt the indoor heat exchanger, which can reduce the complexity of the system and reduce the system pressure loss caused by the supercooling tube group 2 during heating, thereby improving the system. Heat exchange efficiency.

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Abstract

一种换热器和空调器，换热器包括换热管组（1）、过冷管组（2）、过冷旁通管（3）、分流旁通管（5）、过冷单向阀（4）和分流单向阀（6），过冷管组（2）与所述换热管组（1）串联连接，过冷管组（2）和换热管组（1）构成双列排布结构的流路，过冷旁通管（3）与过冷管组（2）并联设置，过冷单向阀（4）设置于过冷旁通管（3）上，分流单向阀（6）设置于分流旁通管（5）上。换热器在制热运行时，通过单向阀实现对换热器进行分流，可以降低系统复杂程度，减轻在制热时经过过冷管组而产生的系统压损，从而提高系统换热效率。

Description

一种换热器和空调器
本申请基于申请号为201910023141.8、申请日为2019年01月10日的中国专利申请提出，并要求该中国专利申请的优先权，该中国专利申请的全部内容在此引入本申请作为参考。
技术领域
本发明涉及换热器技术领域，特别涉及一种换热器和空调器。
背景技术
现有换热器如果需要进行分流，通常采用分流管或者分流器进行分流设计，但是常规的分流方式，没有方向区分，在进行制冷运行和进行制热运行时经过同样的管路，在换热器进行制冷运行时，通过过冷管路，满足制冷运行需求，而在进行制热运行时，仍然经过会经过过冷管路，会导致增大系统压损，进而降低系统换热效率。
发明内容
本发明实施例提供了一种换热器和空调器，以解决换热器在加热运行时换热效率降低的问题。为了对披露的实施例的一些方面有一个基本的理解，下面给出了简单的概括。该概括部分不是泛泛评述，也不是要确定关键/重要组成元素或描绘这些实施例的保护范围。其唯一目的是用简单的形式呈现一些概念，以此作为后面的详细说明的序言。
根据本发明实施例的第一方面，提供了一种换热器。
在一些可选实施例中，上述换热器，包括换热管组；
过冷管组，与换热管组串联连接；且过冷管组和换热管组构成双列排布结构的流路；
过冷旁通管，过冷旁通管与过冷管组、换热管组的连接过冷管组的第一管段并联连接；
分流旁通管，分流旁通管与换热管组的第一管段、除第一管段之外的第二管段的至少部分管段并联连接；
过冷单向阀，设置于过冷旁通管上，过冷单向阀的导通方向限定为由过冷旁通管的与过冷管组的并联节点流向与第一管段的并联节点；
分流单向阀，设置于分流旁通管上，分流单向阀的导通方向限定为由换热管组的与第一管段的并联节点流向与第二管段的至少部分管段的并联节点。
可选地，过冷旁通管所并联的换热管组的第一管段的换热管的数量，小于或等于其所并联的过冷管组的换热管的数量。
可选地，过冷旁通管所并联的换热管组的第一管段的换热管的数量，小于或等于分流旁通管所并联的第二管段的至少部分管段的换热管的数量。
可选地，过冷旁通管所并联的过冷管组的换热管的数量，大于或等于分流旁通管所并 联的第二管段的至少部分管段的换热管的数量。
可选地，过冷旁通管的数量为多个，多个过冷旁通管并联连接。
可选地，多个过冷旁通管所并联的换热管组的第一管段的换热管的数量相同或者不相同。
可选地，分流旁通管的数量为多个，多个过冷旁通管并联连接。
可选地，多个分流旁通管所并联的换热管组的第二管段的换热管的数量相同或者不相同。
根据本发明实施例的第二方面，提供了一种空调器。
在一些可选实施例中，上述空调器包括室内换热器、室外换热器、压缩机和四通阀连接构成的冷媒循环流路；其中，室外换热器为如上述任意可选实施例所述的换热器，换热器的换热管组与压缩机相连通，过冷管组与室内换热器相连通。
根据本发明实施例的第三方面，进一步提供了另一种空调器。
在一些可选实施例中，上述空调器包括室内换热器、室外换热器、压缩机和四通阀连接构成的冷媒循环流路；其中，室内换热器为如上述任意可选实施例所述的换热器，换热器的换热管组与压缩机相连通，过冷管组与室内换热器相连通。
本发明实施例提供的技术方案可以包括以下有益效果：实现换热器在制热运行时，通过单向阀实现对换热器进行分流，可以降低系统复杂程度，减轻在制热时经过过冷管组而产生的系统压损，从而提高系统换热效率。
应当理解的是，以上的一般描述和后文的细节描述仅是示例性和解释性的，并不能限制本发明。
附图说明
此处的附图被并入说明书中并构成本说明书的一部分，示出了符合本发明的实施例，并与说明书一起用于解释本发明的原理。
图1是根据一示例性实施例示出的一种换热器的结构示意图。
具体实施方式
以下描述和附图充分地示出本文的具体实施方案，以使本领域的技术人员能够实践它们。一些实施方案的部分和特征可以被包括在或替换其他实施方案的部分和特征。本文的实施方案的范围包括权利要求书的整个范围，以及权利要求书的所有可获得的等同物。本文中，术语“第一”、“第二”等仅被用来将一个元素与另一个元素区分开来，而不要求或者暗示这些元素之间存在任何实际的关系或者顺序。实际上第一元素也能够被称为第二元素，反之亦然。而且，术语“包括”、“包含”或者其任何其他变体意在涵盖非排他性的包含，从而使得包括一系列要素的结构、装置或者设备不仅包括那些要素，而且还包括没有明确列出的其他要素，或者是还包括为这种结构、装置或者设备所固有的要素。在没 有更多限制的情况下，由语句“包括一个……”限定的要素，并不排除在包括所述要素的结构、装置或者设备中还存在另外的相同要素。本文中各个实施例采用递进的方式描述，每个实施例重点说明的都是与其他实施例的不同之处，各个实施例之间相同相似部分互相参见即可。
本文中的术语“纵向”、“横向”、“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文和简化描述，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。在本文的描述中，除非另有规定和限定，术语“安装”、“相连”、“连接”应做广义理解，例如，可以是机械连接或电连接，也可以是两个元件内部的连通，可以是直接相连，也可以通过中间媒介间接相连，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的具体含义。
本文中，除非另有说明，术语“多个”表示两个或两个以上。
本文中，字符“/”表示前后对象是一种“或”的关系。例如，A/B表示：A或B。
本文中，术语“和/或”是一种描述对象的关联关系，表示可以存在三种关系。例如，A和/或B，表示：A或B，或，A和B这三种关系。
在一些可选实施例中，提供了一种换热器包括换热管组1、过冷管组2、过冷旁通管3、分流旁通管5、过冷单向阀4、分流单向阀6，其中过冷管组2与换热管组1是串联连接的，且过冷管组2和换热管组1构成双列排布结构的流路；过冷旁通管3与过冷管组2和第一管段并联连接；分流旁通管5与第一管段和第二管段的至少部分管段并联连接；过冷单向阀4设置于过冷旁通管3上；分流单向阀6，设置于分流旁通管5上；换热管组1包括第一管段和第二管段。
可选地，过冷单向阀4的导通方向限定为，由过冷旁通管3与过冷管组2的并联节点，流向过冷旁通管3与第一管段的并联节点；
可选地，分流单向阀6的导通方向限定为，由换热管组1与第一管段的并联节点，流向换热管组1与第二管段的至少部分管段的并联节点。
本文中，换热管组1包括串联连接的第一管段和第二管段，第一管段可以为换热管组1的与过冷管组2相连的，与过冷旁通管3相并联的换热管组1的一段，第二管段可以为换热管组1除第一管段之外的部分，其中，第二管段与分流旁通管5并联的部分为第二管段的至少部分管段，第二管段的除第二管段的至少部分管段外的部分为第二管段的其他管段。
本文中，过冷管组2与过冷旁通管3的并联节点可以为第一节点，第一管段与分流旁通管5的并联节点可以为第二节点，第一管段与过冷旁通管3的并联节点可以为第三节点，分流旁通管5与第二管段的至少部分管段的并联节点可以为第四节点。
可选地，换热器在制冷运行时，制冷剂在第二管段、第一管段、过冷管组2中流通， 制冷剂的流通路径为从第四节点进入第二管段的至少部分管段，流经第三节点，到第一管段，流经第二节点，到过冷管组2，由于过冷单向阀4和分流单向阀6均为单向阀，因此在制冷运行时，制冷剂从第四节点到第一节点的流通过程，不流经过冷单向阀4和分流单向阀6，即，制冷剂从第四节点到第一节点的流通过程，不流经过冷旁通管3和分流旁通管5，制冷剂通过换热管组1的第二管段到第一管段，然后经过过冷管组2，使制冷剂在经过过冷管组2的时候得到再冷却，使制冷剂能够充分冷却，使其不会过快蒸发，从而提高制冷运行过程的换热效率。
可选地，本发明提供的制冷剂不作限定，可以为冷媒，换热器在制冷运行时，冷媒的流路为一条路径，在冷媒进入第二管段的至少部分管段时，冷媒为气态，伴随冷媒依次经过第一管段和过冷管组2，冷媒的状态逐渐经过气液混合，经过过冷管组2，最后在第一节点流出的冷媒保证充分冷凝为液态，为使冷凝过程充分进行，通过较长的过冷管组2十分必要，保证了冷却效果，加入过冷管组2的换热器与只经过换热管组1的换热器相比，冷却效果更好，制冷效果更好，换热效率得以保证。
可选地，换热器在制热运行时，制冷剂在过冷旁通管3、第一管段、分流旁通管5中流通，制冷剂的流通路径为从第一节点进入过冷旁通管3，并在第一节点分流两路，一路流向过冷管组2，另一路流向过冷旁通管3，流向过冷旁通管3的制冷剂流到第三节点，在点三节点再次分流两路，一路流向第一管段，在第二节点，流经过冷管组2的一路制冷剂与流经第一管段的一路制冷剂汇合，流向分流旁通管5，在第三节点的另一路流向第二管段的至少部分管段，在第四节点，流经分流旁通管5的一路制冷剂与流经第二管段的至少部分管段的一路制冷剂汇合，流向第二管段的其他管段，形成三路分流，当气液混合状态的制冷剂从第一节点进入时，若没有设有过冷单向阀4的过冷旁通管3和设有分流单向阀6的分流旁通管5，制冷剂阻力较大，会降低换热效率，影响制热效果。
本文中，从第一节点经过过冷管组2到第二节点的流通路径可以为第一流路，从第一节点经过过冷旁通管3到第三节点的流通路径可以为第二流路，从第二节点经过分流旁通管5到第四节点的流通路径可以为第三流路，从第三节点经过第一管段到第二节点的路通路径可以为第四流路，从第三节点经过第二管段的至少部分管段到第四节点的流通路径可以为第五流路。
可选地，本发明提供的制冷剂不作限定，可以为冷媒，换热器在制热运行时，冷媒的流路为三条路径，一条路径为从第一节点经过过冷管组2到第二节点，经过分流旁通管5到第四节点；一条路径为第一节点经过过冷旁通管3到第三节点，经过第一管段到第二节点，经过分流旁通管5到第四节点；另一路径为第一节点经过过冷旁通管3到第三节点，经过第二管段的至少部分管段到第四节点。即，第一路径为第一流路到第三流路；第二路径为第二流路到第四流路到第三流路；第三路径为第二流路到第五流路。换热器在制热运行时，通过多路径分流，缓解了制冷剂进入第一节点时的较大阻力，降低了流路阻力损失，提高了制热效率。
这样，就实现了换热器在制热运行时，通过单向阀实现对换热器进行分流，可以减小系统复杂程度，降低在制热时经过过冷管组2而产生的系统压损，从而提高系统换热效率。
可选地，过冷旁通管3所并联的换热管组1的第一管段的换热管的数量，小于或等于其所并联的过冷管组2的换热管的数量。
可选地，换热器在制热运行时，制冷剂的流路为三条路径，一条路径为从第一节点经过过冷管组2到第二节点，经过分流旁通管5到第四节点；一条路径为第一节点经过过冷旁通管3到第三节点，经过第一管段到第二节点，经过分流旁通管5到第四节点；另一路径为第一节点经过过冷旁通管3到第三节点，经过第二管段的至少部分管段到第四节点。即，第一路径为第一流路到第三流路；第二路径为第二流路到第四流路到第三流路；第三路径为第二流路到第五流路。若第一管段的换热管数量大于过冷管组2的换热管的数量，第一管段两端流量压强差会大于过冷管组2两端流量压强差，则制冷剂在第一节点，向第一路径流通的制冷剂流量会大于向第二路径流通的制冷剂流量，此时，过冷旁通管3的作用会被大大削弱，过冷旁通管3的设置就起不到预期作用，无法让制冷剂流通实现多路径分流，不能很好地缓解流路阻力损失。所以，当换热管组1的第一管段的换热管的数量小于或等于过冷管组2的换热管的数量时，换热器在制热运行时，才可以更好实现多路径分流，缓解了制冷剂进入第一节点时的较大阻力，降低了流路阻力损失，提高了制热效率。
这样，就实现了换热器在制热运行时，通过单向阀实现对换热器进行分流，可以减小系统复杂程度，降低在制热时经过过冷管组2而产生的系统压损，从而提高系统换热效率。
可选地，过冷旁通管3所并联的换热管组1的第一管段的换热管的数量，小于或等于分流旁通管5所并联的第二管段的至少部分管段的换热管的数量。
可选地，换热器在制热运行时，制冷剂的流路为三条路径，一条路径为从第一节点经过过冷管组2到第二节点，经过分流旁通管5到第四节点；一条路径为第一节点经过过冷旁通管3到第三节点，经过第一管段到第二节点，经过分流旁通管5到第四节点；另一路径为第一节点经过过冷旁通管3到第三节点，经过第二管段的至少部分管段到第四节点。即，第一路径为第一流路到第三流路；第二路径为第二流路到第四流路到第三流路；第三路径为第二流路到第五流路。若第一管段的换热管数量大于第二管段的至少部分管段的换热管的数量，第一管段两端流量压强差会大于第二管段的至少部分管段两端流量压强差，则制冷剂在第三节点，向第五路径流通的制冷剂流量会大于向第四路径流通的制冷剂流量，此时，分流旁通管5的作用会被大大削弱，分流旁通管5的设置就起不到预期作用，无法让制冷剂的流通实现多路径分流，不能很好地缓解流路阻力损失。所以，当换热管组1的第一管段的换热管的数量小于或等于第二管段的至少部分管段的换热管的数量时，换热器在制热运行时，才可以更好实现多路径分流，缓解了制冷剂进入第一节点时的较大阻力，降低了流路阻力损失，提高了制热效率。
这样，就实现了换热器在制热运行时，通过单向阀实现对换热器进行分流，可以减小系统复杂程度，降低在制热时经过过冷管组2而产生的系统压损，从而提高系统换热效率。
可选地，过冷旁通管3所并联的过冷管组2的换热管的数量，大于或等于分流旁通管5所并联的第二管段的至少部分管段的换热管的数量。
可选地，换热器在制热运行时，制冷剂的流路为三条路径，一条路径为从第一节点经过过冷管组2到第二节点，经过分流旁通管5到第四节点；一条路径为第一节点经过过冷旁通管3到第三节点，经过第一管段到第二节点，经过分流旁通管5到第四节点；另一路径为第一节点经过过冷旁通管3到第三节点，经过第二管段的至少部分管段到第四节点。即，第一路径为第一流路到第三流路；第二路径为第二流路到第四流路到第三流路；第三路径为第二流路到第五流路。若第二管段的至少部分管段的换热管数量大于过冷管组2的换热管的数量，第二管段的至少部分管段两端流量压强差会大于过冷管组2两端流量压强差，则制冷剂在第一节点，向第一路径流通的制冷剂流量会大于向第三路径流通的制冷剂流量，此时，过冷旁通管3的作用会被大大削弱，过冷旁通管3的设置就起不到预期作用，无法让制冷剂流通实现多路径分流，不能很好地缓解流路阻力损失。所以，当过冷管组2的换热管的数量大于或等于第二管段的至少部分管段的换热管的数量时，换热器在制热运行时，才可以更好实现多路径分流，缓解了制冷剂进入第一节点时的较大阻力，降低了流路阻力损失，提高了制热效率。
这样，就实现了换热器在制热运行时，通过单向阀实现对换热器进行分流，可以减小系统复杂程度，降低在制热时经过过冷管组2而产生的系统压损，从而提高系统换热效率。
可选地，过冷旁通管3的数量为多个，多个过冷旁通管3并联连接。
可选地，过冷旁通管3的数量，不作限定，可以包括第一过冷旁通管3和第二过冷旁通管3，第一过冷旁通管3和第二过冷旁通管3可以为并联连接方式，在过冷旁通管3两端流量压强差不变的情况下，可以对进入第一节点的制冷剂起到更好的分流作用。
这样，就实现了换热器在制热运行时，通过单向阀实现对换热器进行分流，可以减小系统复杂程度，降低在制热时经过过冷管组2而产生的系统压损，从而提高系统换热效率。
可选地，多个过冷旁通管3所并联的换热管组1的第一管段的换热管的数量相同或者不相同。
可选地，多个过冷旁通管3的连接方式为并联连接，在过冷旁通管3两端流量压强差不变的情况下，可以对进入第一节点的制冷剂起到分流作用，而换热管组1中的各换热管可以为串联连接方式，串联的换热管数量越多，制冷剂流通路径越长，换热管组1的压阻越大，功率损耗也越大，换热管组1的第一管段属于换热管组1，同理，所以，换热管组1的第一管段的换热管的数量与过冷旁通管3所并联的换热管组1的数量可以相同。
可选地，多个过冷旁通管3的连接方式为并联连接，在过冷旁通管3两端流量压强差不变的情况下，可以对进入第一节点的制冷剂起到分流作用，而换热管组1中的各换热管可以为串联连接方式，串联的换热管数量越多，制冷剂流通路径越长，换热管组1的压阻越大，功率损耗也越大，换热管组1的第一管段属于换热管组1，同理，所以，换热管组1的第一管段的换热管的数量与过冷旁通管3所并联的换热管组1的数量可以不相同。
这样，就实现了换热器在制热运行时，通过单向阀实现对换热器进行分流，可以减小系统复杂程度，降低在制热时经过过冷管组2而产生的系统压损，从而提高系统换热效率。
可选地，分流旁通管5的数量为多个，多个过冷旁通管3并联连接。
可选地，分流旁通管5的数量，不作限定，可以包括第一分流旁通管和第二分流旁通管，第一分流旁通管和第二分流旁通管可以为并联连接方式，在分流旁通管5两端流量压强差不变的情况下，可以对进入第三节点的制冷剂起到更好的分流作用。
这样，就实现了换热器在制热运行时，通过单向阀实现对换热器进行分流，可以减小系统复杂程度，降低在制热时经过过冷管组2而产生的系统压损，从而提高系统换热效率。
可选地，多个分流旁通管5所并联的换热管组1的第二管段的换热管的数量相同或者不相同。
可选地，多个分流旁通管5的连接方式为并联连接，在分流旁通管5两端流量压强差不变的情况下，可以对进入第三节点的制冷剂起到分流作用，而换热管组1中的各换热管可以为串联连接方式，串联的换热管数量越多，制冷剂流通路径越长，换热管组1的压阻越大，功率损耗也越大，换热管组1的第二管段属于换热管组1，同理，所以，换热管组1的第二管段的换热管的数量与分流旁通管5所并联的换热管组1的数量可以相同。
可选地，多个分流旁通管5的连接方式为并联连接，在分流旁通管5两端流量压强差不变的情况下，可以对进入第三节点的制冷剂起到分流作用，而换热管组1中的各换热管可以为串联连接方式，串联的换热管数量越多，制冷剂流通路径越长，换热管组1的压阻越大，功率损耗也越大，换热管组1的第二管段属于换热管组1，同理，所以，换热管组1的第二管段的换热管的数量与分流旁通管5所并联的换热管组1的数量可以不相同。
这样，就实现了换热器在制热运行时，通过单向阀实现对换热器进行分流，可以减小系统复杂程度，降低在制热时经过过冷管组2而产生的系统压损，从而提高系统换热效率。
本发明实施例进一步提供了一种空调器，包括室内换热器、室外换热器、压缩机和四通阀连接构成的冷媒循环流路；其中，室外换热器为如上述任意可选实施例所述的换热器，换热器的换热管组1与压缩机相连通，过冷管组2与室内换热器相连通。
可选地，空调的室外换热器安装在空调室外机中，空调的室外机体积更加不受限制，室外换热器为如上任意可选实施例所述的室外换热器时，过冷旁通管3组中并联的多个过冷旁通管3，和，多个分流旁通管5，所占空间可以更大，空调换热效率也更高。
可选地，空调器在进行制冷运行时，室外换热器包括换热管组1、过冷管组2、过冷旁通管3、分流旁通管5、过冷单向阀4、分流单向阀6，其中过冷管组2与换热管组1是串联连接的，且过冷管组2和换热管组1构成双列排布结构的流路；过冷旁通管3与过冷管组2和第一管段并联连接；分流旁通管5与第一管段和第二管段的至少部分管段并联连接；过冷单向阀4设置于过冷旁通管3上；分流单向阀6，设置于分流旁通管5上。冷媒在第二管段、第一管段、过冷管组2中流通，冷媒的流通路径为从第四节点进入第二管段的至少部分管段，流经第三节点，到第一管段，流经第二节点，到过冷管组2，由于过冷 单向阀4和分流单向阀6均为单向阀，因此在制冷运行时，冷媒从第四节点到第一节点的流通过程，不流经过冷单向阀4和分流单向阀6，即，冷媒从第四节点到第一节点的流通过程，不流经过冷旁通管3和分流旁通管5，冷媒通过换热管组1的第二管段到第一管段，然后经过过冷管组2，使冷媒在经过过冷管组2的时候得到再冷却，使冷媒能够充分冷却，使其不会过快蒸发，从而提高空调器整机系统的制冷效果。
可选地，空调器在进行制冷运行时，室外换热器中冷媒的流路为一条路径，在冷媒进入第二管段的至少部分管段时，冷媒为气态，伴随冷媒依次经过第一管段和过冷管组2，冷媒的状态逐渐经过气液混合，经过过冷管组2，最后在第一节点流出的冷媒保证充分冷凝为液态，为使冷凝过程充分进行，通过较长的过冷管组2十分必要，保证了冷却效果，加入过冷管组2的室外换热器与只经过换热管组1的室外换热器相比，冷却效果更好，制冷效果更好，换热效率得以保证，也提高了空调器整机系统的制冷工作效率。
可选地，空调器在进行制热运行时，室外换热器中冷媒在过冷旁通管3、第一管段、分流旁通管5中流通，冷媒的流通路径为从第一节点进入过冷旁通管3，并在第一节点分流两路，一路流向过冷管组2，另一路流向过冷旁通管3，流向过冷旁通管3的冷媒流到第三节点，在点三节点再次分流两路，一路流向第一管段，在第二节点，流经过冷管组2的一路冷媒与流经第一管段的一路冷媒汇合，流向分流旁通管5，在第三节点的另一路流向第二管段的至少部分管段，在第四节点，流经分流旁通管5的一路冷媒与流经第二管段的至少部分管段的一路冷媒汇合，流向第二管段的其他管段，形成三路分流，当气液混合状态的冷媒从第一节点进入时，若没有设有过冷单向阀4的过冷旁通管3和设有分流单向阀6的分流旁通管5，冷媒阻力较大，会降低换热效率，影响空调的制热效果。
可选地，空调器在进行制热运行时，室外换热器中冷媒的流路为三条路径，一条路径为从第一节点经过过冷管组2到第二节点，经过分流旁通管5到第四节点；一条路径为第一节点经过过冷旁通管3到第三节点，经过第一管段到第二节点，经过分流旁通管5到第四节点；另一路径为第一节点经过过冷旁通管3到第三节点，经过第二管段的至少部分管段到第四节点。即，第一路径为第一流路到第三流路；第二路径为第二流路到第四流路到第三流路；第三路径为第二流路到第五流路。室外换热器在制热运行时，通过多路径分流，缓解了冷媒进入第一节点时的较大阻力，降低了流路阻力损失，提高了空调的制热效率。
可选地，第一管段的换热管的数量小于或等于过冷管组2的换热管的数量，第一管段两端流量压强差会小于过冷管组2两端流量压强差，则制冷剂在第一节点，向第一路径流通的制冷剂流量会小于向第二路径流通的制冷剂流量，此时，过冷旁通管3的设置达到预期效果，使制冷剂流通实现多路径分流，很好地缓解流路阻力损失，提高了制热效率。
可选地，第一管段的换热管的数量小于或等于第二管段的至少部分管段的换热管的数量，第一管段两端流量压强差会小于第二管段的至少部分管段两端流量压强差，则制冷剂在第三节点，向第五路径流通的制冷剂流量会小于向第四路径流通的制冷剂流量，此时，分流旁通管5的作用会被大大削弱，分流旁通管5的设置就起不到预期作用，无法让制冷 剂的设置达到预期效果，使制冷剂流通实现多路径分流，很好地缓解流路阻力损失，提高了制热效率。
可选地，过冷管组2的换热管的数量大于或等于第二管段的至少部分管段的换热管的数量，第二管段的至少部分管段两端流量压强差会小于过冷管组2两端流量压强差，则制冷剂在第一节点，向第一路径流通的制冷剂流量会小于向第三路径流通的制冷剂流量，此时，过冷旁通管3的设置达到预期效果，使制冷剂流通实现多路径分流，很好地缓解流路阻力损失，提高了制热效率。
可选地，过冷旁通管3可以为两个通过并联方式连接的第一过冷旁通管3和第二过冷旁通管3，第一过冷旁通管3和第二过冷旁通管3可以为并联连接方式，在过冷旁通管3两端流量压强差不变的情况下，可以对进入第一节点的制冷剂起到更好的分流作用。
可选地，分流旁通管5可以为两个通过并联方式连接的第一分流旁通管和第二分流旁通管，第一分流旁通管和第二分流旁通管可以为并联连接方式，在分流旁通管5两端流量压强差不变的情况下，可以对进入第三节点的制冷剂起到更好的分流作用。
这样，空调在制热运行时，通过单向阀实现对室外换热器进行分流，可以减小系统复杂程度，降低在制热时经过过冷管组2而产生的系统压损，从而提高系统换热效率。
本发明实施例进一步提供了另一种空调器，包括室内换热器、室外换热器、压缩机和四通阀连接构成的冷媒循环流路；其中，室内换热器为如上述任意可选实施例所述的换热器，换热器的换热管组1与压缩机相连通，过冷管组2与室内换热器相连通。
可选地，空调还可以包括节流装置，不作限定，节流装置可以为毛细管，空调的压缩机可以为定频压缩机，毛细管可以连接在过冷管组2与过冷旁通管3并联节点的远离换热管组1的一端。
可选地，空调还可以包括节流装置，不作限定，节流装置可以为电子膨胀阀，空调的压缩机可以为变频压缩机，电子膨胀阀可以连接在过冷管组2与过冷旁通管3并联节点的远离换热管组1的一端。
可选地，空调器在进行制冷运行时，室内换热器包括换热管组1、过冷管组2、过冷旁通管3、分流旁通管5、过冷单向阀4、分流单向阀6，其中过冷管组2与换热管组1是串联连接的，且过冷管组2和换热管组1构成双列排布结构的流路；过冷旁通管3与过冷管组2和第一管段并联连接；分流旁通管5与第一管段和第二管段的至少部分管段并联连接；过冷单向阀4设置于过冷旁通管3上；分流单向阀6，设置于分流旁通管5上。冷媒在第二管段、第一管段、过冷管组2中流通，冷媒的流通路径为从第四节点进入第二管段的至少部分管段，流经第三节点，到第一管段，流经第二节点，到过冷管组2，由于过冷单向阀4和分流单向阀6均为单向阀，因此在制冷运行时，冷媒从第四节点到第一节点的流通过程，不流经过冷单向阀4和分流单向阀6，即，冷媒从第四节点到第一节点的流通过程，不流经过冷旁通管3和分流旁通管5，冷媒通过换热管组1的第二管段到第一管段，然后经过过冷管组2，使冷媒在经过过冷管组2的时候得到再冷却，使冷媒能够充分冷却， 使其不会过快蒸发，从而提高空调器整机系统的制冷效果。
可选地，空调器在进行制冷运行时，室内换热器中冷媒的流路为一条路径，在冷媒进入第二管段的至少部分管段时，冷媒为气态，伴随冷媒依次经过第一管段和过冷管组2，冷媒的状态逐渐经过气液混合，经过过冷管组2，最后在第一节点流出的冷媒保证充分冷凝为液态，为使冷凝过程充分进行，通过较长的过冷管组2十分必要，保证了冷却效果，加入过冷管组2的室内换热器与只经过换热管组1的室内换热器相比，冷却效果更好，制冷效果更好，换热效率得以保证，也提高了空调器整机系统的制冷工作效率。
可选地，节流装置可以设置在过冷管组2与过冷旁通管3并联节点的远离换热管组1的一端，与过冷管组2相连，过冷管组2使冷媒再冷却，有足够的过冷度能够控制冷媒在节流部件前不产生过快蒸发，从而提高空调器的制冷效率。
可选地，空调器在进行制热运行时，室内换热器中冷媒在过冷旁通管3、第一管段、分流旁通管5中流通，冷媒的流通路径为从第一节点进入过冷旁通管3，并在第一节点分流两路，一路流向过冷管组2，另一路流向过冷旁通管3，流向过冷旁通管3的冷媒流到第三节点，在点三节点再次分流两路，一路流向第一管段，在第二节点，流经过冷管组2的一路冷媒与流经第一管段的一路冷媒汇合，流向分流旁通管5，在第三节点的另一路流向第二管段的至少部分管段，在第四节点，流经分流旁通管5的一路冷媒与流经第二管段的至少部分管段的一路冷媒汇合，流向第二管段的其他管段，形成三路分流，当气液混合状态的冷媒从第一节点进入时，若没有设有过冷单向阀4的过冷旁通管3和设有分流单向阀6的分流旁通管5，冷媒阻力较大，会降低换热效率，影响空调的制热效果。
可选地，空调器在进行制热运行时，室内换热器中冷媒的流路为三条路径，一条路径为从第一节点经过过冷管组2到第二节点，经过分流旁通管5到第四节点；一条路径为第一节点经过过冷旁通管3到第三节点，经过第一管段到第二节点，经过分流旁通管5到第四节点；另一路径为第一节点经过过冷旁通管3到第三节点，经过第二管段的至少部分管段到第四节点。即，第一路径为第一流路到第三流路；第二路径为第二流路到第四流路到第三流路；第三路径为第二流路到第五流路。室内换热器在制热运行时，通过多路径分流，缓解了冷媒进入第一节点时的较大阻力，降低了流路阻力损失，提高了空调的制热效率。
可选地，第一管段的换热管的数量小于或等于过冷管组2的换热管的数量，第一管段两端流量压强差会小于过冷管组2两端流量压强差，则制冷剂在第一节点，向第一路径流通的制冷剂流量会小于向第二路径流通的制冷剂流量，此时，过冷旁通管3的设置达到预期效果，使制冷剂流通实现多路径分流，很好地缓解流路阻力损失，提高了制热效率。
可选地，第一管段的换热管的数量小于或等于第二管段的至少部分管段的换热管的数量，第一管段两端流量压强差会小于第二管段的至少部分管段两端流量压强差，则制冷剂在第三节点，向第五路径流通的制冷剂流量会小于向第四路径流通的制冷剂流量，此时，分流旁通管5的作用会被大大削弱，分流旁通管5的设置就起不到预期作用，无法让制冷剂的设置达到预期效果，使制冷剂流通实现多路径分流，很好地缓解流路阻力损失，提高 了制热效率。
可选地，过冷管组2的换热管的数量大于或等于第二管段的至少部分管段的换热管的数量，第二管段的至少部分管段两端流量压强差会小于过冷管组2两端流量压强差，则制冷剂在第一节点，向第一路径流通的制冷剂流量会小于向第三路径流通的制冷剂流量，此时，过冷旁通管3的设置达到预期效果，使制冷剂流通实现多路径分流，很好地缓解流路阻力损失，提高了制热效率。
可选地，过冷旁通管3可以为两个通过并联方式连接的第一过冷旁通管3和第二过冷旁通管3，第一过冷旁通管3和第二过冷旁通管3可以为并联连接方式，在过冷旁通管3两端流量压强差不变的情况下，可以对进入第一节点的制冷剂起到更好的分流作用。
可选地，分流旁通管5可以为两个通过并联方式连接的第一分流旁通管和第二分流旁通管，第一分流旁通管和第二分流旁通管可以为并联连接方式，在分流旁通管两端流量压强差不变的情况下，可以对进入第三节点的制冷剂起到更好的分流作用。
这样，空调在制热运行时，通过单向阀实现对室内换热器进行分流，可以减小系统复杂程度，降低在制热时经过过冷管组2而产生的系统压损，从而提高系统换热效率。
本发明并不局限于上面已经描述并在附图中示出的结构，并且可以在不脱离其范围进行各种修改和改变。本发明的范围仅由所附的权利要求来限制。

Claims (10)

  1. 一种换热器，其特征在于，所述换热器包括：
    换热管组；
    过冷管组，与所述换热管组串联连接；且所述过冷管组和所述换热管组构成双列排布结构的流路；
    过冷旁通管，所述过冷旁通管与所述过冷管组、所述换热管组的连接所述过冷管组的第一管段并联连接；
    分流旁通管，所述分流旁通管与所述换热管组的所述第一管段、除所述第一管段之外的第二管段的至少部分管段并联连接；
    过冷单向阀，设置于所述过冷旁通管上，所述过冷单向阀的导通方向限定为由所述过冷旁通管的与所述过冷管组的并联节点流向与所述第一管段的并联节点；
    分流单向阀，设置于所述分流旁通管上，所述分流单向阀的导通方向限定为由所述换热管组的与所述第一管段的并联节点流向与所述第二管段的所述至少部分管段的并联节点。
  2. 根据权利要求1所述的换热器，其特征在于，所述过冷旁通管所并联的所述换热管组的所述第一管段的换热管的数量，小于或等于其所并联的所述过冷管组的换热管的数量。
  3. 根据权利要求1所述的换热器，其特征在于，所述过冷旁通管所并联的所述换热管组的所述第一管段的换热管的数量，小于或等于所述分流旁通管所并联的所述第二管段的所述至少部分管段的换热管的数量。
  4. 根据权利要求1所述的换热器，其特征在于，所述过冷旁通管所并联的所述过冷管组的换热管的数量，大于或等于所述分流旁通管所并联的所述第二管段的所述至少部分管段的换热管的数量。
  5. 根据权利要求1所述的换热器，其特征在于，所述过冷旁通管的数量为多个，多个所述过冷旁通管并联连接。
  6. 根据权利要求5所述的换热器，其特征在于，多个所述过冷旁通管所并联的所述换热管组的第一管段的换热管的数量相同或者不相同。
  7. 根据权利要求1所述的换热器，其特征在于，所述分流旁通管的数量为多个，多个所述过冷旁通管并联连接。
  8. 根据权利要求7所述的换热器，其特征在于，多个所述分流旁通管所并联的所述换热管组的第二管段的换热管的数量相同或者不相同。
  9. 一种空调器，其特征在于，所述空调器包括室内换热器、室外换热器、压缩机和四通阀连接构成的冷媒循环流路；其中，所述室外换热器为如权利要求1-8的任一项所述的换热器，所述换热器的所述换热管组与所述压缩机相连通，所述过冷管组与所述室内换热器相连通。
  10. 一种空调器，其特征在于，所述空调器包括室内换热器、室外换热器、压缩机和四通阀连接构成的冷媒循环流路；其中，所述室内换热器为如权利要求1-8的任一项所述的换热器，所述换热器的所述换热管组与所述压缩机相连通，所述过冷管组与所述室内换热器相连通。
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