WO2022166235A1 - 换热器、电控盒及空调系统 - Google Patents

换热器、电控盒及空调系统 Download PDF

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Publication number
WO2022166235A1
WO2022166235A1 PCT/CN2021/122412 CN2021122412W WO2022166235A1 WO 2022166235 A1 WO2022166235 A1 WO 2022166235A1 CN 2021122412 W CN2021122412 W CN 2021122412W WO 2022166235 A1 WO2022166235 A1 WO 2022166235A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
heat
plate
heat exchange
header
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/CN2021/122412
Other languages
English (en)
French (fr)
Inventor
王国春
王命仁
徐安
罗华东
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
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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
Publication of WO2022166235A1 publication Critical patent/WO2022166235A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/20—Electric components for separate outdoor units
    • F24F1/24—Cooling of electric components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/26—Refrigerant piping
    • F24F1/32—Refrigerant piping for connecting the separate outdoor units to indoor units
    • 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
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems

Definitions

  • the present application relates to the technical field of air conditioning, and in particular, to a heat exchanger, an electric control box and an air conditioning system.
  • An electric control box is generally provided in the outdoor unit of the air conditioner, and the electronic control box is provided with electronic components to detect and/or control the operation state of each component of the outdoor unit of the air conditioner.
  • electronic components generate a large amount of heat during operation, so a radiator needs to be provided to dissipate heat from the electronic components.
  • the existing radiator has the disadvantages of complex structure and low heat dissipation efficiency.
  • the present application provides a heat exchanger, an electric control box and an air conditioning system, which can simplify the structure of the heat exchanger and improve the heat exchange efficiency of the heat exchanger.
  • a first aspect of the present application provides a heat exchanger, the heat exchanger includes: a heat exchange body and a header assembly, the header assembly is used to provide a refrigerant flow to the heat exchange body, and the heat exchange bodies include a parallel and spaced arrangement at least two plate body assemblies; heat dissipation fins are arranged on at least two plate body assemblies, and the heat dissipation fins are thermally connected to the heat exchange main body; the fixing plate, while the heat dissipation fins covering the at least two plate body assemblies are away from One side of the board assembly to form a cooling air duct.
  • the fixing plate includes a top panel and at least one side panel, the heat dissipation fins on the top panel cover the at least two panel assemblies at the same time away from the panel assembly, the side panel is connected to the top panel by bending, and faces the panel body. Component extension.
  • the number of side panels is two, the two side panels are arranged at intervals along the vertical direction of the spacing direction of the at least two board assemblies, the top panel is respectively connected to the two side panels to form a accommodating space, and the heat dissipation fins are located in the accommodating space. in the setting space.
  • the number of heat dissipation fins is at least two, each heat dissipation fin is disposed on the corresponding plate body assembly, and the at least two heat dissipation fins are spaced apart from each other along the spacing direction of the at least two plate body assemblies.
  • the heat dissipation fins are integrally arranged and arranged on at least two plate body components.
  • both ends of the fixing plate along the spacing direction of the at least two plate body assemblies are open, so that the airflow in the heat dissipation air duct flows along the spacing direction of the at least two plate body assemblies.
  • the flow direction of the refrigerant flow is perpendicular to the spacing direction of the at least two plate assemblies.
  • each plate body assembly includes a first plate body and a second plate body arranged in layers, the first plate body is provided with a plurality of first microchannels for the flow of the first refrigerant flow, and the second plate body is provided with a plurality of first microchannels for the flow of the first refrigerant flow.
  • a plurality of second microchannels in which two refrigerant streams flow the second refrigerant stream absorbs heat from the first refrigerant stream, so that the first refrigerant stream is supercooled, or the first refrigerant stream absorbs heat from the second refrigerant stream, so that the second refrigerant stream absorbs heat from the second refrigerant stream.
  • the refrigerant stream is too cold.
  • a second aspect of the present application provides an electric control box, the electric control box includes a box body and the heat exchanger according to any of the above embodiments, the heat exchanger is connected to the electric control box, and the heat exchanger is used to dissipate heat for the electric control box .
  • a third aspect of the present application provides an air-conditioning system
  • the air-conditioning system includes a compressor, an outdoor heat exchanger, an indoor heat exchanger and the heat exchanger of any of the above embodiments
  • the compressor is connected to the outdoor heat exchanger through a connecting pipeline
  • a circulating refrigerant flow is provided between the indoor heat exchanger and the outdoor heat exchanger
  • the heat exchanger is arranged between the outdoor heat exchanger and the indoor heat exchanger and communicated with the connecting pipeline.
  • heat dissipation fins are arranged on the heat exchange body of the heat exchanger, so as to use the heat dissipation fins to increase the contact area between the heat exchange body and the air, so as to facilitate contact with the air. Carry out heat exchange to improve the heat exchange efficiency of the heat exchanger.
  • the heat dissipation fins are provided with fixed plates, and the fixed plates cover the side of the heat dissipation fins on at least two plate body assemblies away from the plate body assemblies at the same time to form heat dissipation air ducts.
  • the sealing of the heat dissipation fins of the present application adopts an integral fixed plate
  • the structure and few parts make the production of the heat exchanger simple and reliable, and the heat dissipation efficiency is high.
  • FIG. 1 is a schematic block diagram of an embodiment of an air conditioning system of the present application
  • FIG. 2 is a schematic block diagram of another embodiment of the air conditioning system of the present application.
  • FIG. 3 is a schematic block diagram of another embodiment of the air conditioning system of the present application.
  • FIG. 4 is a schematic block diagram of another embodiment of the air conditioning system of the present application.
  • FIG. 5 is a schematic structural diagram of an embodiment of a heat exchange body of the heat exchanger of the present application.
  • FIG. 6 is a schematic structural diagram of another embodiment of the heat exchange body of the heat exchanger of the present application.
  • FIG. 7 is a schematic structural diagram of another embodiment of the heat exchange body of the heat exchanger of the present application.
  • FIG. 8 is a schematic structural diagram of an embodiment of a heat exchange body and a header assembly of a heat exchanger of the present application
  • FIG. 9 is a schematic structural diagram of another embodiment of the heat exchanger body and the header assembly of the heat exchanger of the present application.
  • FIG. 10 is a schematic structural diagram of another embodiment of the heat exchange main body and the header assembly of the heat exchanger of the present application;
  • FIG. 11 is a schematic structural diagram of another embodiment of the heat exchange main body and the header assembly of the heat exchanger of the present application.
  • FIG. 12 is a schematic structural diagram of another embodiment of the heat exchange body of the heat exchanger of the present application.
  • FIG. 13 is a schematic structural diagram of another embodiment of the heat exchange main body and the header assembly of the heat exchanger of the present application.
  • FIG. 14 is a schematic structural diagram of another embodiment of the heat exchange main body and the header assembly of the heat exchanger of the present application.
  • FIG. 15 is a schematic structural diagram of another embodiment of the heat exchange body of the heat exchanger of the present application.
  • Fig. 16 is a three-dimensional schematic diagram of the arrangement plane of the first pipe body in Fig. 15;
  • 17 is a schematic structural diagram of another embodiment of the heat exchange body of the heat exchanger of the present application.
  • FIG. 18 is a schematic structural diagram of another embodiment of the heat exchange main body and the header assembly of the heat exchanger of the present application.
  • FIG. 19 is a schematic structural diagram of another embodiment of the heat exchange body of the heat exchanger of the present application.
  • FIG. 20 is a schematic flowchart of an embodiment of a method for manufacturing the heat exchanger in FIG. 19;
  • 21 is a schematic structural diagram of another embodiment of the heat exchange main body and the header assembly of the heat exchanger of the present application.
  • FIG. 22 is a schematic structural diagram of an embodiment of the header in FIG. 21;
  • FIG. 23 is a schematic structural diagram of another embodiment of the heat exchanger of the present application.
  • Figure 24 is an enlarged schematic cross-sectional view at the circle B in Figure 23;
  • FIG. 25 is a schematic structural diagram of an embodiment of the heat dissipation fin in FIG. 23;
  • FIG. 26 is a schematic structural diagram of another embodiment of the heat dissipation fin in FIG. 23;
  • FIG. 27 is a schematic three-dimensional structural diagram of an embodiment of the electric control box of the present application with some components hidden;
  • FIG. 28 is a schematic three-dimensional structural diagram of an embodiment of the heat sink in FIG. 27;
  • FIG. 29 is a schematic three-dimensional structure diagram of another embodiment of the heat sink in FIG. 27;
  • FIG. 30 is a schematic three-dimensional structural diagram of an embodiment of the heat dissipation fixing plate and the heat sink of the present application.
  • FIG. 31 is a schematic plan view of an embodiment of the heat dissipation fixing plate in FIG. 30;
  • 32 is a cross-sectional structural schematic diagram of another embodiment of the radiator and the electrical control box of the present application.
  • FIG. 34 is a schematic plan view of the structure of a radiator in cooperation with an electric control box in another embodiment of the present application.
  • 35 is a schematic cross-sectional structural diagram of another embodiment of the radiator of the present application in cooperation with the electric control box;
  • FIG. 36 is a schematic structural diagram of an embodiment of the deflector in FIG. 35;
  • FIG. 37 is a schematic structural diagram of another embodiment of the deflector in FIG. 35;
  • FIG. 38 is a schematic structural diagram of another embodiment of the deflector in FIG. 35;
  • Figure 39 is a schematic plan view of the structure of a radiator and an electrical control box in yet another embodiment of the present application.
  • Figure 40 is a schematic cross-sectional view of the radiator in Figure 39 in cooperation with the electric control box;
  • 41 is a cross-sectional structural schematic diagram of the cooperation of a heat sink and an electric control box in another embodiment of the present application.
  • 43 is a schematic three-dimensional structure diagram of the electric control box in another embodiment of the present application after some components are hidden;
  • 44 is a schematic plan view of the electric control box in another embodiment of the present application after some components are hidden;
  • Fig. 45 is a schematic cross-sectional view of the electric control box in Fig. 44
  • 46 is a schematic structural diagram of another embodiment of the air conditioning system of the present application.
  • Figure 47 is a schematic diagram of the internal structure of the air-conditioning system in Figure 46 after removing the box;
  • Figure 48 is a schematic structural diagram of an embodiment of the drainage sleeve in Figure 46;
  • Figure 49 is a schematic structural diagram of another embodiment of the drainage sleeve in Figure 46;
  • FIG. 50 is a schematic cross-sectional structural diagram of the air-conditioning system in FIG. 46 along the direction A-A.
  • FIG. 1 is a schematic block diagram of an air conditioning system in an embodiment of the present application.
  • the air conditioning system 1 mainly includes a compressor 2 , a four-way valve 3 , an outdoor heat exchanger 4 , an indoor heat exchanger 5 , a heat exchanger 6 , an expansion valve 12 and an expansion valve 13 .
  • the expansion valve 13 and the heat exchanger 6 are arranged between the outdoor heat exchanger 4 and the indoor heat exchanger 5, and the compressor 2 provides a circulating flow between the outdoor heat exchanger 4 and the indoor heat exchanger 5 through the four-way valve 3. refrigerant flow.
  • the heat exchanger 6 includes a first heat exchange channel 610 and a second heat exchange channel 611 .
  • the first end of the first heat exchange channel 610 is connected to the outdoor heat exchanger 4 through the expansion valve 13
  • the second heat exchange channel 610 is connected to the outdoor heat exchanger 4 through the expansion valve 13 .
  • the first end of the second heat exchange channel 611 is connected to the second end of the first heat exchange channel 610 through the expansion valve 12, and the second end of the second heat exchange channel 611 is connected to the compressor 2
  • the suction port 22 is connected.
  • the path of the refrigerant flow is:
  • the path (main path) of the refrigerant flow of the first heat exchange channel 610 is: the first end of the first heat exchange channel 610 - the second end of the first heat exchange channel 610 - the indoor heat exchanger 5 .
  • the refrigerant flow path (auxiliary path) of the second heat exchange channel 611 is: the second end of the first heat exchange channel 610 - the expansion valve 12 - the first end of the second heat exchange channel 611 - the second end of the second heat exchange channel 611 Two-end - suction port 22 of compressor 2 .
  • the working principle of the air-conditioning system at this time is as follows: the outdoor heat exchanger 4 is used as a condenser, which outputs a medium-pressure and medium-temperature refrigerant flow through the expansion valve 13 (the temperature can be 40°, the liquid-phase refrigerant flow), and the first heat exchange channel
  • the refrigerant flow of 610 is a medium-pressure and medium-temperature refrigerant flow.
  • the expansion valve 12 converts the medium-pressure and medium-temperature refrigerant flow into a low-pressure and low-temperature refrigerant flow (the temperature can be 10°, and the gas-liquid two-phase refrigerant flow).
  • the refrigerant flow is a low-pressure and low-temperature refrigerant flow.
  • the low-pressure and low-temperature refrigerant flow in the second heat exchange channel 611 absorbs heat from the medium-pressure and medium-temperature refrigerant flow in the first heat exchange channel 610, and then the refrigerant flow in the second heat exchange channel 611 is vaporized, so that the first heat exchange channel
  • the refrigerant flow of 610 achieves further subcooling.
  • the vaporized refrigerant flow in the second heat exchange channel 611 is used to increase the enthalpy of the compressor 2 by air injection, so as to improve the refrigeration capacity of the air conditioning system 1 .
  • the expansion valve 12 is used as a throttling component of the second heat exchange channel 611 to adjust the flow rate of the refrigerant flow in the second heat exchange channel 611 .
  • the refrigerant flow in the first heat exchange channel 610 and the refrigerant flow in the second heat exchange channel 611 perform heat exchange, so as to realize subcooling of the refrigerant flow in the first heat exchange channel 610 . Therefore, the heat exchanger 6 can be used as an economizer of the air conditioning system 1 to improve the degree of subcooling, thereby improving the heat exchange efficiency of the air conditioning system 1 .
  • connection port 31 of the four-way valve 3 is connected to the connection port 33
  • connection port 32 of the four-way valve 3 is connected to the connection port 34 .
  • the refrigerant flow output by the compressor 2 through the exhaust port 21 flows from the indoor heat exchanger 5 to the outdoor heat exchanger 4, and the indoor heat exchanger 5 is used as a condenser.
  • the refrigerant flow output by the indoor heat exchanger 5 is divided into two paths, one of which flows into the first heat exchange passage 610 (main passage), and the other flows into the second heat exchange passage 611 (auxiliary passage) through the expansion valve 12 .
  • the refrigerant flow in the second heat exchange channel 611 can also supercool the refrigerant flow in the first heat exchange channel 610, thereby improving the heating capacity of the air conditioner.
  • the first end of the second heat exchange channel 611 may not be connected with the second end of the first heat exchange channel 610 , and the second heat exchange channel 610
  • the first end of the hot channel 611 can be directly connected to the first end of the expansion valve 13 or the second end of the expansion valve 13, so that the refrigerant flow in the second heat exchange channel 611 can also be connected to the refrigerant flow in the first heat exchange channel 610.
  • the flow is supercooled to improve the cooling or heating capacity of the air conditioning system 1 .
  • FIG. 4 is a schematic block diagram of an air conditioning system in another embodiment of the present application.
  • the difference between the air conditioning system 1 shown in FIG. 4 and the air conditioning system 1 shown in FIG. 1 is mainly that a gas-liquid separator 8 is added.
  • the heat exchanger 6 includes a first heat exchange channel 610 for the flow of the first refrigerant flow and a second heat exchange channel 611 for the flow of the second refrigerant flow.
  • the second refrigerant flow absorbs heat from the first refrigerant flow during the flow along the second heat exchange channel 611, so that the first refrigerant flow is supercooled.
  • the first refrigerant flow may also absorb heat from the second refrigerant flow during the flow along the first heat exchange channel 610, so that the second refrigerant flow is supercooled. Therefore, the heat exchanger 6 can be used as an economizer of the air conditioning system 1 to improve the degree of subcooling, thereby improving the heat exchange efficiency of the air conditioning system 1 .
  • the intake port of the compressor 2 includes an enthalpy-increasing intake port 221 and an air return port 222 .
  • the second refrigerant flow flowing through the second heat exchange channel 611 is further transported to the enthalpy increasing air inlet 221 of the compressor 2 or the inlet 81 of the gas-liquid separator 8, wherein the outlet 82 of the gas-liquid separator 8 is further
  • the air return port 222 of the compressor 2 is connected to provide the compressor 2 with a low-pressure gaseous refrigerant flow.
  • the air conditioning system 1 further includes a four-way valve 3 , an expansion valve 12 and an expansion valve 13 .
  • the expansion valve 13 and the heat exchanger 6 are arranged between the outdoor heat exchanger 4 and the indoor heat exchanger 5, and the compressor 2 provides a circulating flow between the outdoor heat exchanger 4 and the indoor heat exchanger 5 through the four-way valve 3. refrigerant flow.
  • the four-way valve 3 includes a connection port 31 , a connection port 32 , a connection port 33 and a connection port 34 .
  • the connection port 32 of the four-way valve 3 is connected to the outdoor heat exchanger 4 ; the connection port 34 of the four-way valve 3 is connected to the gas-liquid separator 8 .
  • the connection port 31 of the four-way valve 3 is connected to the compressor 2, specifically the exhaust port 21 of the compressor 2; the connection port 33 of the four-way valve 3 is connected to the indoor heat exchanger 5.
  • the function of the four-way valve 31 in the air conditioning system 1 is to realize the mutual conversion between cooling and heating by changing the flow direction of the refrigerant flow in the system pipeline, so that the air conditioning system 1 can be in the cooling mode and To switch between heating modes, when the air conditioning system 1 has both cooling and heating functions, the above-mentioned four-way valve 31 can be used to switch directions.
  • the air conditioning system 1 may not use the four-way valve 31 .
  • the compressor 2 can be directly connected to the outdoor heat exchanger 4 through the connecting pipeline. Specifically, the compressor 2 is connected to the outdoor heat exchanger 4 and the indoor heat exchanger through the connecting pipeline. A circulating refrigerant flow is provided between 5, and the heat exchanger 6 is arranged between the outdoor heat exchanger 4 and the indoor heat exchanger 5, and is communicated with the connecting pipeline.
  • the air-conditioning system 1 may not use the above-mentioned four-way valve 31 .
  • the structure of the air conditioning system 1 can be simplified, and the production cost of the air conditioning system 1 can be saved.
  • the heat exchanger 6 when the heat exchanger 6 is not used as an economizer, the heat exchanger 6 can also be communicated with connecting pipelines at other locations.
  • the first end of the first heat exchange channel 610 is connected to the outdoor heat exchanger 4 via the expansion valve 13 , the second end of the first heat exchange channel 610 is connected to the indoor heat exchanger 5 , and the first end of the second heat exchange channel 611
  • the expansion valve 12 is connected to the second end of the first heat exchange passage 610 , and the second end of the second heat exchange passage 611 is connected to the enthalpy inlet 221 of the compressor 2 or the inlet 81 of the gas-liquid separator 8 .
  • the second end of the second heat exchange channel 611 When the second end of the second heat exchange channel 611 is connected to the enthalpy increasing air inlet 221 of the compressor 2, it can provide a gaseous refrigerant with an intermediate pressure for the enthalpy increasing of the air jet of the compressor 2, thereby improving the refrigeration and/or cooling of the air conditioning system 1. heating capacity.
  • the principle and function of the enthalpy increase by the gas injection belong to the understanding category of those skilled in the art, and will not be repeated here.
  • the evaporation temperature of the refrigerant flow is lower and the temperature difference is larger, which further improves the heat exchange efficiency of the air conditioning system 1 .
  • the air conditioning system 1 may further include a switching component for selectively connecting the second end of the second heat exchange passage 611 to the enthalpy increasing air inlet 221 of the compressor 2 and the inlet 81 of the gas-liquid separator 8 . That is, the switching assembly can be used to selectively deliver the second refrigerant flow flowing through the second heat exchange channel 611 to the enthalpy-increasing air inlet 221 of the compressor 2 and the inlet 81 of the gas-liquid separator 8 .
  • the switching assembly may include a solenoid valve 15 .
  • the solenoid valve 15 is connected between the enthalpy-increasing air inlet 221 of the compressor 2 and the second end of the second heat exchange passage 611 , so as to open the solenoid valve 15 when the compressor 2 needs to increase the enthalpy by air injection, so as to provide the air injection of the compressor 2 .
  • Enthalpy increase provides intermediate pressure gaseous refrigerant.
  • the switching assembly may also include a solenoid valve 14 .
  • the solenoid valve 14 is connected between the second end of the second heat exchange channel 611 and the inlet 81 of the gas-liquid separator 8, and the solenoid valve 14 is used to open when the compressor 2 does not need or is not suitable for increasing the enthalpy of air injection, so as to The second refrigerant flow output from the second end of the second heat exchange channel 611 is guided into the gas-liquid separator 8 .
  • the solenoid valve 15 and the solenoid valve 14 are respectively connected to the second ends of the second heat exchange passages 612 .
  • the expansion valve 12 acts as a throttling component of the second heat exchange passage 611 to adjust the flow rate of the second refrigerant flow in the second heat exchange passage 611 .
  • the cooling and heating principles of the air conditioning system 1 shown in FIG. 4 are basically the same as those of the air conditioning system 1 shown in FIG. 1 , and details are not described herein again.
  • the air conditioning system 1 further includes an electric control box 7 , and the heat exchanger 6 is connected to the electric control box 7 , and the heat exchanger 6 is arranged to dissipate heat from the electronic components in the electric control box 7 .
  • the heat exchanger 6 not only acts as an economizer of the air conditioning system 1 to increase the degree of subcooling, but also acts as a radiator to dissipate heat for the electric control box 7 , and specifically, to dissipate heat for the electronic components in the electric control box 7 .
  • the present application further optimizes the following aspects based on the overall structure of the air conditioning system 1 described above:
  • the heat exchanger 6 includes a heat exchange body 61 , and the heat exchange body 61 is provided with a plurality of microchannels 612 , and the plurality of microchannels 612 includes a first microchannel and a second microchannel , and in the air conditioning system shown in FIGS. 1-4 , the first microchannel serves as the first heat exchange channel 610 of the heat exchanger 6 , and the second microchannel serves as the second heat exchange channel 611 of the heat exchanger 6 . Therefore, the first microchannel 610 and the first heat exchange channel 610 use the same reference number, and the second microchannel 611 and the second heat exchange channel 611 use the same reference number.
  • the heat exchange body 61 may include a single or multiple plate bodies 613 .
  • each microchannel 612 perpendicular to its extending direction may be a rectangle, and the side length of each microchannel 612 is 0.5mm-3mm.
  • the thickness between each microchannel 612 and the surface of the plate body 613 and between the microchannels 612 is 0.2mm-0.5mm, so that the microchannels 612 meet the requirements of pressure resistance and heat transfer performance.
  • the cross-sectional shape of the microchannel 612 may be other shapes, such as circular, triangular, trapezoidal, elliptical, or irregular.
  • the plurality of microchannels 612 can be configured as single-layer microchannels or multi-layer microchannels. When the flow rate of the refrigerant flow is low and the flow state of the refrigerant flow is laminar flow, the larger the cross-sectional area of the plurality of microchannels 612, the shorter the length of the plurality of microchannels 612, which can reduce the flow resistance of the refrigerant flow loss.
  • the plurality of microchannels 612 of the plate body 613 may include alternately arranged first microchannels 610 and second microchannels 611 , and the extending direction D1 of the first microchannel 610 and the extending direction D2 of the second microchannel 611 are parallel to each other. Specifically, as shown in FIG.
  • a first preset number of microchannels in the plurality of microchannels 612 are divided into first microchannels 610
  • a second preset number of microchannels in the plurality of microchannels 612 are divided into second microchannels Channels 611
  • multiple groups of first microchannels 610 and multiple groups of second microchannels 611 are alternately arranged in sequence, that is, a second microchannel 611 is arranged between the two groups of first microchannels 610, and a second microchannel 611 is arranged between the two groups of second microchannels 611.
  • a first microchannel 610 is arranged between the two groups, so that the at least two groups of the first microchannels 610 and the second microchannels 611 are spaced apart from each other to form a heat exchanger 6 in which the first microchannels 610 and the second microchannels 611 are alternately arranged.
  • the first preset number and the second preset number may or may not be equal.
  • the first microchannel 610 and the second microchannel 611 can be independent of each other, so that different refrigerant streams can flow, and then one refrigerant stream can flow through the other refrigerant stream. cold.
  • the first microchannel 610 and the second microchannel 611 may be communicated with each other, and serve as one microchannel for the flow of the same refrigerant flow.
  • the first microchannels 610 and/or the second microchannels 611 are arranged in two or more layers, the two or more layers of the first microchannels 610 and/or the second microchannels can be made through the reverse header.
  • the microchannels 611 communicate with each other, or the plate body 613 is bent by 180 degrees to form two or more layers of the first microchannel 610 and/or the second microchannel 611 .
  • the heat exchange body 61 may include at least one group of first microchannels 610 and at least one group of second microchannels 611 , the at least one group of first microchannels 610 and At least one group of the second microchannels 611 are spaced apart from each other along the width direction of the plate body 613 , the width direction being perpendicular to the extending direction of the plate body 613 .
  • the at least one group of the first microchannels 610 and the at least one group of the second microchannels 611 may also be spaced apart from each other along the thickness direction of the plate body 613 , which is different from the plate body 613 in the thickness direction.
  • the extension direction is vertical.
  • the first microchannel 610 and the second microchannel 611 are independent of each other, and are respectively disposed in different plates 613 , so that the extension direction D1 of the first microchannel 610 and the The extending directions D2 of the second microchannels 611 are arranged perpendicular to each other, so that the first and second headers described below can be arranged on different sides of the heat exchanger 6 respectively, thereby facilitating the arrangement of headers of the heat exchanger 6 .
  • the first microchannel 610 and the second microchannel 611 are used for the flow of different refrigerant streams, so that one refrigerant stream can be used to subcool the other refrigerant stream.
  • the plate body 613 can be a flat tube, so that heat dissipation elements or electronic components can be arranged on the plate body 613 .
  • the plate body 613 may also be a carrier with other cross-section shapes, such as a cylinder, a rectangular parallelepiped, a cube, and the like.
  • the heat exchange body 61 may also include at least two plate bodies 613 stacked on each other or two tube bodies nested with each other.
  • the first refrigerant flow (ie, the medium-pressure and medium-temperature refrigerant flow) flows through the first microchannel 610
  • the second refrigerant flow (ie, the low-pressure and low-temperature refrigerant flow) flows through the first microchannel 610
  • the first refrigerant flow can be a liquid-phase refrigerant flow
  • the second refrigerant flow can be a gas-liquid two-phase refrigerant flow.
  • the second refrigerant flow absorbs heat from the first refrigerant flow in the first microchannel 610 during the flow along the second microchannel 611 and is further vaporized, so that the first refrigerant flow is further subcooled.
  • the heat exchanger 6 based on the microchannel structure described above and below is not limited to the application scenarios shown in FIGS. 1-4 , so the first microchannel 610 and the second microchannel 611 and the first refrigerant
  • the "first" and “second” in the flow and the second refrigerant flow are only used to distinguish different microchannels and refrigerant flows, and should not be regarded as a limitation on the specific application of the microchannel 612 and the refrigerant flow.
  • the first refrigerant flow through the first microchannel 610 may absorb heat on the second refrigerant flow in the second microchannel 611, and the first refrigerant flow and the second refrigerant flow
  • the state is also not limited to the liquid phase or the gas-liquid two-phase as defined above.
  • the flow direction A1 of the first refrigerant flow is opposite to the flow direction A2 of the second refrigerant flow, so that the temperature of the first refrigerant flow and the temperature of the second refrigerant flow can always exist in the heat exchange area Larger temperature difference, thereby improving the heat exchange efficiency of the first refrigerant flow and the second refrigerant flow.
  • the flow direction A1 of the first refrigerant flow can be the same as or perpendicular to the flow direction A2 of the second refrigerant flow.
  • the temperature of the heat exchanger 6 on the side close to the inlet can be higher than that of the heat exchanger 6.
  • the heat exchange effect of this area is further improved.
  • the area is connected to the area with large electric control heat to improve the heat dissipation effect; when the refrigerant flow directions are perpendicular to each other, the first and second headers are respectively arranged in the heat exchange area.
  • the different sides of the heat exchanger 6 are arranged, so that the arrangement of the refrigerant headers of the heat exchanger can be facilitated.
  • the heat exchanger 6 further includes a header assembly 62 .
  • the extension direction of the header assembly 62 and the extension direction of the heat exchange body 61 are arranged perpendicular to each other.
  • the header assembly 62 is arranged vertically along the direction of gravity.
  • the piping arrangement of the header assembly 62 can be facilitated.
  • the header assembly 62 is arranged along the horizontal plane, which can improve the uniformity of the refrigerant distribution in the header assembly 62, thereby making the refrigerant distribution in the heat exchange main body 6 more uniform .
  • the header assembly 62 includes a first header 621 and a second header 622 , the first header 621 is provided with a first header channel, and the second header 622 is provided with a second header collection channel.
  • the cross-sectional shape of the heat exchanger 6 along the flow direction of the refrigerant flow (the first refrigerant flow or the second refrigerant flow) in the heat exchange main body 61 is an I-shape.
  • the cross-sectional shape of the heat exchanger 6 along the flow direction of the refrigerant flow in the heat exchange main body 61 may be L-shaped, U-shaped, G-shaped, or circular.
  • the first header channel is connected to the first microchannel 610 to provide the first refrigerant flow to the first microchannel 610 through the first header channel and/or collect the first refrigerant flow flowing through the first microchannel 610 .
  • the first end of the first microchannel 610 is connected to the outdoor heat exchanger 4 through one of the two first headers 621 via the expansion valve 13 to provide cooling
  • the first refrigerant flow is provided to the first microchannel 610
  • the second end of the first microchannel 610 is connected to the indoor heat exchanger 5 through the other of the two first headers 621 to collect the flow through the first A first refrigerant flow of a microchannel 610.
  • the heating mode since the flow directions of the first refrigerant flow in the first microchannels 610 are opposite, the functions of the two first headers 621 are interchanged compared to the cooling mode.
  • the second header channel is connected to the second microchannel 611 to provide the second refrigerant flow to the second microchannel 611 through the second header channel and/or collect the second refrigerant flow flowing through the second microchannel 611 .
  • the first end of the second microchannel 611 is connected to the second expansion valve 12 through one of the two second headers 622 to connect the second microchannel 611 to the second expansion valve 12 .
  • a second refrigerant flow is provided; the second end of the second microchannel 611 is connected to the enthalpy-increasing air inlet 221 of the compressor 2 or the inlet 81 of the gas-liquid separator 8 through the other of the two second headers 622 , to collect the second refrigerant flow flowing through the second microchannel 611 .
  • the first microchannel 610 and/or the second microchannel 611 are connected by 180° bending or reversed headers to form two layers of the first microchannel 610 or the second microchannel 611
  • the first microchannel 610 and/or the second microchannel 611 Or the inflow port and the outflow port of the second microchannel 611 may be disposed on the same side of the heat exchange body 61 .
  • the above-mentioned first and second header channels can be divided into a refrigerant supply area and a refrigerant collection area, and the inflow inlet and outlet of the first and/or second microchannels are respectively connected with the refrigerant area and collection area provided by the header assembly 62 .
  • the refrigerant area is connected.
  • the heat exchange body 61 includes at least two groups of first microchannels 610 and at least two groups of second microchannels 611 , wherein the at least two groups of first microchannels 610 have the same end and the same first collector.
  • the tubes 621 are connected, and the same ends of the at least two groups of second microchannels 611 are connected to the same second header 622 . That is, one header can correspond to multiple groups of microchannels, which avoids setting a corresponding header for each microchannel and reduces costs.
  • the extension directions of the first header 621 and the second header 622 are parallel to each other.
  • the extension directions of the first header 621 and the second header 622 can be adjusted according to the extension directions of the first microchannel 610 and the second microchannel 611, for example, they are arranged perpendicular to each other.
  • the first header 621 and the second header 622 are arranged at intervals, and the second header 622 is arranged farther from the heat exchange main body 61 than the first header 621 .
  • 621 is provided between the second header 622 and the heat exchange main body 61 .
  • the second microchannel 611 penetrates the first header 621 and is inserted into the second header 622 and fixed by welding.
  • the first microchannel 610 is inserted into the first header 621 and fixed by welding.
  • the first header 621 is disposed farther from the heat exchange main body 61 than the second header 622
  • the second header 622 is disposed between the first header 621 and the second header 622 . between the heat exchange bodies 61 .
  • the first microchannel 610 is inserted through the second header 622 into the first header 621 and fixed by welding.
  • microchannels described here and in the context of running through a certain header refer to the microchannels passing through the headers and not communicating with the headers
  • microchannels inserted into the headers refer to the The microchannel communicates with the header
  • the second microchannel 611 passing through the first header 621 means that the second microchannel 611 passes through the first header 621 and is not communicated with the first header 621.
  • the insertion of the two microchannels 611 into the second header 622 means that the second microchannel 611 communicates with the second header 622 .
  • One or more groups of the first microchannel 610 and the second microchannel 611 may be provided respectively.
  • two groups of the first microchannel 610 may be provided, one The microchannels 611 are located between the two sets of first microchannels 610 .
  • the first microchannels 610 and the second microchannels 611 can be arranged in two groups or more, and the first microchannels 610 and the second microchannels are arranged alternately on top of each other, such as forming a first microchannel 610-second microchannel 611-first microchannel 610-second microchannel 611 or first microchannel 610-second microchannel 611-second microchannel 611-first microchannel 610 and so on.
  • one of the first microchannel 610 and the second microchannel 611 may be used as the main channel, and the other of the first microchannel 610 and the second microchannel 611 may be used as the auxiliary channel , and use the refrigerant flow in the auxiliary channel to supercool the refrigerant flow in the main channel.
  • the main channel can be arranged outside the heat exchange main body 61 to facilitate its connection with the electric control box 6. It is used to dissipate heat for the electric control box 6 .
  • the main channel with a large refrigerant flow penetrate through the header corresponding to the auxiliary channel, and insert it into the header corresponding to the main channel, in this way, compared with the auxiliary channel running through the main channel
  • the corresponding header does not occupy the space of the header corresponding to the main channel, which can reduce the pressure loss of the flow path of the header corresponding to the main channel and make the flow more uniform.
  • the first microchannel 610 when the first microchannel 610 is a main channel with a large refrigerant flow rate, and the second microchannel 611 is an auxiliary channel with a small refrigerant flow rate, the first microchannel 610 runs through the second header 622 and Inserted into the first header 621 , in this way, the second microchannel 611 can not occupy the space of the first header 621 , compared with the method of making the second microchannel 610 penetrate the first header 621 , the pressure loss of the flow path of the first header 621 can be reduced, and the flow splitting can be made more uniform.
  • first header 621 and the second header 622 may be welded together to reduce the distance between the first header 621 and the second header 622 .
  • first header 621 and the second header 622 may be bonded or snapped together.
  • first microchannel 610 can bypass the second header 622 and then be connected to the first header 621.
  • first microchannel 610 is disposed outside the second header 622 to bypass the second header.
  • the pipe 622 is then connected to the first header 621 .
  • second microchannel 611 may bypass the first header 621 and then be connected to the second header 622 .
  • the microchannels on the heat exchange body 61 may also be arranged in other ways. At least some of the microchannels penetrate one of the at least two headers and are inserted into the other header. In this way, the volume of the heat exchanger 6 can be reduced. In the specific setting, the microchannel with a large refrigerant flow can be made to penetrate one of the at least two headers and be inserted into the other header. In this way, the pressure loss of the header can be reduced. small, making the microchannel shunt more uniform.
  • the above-mentioned heat exchange main body 61 can be composed of either a single plate body 613 or a plurality of plate bodies 613.
  • the first microchannel 610 and the second microchannel 611 can be arranged on the same plate body 613 , it can also be arranged in different plate bodies 613 .
  • one end of part of the microchannels penetrates one of the at least two headers and is inserted into the other header
  • the other end of the at least part of the microchannels is inserted into the header pipe through which the microchannel passes through.
  • This arrangement can improve the integration of the heat exchange body 61, save welding and other processes, and improve the heat exchange effect.
  • the at least two headers are not limited to the above-mentioned ways of being spaced apart from each other, and may be at least two headers formed by the overall header and the baffle plate described below.
  • the main header is divided into two headers
  • the header assembly 62 includes a main header 623 and a baffle plate 624 , and the baffle plate 624 is provided in the main header 623 to dispose the main header 623 to be separated by the baffle plate 624
  • the first header 621 and the second header 622 are separated.
  • the number of baffles 624 and the headers formed can be set as desired.
  • the first microchannel 610 penetrates the tube wall of the general header 623 and is inserted into the first header 621
  • the second microchannel 611 penetrates the tube wall of the general header 623 and The baffle plate 624 (ie, penetrates through the first header 621 ), and is inserted into the second header 622
  • the second microchannel 611 may penetrate the tube wall of the general header 623 and be inserted into the second header 622
  • the first microchannel 610 may penetrate the tube wall and partition of the general header 623
  • the flow plate 624 is inserted into the first header 621 .
  • the functions of the first header 621 and the second header 622 are simultaneously realized by a single header 623 , which can reduce the number of header assemblies. 62 for the cost and volume.
  • the baffle plate 624 may be used to separate the main header 623 into two first headers 621 or two second headers 622 .
  • first microchannel 610 or the second microchannel 611 is bent by 180° or reversed to form two layers of the first microchannel 610 or the second microchannel 611, one end of the first microchannel 610 penetrates through The tube wall of the main header 623 is inserted into one of the first headers 621, and the other end of the first microchannel 610 penetrates the tube wall of the main header 623 and the baffle plate 624 and is inserted into it.
  • another first header 621 In another first header 621 .
  • one end of the second microchannel 611 penetrates the pipe wall of the general header 623 and is inserted into one of the second headers 622
  • the other end of the second microchannel 611 penetrates the pipe wall of the general header 623 and the baffle plate 624 and inserted into another second header 622 therein.
  • a slot 601 may be provided on the end face of the heat exchange body 61 , and the slot 601 is located between the first microchannel 610 and the second microchannel 611 .
  • the flow plate 624 is embedded in the slot 601, so that the first microchannel 610 penetrates the tube wall of the general header 623 and is inserted into the first header 621, and the second microchannel 611 passes through the tube of the general header 623 The wall is inserted into the second header 622 .
  • the heat exchange body 61 when the first microchannel 610 or the second microchannel 611 is bent by 180° or reversed to form two layers of the first microchannel 610 or the second microchannel 611, the heat exchange body 61 The inlet and outlet ends are on the same side. At this time, one end of the first microchannel 610 penetrates the tube wall of the general header 623 and is inserted into one of the first headers 621 , and the other end of the first microchannel 610 penetrates the tube of the general header 623 wall and inserted into another first header 621 therein.
  • one end of the second microchannel 611 penetrates the pipe wall of the general header 623 and is inserted into one of the second headers 622 , and the other end of the second microchannel 611 penetrates the pipe wall of the general header 623 and inserted into the other second header 622 therein.
  • the heat exchange body 61 may be a single plate body 613 or a plurality of plate bodies 613 .
  • the heat exchange main body 61 may be a single plate body 613 , and the first microchannel 610 and the second microchannel 611 are arranged in the single plate body 613 .
  • an interval area is provided between the first microchannel 610 and the second microchannel 61 , and the slot 601 is arranged in the interval area.
  • the heat exchange main body 61 is integrally arranged, the structure is simple, the reliability is high, and the heat transfer efficiency of the heat exchange main body 61 can be improved.
  • the heat exchange main body 61 may also include at least two plate bodies 613, the at least two plate bodies 613 are stacked, and the end faces of the at least two plate bodies 613 are provided with slots 601, The slot 601 is disposed between the adjacent plates 613 , and the baffle plate 624 is embedded in the slot 601 .
  • the above-described matching method of the baffle plate 624 and the slot 601 can be applied to other microchannel grouping methods, as long as at least two groups of microchannels are provided on the heat exchange body 61, and the at least two groups of microchannels can be They are connected to each other for the flow of the same refrigerant flow, and can be independent of each other for the flow of different refrigerant flows.
  • the diameter of the second header 622 is smaller than the diameter of the first header 621 , the first header 621 is sleeved outside the second header 622 , and the first microchannel 610 penetrates the first header 621 .
  • the tube wall of the header 621 is inserted into the first header 621 .
  • the second microchannel 611 penetrates the tube walls of the first header 621 and the second header 622 and is inserted into the second header 622 .
  • the second header 622 may be sleeved on the outside of the first header 621, and at this time, the second microchannel 611 penetrates the wall of the second header 622 and is inserted into the second header within the flow tube 622.
  • the first microchannel 610 penetrates through the tube walls of the second header 622 and the first header 621 , and is inserted into the first header 621 .
  • the volume of the header assembly 62 can be reduced by the nested arrangement.
  • two first headers 621 may be nested with each other, or two second headers 622 may be nested with each other.
  • one end of the first microchannel 610 penetrates the tube wall of the outer first header 621 and is inserted into the outer first header 621 .
  • the other end of the first microchannel 610 penetrates the tube walls in the two first headers 621 and is inserted into the inner first header 621 .
  • one end of the second microchannel 611 penetrates the tube wall of the second outer header 622 and is inserted into the outer second header 622 .
  • the other end of the second microchannel 611 penetrates the tube walls in the two second headers 622 and is inserted into the inner first header 622 .
  • the heat exchanger 6 includes a heat exchange main body 61, and the heat exchange main body 61 includes a first tube body 614 and a second tube body 615 nested with each other, that is, the heat exchanger 6 is a sleeve-type heat exchanger .
  • the first tube body 614 is provided with a plurality of first microchannels 610
  • the second tube body 615 is provided with a plurality of second microchannels 611.
  • the microchannels 612 shown in 5 are the same, so the length of the heat exchange body 61 is shortened, thereby reducing the volume of the heat exchanger 6 .
  • the extending direction of the first microchannel 610 and the extending direction of the second microchannel 611 are parallel to each other, for example, the extending direction of the first microchannel 610 and the extending direction of the second microchannel 611 are the same.
  • the first tube body 614 is sleeved on the outside of the second tube body 615 , and at least one flat surface 616 is provided on the outer surface of the first tube body 614 to form the first tube body 614 heat exchange contact surface.
  • Heat dissipation components or electronic components can be arranged on the plane 616 for ease of installation.
  • the second pipe body 615 can be sleeved on the outer side of the first pipe body 614 and form a similar plane.
  • the first refrigerant flow flows through a plurality of first microchannels 610
  • the second refrigerant flow flows through a plurality of second microchannels 611
  • the first refrigerant flow may be a liquid-phase refrigerant.
  • the second refrigerant flow can be a gas-liquid two-phase refrigerant flow.
  • the second refrigerant stream absorbs heat from the first refrigerant stream of the plurality of first microchannels 610 during its flow along the plurality of second microchannels 611 and is further vaporized, so that the first refrigerant stream is further subcooled.
  • the first refrigerant flow passing through the first microchannel 610 may absorb heat to the second refrigerant flow in the second microchannel 611 , and the state of the first refrigerant flow and the second refrigerant flow Nor is it limited to the liquid or gas-liquid two phases as defined above.
  • the cross-sectional area of the heat exchange main body 61 is increased, and the pressure loss of the refrigerant flow can be reduced.
  • the first tube body 614 and the second tube body 615 are provided with sleeves, which can improve the heat exchange area between the plurality of first microchannels 610 and the plurality of second microchannels 611, and improve the first microchannels 610 and the second microchannels. The heat exchange efficiency between 611.
  • the heat exchanger 6 further includes a header assembly 62 , the header assembly 62 includes a first header 621 and a second header 622 , and the first header 621 is provided with a first header channel , the first collecting channel is used for providing the first refrigerant flow to the first microchannel 610 and/or collecting the first refrigerant flow flowing through the first microchannel 610 .
  • the second header 622 is provided with a second header channel that provides the second refrigerant flow to the second microchannel 611 and/or collects the second refrigerant flow flowing through the second microchannel 611 .
  • the cross-sectional shape of the heat exchanger 6 along the flow direction of the refrigerant flow in the heat exchange main body 61 is an I-shape.
  • the cross-sectional shape of the heat exchanger 6 along the flow direction of the refrigerant flow in the heat exchange main body 61 may be L-shaped, U-shaped, G-shaped, or circular.
  • the header assembly 62 may employ the various header arrangements described above, such as the spaced arrangement of the first header 621 and the second header 622 described above, the overall header 623 and the flow divider
  • the arrangement of the plates 624, or the arrangement of the first header 621 and the second header 622 are nested with each other.
  • the first tube body 614 together with the first microchannel 610 thereon and the second tube body 615 together with the second microchannel 611 thereon can be matched with the above-mentioned collecting tube in the manner described above, which is not described here. Repeat.
  • the heat exchanger has a plurality of plates arranged on top of each other
  • the heat exchanger 6 includes a heat exchange body 61 , and the heat exchange body 61 includes a first plate body 631 and a second plate body 632 , and the first plate body 631 and the second plate body 632 are stacked on each other.
  • the first plate body 631 is provided with a plurality of first microchannels 610, and the second plate body 632 is provided with a plurality of second microchannels 611.
  • 5-The microchannel 612 shown in FIG. 7 is the same, and will not be repeated here.
  • the contact area between the first plate body 631 and the second plate body 632 is increased, so as to increase the exchange between the first microchannel 610 and the second microchannel 611 heat area to improve heat exchange efficiency.
  • the first refrigerant flow flows through the plurality of first microchannels 610
  • the second refrigerant flow flows through the plurality of second microchannels 611
  • the second refrigerant flow flows along the plurality of second microchannels 611 .
  • heat is absorbed from the first refrigerant streams of the plurality of first microchannels 610 and further vaporized, so that the first refrigerant streams are further subcooled.
  • the first refrigerant flow passing through the first microchannel 610 may absorb heat to the second refrigerant flow in the second microchannel 611 , and the state of the first refrigerant flow and the second refrigerant flow Nor is it limited to the liquid or gas-liquid two phases as defined above.
  • first plate body 631 and the second plate body 632 may be provided respectively.
  • the number of the first plate bodies 631 may be two, and the second plate body 632 is sandwiched between the two first plate bodies 631 , for example, the first plate body 631 , the second plate body 632 and the first plate body 631 are stacked in sequence.
  • the second plate body 632 is sandwiched between the two first plate bodies 631, so that the second refrigerant flow of the second plate body 632 absorbs heat to the first refrigerant flow of the two first plate bodies 631 at the same time, Subcooling of the first refrigerant flow of the two first plates 631 is achieved.
  • the heat dissipating element or the electronic element can be arranged to be thermally connected with the first plate body 631 , for example, the first plate body 631 is disposed on the surface of the first plate body 631 away from the second plate body 632 to facilitate installation.
  • the first plate body 631 and the second plate body 632 may be provided, and the first plate body 631 and the second plate body are alternately stacked.
  • the two first plate bodies 631 may be two independent plate bodies. In other embodiments, the two first plates 631 may also be integrally connected in a U-shape or connected by reverse headers. In this case, the first microchannels 610 in the two first plates 631 are connected in a U-shape. Further, the inlet and outlet of the first microchannel 610 are located on the same side of the heat exchange body 61 .
  • the number of the second plate bodies 632 may be two, and the first plate body 631 is sandwiched between the two second plate bodies 632 .
  • the heat dissipating element or the electronic element may be arranged to be thermally connected with the second plate body 632 .
  • the heat exchanger 6 further includes a header assembly 62.
  • the header assembly 62 includes a first header 621 and a second header 622.
  • the first header 621 is provided with a first header
  • the first collector channel is used for providing the first refrigerant flow to the first microchannel 610 and/or collecting the first refrigerant flow flowing through the first microchannel 610 .
  • the second header 622 is provided with a second header channel that provides the second refrigerant flow to the second microchannel 611 and/or collects the second refrigerant flow flowing through the second microchannel 611.
  • the header assembly 62 may employ the various header arrangements described above, such as the first header 621 and the second header 622 spaced from each other, the main header 623 and the baffles 624 described above , or the arrangement in which the first header 621 and the second header 622 are nested with each other.
  • the first plate body 631 together with the first microchannels 610 thereon and the second plate body 633 and the second microchannels 611 thereon can be matched with the above-mentioned collectors in the manner described above.
  • the heat exchanger 6 includes a first plate body 631 , a second plate body 632 and a connecting piece 64 .
  • the first board body 631 and the second board body 632 are stacked on top of each other, the connecting piece 64 is sandwiched between the adjacent first board body 631 and the second board body 632, and solder is provided on both sides of the connecting piece 64 (not shown in the figure). (shown), the solder is used to weld and fix the connection piece 64 to the first board body 631 and the second board body 632 on both sides of the connection piece 64 .
  • the first board body 631 and the second board body 632 are welded by disposing solder on both sides of the connecting piece 64 , and then welding the first board body 631 and the second board body 632 through the connecting piece 64 .
  • the first board body 631 and the second board body 632 can be effectively fixed. Since the welding between the adjacent board bodies 613 needs to be coated with solder on the bonding surfaces of the two board bodies 613, Compared with the board body 613 whose surface is coated with solder, by arranging the connecting piece 64 with solder between the two board bodies 613 , the production cost can be greatly reduced.
  • connection piece 64 is higher than the melting point of the solder.
  • the connection piece 64 can be a metal foil to improve thermal conductivity.
  • the connecting piece 64 may be aluminum foil or copper foil, or the like. The cost of the metal foil is relatively low, and the process of arranging the solder on both sides of the metal foil is relatively simple, so the metal foil with the solder is easier to obtain and has a lower production cost.
  • the coverage area of the solder on the connecting piece 64 for the first board body 631 and the second board body 632 adjacent to both sides is not less than 80% of the overlapping area of the first board body 631 and the second board body 632, so as to improve the first board body 631 and the second board body 632. Reliability of welding between the board body 631 and the second board body 632 .
  • the coverage area of the first board body 631 and the second board body 632 by the solder on the connecting piece 64 may be 80% of the overlapping area of the first board body 631 and the second board body 632 adjacent to both sides; or , the coverage area of the first plate body 631 and the second plate body 632 by the solder on the connecting piece 64 can be equal to the overlapping area of the first plate body 631 and the second plate body 632 . In this way, the reliability of the heat exchanger 6 can be further improved. sex.
  • the connecting piece 64 between the first board body 631 and the second board body 632 may be a single-layer structure, that is, only one layer of connecting piece 64 is provided between the first board body 631 and the second board body 632 .
  • the connecting piece 64 between the first board body 631 and the second board body 632 is at least two layers.
  • the connecting piece 64 may be a two-layer, three-layer or four-layer structure.
  • the at least two layers of connecting pieces 64 are further fixed by soldering.
  • the distance between the first plate body 631 and the second plate body 632 can be adjusted, so that the heat exchanger 6 can be adapted to different application scenarios.
  • a slot with a width equal to the stacking thickness of the at least two layers of connecting sheets 64 is formed to match the baffle plate described above.
  • the thickness of the connecting piece 64 ranges from 0.9 mm to 1.2 mm.
  • the thickness of the connecting piece 64 may be 0.9 mm, 1 mm, or 1.2 mm, or the like.
  • connecting piece 64 may be disposed between adjacent plates of other at least two plates having microchannels, for example, two first plates 631 or two second plates 632 .
  • the above-mentioned manufacturing method of the heat exchanger 6 may include: S11 : providing at least two plate bodies. S12: A connecting piece is provided, and solder is provided on both sides of the connecting piece. S13: Lay up at least two boards, and sandwich the connecting piece between adjacent boards. S14: Heating the at least two board bodies and the connecting piece, so that the connecting piece and the board body 3 located on both sides of the connecting piece are welded and fixed by the solder.
  • the heat exchanger 6 includes at least two plate bodies 613 and at least one header 620 .
  • the plate body 613 includes a main body portion 671 and a connecting portion 672 , and the main body portions 671 of the at least two plate bodies 613 are stacked on each other. It is provided that one end of the connection part 672 is connected to the main body part 671 , and the other end of the connection part 672 is connected to the header 620 .
  • At least two insertion holes 602 are provided on the tube wall of the header 620 , and the other end of the connecting portion 672 of the plate body 613 corresponds to the insertion holes 602 and is fixed to the header 620 by welding. That is, the connecting portion 672 is located at the end of the plate body 613 and is used for fixing with the header 620 .
  • the at least two plates 613 are welded with the header 620, if the distance between the two adjacent plates 613 is small at the welding place, the difficulty of welding will be increased, and the solder will flow along the adjacent two plates.
  • the gaps between the individual plates 613 flow, resulting in poor welding between the plates 613 and the headers 620, resulting in the risk of refrigerant flow leakage.
  • first distance d1 between two adjacent insertion holes 602 on the header 620
  • second distance d2 between the main body portions 671 of two adjacent plates 613
  • the first distance d1 is greater than the first distance d1.
  • Two spacing d2. In this way, the distance between the connecting portions 671 of the two adjacent plates 613 at the welding place can be increased, the capillary action between the two adjacent plates 613 can be reduced, and the plate 613 and the header 620 can be improved. Soldering reliability.
  • the first distance d1 is not less than 2mm, for example, the first distance d1 can be 2mm or 3mm, etc., so as to reduce the capillary action between the connecting parts 672 of the plate body 613, which is beneficial to the connecting parts 672 of the plate body 613 and the collectors. Welds between flow tubes 620. Furthermore, the first distance d1 is further not greater than 6 mm, so that the heat exchanger 6 has higher structural strength and improves the reliability of the heat exchanger 6 .
  • At least part of the connecting parts 672 of the plate body 613 are arranged in a curved shape, for example, at least part of the connecting parts 672 of the plate body 613 are arranged in an arc shape.
  • This curved arrangement is convenient to adjust the distance between the connecting portions 672 of the two adjacent plates 613 , facilitates the welding and fixing between the plates 613 and the headers 620 , and reduces the reduction of the two adjacent plates during welding. Capillary action between 613.
  • one end of the connecting portion 672 of the plate body 613 is curved and the other end is straight, so as to simplify the processing process.
  • the connecting parts 672 of at least part of the adjacent plate bodies 613 there is a third distance d3 between the connecting parts 672 of at least part of the adjacent plate bodies 613 , and the third distance d3 is gradually increased in at least part of the range from the main body part 671 to the collecting pipe 620 , so that the phase The distance between the adjacent connecting parts 672 gradually increases, reducing the capillary action between the two adjacent plate bodies 613 .
  • the at least two plate bodies 61 may include the first plate body 631 and the second plate body 632 described above.
  • the number of the first plate bodies 631 is two
  • the number of the second plate bodies 632 is two
  • the first plate bodies 631 and the second plate bodies 632 are stacked in sequence.
  • One of the second plates 632 is sandwiched between the two first plates 631
  • the other second plate 632 is stacked on the outer side of the first plate 631 away from the sandwiched second plate 632 .
  • the header 620 includes a first header 621 and a second header 622 arranged at intervals.
  • the first plate body 631 is provided with a plurality of first microchannels for the flow of the first refrigerant flow
  • the second plate body 632 is provided with a plurality of second microchannels for the flow of the second refrigerant flow.
  • connection portion 672 of the first plate body 631 is welded and fixed to the first header 621
  • connection portion 672 of the second plate body 632 is welded and fixed to the second header 621 .
  • the connecting portion 672 of the sandwiched second plate body 632 can penetrate through the first header 621 and be connected to the second header 622 , and the connecting portion 672 of the second plate body 632 located on the outside
  • the first header 621 and the second header 622 can be bypassed and welded and fixed.
  • the number of sockets 602 on the first header 621 can be reduced, and the distance between the sockets 602 can be increased. It is beneficial to the assembly of the heat exchanger 6, so that the heat exchanger 6 has high reliability. At the same time, the disturbance to the refrigerant flow in the first header 621 can be reduced.
  • the connecting portions 672 of the second plate body 632 all penetrate the first header 621 and are connected to the second header 622 .
  • the connecting portion 672 of the first plate body 631 may penetrate through the second header 622 and be connected to the first header 621 , and details are not described herein again.
  • the number of the first plate body 631 and the second plate body 632 can be selected and set according to actual application needs, which is not specifically limited here.
  • the headers 620 may also adopt various arrangement manners of the headers described above, which will not be repeated here.
  • main body portion 672 of the board body 613 has a linear structure, so the main body portion 671 of the first board body 631 and the main body portion 671 of the second board body 632 can be directly welded by solder.
  • main body portion 671 of the first board body 631 and the main body portion 671 of the second board body 672 are connected by the above-described connecting piece with solder, which is not repeated here.
  • the heat exchanger 6 includes a heat exchange body 61 and heat dissipation fins 65 .
  • the heat dissipation fins 65 can be disposed on the heat exchange body 61 and thermally connect the heat dissipation fins 65 to the heat exchange body 61 . , to increase the contact area between the heat exchange body 61 and the air by using the heat dissipation fins 65 to facilitate heat exchange with the air, improve the heat exchange efficiency of the heat exchanger 6 , and improve the heat dissipation effect of the heat exchanger 6 .
  • the heat dissipation fins 65 may be connected to the surface of the heat exchange main body 61 by welding, bonding or fastening.
  • the heat exchange main body 61 includes at least two plate body assemblies 603 arranged side by side and spaced apart, and the heat dissipation fins 65 are arranged on the at least two plate body assemblies 603 .
  • the heat exchanger 6 further includes a fixing plate 66, the fixing plate 66 covers the heat dissipation fins 65 on the at least two plate body assemblies 603 at the same time, and the fixing plate 66 is located on the side of the heat dissipation fins 65 away from the plate body assembly 603, to form cooling air ducts.
  • the sealing of the heat dissipation fins 65 adopts the structure of the integral fixing plate 66, and there are few parts, so that the production of the heat exchanger 6 is simple and reliable, and the formed heat dissipation air duct can improve the heat dissipation effect.
  • the airflow directions defined by the heat dissipation air ducts may be set along the spacing direction of the plate body components, that is, perpendicular to the extending direction of the plate body components 603 , so as to increase the heat dissipation efficiency of the heat exchange fins 65 .
  • the airflow direction defined by the heat dissipation air ducts may be set with the extending direction of the board assembly 603 or set at other angles with the extending direction of the board assembly 603 .
  • the fixing plate 66 includes a top panel 661 , and the top panel 661 covers the heat dissipation fins 65 on the at least two plate assemblies 603 at the same time, so as to facilitate the sealing of the heat dissipation fins 65 .
  • the fixing plate 66 further includes at least one side panel 662, the side panel 662 is connected to the top panel 661 by bending, and extends toward the plate body assembly 603, so as to seal the heat dissipation air duct through the side panel 662 and reduce the number of heat exchangers 6 parts to improve the sealing performance of the cooling air duct.
  • the fixing plate 66 may include a top panel 661 and a side panel 662 , the side panel 662 is connected to one end of the top panel surface 661 by bending, and one end of the heat dissipation fin 65 is in abutment with the side panel 662 , to close the cooling air duct.
  • the other end of the heat dissipation fins 65 can be assembled by splicing other parts, or abutted with the box body of the electric control box described below, so that the heat dissipation fins 65 can form a complete air duct. In this way, the heat dissipation fins can be simplified. 65 package to improve assembly efficiency.
  • the number of the side panels 662 is two, the two side panels 662 are arranged at intervals along the vertical direction of the spacing direction of the at least two panel assemblies 603 , and the top panel 661 is respectively bent with the two side panels 662
  • the heat dissipation fins 65 are located in the accommodation space, that is, between the two side panels 662.
  • the fixed plate 66 can completely seal the heat dissipation fins 65 to form an overall heat dissipation air.
  • There are fewer parts and components which further simplifies the packaging process of the heat dissipation fins 65, so that the production of the heat exchanger 6 is simple and reliable, and the heat exchange capacity is improved at the same time.
  • the heat dissipation fins 65 are wavy structures formed by extruding sheets, and the crests and troughs of the wavy structures are in contact with the surfaces of the top panel 661 and the panel assembly 603 facing each other, respectively. .
  • the number of heat dissipation fins 65 may be at least two. As shown in FIG. 25 , the number of heat dissipation fins 65 may be equal to the number of plate body assemblies 603 , and each heat dissipation fin 65 is disposed on the corresponding plate body component 603. The width of each heat dissipation fin 65 in the vertical direction along the extending direction of the plate assembly 603 can be equal to the width of the corresponding plate assembly 603 , so as to improve the heat exchange capacity and save the material cost.
  • each heat dissipation fin 65 can be attached to one board assembly 603 , and a plurality of heat dissipation fins 65 can be arranged at intervals along the spacing direction of the board assembly 603 .
  • the temperature of the space between the 613 is higher than that of the plate body 613 , and this arrangement can prevent the heat dissipation fins 65 from being melted and deformed.
  • the number of heat dissipation fins 65 may also be one, that is, the heat dissipation fins 65 are integrally formed and disposed on at least two plate assemblies 603 at the same time.
  • the width of the heat dissipation fins 65 in the vertical direction along the extending direction of the plate assembly 603 may be greater than or equal to the width of the heat exchange main body 61 . In this way, the number of integrated heat dissipation fins 65 is small and the surface area is large.
  • the heat dissipation fins 65 it is convenient to connect the heat dissipation fins 65 to the heat exchange main body 61 and improve the installation efficiency of the heat dissipation fins 65 and the heat exchange main body 61;
  • the contact area between the heat dissipation fins 65 and the air can also be increased to enhance the heat exchange effect.
  • both ends of the fixing plate 66 along the spacing direction of the at least two plate body assemblies 603 are openly disposed, so that the flow direction of the airflow in the cooling air duct is disposed along the spacing direction of the at least two plate body assemblies 603 .
  • the flow direction of the refrigerant flow in the plate assembly 603 is perpendicular to the spacing direction of the at least two plate assemblies 603 to enhance the heat dissipation effect of the heat dissipation air duct and improve the overall heat exchange efficiency of the heat exchanger 6 .
  • each plate body assembly 603 may be provided with a microchannel, for example, various combinations of the plate body and the microchannel described above are used, which will not be repeated here.
  • heat dissipation fins 65 is applicable to various forms of heat exchangers 6 described in this application, and should not be limited to a specific embodiment.
  • the present application can also use the above-mentioned heat exchanger 6 as a radiator (the radiator 6 will be described below), the radiator 6 includes a heat exchange body 61 and a header assembly 62, and the radiator 6 is arranged to be opposite to the electric control box
  • the electronic components within 7 are dissipated for heat dissipation. It is worth noting that, as understood by those skilled in the art, the radiator 6 mentioned here should include various forms of heat exchangers described above, and should not be limited to a specific embodiment.
  • the radiator 6 serves as an economizer of the air-conditioning system 1 and also replaces the modular radiator in the electric control box 6 to dissipate heat to the electric control box 7 to simplify the pipeline of the air-conditioning system 1
  • the number of components and modules reduces costs.
  • the electric control box 7 includes a box body 72 and a radiator 6 .
  • the box body 72 is provided with an installation cavity 721 , the electronic components 71 are arranged in the installation cavity 721 , and the radiator 6 is arranged in the installation cavity 721 . It is used to dissipate heat for the electronic components 71 in the mounting cavity 721 .
  • the heat sink 6 may also be disposed outside the box body 72 , and is disposed to dissipate heat for the electronic components 71 in the mounting cavity 721 .
  • the box body 72 includes a top plate (not shown in the figure, arranged opposite to the bottom plate 723 to cover the opening of the installation cavity 721 ), a bottom plate 723 and a circumferential side plate 724 .
  • the side plate 724 is connected to the top plate and the bottom plate 723 , thereby forming an installation cavity 721 .
  • the bottom plate 723 and the top plate are rectangular, the number of circumferential side plates 724 is four, and the four circumferential side plates 724 are respectively connected to the corresponding side edges of the bottom plate 723 and the top plate, and further connected to the bottom plate 723 It is enclosed with the top plate to form a cuboid-shaped electric control box 7 .
  • the size of the long side of the bottom plate 723 is the length of the electric control box 7
  • the size of the short side of the bottom plate 723 is the width of the electric control box 7 .
  • the height of the circumferential side plate 724 perpendicular to the bottom plate 723 is the height of the electric control box 7 .
  • the length of the electric control box 7 in the X direction is the length of the electric control box 7
  • the length of the electric control box 7 in the Y direction is the height of the electric control box 7
  • the electric control box 7 in the Z direction is the height of the electric control box 7.
  • the length in the direction is the width of the electric control box 7 .
  • the heat exchange main body 61 is arranged in a straight shape, as shown in FIG. 18 , the heat exchange main body 61 has an overall length, an overall width and an overall height.
  • the overall length is the length of the heat exchange main body 61 along the extending direction thereof, that is, the length of the heat exchange main body 61 along the X direction shown in FIG. 18 .
  • the overall width is the length of the heat exchange body 61 in the direction perpendicular to the extending direction of the heat exchange body 61 and perpendicular to the plane where the heat exchange body 61 is located, that is, the length of the heat exchange body 61 along the Y direction shown in FIG. 18 .
  • the overall height is the length of the heat exchange body 61 in the Z direction shown in FIG. 18 .
  • the plane where the heat exchange body 61 is located refers to the plane where the header assembly 62 is located, that is, the XOZ plane shown in FIG. 18 .
  • the heat exchange main body 61 can be arranged on the bottom plate 723 of the electric control box 7 .
  • the heat exchange main body 61 may be disposed on the circumferential side plate 724 of the electric control box 7 .
  • the heat exchange main body 61 may also be fixed at other positions of the electric control box 7 according to the arrangement positions of the electronic components 71 and the like, which are not specifically limited in the embodiments of the present application.
  • the heat exchange body 61 When the heat exchange body 61 is in a straight shape as shown in FIG. 18 , the heat exchange body 61 can be in contact with the bottom plate 723 , or can be arranged at a distance from the bottom plate 723 . In this way, the size of the bottom plate 723 in the longitudinal direction can be fully utilized, and the Possibly long heat exchange body 61 to improve heat exchange effect.
  • the heat exchange main body 61 may also abut against the circumferential side plate 724, or be spaced apart from the circumferential side plate 724, which is not specifically limited in the embodiment of the present application.
  • the heat exchange body 61 in order to reduce the overall length of the heat exchange body 61 , the heat exchange body 61 can be divided into a first extension part 617 and a second extension part 618 , and the second extension part 618 is connected to the first extension part 617 The end of the heat exchange body 61 is bent to one side of the first extension part 617 so that the heat exchange body 61 is L-shaped.
  • the overall length of the heat exchange body 61 can be reduced on the condition that the heat exchange body 61 has a sufficiently long extension length , so that the length of the electric control box 7 matched with the radiator 6 along the X direction can be reduced, so as to reduce the volume of the electric control box 7 .
  • the first extension portion 617 can be arranged parallel to the bottom plate 723 to make full use of the lengthwise dimension of the bottom plate 723 to set the heat exchange main body 61 as long as possible to improve the heat exchange effect.
  • the second extension 618 may be arranged parallel to the circumferential side plate 724 to reduce the space occupied by the second extension 618 in the X direction.
  • first extension 617 may be arranged to be parallel to one of the circumferential side plates 724 and the second extension 618 may be arranged to be parallel to the circumferential side plate 724 adjacent to the circumferential side plate 724 to connect the heat sink 6 It is arranged on one side of the installation cavity 721 .
  • first extension portion 617 may abut against the bottom plate 723 or be spaced from the bottom plate 723
  • second extension portion 618 may abut against the circumferential side plate 724 or be spaced from the circumferential side plate 724 .
  • the embodiment is not specifically limited.
  • the number of the second extension portion 618 may be one, and one second extension portion 618 is connected to one end of the first extension portion 617 , so that the heat exchange main body 61 is L-shaped.
  • the number of the second extension parts 618 can be two, and the two second extension parts 618 are respectively connected to opposite ends of the first extension part 617 and are respectively bent to the same side of the first extension part 617 . fold.
  • the two second extending portions 618 may be disposed at opposite ends of the first extending portion 617 in parallel and spaced apart, so as to further reduce the overall length of the heat exchanging main body 61 while ensuring the heat exchange effect of the heat exchanging main body 61 , reducing the volume of the radiator 6 .
  • the two second extending portions 618 are bent and arranged on the same side of the first extending portion 617, and are located on opposite sides of the first extending portion 617 relative to the two second extending portions 618, which can also facilitate shortening the heat sink. 6 overall width.
  • the two second extension parts 618 may be perpendicular to the first extension part 617 to form a U-shaped heat exchange body 61 .
  • the two second extension parts 618 may be perpendicular to the first extension part 617 to form a U-shaped heat exchange body 61 .
  • the space occupied by the second extending portion 618 in the X direction can be reduced, avoiding the two second extending portions 618 and the electronic components 71 disposed in the mounting cavity 721 . interfere.
  • the two second extension parts 618 may also be inclined relative to the first extension part 617 , and the inclination angles of the two second extension parts 618 relative to the first extension part 617 may be the same or different, so as to shorten the electric control box 7 the overall width.
  • the extension length of the first extension part 617 is set to be greater than the extension length of the second extension part 618 , so that the first extension part 617 is arranged along the length direction of the electric control box 7 , and the second extension part 618 is arranged along the length direction of the electric control box 7 .
  • the number of radiators 6 provided in the installation cavity 721 may be one, and one radiator 6 may be extended in the installation cavity 721 along the length direction of the box body 72 .
  • a heat sink 6 may be extended in the installation cavity 721 along the height direction of the box body 72 .
  • the number of the heat sinks 6 provided in the installation cavity 721 may be at least two, for example, the number of the heat sinks 6 may be two, three, four or five, and so on.
  • the number of the heat sinks 6 may be two, three, four or five, and so on.
  • the radiator is set in the electric control box
  • the various forms of heat sinks 6 disclosed in this application can also be arranged in the installation cavity 721 of the electrical control box 7 or applied to the heat dissipation of the electrical control box 7, and can be directly or It is thermally connected to the electronic component 71 in an indirect manner.
  • the radiator 6 is arranged in the installation cavity 721 of the electric control box 7 .
  • the heat sink 6 can be thermally connected to the electronic components 71 provided in the mounting cavity 721 to dissipate heat for the electronic components 71 .
  • the electronic element 71 can be thermally connected to the heat exchange main body 61 , and the electronic element 71 can be thermally connected to any position of the heat exchange main body 61 .
  • the electronic components 71 can be arranged at any position on the heat exchange body 61 . assembly.
  • the electronic components 71 may be arranged at the middle position of the heat exchange body 61 , or the electronic components 71 may be arranged at the positions of both ends of the heat exchange body 61 .
  • the electronic components 71 may be arranged on one side of the heat exchange body 61 , or the electronic components 71 may be arranged on opposite sides of the heat exchange body 61 according to actual application scenarios.
  • the electronic element 71 when the heat sink 6 is L-shaped or U-shaped, the electronic element 71 can be thermally connected to the first extension part 617 , and the electronic element 71 can be connected to the second extension part 618 is arranged on the same side of the first extension portion 617 to shorten the height of the electric control box 7, that is, the dimension along the Y direction.
  • the electronic element 71 can be thermally connected to the second extension portion 618 , and specifically, the electronic element 71 can be disposed on the side of the second extension portion 618 facing the first extension portion 617 to shorten the length of the electrical control box 7 , that is, Dimensions along the X direction.
  • the electronic components 71 may also be partially disposed on the first extending portion 617 and partially disposed on the second extending portion 618 , so that the electronic components 71 are evenly distributed.
  • a heat dissipation fixing plate 74 can also be arranged in the electric control box 7 , the electronic components 71 can be arranged on the heat dissipation fixing plate 74 , and then the heat dissipation fixing plate 74 is connected with the heat exchange main body 61 to pass The heat dissipation fixing plate 74 thermally connects the electronic components 71 and the heat exchange main body 61 , so that the installation efficiency of the electronic components 71 can be greatly improved.
  • the heat dissipation fixing plate 74 can be made of a metal plate or an alloy plate with good thermal conductivity.
  • the heat dissipation fixing plate 74 can be made of an aluminum plate, a copper plate, an aluminum alloy plate, etc. to improve the heat conduction efficiency.
  • a heat pipe 741 can also be embedded in the heat dissipation fixing plate 74.
  • the heat pipe 741 is used to rapidly conduct heat from a relatively concentrated high-density heat source and then spread it to the entire surface of the heat dissipation fixing plate 74, so that the heat dissipation fixing plate
  • the heat distribution on the 74 is uniform, and the heat exchange effect between the heat dissipation fixing plate 74 and the heat exchange main body 61 is enhanced.
  • the heat pipes 741 may be arranged in a strip shape, the number of the heat pipes 741 may include multiple, and the multiple heat pipes 741 may be arranged in parallel and spaced apart.
  • the plurality of heat pipes 741 may also be connected in sequence in a ring or frame shape, which is not specifically limited in the embodiment of the present application.
  • the radiator is set outside the electric control box
  • the radiator 6 is disposed outside the electric control box 7 , an assembly port 726 can be opened on the box body 72 of the electric control box 7 , and the electronic components 71 are thermally connected to the radiator 6 through the assembly port 726 .
  • the electronic component 71 is disposed on the surface of the heat dissipation fixing plate 74 on the side facing away from the heat sink 6 .
  • a heat pipe 741 may be provided to thermally connect the electronic component 71 and the heat sink 6 .
  • the heat pipe 741 may include a heat absorption end 741a and a heat release end 741b, and the heat absorption end 741a of the heat pipe 741 may be inserted into the interior of the mounting cavity 721 and thermally connected with the electronic component 71 for absorbing the heat of the electronic component 71.
  • the radiating end 741b of the heat pipe 741 is disposed outside the electric control box 7 and is thermally connected to the radiator 6 to dissipate heat from the radiating end 741b of the heat pipe 741 by the radiator 6 .
  • the heat sink 6 includes heat dissipation fins 65 .
  • the heat dissipation fins 65 can be used to increase heat exchange.
  • the contact area between the main body 61 and the air in the electric control box 7 facilitates heat exchange with the air, reduces the temperature in the installation cavity 721 , and protects the electronic components 71 .
  • the electronic components 71 and the heat dissipation fins 65 may be arranged on the same side of the heat exchange body 6, and the electronic components 71 and the heat dissipation fins 65 may be staggered to avoid interference between the electronic components 71 and the heat dissipation fins 65, and Setting a larger distance between the electronic components 71 and the heat dissipation fins 65 can also lower the temperature of the refrigerant in contact with the heat dissipation fins 65 and the electronic components 71 , so as to improve the heat dissipation effect of the heat exchange body 61 .
  • the electronic components 71 are disposed on one side of the heat exchange body 61
  • the heat dissipation fins 65 are disposed on the other side of the heat exchange body 61
  • the heat dissipation fins 65 may be disposed on the other side of the heat exchange body 61 . anywhere on one side.
  • the heat dissipation fins 65 may extend to the outside of the electrical control box 7, for example, an assembly opening is provided on the box body 72, the heat exchange body 61 is arranged in the box body 72, and is thermally connected with the electronic components 71, while One side of the heat dissipation fins 65 is thermally connected to the heat exchange main body 61 , and extends to the outside of the box body 72 through the assembly port, and can further improve the heat dissipation capability of the heat exchange main body 61 through the assistance of air cooling.
  • the electronic components are set in the position where the temperature of the radiator is higher
  • the electric control box 7 in this embodiment includes a box body 72, a heat sink 6 and electronic components 71.
  • the box body 72 is provided with an installation cavity 721, and the heat sink 6 is at least partially disposed in the installation cavity 721.
  • the electronic components 71 is arranged in the installation cavity 721 .
  • the structures of the box body 72 and the heat sink 6 are substantially the same as those in the above-mentioned embodiments, please refer to the descriptions in the above-mentioned embodiments.
  • the heat exchange main body 61 may be entirely disposed in the installation cavity 721 of the electric control box 7 , and the heat exchange main body 61 may also be partially disposed in the installation cavity 721 of the electric control box 7 and partially protrude out of the electric control box 7 . , for connection with the header assembly 62 and external piping.
  • the flow of the refrigerant flow makes the temperature of the radiator 6 lower, and the temperature in the installation cavity 721 of the electric control box 7 is higher due to the heat generated by the electronic components 71 in the electric control box 7.
  • the air with a higher temperature in the electric control box 7 contacts When it reaches the radiator 6 , it is easy to condense, and condensed water is formed on the surface of the radiator 6 . If the generated condensed water flows to the position of the electronic components 71 , the electronic components 71 may be easily short-circuited or damaged, and a fire hazard may be more serious.
  • the heat exchange main body 61 can be divided into a first end 61a and a second end 61b along the flow direction of the refrigerant flow.
  • the temperature of the heat exchange main body 61 increases from the first end 61a It gradually decreases in the direction to the second end 61b, that is, the temperature of the first end 61a is higher than that of the second end 61b.
  • the electronic component 71 is disposed at a position close to the first end 61 a and thermally connects the electronic component 71 with the heat exchange body 61 .
  • the temperature of the heat exchange body 61 described above and below refers to the surface temperature of the heat exchange body 61 .
  • the surface temperature change of the heat exchange body 61 is determined by the heat exchange channels adjacent to the surface.
  • the surface temperature of the heat exchange main body 61 is The refrigerant flow direction along the main road channel gradually decreases, and at this time, the first end 61a is located upstream of the second end 61b along the refrigerant flow direction of the main road channel.
  • the heat exchange channel adjacent to the surface of the heat exchange main body 61 is an auxiliary road channel
  • the surface temperature of the heat exchange main body 61 gradually decreases and increases along the refrigerant flow direction of the auxiliary road channel.
  • the first end 61a is located along the refrigerant flow direction of the auxiliary road channel. Downstream of the second end 61b.
  • the heat exchange main body 61 by dividing the heat exchange main body 61 into a first end 61a with a higher temperature and a second end 61b with a lower temperature according to the change of the temperature on the heat exchange main body 61 during operation, because the first end 61a with a higher temperature and the The temperature difference between the hot air is small, and no or a small amount of condensed water is generated.
  • the electronic component 71 By arranging the electronic component 71 near the first end 61a, the contact between the electronic component 71 and the condensed water can be reduced. probability, thereby protecting the electronic components 71 .
  • the temperature of the heat exchange body 61 has an opposite trend of change from the first end 61a to the second end 61b, that is, in one mode, the temperature of the heat exchange body 61 gradually decreases from the first end 61a to the second end 61b , and in another mode, the temperature of the heat exchange body 61 gradually increases from the first end 61a to the second end 61b.
  • the ambient temperature is low, for example, when the air conditioner works for heating in winter, the temperature of the air in the electrical control box 7 is low, and at this time, the temperature difference between the air in the electrical control box 7 and the radiator 6 Smaller, the air does not easily condense to form condensed water.
  • the ambient temperature is high, for example, when the air conditioner works for cooling in summer, the temperature of the air in the electric control box 7 is relatively high, the temperature difference between the air in the electric control box 7 and the radiator 6 is relatively large, and the air Easily condensed to form condensed water.
  • the temperature of the heat exchange main body 61 may be gradually decreased in the direction from the first end 61a to the second end 61b, so as to prevent the radiator 6 from being in the cooling mode. Condensed water is produced.
  • arranging the electronic component 71 at a position close to the first end 61a means that the electronic component 71 has a first distance between the thermally conductive connection position of the electronic component 71 on the heat exchange body 61 and the first end 61a, and is a distance from the second end 61a. There is a second distance between 61b, and the first distance is smaller than the second distance.
  • the temperature of the heat exchange body 61 gradually decreases in the direction from the first end 61a to the second end 61b, the temperature of the first end 61a is the highest, the temperature of the second end 61b is the lowest, and the heat exchange body 61
  • the lower the temperature of the heat exchange main body 61 the greater the temperature difference with the hot air, and the easier it is for the condensed water to condense. That is, in the direction from the first end 61 a to the second end 61 b of the heat exchange body 61 , the probability of generating condensed water gradually increases.
  • the electronic component 71 by arranging the electronic component 71 near the higher temperature end of the heat exchange body 61 , that is, at a position where condensed water is not easy to accumulate, the risk of contacting the electronic component 71 with the condensed water can be reduced, thereby protecting the electronic component 71 .
  • the extending direction of the heat exchange body 61 can be set along the vertical direction, and the first end 61a can be set on the upper part of the second end 61b, so that when the heat exchange body 61 is close to the second end 61b
  • the condensed water will flow down in the vertical direction, that is, the condensed water will flow in a direction away from the electronic component 71 to prevent the electronic component 71 from contacting the condensed water.
  • the extension direction of the heat exchange main body 61 can also be set in the horizontal direction as required, so that the condensed water generated near the second end 61b can be quickly separated from the heat exchange main body 61 under the action of gravity, so as to avoid contact with the electronic components 71 touch.
  • the extending direction of the heat exchange main body 61 may also be inclined relative to the horizontal direction, which is not specifically limited in the embodiment of the present application.
  • the structure of the heat sink 6 in this embodiment can be set to be the same as that in the above-mentioned embodiment, that is, a bent heat exchange body 61 is used.
  • the structure of the heat sink 6 in this embodiment may also adopt a straight heat exchange body 61 .
  • other types of heat sinks may also be used, and the specific structure of the heat sink 6 is not limited in the embodiment of the present application.
  • various heat sinks disclosed in the present application or other heat sinks known in the art may be used.
  • the electric control box 7 in this embodiment includes a box body 72 , a mounting plate 76 , an electronic component 71 and a heat sink 6 .
  • the box body 72 is provided with an installation cavity 721, and the installation plate 76 is disposed in the installation cavity 721, so that the installation cavity 721 forms a first cavity 7212 and a second cavity 7214 on both sides of the installation board 76, and the electronic components 71 are provided with In the second chamber 7214, at least part of the heat exchange body 61 is disposed in the first chamber 7212, and is thermally connected with the electronic components 71.
  • the mounting plate 76 is used to block the condensed water on the radiator 6 from flowing into the second chamber. Room 7214.
  • the mounting plate 76 By disposing the mounting plate 76 in the electrical control box 7 to separate the mounting cavity 721, and disposing the heat exchange main body 61 and the electronic component 71 in the independent first cavity 7212 and the second cavity 7214, respectively, it is possible to The electronic components 71 are completely isolated from the condensed water, so as to prevent the electronic components 71 from being short-circuited or damaged by contacting the condensed water.
  • the heat dissipation fixing plate 74 may be used to indirectly connect the electronic components 71 and the heat exchange main body 61 .
  • avoidance holes 762 may be provided at positions corresponding to the mounting plate 76 and the heat dissipation fixing plate 74 , the heat dissipation fixing plate 74 is connected to the heat exchange main body 61 and blocks the escape holes 762 , and the electronic components 71 are provided on the heat dissipation fixing plate 74 away from One side of the heat exchange body 61 .
  • the electronic component 71 and the heat exchange main body 61 can be thermally connected by the heat dissipation fixing plate 74 , and the first chamber 7212 and the second chamber 7214 can be separated by the heat dissipation fixing plate 74 to prevent condensed water from passing through the avoidance hole 762 It flows into the second chamber 7214 provided with the electronic components 71 , thereby preventing the condensed water from contacting the electronic components 71 .
  • the condensed water will fall under the action of gravity after accumulation, and the dripping condensed water is easy to be sputtered, thereby bringing hidden dangers to the circuit in the electric control box 7. , and the relatively dispersed condensed water is not conducive to the discharge of the electric control box 7 .
  • a baffle plate 77 may be provided in the electric control box 7 , and the baffle plate 77 is disposed on the lower side of the radiator 6 for collecting the condensed water dripping from the radiator 6 .
  • the arrangement of the baffle plate 77 can not only reduce the height of the condensed water droplets and prevent the condensed water droplets from sputtering, but also have a certain accumulation effect on the condensed water, so that the condensed water can be collected and discharged together from the electric control box 7.
  • the deflector 7 is fixed on the bottom plate 723 of the electric control box 7 , one end of the deflector 77 is connected to the bottom plate 723 , and the other end of the deflector 77 extends into the first chamber 7212 and dissipates heat.
  • the projection of the damper 6 in the vertical direction falls inside the deflector 77 . In this way, it can be ensured that the condensed water dripping from the radiator 6 is all located on the deflector 77 to prevent the condensed water from dripping to other positions of the electric control box 7 .
  • the radiator 6 can also be arranged on the mounting plate 76. At this time, one end of the deflector 77 is connected to the mounting plate 76, and the other end of the deflector 77 extends toward the inside of the first chamber 7212, and the radiator The projection of 6 in the vertical direction falls on the inside of the deflector 77 .
  • a drainage port 725 can also be opened on the bottom wall of the box body 72, and the deflector 77 is opposite to the box body.
  • the bottom wall of 72 is inclined, and the condensed water is diverted through the deflector 77 and then drained out of the box body 72 through the drain port 725 .
  • a drain port 725 can be provided on the circumferential side plate 724 of the electric control box 7, and the deflector plate 77 is connected to the mounting plate 76 or the bottom plate 723 of the box body 72, and is inclined to the direction of the drain port 725 to prevent condensation. After the water droplets land on the deflector 77 , they will converge along the inclined deflector 77 to the position of the drain port 725 , and then discharge the electric control box 7 from the drain port 725 .
  • the number and size of the drain ports 725 can be flexibly set according to the amount of condensed water, which is not specifically limited in the embodiment of the present application.
  • the flow direction of the refrigerant flow in the heat exchange main body 61 can be arranged in the horizontal direction, that is, the extension direction of the heat exchange main body 61 can be arranged in the horizontal direction, on the one hand, the flow of the condensed water on the heat exchange main body 61 can be shortened.
  • the height of the baffle plate 77 in the vertical direction is gradually decreased, so that the droplets fall on the baffle plate 77 .
  • the condensed water on 77 flows to both ends of the baffle plate 77 . That is, the deflector 77 is arranged in an inverted V shape. In this way, the overall height of the deflector 77 in the vertical direction can be reduced, the interference between the deflector 77 and other components in the electric control box 7 can be avoided, and the The condensed water dripped on the deflector 77 of the radiator 6 is discharged.
  • the box body 72 is provided with a first drain port 771 and a second drain port 772 respectively corresponding to the two ends of the baffle plate 77 to discharge the condensed water flowing to the two ends of the baffle plate 77 .
  • the condensed water dripping on the deflector 77 flows to both ends of the deflector 77 and is discharged from the box body 72 through the first drain port 771 and the second drain port 772 .
  • the height of the baffle plate 77 in the vertical direction is gradually increased, so that the droplets fall on the baffle plate 77 .
  • the condensed water on 77 flows to the central region of the baffle plate 77 . That is, the baffles 77 can be arranged in a V-shape, in this way, the condensed water can be collected to the middle area of the baffles through the baffles 77 and discharged from the middle area.
  • the box body 72 is provided with a drain port 725 corresponding to the position of the middle region of the baffle plate 77 to discharge the condensed water flowing to the middle region of the baffle plate 77 . This way is conducive to condensation Collection and discharge of water.
  • the number and size of the above-mentioned drain port 725 , the first drain port 771 and the second drain port 772 can be flexibly set according to the amount of condensed water, which is not specifically limited in the embodiment of the present application.
  • the above-mentioned deflector 77 can be disposed below the radiator 6 which is installed in the electric control box 7 in other installation manners and is used to dissipate heat for the electronic components 71 in the electric control box 7 , and is not limited to embodiments described above.
  • the box body 72 is provided with an installation cavity 721, and at least part of the heat exchange main body 61 is disposed in the installation cavity 721; the electronic components 71 are thermally connected to the heat exchange main body 61 at the first position, and the heat dissipation fins 65 are located at the first position.
  • the second position is thermally connected to the heat exchange main body 61 , wherein the first position and the second position are spaced apart from each other along the flow direction of the refrigerant flow of the heat exchange main body 61 .
  • the refrigerant flow mentioned here can be the main refrigerant flow in the air conditioning system shown in Figs. 1-4, or the auxiliary refrigerant flow.
  • the space on the heat exchange main body 61 can be fully utilized, and not only the heat exchange main body 61 can be used for the electronic components 71 .
  • the heat dissipation fins 65 can also be used to reduce the temperature in the installation cavity 721 of the electric control box 7 , thereby protecting the electronic components 71 disposed in the installation cavity 721 .
  • the heat exchange body 61 includes a first end 61a and a second end 61b spaced apart from each other along the flow direction of the refrigerant flow, wherein the temperature of the heat exchange body 61 gradually decreases in the direction from the first end 61a to the second end 61b , that is, the temperature of the first end 61a is greater than the temperature of the second end 61b.
  • the first position is disposed closer to the first end 61a than the second position.
  • the surface temperature of the heat exchange body 61 will change with the flow direction of the refrigerant flow, thereby forming a first end 61a with a higher temperature and a second end with a lower temperature 61b, since the temperature difference between the higher temperature first end 61a and the hot air in the installation cavity 721 is small, it is not easy to generate condensed water, so the electronic component 71 can be arranged close to the first end 61a, that is, the first A position is provided near the first end 61a.
  • the heat dissipation fins 65 can be arranged close to the second end 61b, on the one hand, the lower temperature
  • the heat dissipation fins 65 can ensure that the heat dissipation fins 65 and the hot air have a large enough temperature difference, which is convenient for the heat dissipation of the electric control box 7.
  • the condensed water formed by condensation on the heat dissipation fins 65 will also evaporate under the action of the hot air. , the condensed water evaporates and absorbs heat, so as to further reduce the temperature of the refrigerant flow and improve the heat exchange effect of the radiator 6 .
  • a cooling fan 78 can also be arranged in the electric control box 7, and the cooling fan 78 is used to form a cooling airflow acting on the cooling fins 65 in the electric control box 7, so that the heat dissipation can be accelerated. The flow speed of the air flow, thereby improving the heat exchange effect.
  • the cooling fan 78 may be disposed close to the cooling fins 65 to directly act on the cooling fins 65 .
  • a mounting plate 76 may also be provided in the electrical control box 7 , and the mounting plate 76 is provided in the mounting cavity 721 , so that the mounting cavity 721 forms the first cavity 7212 and In the second chamber 7214, a first vent 764 and a second vent 766 are spaced apart on the mounting plate 76, so that the gas in the first chamber 7212 flows into the second chamber 7214 through the first vent 764, and the second The gas in the chamber 7214 flows into the first chamber 7212 through the second vent 766 , at least part of the heat exchange body 61 is located in the first chamber 7212 , and the electronic components 71 and the cooling fan 78 are arranged in the second chamber 7214 .
  • a circulating airflow can be formed in the first chamber 7212 and the second chamber 7214 to increase the The air volume in contact with the heat dissipation fins 65 disposed in the first chamber 7212 is large, and the air flow after cooling can facilitate the heat dissipation of the electronic components 71 disposed in the second chamber 7214, so as to avoid gas mixing, so as to improve the heat dissipation fins 65 heat dissipation efficiency.
  • the cooling fan 78 disposed in the second chamber 7214 is used to accelerate the flow speed of the air in the second chamber 7214, thereby accelerating the circulation speed of the air between the first chamber 7212 and the second chamber 7214, The heat dissipation efficiency of the electric control box 7 is improved.
  • the flow direction of the heat dissipation air flowing through the heat dissipation fins 65 can be set to be perpendicular to the flow direction of the refrigerant flow.
  • the cooling airflow can be set to flow in a vertical direction to prevent the cooling airflow from flowing to the position of the electronic components 71 .
  • first ventilation openings 764 and the second ventilation openings 766 may be arranged on opposite sides of the heat dissipation fins 65 at intervals along the vertical direction.
  • the number and arrangement density of the first ventilation openings 764 and the second ventilation openings 766 can be set as required.
  • the cooling airflow may be arranged to flow in a horizontal direction to prevent the cooling airflow from flowing to the position of the electronic components 71 .
  • the flow direction of the cooling air flow and the flow direction of the refrigerant flow may also be set to be along other two mutually perpendicular directions, which are not specifically limited in the embodiment of the present application.
  • the first ventilation port 764 and the second ventilation port 766 arranged in the vertical direction are adopted, the first ventilation port 764 can be arranged on the upper part of the second ventilation port 766, so that the first ventilation port 764 can enter the first ventilation port 766 through the second ventilation port 766.
  • the hot air in a chamber 7212 automatically rises to the position of the heat exchange body 61 and exchanges heat with the heat exchange body 61 .
  • the cooling fan 78 can be positioned close to the first vent 764 so that the cool air at the top of the first chamber 7212 can enter the second chamber 7214 in time, and the cooling fan 78 can accelerate the cooling air , so as to improve the heat dissipation efficiency of the electronic components 71 .
  • a heat dissipation hole that communicates with the installation cavity 721 is usually opened on the box body 72 of the electric control box 7, so as to exchange heat with the natural convection of the outside air through the heat dissipation hole, and then to the electric control box 7.
  • the control box 7 is cooled down.
  • the method of opening heat dissipation holes on the box body 72 will reduce the sealing performance of the electric control box 7, and impurities such as moisture and dust from the outside will enter the installation cavity 721 through the heat dissipation holes, thereby damaging the components disposed in the installation cavity 721.
  • Electronic component
  • the box body 72 of the electric control box 7 can be set to a sealed structure.
  • the electric control box 7 includes a box body 72 , a mounting plate 76 , a heat sink 6 , an electronic component 71 and a cooling fan 78 .
  • the box body 72 is provided with an installation cavity 721 , and the installation plate 76 is disposed in the installation cavity 721 , so that the installation cavity 721 forms a first cavity 7212 and a second cavity 7214 on both sides of the installation plate 76 .
  • a spaced first vent 764 and a second vent 766 are provided, and the first vent 764 and the second vent 766 communicate with the first chamber 7212 and the second chamber 7214; the radiator 6 is at least partially provided in the first chamber
  • the electronic component 71 is arranged in the second chamber 7214 and is thermally connected to the radiator 6; the cooling fan 78 is used for air supply, so that the gas in the first chamber 7212 flows into the first chamber 7212 through the first vent 764.
  • Two chambers 7214 Two chambers 7214.
  • the heat sink 6 is arranged in the first cavity 7212
  • the electronic components 71 and the cooling fan 78 are arranged in the second cavity 7214
  • the first cavity is connected to the mounting plate 76 at intervals.
  • the first vent 764 and the second vent 766 of the chamber 7212 and the second chamber 7214 in this way, the electronic components 71 generate heat, so that the temperature of the air in the second chamber 7214 is higher, and the heat dissipation fan 78 sends the hot air into the second chamber 7214.
  • the second ventilation port 766 due to the low density of the hot air, the hot air naturally rises to contact the radiator 6 provided in the first chamber 7212, the radiator 6 is used for cooling the hot air to form cold air, and the cold air is
  • the first ventilation port 764 flows into the second chamber 7214 , and the cooling fan 78 is used to accelerate the cold air, so as to use the cold air to cool down the electronic components 71 disposed in the second chamber 7214 , after heat exchange with the electronic components 71 .
  • the temperature of the cold air rises, and the cold air after the temperature rise continues to enter the second vent 766 under the action of the cooling fan 78, and circulates through this, and then through the internal circulation method for the electric control box 7.
  • the electronic components 71 are cooled.
  • the electric control box 7 in the present application is a fully enclosed electric control box 7, which can effectively solve the problems of waterproof, insect-proof, dust-proof, etc. Moisture-proof and other problems, thereby improving the electrical control reliability of the electrical control box 7 .
  • the plane where the cooling fan 78 is located is perpendicular to the plane where the mounting plate 76 is located, and the leeward side of the cooling fan 78 is disposed toward the first vent 764 .
  • the cooling fan 78 can be disposed on the side of the mounting plate 76 facing the second chamber 7214 , the direction of the rotation axis of the cooling fan 78 is parallel to the plane where the mounting plate 76 is located, and the leeward side of the cooling fan 78 refers to the cooling fan 78 the air inlet side.
  • the cooling fan 78 can be arranged between the first vent 764 and the electronic component 71 , and the cool air entering the second chamber 7214 through the first vent 764 is accelerated by the cooling fan 78 and then flows out to prevent The flow speed of the cold air is increased, and the heat dissipation efficiency of the electric control box 7 is improved.
  • the cooling fan 78 can also be configured as a centrifugal fan.
  • the centrifugal fan is a machine that relies on the input mechanical energy to increase the gas pressure and discharge the gas.
  • the working principle of a centrifugal fan is to use a high-speed rotating impeller to accelerate the gas. Therefore, in this embodiment, by setting the cooling fan 78 as a centrifugal fan, on the one hand, high-speed cold air can be obtained to improve the heat dissipation efficiency of the electronic components 71, and on the other hand, the centrifugal fan can also simplify the structure of the cooling fan 78. And improve installation efficiency.
  • Air guide plates may also be arranged on the mounting plate 76 at intervals, and air guide channels are formed between the air guide plates for guiding the air blown out by the cooling fan 78 .
  • two parallel and spaced air guide plates can be arranged between the electronic components 71 that are dispersedly arranged, and the extension direction of the air guide plates is along the spacing direction of the electronic components 71, so as to define a space along the electronic components between the two air guide plates.
  • 71 air guide runners in the spacing direction.
  • the cold air blown by the cooling fan 78 first flows to the position of some electronic components 71 to dissipate heat from the electronic components 71 , and the air after passing through some electronic components 71 further flows to the position of another part of the electronic components 71 through the air guide channel, It is used to dissipate heat to another part of the electronic components 71 .
  • the heat dissipation of the electronic components 71 can be more evenly dissipated, and the temperature of the local electronic components 71 can be prevented from being too high and damaged.
  • the radiator 6 can be arranged inside the electric control box 7 , that is, the heat exchange main body 61 can be arranged in the first chamber 7212 for cooling the air in the first chamber 7212 .
  • the radiator 6 can also be disposed outside the electric control box 7 , and at least a part of the radiator 6 can be extended in the first chamber 7212 .
  • the radiator 6 includes the heat exchange body 61 , the integrated piping assembly 62 and the heat dissipation fins 65 , an assembly port (not shown) that communicates with the first chamber 7212 may be opened on the box body 72 .
  • the heat exchange body 61 is connected to the outer side wall of the box body 72
  • the heat dissipation fins 65 are connected to the heat exchange body 61 and inserted into the first chamber 7212 through the assembly port.
  • the matching manner of the radiator 6 and the electric control box 7 in this embodiment is the same as that in the above-mentioned embodiment, please refer to the description in the above-mentioned embodiment, which will not be repeated here.
  • the electronic components 71 can be arranged within the air supply range of the cooling fan 78 , so that the cooling fan 78 can directly act on the electronic components 71 to cool down.
  • the electronic element 71 may include, for example, a common mode inductor 711 , a reactance 712 , a capacitor 713 , and other primary heating elements that generate relatively large amounts of heat, and a secondary heating element such as the fan module 714 that generates relatively small amounts of heat.
  • the distance between the main heating element and the first ventilation port 764 can be set to be smaller than the distance between the secondary heating element and the first ventilation port 764, that is, the main heating element with larger calorific value can be Set at a position close to the first ventilation port 764, and set the secondary heating element with a smaller calorific value at a position away from the first ventilation port 764, so that the air with a lower temperature entering through the first ventilation port 764 acts first It is used for the main heating element with a large amount of heat, so as to improve the heat dissipation efficiency of the main heating element with a large amount of heat.
  • the second vent 766 can be opened at the end of the cooling fan 78 for air supply, and is opened at a position close to the electronic component 71 that generates a larger amount of heat, on the one hand, the radiation range of the cooling fan 78 can be expanded, and the first The circulation efficiency of the air in the second chamber 7214 can also make the hot air after heat exchange with the electronic component 71 with a large calorific value to be discharged out of the second chamber 7214 in time to avoid raising the temperature of the entire second chamber 7214 .
  • the second ventilation port 766 can be arranged at a position close to the first ventilation port 764, so as to shorten the circulation path of the air in the second chamber 7214, reduce the air flow resistance, improve the circulation efficiency of the air, and further improve the electric power.
  • the sizes of the first vent 764 and the second vent 766 may also be set according to the arrangement of the electronic components 71 .
  • the number of the second ventilation openings 766 may be multiple, and the multiple second ventilation openings 766 are respectively provided at different positions of the mounting plate 76 .
  • the size of the second vent 766 located at the position of the electronic component 71 with a large heat generation can be set relatively large, the number of the second vent 766 can also be set relatively large, and a plurality of the second vent 766
  • the distribution density of can be set relatively large.
  • the size of the second vent 766 located at the position of the electronic component 71 with less heat generation can be set relatively small, the number of the second vent 766 can also be set relatively small, and a plurality of the second vent 766 The distribution density of can be set relatively small.
  • the size of the first vent 764 may be set larger than the size of the second vent 766 to increase the return air volume and improve the efficiency of the cooling fan 78 .
  • the electrical control box 7 includes a box body 72 , a mounting plate 76 , a heat sink 6 and a main heating element 715 .
  • the box body 72 is provided with an installation cavity 721 , and the installation plate 76 is disposed in the installation cavity 721 , so that the installation cavity 721 forms a first cavity 7212 and a second cavity 7214 on both sides of the installation plate 76 .
  • a first ventilation port 764 and a second ventilation port 766 spaced in the vertical direction are provided; the radiator 6 is at least partially provided in the first chamber 7212; the main heating element 715 is provided in the second chamber 7214; the first ventilation The port 764 and the second ventilation port 766 communicate with the first chamber 7212 and the second chamber 7214 to form a circulating flow between the first chamber 7212 and the second chamber 7214 by utilizing the temperature difference between the main heating element 715 and the radiator 6 cooling airflow.
  • the main heating element 715 is arranged in the second chamber 7214, and the heat generated by the operation of the main heating element 715 causes the temperature in the second chamber 7214 to rise. Due to the low density of the hot air, the hot air naturally rises and increases. After entering the first chamber 7212 through the first vent 764 at the top of the second chamber 7214, the hot air contacts the radiator 6 and exchanges heat with the radiator 6, the temperature of the hot air decreases, and the density increases.
  • a first vent 764 and a second vent 766 are formed on the mounting plate 76 to communicate with the first chamber 7212 and the second chamber 7214, and the first vent 764 and the second vent 766 are vertically arranged.
  • the air can circulate between the first chamber 7212 and the second chamber 7214 by its own gravity, so as to cool down the electronic components 71 arranged in the second chamber 7214, and can reduce the electrical control
  • the overall temperature of the box 7, compared with the solution of using the cooling fan 78 for air supply, the structure of the electric control box 7 in this embodiment is more concise, which can improve the assembly efficiency of the electric control box 7 and reduce the temperature of the electric control box 7. Cost of production.
  • the radiator 6 can be arranged on the upper side of the main heating element 715 in the direction of gravity, that is, the radiator 6 can be arranged at a position close to the top of the first chamber 7212, and the main heating element 715 can be arranged close to the second chamber. 7214 at the bottom of the location.
  • the distance between the radiator 6 and the first vent 764 can be reduced, so that the hot air entering the first chamber 7212 through the first vent 764 quickly contacts the radiator 6 to cool down, and is cooled by gravity. Under the action of natural subsidence.
  • the hot air entering the second chamber 7214 through the second vent 766 quickly contacts the main heating element 715 to heat up, and naturally under the action of buoyancy In this way, the circulation speed of the air flow in the electric control box 7 can be increased, and the heat dissipation efficiency can be improved.
  • a secondary heating element 716 can also be arranged in the electric control box 7 , and the secondary heating element 716 is arranged in the second chamber 7214 and is thermally connected with the heat exchange main body 61 , wherein the secondary heating element 716
  • the calorific value of 716 is smaller than the calorific value of the main heating element 715 .
  • the main heating element 715 with a larger calorific value can be arranged at a position close to the second vent 766, on the one hand, the cold air entering through the first chamber 7212 can be first mixed with the generator. Contacting the electronic components 71 with a large amount of heat can improve the heat dissipation efficiency of the electronic components 71. On the other hand, it can also make a large temperature difference between the cold air and the electronic components 71 with a large amount of heat, so that the cold air can be heated up quickly, and then It rises rapidly under the action of buoyancy.
  • the secondary heating element 716 with smaller calorific value is disposed on the heat exchange main body 61 and in contact with the heat exchange main body 61 , and the heat exchange main body 61 can be used to directly cool down the electronic element 71 with smaller calorific value.
  • the main heating element 715 with a larger calorific value and the secondary heating element 716 with a smaller calorific value in different regions, the distribution of the electronic elements 71 can be made reasonable, and the internal space of the electric control box 7 can be fully utilized.
  • the secondary heating element 716 is connected to the heat exchange main body 61 through the heat dissipation fixing plate 74 to improve the assembly efficiency of the secondary heating element 716 .
  • connection manner between the secondary heating element 716 and the heat exchange main body 61 may be the same as that in the above-mentioned embodiment, and the specific reference is made to the description in the above-mentioned embodiment, which will not be repeated here.
  • the radiator 6 can also be disposed outside the electric control box 7 , and at least a part of the radiator 6 can be extended in the first chamber 7212 .
  • the matching manner of the radiator 6 and the electric control box 7 is the same as that in the above-mentioned embodiment, please refer to the description in the above-mentioned embodiment.
  • the air conditioning system 1 of this embodiment includes a radiator 6 , a pipeline 710 and a drainage sleeve 79 .
  • the pipeline 710 is used to connect the radiator 6 to provide the refrigerant flow to the radiator 6 or collect the refrigerant flow flowing out of the radiator 6 .
  • the line 710 connects the header assembly of the radiator 6 .
  • the pipeline 710 may include an input pipeline and an output pipeline, the input pipeline is used to provide the refrigerant flow to the radiator 6 , and the output pipeline is used to collect the refrigerant flow in the radiator 6 .
  • the drainage sleeve 79 is sleeved on the pipeline 710 for draining the condensed water formed on the pipeline 710 or the condensed water flowing through the pipeline.
  • the drainage sleeve 79 can guide the condensed water on the pipeline 710 , and has the function of protecting the pipeline 710 , thereby improving the reliability of the air conditioning system 1 .
  • the drainage sleeve 79 includes a sleeve body 791 and a flange 792 .
  • the sleeve body 791 is provided with an insertion hole 793 and a drainage groove 708 , and the insertion hole 793 is used for accommodating the pipeline 710 .
  • the number and size of the insertion holes 793 can be set according to the distribution and size of the pipelines 710 .
  • the number of insertion holes 793 may be two, and in other embodiments, the number of insertion holes 793 may be one or three.
  • the sleeve body 791 can be made of a flexible material, such as thermoplastic polyurethane elastomer rubber, to protect the pipeline 710 and prevent the pipeline 710 from contacting and wearing the sheet metal of the electric control box when it vibrates.
  • the flange 792 is arranged on the end face of the sleeve body 791 and is located at the periphery of the insertion hole 793, and then cooperates with the sleeve body 791 to form a water collecting groove 794.
  • the water collecting groove 794 is used to collect the condensed water on the pipeline 710.
  • the drainage groove 708 and the water collecting groove 794 is connected to drain the condensed water in the sump 794.
  • the condensed water flows along the pipeline 710 into the water collecting tank 794 of the drainage sleeve 79 , and is then discharged through the drainage groove 708 on the sleeve body 791 .
  • the outer side wall of the flange 793 is flush with the outer side wall of the sleeve body 791 , so as to increase the volume of the water collecting tank 794 , which is more conducive to the collection of condensed water.
  • the pipeline 710 can be arranged along the direction of gravity.
  • the sleeve body 791 includes an upper end surface and a lower end surface arranged opposite to each other.
  • the flange 792 and the water collecting groove 794 are arranged on the upper end surface of the sleeve body 791.
  • the drainage groove 708 communicates with the upper end surface of the sleeve body 791 and lower end face.
  • the condensed water on the pipeline 710 can flow into the water collecting tank 794 under the action of gravity, and then the condensed water is discharged through the drainage groove 708 communicating with the water collecting tank 794 . In this way, the condensed water on the pipeline 710 can be automatically discharged.
  • the pipeline 710 can also be inclined to suit different application scenarios.
  • the drainage groove 708 is formed on the side wall of the sleeve body 791 and further communicates with the insertion hole 793 and the outer side of the sleeve body 791 to allow the pipeline 710 to be inserted into the insertion hole 793 through the drainage groove 708 .
  • the drainage sleeve 79 can be sleeved on the pipeline 710 through the drainage groove 708 to facilitate the assembly of the drainage sleeve 79 and the pipeline 710, and on the other hand, the drainage sleeve 708 can be drained into the water collecting tank 794.
  • the size of the drainage groove 708 can be selected and set according to the amount of condensed water, which is not specifically limited herein.
  • the flange 792 has an opening on the side where the drainage groove 708 is located, so as to allow the pipeline 710 to enter the sump 794 through the opening, which facilitates the assembly of the drainage sleeve 79 .
  • the air conditioning system 1 further includes an electric control box 7 , the electric control box 7 includes a box body 72 , and the radiator 6 is disposed in the box body 72 .
  • a drain port 725 is provided on the box body 72 , and the drainage sleeve 79 is embedded in the drain port 725 .
  • the condensed water in the electric control box 7 can be collected into the water collecting groove 794 of the drainage sleeve 79 and discharged through the drainage groove 708 . In this way, not only the discharge of condensed water can be facilitated, but also the electric control box 7 can be sealed by the drainage sleeve 79 to improve the reliability of the electric control box 7 .
  • the sleeve body 791 and the flange 792 are in contact with the box body 72, and the openings on the drainage groove 708 and the flange 792 are located on the side where the sleeve body 791 and the flange 792 abut the box body 72, so that the box body 72 is removed from the drainage sleeve 79.
  • the lateral blocking drain groove 708 and opening In this way, the sealing performance of the electric control box 7 can be improved, and the area communicating with the electric control box 7 and the outside world can be reduced.
  • a plurality of protruding ribs 796 may be provided inside the insertion hole 793 , and the plurality of protruding ribs 796 surround The pipelines 710 are arranged at intervals and abut against the pipelines 710 to further form drainage grooves 709 between the protruding ribs 796 .
  • the water collecting groove 794 communicates with the drainage groove 709 , and the condensed water collected in the water collecting groove 794 can also be drained through the drainage groove 709 .
  • the drainage sleeve 79 is provided with a drainage groove 708 and a drainage groove 709 at the same time.
  • the condensed water in the water collecting groove 794 can be discharged more easily and the condensed water in the water collecting groove 794 can be prevented from overflowing.
  • the protruding ribs 796 can connect the upper end surface and the lower end surface of the sleeve body 791, the number of the protruding ribs 796 can be 2, 3, 4 or 5, etc., and the extending direction of the protruding ribs 796 is the same as the extending direction of the pipeline 710. The same, in order to facilitate the discharge of condensed water.
  • the protruding ribs 796 can be integrally formed with the sleeve body 791 to facilitate processing and make the structure of the drainage sleeve 79 more reliable.
  • the protruding ribs 796 can also be bonded to the inner surface of the insertion hole 793 , and the number of the protruding ribs 796 can be selected and set according to the actual quantity of condensed water discharged, which is not specifically limited in this application.
  • the drainage sleeve 79 may only be provided with the drainage groove 709 without the drainage groove 708 . In this way, the condensed water in the water collecting tank 794 can also be discharged, and the structure of the drainage sleeve 79 is made simpler.
  • the sleeve body 791 may also be provided with a fixing groove 797 , and the fixing groove 797 is used for engaging with the box body 72 to fix the drainage sleeve 79 .
  • the fixing groove 797 may be disposed on the side of the sleeve body 791 where the drainage groove 708 is disposed, so as to facilitate the installation of the drainage sleeve 79 .
  • the drainage sleeve 79 can be fixed by the fixing grooves 797 to prevent the drainage sleeve 79 from sliding on the pipeline 710.
  • the drainage sleeve 79 can fix the pipeline 710 to prevent the pipeline 710 from tilting under the action of external force, improving the performance of the pipeline 710. Reliability of Air Conditioning System 1.
  • a drainage sleeve 79 is set on the pipeline 710 of the air-conditioning system 1, which can drain the condensed water on the pipeline 710, protect the pipeline 710, and seal the electric control box 7 to improve the performance of the pipeline. Reliability of Air Conditioning System 1.

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Abstract

一种换热器(6)、电控盒(7)及空调系统(1)；换热器（6）包括：换热主体（61）、集流管组件（62）、散热翅片（65）和固定板（66）；其中，集流管组件（62）用于向换热主体（61）提供冷媒流，换热主体（61）包括并列且间隔设置的至少两个板体组件（603）；散热翅片（65）设置于至少两个板体组件（603）上，散热翅片（65）与换热主体（61）导热连接；固定板（66）同时覆盖于至少两个板体组件（603）上的散热翅片（65）背离板体组件（603）的一侧，以形成散热风道。该换热器（6）结构简单，方便生产，且具有较高的换热效率。

Description

换热器、电控盒及空调系统
本申请要求于2021年02月08日提交的申请号202110170451.X，发明名称为“换热器、电控盒及空调系统”的中国专利申请的优先权，其通过引用方式全部并入本申请。
【技术领域】
本申请涉及空调技术领域，特别是涉及一种换热器、电控盒及空调系统。
【背景技术】
在空调室外机内一般都设置有电控盒，电控盒设置有电子元件，以检测和/或控制空调室外机的各部件的运行状态。一般来说，电子元件在运行过程中都会产生大量的热量，因此需要设置散热器来对电子元件进行散热，然而现有的散热器存在结构复杂，散热效率低的缺点。
【发明内容】
本申请提供了一种换热器、电控盒及空调系统，能够简化换热器的结构，提高换热器的换热效率。
本申请第一方面提供了一种换热器，该换热器包括：换热主体及集流管组件，集流管组件用于向换热主体提供冷媒流，换热主体包括并列且间隔设置的至少两个板体组件；散热翅片，设置于至少两个板体组件上，散热翅片与换热主体导热连接；固定板，同时覆盖于至少两个板体组件上的散热翅片背离板体组件的一侧，以形成散热风道。
其中，固定板包括顶面板和至少一侧面板，顶面板同时覆盖于至少两个板体组件上的散热翅片背离板体组件的一侧，侧面板与顶面板弯折连接，且向板体组件延伸。
其中，侧面板的数量为两个，两个侧面板沿至少两个板体组件的间隔方向的垂直方向间隔设置，顶面板分别连接两个侧面板，以形成容置空间，散热翅片位于容置空间内。
其中，散热翅片的数量为至少两个，每个散热翅片设置于对应的板体组件上，至少两个散热翅片沿至少两个板体组件的间隔方向彼此间隔分布。
其中，散热翅片为一体式设置，并设置于至少两个板体组件上。
其中，固定板的沿至少两个板体组件的间隔方向的两端开放，以使得散热风道内的气流沿至少两个板体组件的间隔方向流动。
其中，冷媒流的流动方向垂直于至少两个板体组件的间隔方向。
其中，每个板体组件包括层叠设置的第一板体和第二板体，第一板体上设置供第一冷媒流流动的多个第一微通道，第二板体上设置有供第二冷媒流流动的多个第二微通道，第二冷媒流从第一冷媒流吸热，以使得第一冷媒流过冷，或者第一冷媒流从第二冷媒流吸热，以使得第二冷媒流过冷。
本申请第二方面提供了一种电控盒，该电控盒包括盒体和上述任一实施例的换热器，换热器与电控盒相连，换热器用于为电控盒进行散热。
本申请第三方面提供了一种空调系统，该空调系统包括压缩机、室外换热器、室内换热器和上述任一实施例的换热器，压缩机通过连接管路在室外换热器和室内换热器之间提供循环流动的冷媒流，换热器设置在室外换热器和室内换热器之间，并与连接管路相连通。
本申请的有益效果是：区别于现有技术的情况，本申请在换热器的换热主体上设置散热翅片，以利用散热翅片增大换热主体与空气的接触面积，便于与空气进行换热，提高换热器的换热效率。散热翅片上设置有固定板，固定板同时覆盖于至少两个板体组件上的散热翅片背离板体组件的一侧，以形成散热风道，本申请的散热翅片的密封采用整体固定板结构，零部件少，使换热器的生产简单可靠，同时散热效率高。
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，而非限制本申请。
【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，这些附图示出了符合本申请的实施例，并与说明书一起用于说明本申请的技术方案。
图1是本申请的空调系统一实施例的示意框图；
图2是本申请的空调系统另一实施例中的示意框图；
图3是本申请的空调系统另一实施例中的示意框图；
图4是本申请的空调系统另一实施例中的示意框图；
图5是本申请的换热器的换热主体的一实施例的结构示意图；
图6是本申请的换热器的换热主体的另一实施例的结构示意图；
图7是本申请的换热器的换热主体的又一实施例的结构示意图；
图8是本申请的换热器的换热主体和集流管组件的一实施例的结构示意图；
图9是本申请的换热器的换热器主体和集流管组件的另一实施例的结构示意图；
图10是本申请的换热器的换热主体和集流管组件的另一实施例的结构示意图；
图11是本申请的换热器的换热主体和集流管组件的另一实施例的结构示意图；
图12是本申请的换热器的换热主体的另一实施例的结构示意图；
图13是本申请的换热器的换热主体和集流管组件的另一实施例的结构示意图；
图14是本申请的换热器的换热主体和集流管组件的另一实施例的结构示意图；
图15是本申请的换热器的换热主体的另一实施例的结构示意图；
图16是图15中第一管体设置平面的立体结构示意图；
图17是本申请的换热器的换热主体的另一实施例的结构示意图；
图18是本申请的换热器的换热主体和集流管组件的另一实施例的结构示意图；
图19是本申请换热器的换热主体的另一实施例的结构示意图；
图20是图19中换热器的制造方法的一实施例的流程示意图；
图21是本申请的换热器的换热主体和集流管组件的另一实施例的结构示意图；
图22是图21中的集流管一实施例的结构示意图；
图23是本申请的换热器的另一实施例的结构示意图；
图24是图23中的圈B处的截面放大示意图；
图25是图23中的散热翅片一实施例的结构示意图；
图26是图23中的散热翅片另一实施例的结构示意图；
图27是本申请的电控盒的一实施例隐去部分元件后的立体结构示意图；
图28是图27中的散热器的一实施例的立体结构示意图；
图29是图27中的散热器的另一实施例的立体结构示意图；
图30是本申请的散热固定板与散热器一实施例的立体结构示意图；
图31是图30中的散热固定板一实施例的平面结构示意图；
图32是本申请的散热器与电控盒的另一实施例的剖视结构示意图；
图33是本申请的散热器与电控盒的另一实施例的剖视结构示意图；
图34是本申请另一实施例中的散热器与电控盒配合的平面结构示意图；
图35是本申请的散热器与电控盒配合的另一实施例的剖视结构示意图；
图36是图35中的导流板的一实施例的结构示意图；
图37是图35中的导流板的另一实施例的结构示意图；
图38是图35中的导流板的另一实施例的结构示意图；
图39是本申请又一实施例中的散热器与电控盒配合的平面结构示意图；
图40是图39中的散热器与电控盒配合的剖视结构示意图；
图41是本申请又一实施例中的散热器与电控盒配合的剖视结构示意图；
图42是本申请又一实施例中的电控盒隐去部分元件后的立体结构示意图；
图43是本申请又一实施例中的电控盒隐去部分元件后的立体结构示意图；
图44是本申请又一实施例中的电控盒隐去部分元件后的平面结构示意图；
图45是图44中的电控盒的剖视结构示意图
图46是本申请的空调系统的另一实施例的结构示意图；
图47是图46中的空调系统去掉盒体后的内部结构示意图；
图48是图46中的引流套一实施例的结构示意图；
图49是图46中的引流套另一实施例的结构示意图；
图50是图46中的空调系统沿A-A方向的剖视结构示意图。
【具体实施方式】
下面将结合本申请实施例中的附图，对本申请实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅是本申请的一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
在本文中提及“实施例”意味着，结合实施例描述的特定特征、结构或特性可以包含在本申请的至少一个实施例中。在说明书中的各个位置出现该短语并不一定均是指相同的实施例，也不是与其他实施例互斥的独立的或备选的实施例。本领域技术人员显式地和隐式地理解的是，本文所描述的实施例可以与其他实施例相结合。
请参阅图1，图1是本申请一实施例中的空调系统的示意框图。如图1所示，空调系统1主要包括 压缩机2、四通阀3、室外换热器4、室内换热器5、换热器6、膨胀阀12以及膨胀阀13。膨胀阀13和换热器6设置在室外换热器4和室内换热器5之间，压缩机2通过四通阀3在室外换热器4和室内换热器5之间提供循环流动的冷媒流。
换热器6包括第一换热通道610和第二换热通道611，第一换热通道610的第一端经膨胀阀13与室外换热器4连接，第一换热通道610的第二端与室内换热器5连接，第二换热通道611的第一端经膨胀阀12与第一换热通道610的第二端连接，第二换热通道611的第二端与压缩机2的吸气口22连接。
当空调系统1处于制冷模式时，冷媒流的路径为：
压缩机2的排气口21-四通阀3的连接口31-四通阀3的连接口32-室外换热器4-换热器6-室内换热器5-四通阀3的连接口33-四通阀3的连接口34-压缩机2的吸气口22。
第一换热通道610的冷媒流的路径(主路)为：第一换热通道610的第一端-第一换热通道610的第二端-室内换热器5。第二换热通道611的冷媒流的路径(辅路)为：第一换热通道610的第二端-膨胀阀12-第二换热通道611的第一端-第二换热通道611的第二端-压缩机2的吸气口22。
例如，此时空调系统的工作原理为：室外换热器4作为冷凝器，其经膨胀阀13输出中压中温的冷媒流(温度可以为40°，液相冷媒流)，第一换热通道610的冷媒流为中压中温的冷媒流，膨胀阀12将中压中温的冷媒流转换为低压低温的冷媒流(温度可以为10°，气液两相冷媒流)，第二换热通道611的冷媒流为低压低温的冷媒流。第二换热通道611的低压低温的冷媒流从第一换热通道610的中压中温的冷媒流吸热，进而第二换热通道611的冷媒流实现气化，以使第一换热通道610的冷媒流实现进一步过冷。气化后的第二换热通道611的冷媒流对压缩机2进行喷气增焓，提高空调系统1的制冷能力。
其中，膨胀阀12作为第二换热通道611的节流部件，调节第二换热通道611的冷媒流的流量。第一换热通道610的冷媒流和第二换热通道611的冷媒流进行热交换，以对第一换热通道610的冷媒流实现过冷。因此，换热器6可以作为空调系统1的经济器，提升过冷度，进而提升空调系统1的换热效率。
进一步，如本领域技术人员所理解的，在制热模式下，四通阀3的连接口31与连接口33连接，四通阀3的连接口32与连接口34连接。压缩机2经排气口21输出的冷媒流从室内换热器5流向室外换热器4，并以室内换热器5作为冷凝器。此时，室内换热器5输出的冷媒流分为两路，一路流入第一换热通道610(主路)，另一路经膨胀阀12流入第二换热通道611(辅路)。第二换热通道611的冷媒流同样也可以对第一换热通道610的冷媒流实现过冷，提高空调的制热能力。
可以理解的是，在另一些实施例中，请参阅图2和图3所示，第二换热通道611的第一端可以不与第一换热通道610的第二端连接，第二换热通道611的第一端可以直接与膨胀阀13的第一端或者膨胀阀13的第二端连接，如此，也能使第二换热通道611的冷媒流对第一换热通道610的冷媒流进行过冷，提高空调系统1的制冷或者制热能力。
请参阅图4，图4是本申请另一实施例中的空调系统的示意框图。图4所示的空调系统1与图1所示的空调系统1的区别主要在于增加了气液分离器8。
与图1所示的实施例相同，换热器6包括供第一冷媒流流动的第一换热通道610以及供第二冷媒流流动的第二换热通道611。第二冷媒流在沿第二换热通道611的流动过程中从第一冷媒流吸热，以使得第一冷媒流过冷。在其他实施例中，也可以是第一冷媒流在沿第一换热通道610的流动过程中从第二冷媒流吸热，以使得第二冷媒流过冷。因此，换热器6可以作为空调系统1的经济器，提升过冷度，进而提升空调系统1的换热效率。
本实施例中，压缩机2的吸气口包括增焓进气口221和回气口222。进一步地，流经第二换热通道611的第二冷媒流进一步被输送至压缩机2的增焓进气口221或者气液分离器8的进口81，其中气液分离器8的出口82进一步连接压缩机2的回气口222，用于向压缩机2提供低压气态的冷媒流。
进一步地，空调系统1还包括四通阀3、膨胀阀12和膨胀阀13。膨胀阀13和换热器6设置在室外换热器4和室内换热器5之间，压缩机2通过四通阀3在室外换热器4和室内换热器5之间提供循环流动的冷媒流。
四通阀3包括连接口31、连接口32、连接口33和连接口34，四通阀3的连接口32连接室外换热器4；四通阀3的连接口34连接气液分离器8；四通阀3的连接口31连接压缩机2，具体是连接压缩机2的排气口21；四通阀3的连接口33连接室内换热器5。
上述实施例中，空调系统1中的四通阀31的作用是通过改变冷媒流在系统管路内的流向来实现制冷、制热之间的相互转换，以使空调系统1能够在制冷模式与制热模式之间切换，当空调系统1同时具备制冷和制热功能时，可使用上述四通阀31来进行换向。
可以理解的是，在另一个实施例中，空调系统1也可以不使用四通阀31。当空调系统1不包括四通阀31时，压缩机2可以直接通过连接管路与室外换热器4连接，具体地，压缩机2通过连接管路在室外换热器4和室内换热器5之间提供循环流动的冷媒流，换热器6设置在室外换热器4和室内换热器5之间，并与连接管路相连通。比如，空调系统1只具备制冷能力或者只具备制热能力时，空调系统1 可以不使用上述四通阀31。此种方式，能够简化空调系统1的结构，节约空调系统1的生产成本。此外，在换热器6不作为经济器使用时，换热器6还可以跟其他位置的连接管路相连通。
第一换热通道610的第一端经膨胀阀13与室外换热器4连接，第一换热通道610的第二端与室内换热器5连接，第二换热通道611的第一端经膨胀阀12与第一换热通道610的第二端连接，第二换热通道611的第二端与压缩机2的增焓进气口221连接或者与气液分离器8的进口81连接。
当第二换热通道611的第二端与压缩机2的增焓进气口221连接时，能够为压缩机2的喷气增焓提供中间压力的气态冷媒，提高空调系统1的制冷和/或制热能力。其中，喷气增焓的原理及作用属于本领域技术人员的理解范畴，在此就不再赘述。当第二换热通道611的第二端与气液分离器8的进口81连接时，对比中压位置，冷媒流的蒸发温度低，温差大，进一步提高空调系统1的换热效率。
空调系统1还可以包括切换组件，切换组件用于将第二换热通道611的第二端选择性地连接压缩机2的增焓进气口221和气液分离器8的进口81。即切换组件可以用于使流经第二换热通道611的第二冷媒流选择性地输送至压缩机2的增焓进气口221和气液分离器8的进口81。
在一个实施例中，切换组件可以包括电磁阀15。电磁阀15连接于压缩机2的增焓进气口221和第二换热通道611的第二端之间，以在压缩机2需要喷气增焓时开启电磁阀15，为压缩机2的喷气增焓提供中间压力的气态冷媒。
切换组件还可以包括电磁阀14。电磁阀14连接于第二换热通道611的第二端和气液分离器8的进口81之间，电磁阀14用于在压缩机2不需要喷气增焓或不适合喷气增焓时开启，以将第二换热通道611的第二端输出的第二冷媒流引导至气液分离器8中。
其中，电磁阀15与电磁阀14分别连接第二换热通道612的第二端。膨胀阀12作为第二换热通道611的节流部件，调节第二换热通道611的第二冷媒流的流量。
图4所示的空调系统1与图1所示的空调系统1的制冷和制热原理基本一致，在此不再赘述。
如图4所示，空调系统1还包括电控盒7，换热器6与电控盒7相连，且换热器6设置成对电控盒7内的电子元件进行散热，具体请见下文的描述。即，换热器6既作为空调系统1的经济器，提升过冷度，又作为散热器，为电控盒7进行散热，并具体为电控盒7内的电子元件进行散热。
本申请进一步在上文描述的空调系统1的整体结构的基础上进行以下几方面的优化：
1、微通道换热器
如图5、图6和图7所示，换热器6包括换热主体61，换热主体61设有多个微通道612，该多个微通道612包括第一微通道和第二微通道，并且在图1-4所示的空调系统中，第一微通道作为换热器6的第一换热通道610，第二微通道作为换热器6的第二换热通道611。因此，第一微通道610与第一换热通道610使用相同的标号，第二微通道611与第二换热通道611使用相同的标号。换热主体61可以包括单个或多个板体613。
每个微通道612垂直于其延伸方向的横截面形状可以为矩形，每个微通道612的边长为0.5mm-3mm。每个微通道612与板体613的表面之间以及微通道612之间的厚度为0.2mm-0.5mm，以使微通道612满足耐压和传热性能的要求。在其他实施例中，微通道612的横截面形状可以为其他形状，例如圆形、三角形、梯形、椭圆形或者不规则的形状。
多个微通道612可以设置为单层微通道或者多层微通道。在冷媒流的流速较低，且冷媒流的流态为层流的情况下，多个微通道612的截面积越大，多个微通道612的长度越短，能够减小冷媒流的流动阻力损失。
板体613的多个微通道612可以包括交替设置的第一微通道610和第二微通道611，第一微通道610的延伸方向D1与第二微通道611的延伸方向D2彼此平行。具体如图5所示，在多个微通道612中第一预设数量的微通道划分为第一微通道610，在多个微通道612中第二预设数量的微通道划分为第二微通道611，多组第一微通道610和多组第二微通道611依次交替设置，即在两组第一微通道610之间设置有第二微通道611，在两组第二微通道611之间设置有第一微通道610，以实现该至少两组第一微通道610和第二微通道611彼此间隔设置，形成第一微通道610和第二微通道611交替排布的换热器6。第一预设数量和第二预设数量可以相等或不相等。
进一步地，在图1-图4的使用场景下，第一微通道610和第二微通道611可以相互独立，以供不同的冷媒流流动，进而可以通过其中一个冷媒流为另一冷媒流过冷。在其他实施例中，第一微通道610和第二微通道611可以彼此连通，并作为一路微通道，以供同一冷媒流流动。此外，在第一微通道610和/或第二微通道611呈两层或多层设置时，可以通过反向集流管使该两层或多层的第一微通道610和/或第二微通道611彼此连通，或者通过对板体613进行180度弯折，而形成两层或多层的第一微通道610和/或第二微通道611。
可选地，在一个实施例中，如图5所示，换热主体61可以包括至少一组第一微通道610和至少一组第二微通道611，该至少一组第一微通道610和至少一组第二微通道611沿板体613的宽度方向彼此 间隔，该宽度方向与板体613的延伸方向垂直。
在另一个实施例中，如图6所示，该至少一组第一微通道610和至少一组第二微通道611也可以沿板体613的厚度方向彼此间隔，该厚度方向与板体613的延伸方向垂直。
在另一实施例中，如图7所示，第一微通道610和第二微通道611相互独立，且分别设置在不同的板体613中，从而使得第一微通道610的延伸方向D1和第二微通道611的延伸方向D2彼此垂直布置，如此可以使下文描述的第一、第二集流管分别设置于换热器6不同的侧面，从而方便换热器6的集流管的布置。本实施例中第一微通道610和第二微通道611供不同的冷媒流流动，进而可以通过其中一个冷媒流为另一冷媒流过冷。
进一步地，板体613可以为扁管，以使散热元件或电子元件可以设置在板体613上。在其他实施例中，板体613还可以为其他形状横截面的载体，例如圆柱体、长方体、正方体等。在其他实施例中，如下文所描述的，换热主体61也可以包括彼此层叠设置的至少两个板体613或彼此嵌套的两个管体。
例如在图1-4所示的空调系统的制冷模式下，第一冷媒流(即中压中温的冷媒流)流经第一微通道610，第二冷媒流(即低压低温的冷媒流)流经第二微通道611，第一冷媒流可为液相冷媒流，第二冷媒流可为气液两相冷媒流。第二冷媒流在沿第二微通道611的流动过程中从第一微通道610的第一冷媒流吸热，并进一步气化，以使得第一冷媒流进一步过冷。
值得注意的是，上文和下文描述的基于微通道结构的换热器6并不局限于图1-4所示的应用场景，因此第一微通道610和第二微通道611以及第一冷媒流和第二冷媒流中的“第一”和“第二”仅是用于区分不同的微通道和冷媒流，并不应视为对微通道612和冷媒流的具体应用的限定。例如，在其他实施例或工作模式下，可以是流经第一微通道610的第一冷媒流对第二微通道611的第二冷媒流进行吸热，且第一冷媒流和第二冷媒流的状态也不限于上文所限定的液相或气液两相。
如图1-4所示，第一冷媒流的流动方向A1与第二冷媒流的流动方向A2相反，这样可以使第一冷媒流的温度与第二冷媒流的温度在换热区域内始终存在较大的温差，从而提高第一冷媒流和第二冷媒流的换热效率。
可选地，第一冷媒流的流动方向A1可以与第二冷媒流的流动方向A2相同或者相互垂直，当冷媒流向相同时，可以使得换热器6在靠近入口一侧换热器6温度较低，进而提高该区域的换热效果，比如将该区域与电控发热较大的区域相连提高散热效果；当冷媒流动方向相互垂直时，使第一、第二集流管分别设置于换热器6不同的侧面，从而可以方便换热器冷媒集流管的布置。
1.1集流管组件
请继续参阅图8所示，换热器6还包括集流管组件62。集流管组件62的延伸方向与换热主体61的延伸方向相互垂直设置，例如当换热主体61沿水平面设置时，集流管组件62沿重力方向竖向设置，如此，当集流管组件62与设置于换热器6下方的压缩机连接时，可以便于集流管组件62的管路布置。
当换热主体61沿重力方向竖向设置时，集流管组件62沿水平面设置，如此可以提高集流管组件62中的冷媒分布的均匀性，进而使得换热主体6内的冷媒分配较为均匀。
如图8所示，集流管组件62包括第一集流管621和第二集流管622，第一集流管621设置有第一集流通道，第二集流管622设置有第二集流通道。其中，换热器6沿冷媒流(第一冷媒流或第二冷媒流)在换热主体61中的流动方向的横截面形状为I形。在其他实施例中，换热器6沿冷媒流在换热主体61中的流动方向的横截面形状可以为L形、U形、G形或者圆形等。
第一集流通道与第一微通道610连接，以通过第一集流通道向第一微通道610提供第一冷媒流和/或收集流经第一微通道610的第一冷媒流。
例如，在图1-4所示的空调系统中，第一微通道610的第一端通过两个第一集流管621中的一个经膨胀阀13与室外换热器4连接，以在制冷模式下，向第一微通道610提供第一冷媒流；第一微通道610的第二端通过两个第一集流管621中的另一个与室内换热器5连接，以收集流经第一微通道610的第一冷媒流。在制热模式下，由于第一冷媒流在第一微通道610中的流动方向相反，则两个第一集流管621的功能相较于制冷模式发生互换。
第二集流通道与第二微通道611连接，以通过第二集流通道向第二微通道611提供第二冷媒流和/或收集流经第二微通道611的第二冷媒流。例如，在图1-4所示的空调系统中，第二微通道611的第一端通过两个第二集流管622中的一个与第二膨胀阀12连接，以向第二微通道611提供第二冷媒流；第二微通道611的第二端通过两个第二集流管622中的另一个与压缩机2的增焓进气口221或气液分离器8的进口81连接，以收集流经第二微通道611的第二冷媒流。
当第一微通道610和/或第二微通道611通过180°弯折或反向集流管连通而形成两层第一微通道610或第二微通道611时，第一微通道610和/或第二微通道611的流入口和流出口可以设置在换热主体61的同一侧。此时上述第一、第二集流通道可划分为提供冷媒区域和收集冷媒区域，第一和/或第二微通道的流入口和流出口分别与集流管组件62提供的冷媒区域和收集冷媒区域相连。
在一实施例中，换热主体61包括至少两组第一微通道610和至少两组第二微通道611，其中，该至少两组第一微通道610的同一端与同一个第一集流管621连接，该至少两组第二微通道611的同一端与同一个第二集流管622连接。即一个集流管可以对应多组微通道，避免每个微通道设置对应的集流管，降低成本。
在图8所示的实施例中，由于第一微通道610的延伸方向D1与第二微通道611的延伸方向D2彼此平行，因此第一集流管621和第二集流管622的延伸方向彼此平行。然而，在其他实施例中，第一集流管621和第二集流管622的延伸方向可以根据第一微通道610和第二微通道611的延伸方向进行调整，例如彼此垂直设置。
1.2第一集流管和第二集流管间隔设置
如图8所示，第一集流管621和第二集流管622间隔设置，且第二集流管622相较于第一集流管621远离换热主体61设置，第一集流管621设置在第二集流管622和换热主体61之间。
在一个实施例中，如图9所示，第二微通道611贯穿第一集流管621插入到第二集流管622中并焊接固定。第一微通道610插入到第一集流管621中并焊接固定。在另一实施例中，如图10所示，第一集流管621相较于第二集流管622远离换热主体61设置，第二集流管622设置在第一集流管621和换热主体61之间。第一微通道610贯穿第二集流管622插入到第一集流管621中并焊接固定。
需要的注意的是，此处及上下文所描述的微通道贯穿某集流管指的是微通道穿过该集流管且不与该集流管相连通，微通道插入集流管指的是微通道与集流管连通，比如，第二微通道611贯穿第一集流管621指的是第二微通道611穿过第一集流管621且不与第一集流管621连通，第二微通道611插入到第二集流管622中指的是第二微通道611与第二集流管622连通。
第一微通道610和第二微通道611可以分别设置一组或者多组，例如，如图9所示，第一微通道610可以设置两组，第二微通道611可以设置一组，第二微通道611位于两组第一微通道610之间。在其他实施例中，第一微通道610和第二微通道611均可以设置为两组或者两组以上，且第一微通道610和第二微通彼此交替层叠设置，如形成第一微通道610-第二微通道611-第一微通道610-第二微通道611或者第一微通道610-第二微通道611-第二微通道611-第一微通道610等布置形态。
在另一个实施例中，如图9所示，第一微通道610和第二微通道611中的一个可以作为主路通道，第一微通道610和第二微通道611中另一个作为辅路通道，并利用辅路通道中的冷媒流对主路通道中的冷媒流进行过冷。此时，由于主路通道内的冷媒流的流量较大，辅路通道内的冷媒流的流量较小，可以将主路通道设置在换热主体61的外侧，便于其与电控盒6连接，用于为电控盒6进行散热。另外，本实施例中，通过使冷媒流量大的主路通道贯穿辅路通道对应的集流管，并插入到主路通道对应的集流管内，此种方式，相较于辅路通道贯穿主路通道对应的集流管，不占用主路通道对应的集流管的空间，能够减小主路通道对应的集流管的流路压损，使分流更加均匀。
例如，如图10所示，当第一微通道610为冷媒流量大的主路通道，第二微通道611为冷媒流量小的辅路通道时，第一微通道610贯穿第二集流管622并插入到第一集流管621内，此种方式，能够使第二微通道611不占用第一集流管621的空间，相较于使第二微通道610贯穿第一集流管621的方式，能够减小第一集流管621的流路压损，使分流更加均匀。
在另一个实施例中，第一集流管621和第二集流管622可以焊接在一起，以缩小第一集流管621和第二集流管622之间的距离。在其他实施例中，第一集流管621和第二集流管622可以粘接或者卡接在一起。
此外，第一微通道610可以绕过第二集流管622后与第一集流管621连接，例如第一微通道610设置在第二集流管622的外侧，以绕过第二集流管622后与第一集流管621连接。或者，第二微通道611可以绕过第一集流管621后与第二集流管622连接。
在其他实施例中，换热主体61上的微通道也可以采用其他方式进行设置。微通道中的至少部分微通道贯穿至少两个集流管中的一个集流管，并插入到另一个集流管内。通过此种方式，能够减小换热器6的体积。在具体设置时，可以使冷媒流流量大的微通道贯穿至少两个集流管中的一个集流管，并插入到另一个集流管内，此种方式，可以使集流管的压损更小，使微通道分流更均匀。
可以理解的是，上述换热主体61既可以是一个板体613，也可以是多个板体613构成，相应的，第一微通道610与第二微通道611既可以设置在同一个板体613中，也可以设置在不同的板体613中。例如，当第一微通道610和第二微通道611设置于同一板体613中时，部分微通道的一端贯穿该至少两个集流管中的一个集流管，并插入到另一个集流管内，而该至少部分微通道的另一端插入到其所贯穿的集流管内，如此设置，可以提高换热主体61的集成度，省却焊接等工序，并且提高换热效果。
该至少两个集流管并不限于上文的彼此间隔方式，可以是下文描述的由总集流管配合隔流板所形成的至少两个集流管。
1.3总集流管划分为两个集流管
如图11所示，集流管组件62包括总集流管623和隔流板624，隔流板624设置在总集流管623内，以将总集流管623设置成由隔流板624分隔的第一集流管621和第二集流管622。在其他实施例中，隔流板624和所形成的集流管的数量可以根据需要进行设置。
此时，如图11所示，第一微通道610贯穿总集流管623的管壁并插入到第一集流管621内，而第二微通道611贯穿总集流管623的管壁和隔流板624(即，贯穿第一集流管621)，并插入到第二集流管622内。在其他实施例中，可以是第二微通道611贯穿总集流管623的管壁并插入到第二集流管622内，而第一微通道610贯穿总集流管623的管壁和隔流板624并插入到第一集流管621内。
与图9或10所示的集流管组件62相比较：本实施例通过一条总集流管623同时实现第一集流管621和第二集流管622的功能，能够降低集流管组件62的成本和体积。
在其他实施例中，可以利用隔流板624将总集流管623分隔成两个第一集流管621或者两个第二集流管622。例如，当第一微通道610或第二微通道611通过弯折180°或者反向集流管后形成两层第一微通道610或第二微通道611时，第一微通道610的一端贯穿总集流管623的管壁并插入到其中的一个第一集流管621内，而第一微通道610的另一端贯穿总集流管623的管壁和隔流板624并插入到其中的另一个第一集流管621内。或者，第二微通道611的一端贯穿总集流管623的管壁并插入到其中的一个第二集流管622内，而第二微通道611的另一端贯穿总集流管623的管壁和隔流板624并插入到其中的另一个第二集流管622内。
在另一实施例中，如图12和图13所示，在换热主体61的端面上可以设置有插槽601，插槽601位于第一微通道610和第二微通道611之间，隔流板624嵌入于插槽601内，以使第一微通道610贯穿总集流管623的管壁插入到第一集流管621内，第二微通道611穿过总集流管623的管壁插入到第二集流管622内。通过此种设置插槽601的方式，能够缩短换热器6的整体长度，减小换热器6的材料成本，且能够简化集流管组件62与换热主体61的焊接工艺。
在一实施例中，当第一微通道610或第二微通道611通过弯折180°或反向集流管后形成两层第一微通道610或第二微通道611时，换热主体61的入口端和出口端位于同一侧。此时，第一微通道610的一端贯穿总集流管623的管壁并插入到其中的一个第一集流管621内，而第一微通道610的另一端贯穿总集流管623的管壁并插入到其中的另一个第一集流管621内。
或者，第二微通道611的一端贯穿总集流管623的管壁并插入到其中的一个第二集流管622内，而第二微通道611的另一端贯穿总集流管623的管壁并插入到其中的另一个第二集流管622内。
进一步地，换热主体61可以为单个板体613或者多个板体613。在图12所示的实施例中，换热主体61可以为单个板体613，第一微通道610和第二微通道611设置于单个板体613内。进一步，在单个板体613的端面上，第一微通道610和第二微通道61之间设置有间隔区域，插槽601设置于该间隔区域内。此种方式，换热主体61一体设置，结构简单，具有较高的可靠性，且可提升换热主体61的传热效率。在另一个实施例中，如下文所描述的，换热主体61也可以包括至少两个板体613，至少两个板体613层叠设置，该至少两个板体613的端面设置插槽601，且插槽601设置于相邻的板体613之间，隔流板624嵌入于插槽601内。
值得注意的是，上文描述的隔流板624和插槽601配合方式可以适用于其他的微通道分组方式，只需换热主体61上设置至少两组微通道，该至少两组微通道可以是彼此连通，以供同一冷媒流流动，可以是相互独立，以供不同的冷媒流流动。
1.4第一集流管与第二集流管嵌套设置
如图14所示，第二集流管622的直径小于第一集流管621的直径，第一集流管621套设在第二集流管622的外侧，第一微通道610贯穿第一集流管621的管壁，并插入到第一集流管621内。第二微通道611贯穿第一集流管621和第二集流管622的管壁，并插入到第二集流管622内。在其他实施例中，可以是第二集流管622套设于第一集流管621的外侧，此时第二微通道611贯穿第二集流管622的管壁，并插入到第二集流管622内。第一微通道610贯穿第二集流管622和第一集流管621的管壁，并插入到第一集流管621内。
与图9或10所示的集流管组件62相比较：通过嵌套设置能够减小集流管组件62的体积。
在其他实施例中，可以是两个第一集流管621彼此嵌套，或者两个第二集流管622彼此嵌套。此时，第一微通道610的一端贯穿外侧的第一集流管621的管壁，并插入到外侧的第一集流管621内。第一微通道610的另一端贯穿两个第一集流管621内的管壁，并插入到内侧的第一集流管621内。
或者，第二微通道611的一端贯穿外侧的第二集流管622的管壁，并插入到外侧的第二集流管622内。第二微通道611的另一端贯穿两个第二集流管622内的管壁，并插入到内侧的第一集流管622内。
2.套管式的换热器
如图15所示，换热器6包括换热主体61，换热主体61包括彼此嵌套的第一管体614和第二管体615，即换热器6为套管式的换热器。第一管体614内设置有多个第一微通道610，第二管体615内设 置有多个第二微通道611，多个第一微通道610和多个第二微通道611均与图5所示的微通道612相同，因此换热主体61的长度缩短，进而缩小换热器6的体积。
其中，第一微通道610的延伸方向与第二微通道611的延伸方向彼此平行，例如第一微通道610的延伸方向与第二微通道611的延伸方向相同。
在本实施例中，如图16所示，第一管体614套设在第二管体615的外侧，第一管体614的外表面设置有至少一个平面616，以形成第一管体614的换热接触面。散热元件或电子元件可以设置在平面616上，便于安装。在其他实施例中，第二管体615可以套设在第一管体614的外侧，并形成类似的平面。
在图1-4所示的空调系统1中，第一冷媒流流经多个第一微通道610，第二冷媒流流经多个第二微通道611，第一冷媒流可为液相冷媒流，第二冷媒流可为气液两相冷媒流。第二冷媒流在沿多个第二微通道611的流动过程中从多个第一微通道610的第一冷媒流吸热，并进一步气化，以使得第一冷媒流进一步过冷。在其他实施例或工作模式下，可以是流经第一微通道610的第一冷媒流对第二微通道611的第二冷媒流进行吸热，且第一冷媒流和第二冷媒流的状态也不限于上文所限定的液相或气液两相。
与图5所示的换热器6进行对比：换热主体61的横截面积变大，能够减少冷媒流的压力损失。此外，第一管体614和第二管体615套管设置，能够提高多个第一微通道610与多个第二微通道611的换热面积，提高第一微通道610和第二微通道611之间的换热效率。
与图8类似，换热器6还包括集流管组件62，集流管组件62包括第一集流管621和第二集流管622，第一集流管621设置有第一集流通道，第一集流通道用于向第一微通道610提供第一冷媒流和/或收集流经第一微通道610的第一冷媒流。第二集流管622设置有第二集流通道，第二集流通道向第二微通道611提供第二冷媒流和/或收集流经第二微通道611的第二冷媒流。其中，换热器6沿冷媒流在换热主体61中的流动方向的横截面形状为I形。在其他实施例中，换热器6沿冷媒流在换热主体61中的流动方向的横截面形状可以为L形、U形、G形或者圆形等。
集流管组件62可以采用上文描述的各种集流管设置方式，例如上文描述的第一集流管621和第二集流管622彼此间隔设置方式、总集流管623和隔流板624的设置方式，或者第一集流管621和第二集流管622彼此嵌套的设置方式。此时，第一管体614连同其上的第一微通道610以及第二管体615连同其上的第二微通道611均可以采用上文描述的方式与上述集流管配合，在此不再赘述。
3.换热器具有彼此层叠设置的多个板体
如图17所示，换热器6包括换热主体61，换热主体61包括第一板体631和第二板体632，第一板体631和第二板体632彼此层叠设置。
第一板体631内设有多个第一微通道610，第二板体632内设有多个第二微通道611，多个第一微通道610和多个第二微通道611均与图5-图7所示的微通道612相同，在此不再赘述。采用多层结构，因此换热主体61的长度缩短，进而缩小换热器6的体积。
由于第一板体631和第二板体632彼此层叠设置，提高第一板体631和第二板体632的接触面积，以增大第一微通道610和第二微通道611之间的换热面积，提高换热效率。
在图1-4所示的空调系统中，第一冷媒流流经多个第一微通道610，第二冷媒流流经多个第二微通道611，第二冷媒流在沿多个第二微通道611的流动过程中从多个第一微通道610的第一冷媒流吸热，并进一步气化，以使得第一冷媒流进一步过冷。
在其他实施例或工作模式下，可以是流经第一微通道610的第一冷媒流对第二微通道611的第二冷媒流进行吸热，且第一冷媒流和第二冷媒流的状态也不限于上文所限定的液相或气液两相。
第一板体631和第二板体632可以分别设置一个或者多个。比如，第一板体631的数量可以为两个，第二板体632夹持设置于两个第一板体631之间，例如第一板体631、第二板体632和第一板体631依次层叠设置。通过第二板体632夹持设置于两个第一板体631之间，以使第二板体632的第二冷媒流同时对两个第一板体631的第一冷媒流进行吸热，实现两个第一板体631的第一冷媒流过冷。此外，散热元件或电子元件可以设置成与第一板体631导热连接，例如设置第一板体631远离第二板体632的表面上，便于安装。在其他实施例中，第一板体631和第二板体632可以均设置两个或者两个以上等，且第一板体631和第二板体交替层叠设置。
在一实施例中，两个第一板体631可以是两个相互独立的板体。在其他实施例中，两个第一板体631也可以是呈U形一体连接或者反向集流管连接，此时两个第一板体631内的第一微通道610呈U形连通，进而使得第一微通道610的入口和出口位于换热主体61的同一侧。
在其他实施例中，第二板体632的数量可以为两个，第一板体631夹持设置于两个第二板体632之间。此时，散热元件或电子元件可以设置成与第二板体632导热连接。
如图18所示，换热器6还包括集流管组件62，集流管组件62包括第一集流管621和第二集流管622，第一集流管621设置有第一集流通道，第一集流通道用于向第一微通道610提供第一冷媒流和/或收集流经第一微通道610的第一冷媒流。第二集流管622设置有第二集流通道，第二集流通道向第二 微通道611提供第二冷媒流和/或收集流经第二微通道611的第二冷媒流。
集流管组件62可以采用上文描述的各种集流管设置方式，例如上文描述的第一集流管621和第二集流管622彼此间隔、总集流管623和隔流板624的设置方式，或者第一集流管621和第二集流管622彼此嵌套的设置方式。此时，第一板体631连同其上的第一微通道610以及第二板体633连同其上的第二微通道611均可以采用上文描述的方式与上述集流管配合。
3.1层叠设置的板体之间的焊接工艺
如图19示，在本实施例中，换热器6包括第一板体631、第二板体632和连接片64。第一板体631和第二板体632彼此层叠设置，连接片64夹置于相邻的第一板体631和第二板体632之间，连接片64的两侧设置有焊料(图未示)，焊料用于将连接片64与连接片64两侧的第一板体631和第二板体632焊接固定。
本实施例中，通过将焊料设置于连接片64的两侧，然后通过连接片64将第一板体631和第二板体632进行焊接。此种方式，能够使得第一板体631和第二板体632之间得到有效固定，由于相邻的板体613之间进行焊接时需要两个板体613的贴合面上涂布焊料，相对于使用表面涂覆焊料的板体613而言，通过在两个板体613之间布置带焊料的连接片64，可以大幅降低生产成本。
进一步地，连接片64的熔点高于焊料的熔点。连接片64可以为金属箔片，以提高导热性。比如，连接片64可以为铝箔或者铜箔等。金属箔片的成本较低，在金属箔片的两侧设置焊料的工艺也较为简单，因此带有焊料的金属箔片较易获得，且具有较低的生产成本。
连接片64上的焊料对两侧相邻的第一板体631和第二板体632的覆盖面积不小于第一板体631和第二板体632的重叠面积的80％，以提高第一板体631和第二板体632之间焊接的可靠性。可选地，连接片64上焊料对第一板体631和第二板体632的覆盖面积可以为两侧相邻的第一板体631和第二板体632的重叠面积的80％；或者，连接片64上焊料对第一板体631和第二板体632的覆盖面积可以等于第一板体631和第二板体632重叠面积，此种方式，能够进一步提高换热器6的可靠性。
可选地，第一板体631和第二板体632之间的连接片64可以为单层结构，即第一板体631和第二板体632之间只设置有一层连接片64。在其他实施例中，第一板体631和第二板体632之间的连接片64为至少两层，比如，连接片64可以为两层、三层或者四层结构等。此时，该至少两层连接片64之间进一步通过焊料焊接固定。通过灵活选择连接片64的层数，能够调整第一板体631和第二板体632之间的距离，使换热器6能够适应不同的应用场景。例如，在第一板体631和第二板体632之间形成宽度等于该至少两层连接片64的叠层厚度的插槽，以配合上文描述的隔流板。
连接片64的的厚度范围为0.9mm-1.2mm。比如，连接片64的厚度可以为0.9mm、1mm或者1.2mm等。
值得注意的是，连接片64可以设置于其他具有微通道的至少两个板体的相邻板体之间，例如，两个第一板体631，或者两个第二板体632。
在一个具体的实施例中，如图20所示，上述换热器6的制造方法可以包括：S11：提供至少两个板体。S12：提供连接片，连接片的两侧设置有焊料。S13：将至少两个板体层叠设置，并将连接片夹置于相邻的板体之间。S14：加热该至少两个板体和连接片，以使得焊料将连接片与位于连接片两侧的板体3焊接固定。
3.2层叠设置的板体与集流管之间的连接
如图21所示，换热器6包括至少两个板体613和至少一集流管620，板体613包括主体部671和连接部672，该至少两个板体613的主体部671彼此层叠设置，连接部672的一端连接主体部671，连接部672的另一端与集流管620连接。
如图22所示，集流管620的管壁上设置有至少两个插孔602，板体613的连接部672的另一端与插孔602相对应，并与集流管620焊接固定。即连接部672位于板体613的端部，用于与集流管620固定。该至少两个板体613在与集流管620进行焊接时，如果在焊接处，相邻两个板体613之间的间隔距离较小，会增大焊接难度，焊料会沿着相邻两个板体613之间的缝隙流动，导致板体613与集流管620之间焊接不良，造成冷媒流泄漏的风险。
本实施例中，集流管620上相邻两个插孔602之间具有第一间距d1，相邻两个板体613的主体部671之间具有第二间距d2，第一间距d1大于第二间距d2。通过此种方式，能够增大焊接处相邻两个板体613的连接部671之间的距离，减小相邻两个板体613之间的毛细作用，提高板体613与集流管620焊接的可靠性。
进一步地，第一间距d1不小于2mm，比如，第一间距d1可以为2mm或者3mm等，以减小板体613的连接部672之间的毛细作用，利于板体613的连接部672与集流管620之间的焊接。更进一步地，第一间距d1进一步不大于6mm，以使换热器6具有较高的结构强度，提高换热器6的可靠性。
可选地，至少部分板体613的连接部672呈弯曲设置，比如，至少部分板体613的连接部672呈弧 形设置。通过此种弯曲设置的方式便于调整相邻两个板体613的连接部672之间的间距，利于板体613与集流管620之间的焊接固定，减小焊接时相邻两个板体613之间的毛细作用。
可选地，板体613的连接部672的一端弯曲设置，另一端呈直线设置，以简化加工工艺。
进一步地，至少部分相邻设置的板体613的连接部672之间具有第三间距d3，第三间距d3在从主体部671到集流管620的至少部分范围内逐渐增大，以使相邻的连接部672之间的距离逐渐增大，减小相邻两个板体613之间的毛细作用。
在图21所示的实施例中，该至少两个板体61可以包括上文描述的第一板体631和第二板体632。
进一步，在本实施例中，第一板体631的数量为2个，第二板体632的数量为2个，第一板体631和第二板体632依次层叠设置。其中，一个第二板体632夹设于两个第一板体631之间，另一个第二板体632叠设于一个第一板体631背离所夹设的第二板体632的外侧。集流管620包括间隔设置的第一集流管621和第二集流管622。第一板体631上设置供第一冷媒流流动的多个第一微通道，第二板体632上设置有供第二冷媒流流动的多个第二微通道，第二冷媒流在沿多个第二微通道611的流动过程中从第一冷媒流吸热，以使得第一冷媒流过冷，或者第一冷媒流在沿多个第一微通道610的流动过程中从第二冷媒流吸热，以使得第二冷媒流过冷。第一板体631的连接部672与第一集流管621焊接固定，第二板体632的连接部672与第二集流管621焊接固定。
如图21所示，被夹设的第二板体632的连接部672可以贯穿第一集流管621，并与第二集流管622连接，位于外侧的第二板体632的连接部672可以绕过第一集流管621与第二集流管622焊接固定，通过此种方式，能够减小第一集流管621上插孔602的数量，增大插孔602之间的距离，利于换热器6的装配，使换热器6具有较高的可靠性。同时可以减少对第一集流管621内的冷媒流的干扰。
在另一个实施例中，第二板体632的连接部672都贯穿第一集流管621，并第二集流管622连接。在其他实施例中，第一板体631的连接部672可以贯穿第二集流管622，并与第一集流管621连接，在此不再赘述。
其中，第一板体631和第二板体632的数量可以根据实际应用需要进行选择设置，在此不做具体限定。
集流管620还可以采用上文描述的各种集流管设置方式，在此不再赘述。
进一步地，板体613的主体部672为直线型结构，因此，第一板体631的主体部671与第二板体632的主体部671之间可以通过焊料直接焊接。
在其他实施例中，第一板体631的主体部671与第二板体672的主体部671之间通过上文描述的带有焊料的连接片进行连接，在此不再赘述。
4.散热翅片
如图23和图24所示，换热器6包括换热主体61和散热翅片65，散热翅片65可以设置于换热主体61上，并将散热翅片65与换热主体61导热连接，以利用散热翅片65增大换热主体61与空气的接触面积，便于与空气进行换热，提高换热器6的换热效率，并提高换热器6的散热效果。
其中，散热翅片65可以通过焊接、粘接或者紧固连接的方式连接于换热主体61的表面。
进一步地，在如图23所示的实施例中，换热主体61包括并列且间隔设置的至少两个板体组件603，散热翅片65设置于该至少两个板体组件603上。
换热器6还包括固定板66，固定板66同时覆盖于该至少两个板体组件603上的散热翅片65上，且固定板66位于散热翅片65背离板体组件603的一侧，以形成散热风道。此种方式，对散热翅片65的密封采用整体固定板66结构，零部件少，使换热器6的生产简单可靠，同时所形成的散热风道可以提高散热效果。散热风道所定义的气流方向可以沿板体组件的间隔方向设置，即与板体组件603的延伸方向垂直，以增大换热翅片65的散热效率。在其他实施例中，散热风道所定义的气流方向可以与板体组件603的延伸方向设置或与板体组件603的延伸方向呈其它角度设置。
如图23所示，固定板66包括顶面板661，顶面板661同时覆盖于该至少两个板体组件603上的散热翅片65上，以方便对散热翅片65的密封。
进一步地，固定板66还包括至少一个侧面板662，侧面板662与顶面板661弯折连接，且向板体组件603延伸，以通过侧面板662对散热风道进行密封，减少换热器6的零部件，提高散热风道的密封性。
具体地，在一个实施例中，固定板66可以包括顶面板661和一个侧面板662，该侧面板662与顶板面661的一端弯折连接，散热翅片65的一端与该侧面板662抵接，以封闭散热风道。散热翅片65的另一端可以通过其他零部件拼接装配，或者与下文描述的电控盒的盒体抵接，以使散热翅片65形成完整的风道，此种方式，能够简化散热翅片65的封装，提高装配效率。
在另一个实施例中，侧面板662的数量为两个，两个侧面板662沿至少两个板体组件603的间隔方向的垂直方向间隔设置，顶面板661分别与两个侧面板662弯折连接，以形成容置空间，散热翅片65 位于容置空间内，即位于两个侧面板662之间，此种方式，能使固定板66对散热翅片65进行完整密封，形成整体散热风道，零部件少，进一步简化散热翅片65的封装工艺，使换热器6的生产简单可靠，同时换热能力提高。
可选地，如图24所示，散热翅片65为由片材挤压形成的波浪式结构，并且该波浪式结构的波峰和波谷分别与顶面板661和板体组件603彼此相对的表面接触。
可选地，散热翅片65的数量可以为至少两个，如图25所示，散热翅片65的数量可以与板体组件603的数量相等，每个散热翅片65设置于对应的板体组件603上。每一散热翅片65沿板体组件603的延伸方向的垂直方向上的宽度可以等于对应的板体组件603的宽度，以提高换热能力，且能节约材料成本。
如图25所示，每一散热翅片65可以贴附于一个板体组件603上，多个散热翅片65可以沿板体组件603的间隔方向彼此间隔排列，由于在焊接工序中，板体613间的空隙处温度会高于板体613处，如此设置可以防止散热翅片65融化变形。通过将散热翅片65设置为间隔的多个，不仅可以保证散热翅片65的换热效率，而且也可以节省材料，降低生产成本。
可选地，如图26所示，散热翅片65的数量也可以为1个，即散热翅片65为一体式设置，并同时设置于至少两个板体组件603上。其中，散热翅片65沿板体组件603延伸方向的垂直方向上的宽度可以大于或者等于换热主体61的宽度。如此，一体式散热翅片65数量较少且表面积较大，一方面可以便于将散热翅片65与换热主体61进行连接，提升散热翅片65与换热主体61的安装效率；另一方面也可以增大散热翅片65与空气的接触面积，增强换热效果。
进一步地，固定板66沿该至少两个板体组件603的间隔方向的两端呈开放式设置，以使得气流在散热风道中的流动方向沿至少两个板体组件603的间隔方向设置。进一步，板体组件603内的冷媒流的流动方向垂直于该至少两个板体组件603的间隔方向，以增强散热风道的散热效果，提高换热器6整体的换热效率。
其中，每个板体组件603内可以设置有微通道，例如采用上文描述的各种板体与微通道的配合方式，在此不再赘述。
值得注意的是，如本领域技术人员所理解的，上述散热翅片65结构适用于本申请描述的各种形式的换热器6，而不应该局限于某一个特定实施例。
5.换热器作为散热器
本申请还可以将上述换热器6用作散热器(以下以散热器6进行描述)，散热器6包括换热主体61和集流管组件62，并将散热器6设置成对电控盒7内的电子元件进行散热。值得注意的是，如本领域技术人员所理解的，此处所提及的散热器6应该包括上文描述的各种形式的换热器，而不应该局限于某一个特定实施例。
在一实施例中，散热器6在作为空调系统1的经济器的同时，也代替电控盒6中的模块散热器，用于对电控盒7进行散热，以简化空调系统1的管路组件以及模块数量，降低成本。
进一步地，如图27所示，电控盒7包括盒体72和散热器6，盒体72设有安装腔721，电子元件71设置于安装腔721，散热器6设置于安装腔721内，以用于为安装腔721内的电子元件71进行散热。在另一个实施例中，散热器6也可以设置于盒体72的外部，且将其设置成为安装腔721内的电子元件71进行散热。
如图27所示，盒体72包括顶板(图中未示出，与底板723相对设置，遮盖安装腔721的开口)、底板723和周向侧板724，顶板和底板723相对间隔设置，周向侧板724连接于顶板和底板723，进而形成安装腔721。
具体来说，在图27中，底板723和顶板呈长方形，周向侧板724的数量为四个，四个周向侧板724分别连接于底板723和顶板的对应侧边，进而与底板723和顶板围合形成长方体状的电控盒7。底板723的长边大小即为电控盒7的长度，底板723的短边大小即为电控盒7的宽度。周向侧板724的垂直于底板723的高度大小即为电控盒7的高度。如图27所示，电控盒7在X方向上的长度即为电控盒7的长度，电控盒7在Y方向上的长度即为电控盒7的高度，电控盒7在Z方向上的长度即为电控盒7的宽度。
以下几个实施例将对散热器6与电控盒7的具体组合方式进行详细的说明。
5.1换热主体形态
在一实施例中，换热主体61呈直条状设置，如图18所示，换热主体61具有整体长度、整体宽度和整体高度。其中，整体长度即为换热主体61沿其延伸方向上的长度，即换热主体61沿图18中所示的X方向的长度。整体宽度为换热主体61在垂直于换热主体61的延伸方向且垂直于换热主体61所在平面的方向上的长度，即换热主体61沿图18中所示的Y方向的长度。整体高度为换热主体61沿图18中所示的Z方向的长度。其中，换热主体61所在平面指的是集流管组件62所处的平面，即图18中所 示的XOZ平面。
在本实施例中，如图27所示，可以将换热主体61设置于电控盒7的底板723上。或者，可以将换热主体61设置于电控盒7的周向侧板724上。在其他实施例中，换热主体61还可以根据电子元件71等的设置位置固定在电控盒7的其他位置处，本申请实施例不做具体限定。
当换热主体61为如图18所示的直条状时，换热主体61可以抵接于底板723，或者与底板723间隔设置，如此，能够充分利用底板723的长度方向的尺寸，设置尽可能长的换热主体61，以提升换热效果。在其他实施例中，换热主体61也可以抵接于周向侧板724，或者与周向侧板724间隔设置，本申请实施例不做具体限定。
进一步地，请参阅图28，为了缩小换热主体61的整体长度，可以将换热主体61划分成第一延伸部617和第二延伸部618，第二延伸部618连接于第一延伸部617的端部并向第一延伸部617的一侧弯折，以使换热主体61呈L型。
通过将换热主体61折弯形成弯折连接的第一延伸部617和第二延伸部618，可以在保证换热主体61具有足够长的延伸长度的条件下，缩小换热主体61的整体长度，进而可以缩小与散热器6配合的电控盒7沿X方向的长度，以缩小电控盒7的体积。
具体来说，可以将第一延伸部617设置成与底板723平行，以充分利用底板723的长度方向的尺寸，设置尽可能长的换热主体61，以提升换热效果。可以将第二延伸部618设置成与周向侧板724平行，以降低第二延伸部618在X方向上所占用的空间。
或者，可以将第一延伸部617设置成与其中一个周向侧板724平行，将第二延伸部618设置成与该周向侧板724邻接的周向侧板724平行，以将散热器6设置于安装腔721的其中一侧。
可选地，第一延伸部617可以抵接于底板723，或者与底板723间隔设置，第二延伸部618可以抵接于周向侧板724，或者与周向侧板724间隔设置，本申请实施例不做具体限定。
进一步地，如图28所示，第二延伸部618的数量可以为一个，一个第二延伸部618连接于第一延伸部617的其中一端，以使得换热主体61呈L型。
如图29所示，第二延伸部618的数量可以为两个，两个第二延伸部618分别连接于第一延伸部617的相对两端，并分别向第一延伸部617的同一侧弯折。
具体来说，两个第二延伸部618可以平行间隔设置于第一延伸部617的相对两端，以在保证换热主体61的换热效果的情况下，进一步缩小换热主体61的整体长度，缩小散热器6的体积。另外，将两个第二延伸部618折弯设置于第一延伸部617的同一侧，相对于两个第二延伸部618分别位于第一延伸部617的相对两侧，也可以便于缩短散热器6的整体宽度。
进一步地，两个第二延伸部618可以与第一延伸部617垂直设置，以形成U型的换热主体61。如此，不仅可以缩小换热主体61的整体长度，而且也可以降低第二延伸部618在X方向上所占用的空间，避免两个第二延伸部618与设于安装腔721内的电子元件71产生干涉。
或者，两个第二延伸部618也可以相对第一延伸部617倾斜设置，且两个第二延伸部618相对于第一延伸部617倾斜的角度可以相同也可以不同，以缩短电控盒7的整体宽度。
进一步地，第一延伸部617的延伸长度设置成大于第二延伸部618的延伸长度，进而使得第一延伸部617沿电控盒7的长度方向设置，而第二延伸部618沿电控盒7的宽度或高度方向设置。
进一步地，如图27所示，设于安装腔721内的散热器6的数量可以为一个，一个散热器6可以沿盒体72的长度方向延伸设置于安装腔721内。或者，一个散热器6可以沿盒体72的高度方向延伸设置于安装腔721内。
或者，设于安装腔721内的散热器6的数量可以为至少两个，例如，散热器6的数量可以为两个、三个、四个或者五个等。通过设置数量较多的散热器6，可以提升电控盒7的散热效果。
5.2散热器设置在电控盒内
如本领域技术人员所理解的，也可以将本申请所公开的各种形式的散热器6设置于电控盒7的安装腔721内或应用于电控盒7的散热，并可以以直接或间接方式与电子元件71导热连接。
进一步地，如图27所示，散热器6设置于电控盒7的安装腔721内。具体地，可以将散热器6与设于安装腔721内的电子元件71导热连接，以用于为电子元件71散热。
具体来说，可以将电子元件71与换热主体61导热连接，电子元件71可以与换热主体61的任意位置进行导热连接。
当散热器6中的换热主体61为直条状时(即散热器6呈I型时)，电子元件71可以设置于换热主体61上的任意位置，此种方式，利于电子元件71的装配。比如，可以将电子元件71设置于换热主体61的中间位置，或者可以将电子元件71设置于换热主体61的两端的位置。可选地，电子元件71可以设置于换热主体61的一侧，也可以根据实际应用场景，将电子元件71设置于换热主体61的相对的两侧。
在如图28和图29所示的实施例中，当散热器6为L型或者U型时，可以将电子元件71与第一延伸部617导热连接，且电子元件71可以与第二延伸部618设置于第一延伸部617的同一侧，以缩短电控盒7的高度，即沿Y方向的尺寸。
或者，可以将电子元件71与第二延伸部618导热连接，并具体可以将电子元件71设置于第二延伸部618朝向第一延伸部617的一侧，以缩短电控盒7的长度，即沿X方向的尺寸。
或者，还可以将电子元件71部分设置于第一延伸部617上，部分设置于第二延伸部618上，以使得电子元件71分布均匀。
如图27和图30所示，还可以在电控盒7内设置散热固定板74，将电子元件71设置于散热固定板74上，然后将散热固定板74与换热主体61连接，以通过散热固定板74将电子元件71和换热主体61导热连接，如此，可以极大的提高电子元件71的安装效率。
其中，散热固定板74可以采用导热性能良好的金属板或者合金板制成，例如，散热固定板74可以采用铝板、铜板、铝合金板等制成，以提升热传导效率。
或者，如图31所示，还可以在散热固定板74内嵌设热管741，热管741用于将较为集中的高密度热源快速导热进而扩散至整个散热固定板74的表面，以使得散热固定板74上的热量分布均匀，增强散热固定板74与换热主体61的换热效果。
其中，如图31中上侧的附图所示，热管741可以呈长条状设置，热管741的数量可以包括多个，多个热管741可以平行间隔排布。或者，如图31中下侧的附图所示，多个热管741也可以顺次连接呈环形或者框型，本申请实施例不做具体限定。
5.3散热器设置在电控盒外
如图32所示，散热器6设置于电控盒7的外部，可以在电控盒7的盒体72上开设装配口726，并将电子元件71通过装配口726与散热器6导热连接。
具体来说，如图32所示，将电子元件71设置于散热固定板74背离散热器6的一侧表面上。
或者，如图33所示，可以设置热管741将电子元件71与散热器6导热连接。例如，热管741可以包括吸热端741a和放热端741b，可以将热管741的吸热端741a插置于安装腔721的内部，并与电子元件71导热连接，以用于吸收电子元件71的热量，将热管741的放热端741b设置于电控盒7的外部，并与散热器6导热连接，以利用散热器6为热管741的放热端741b散热。
5.4散热翅片与电子元件的布置
在图23-26所示的实施例中，散热器6包括散热翅片65，带有散热翅片65的散热器6应用于电控盒7内时，能够利用散热翅片65增大换热主体61与电控盒7内的空气的接触面积，便于与空气进行换热，降低安装腔721内的温度，保护电子元件71。
可选地，可以将电子元件71和散热翅片65设置于换热主体6的同一侧，且将电子元件71和散热翅片65错开设置，避免电子元件71和散热翅片65产生干涉，并且将电子元件71和散热翅片65之间的距离设置的较大，也可以使得与散热翅片65和电子元件71接触的冷媒的温度均较低，以提升换热主体61的散热效果。
在其他实施例中，电子元件71设置于换热主体61的一侧，散热翅片65设置于换热主体61的另一侧，具体地，散热翅片65可以设置于换热主体61的另一侧的任意位置。
在一实施例中，散热翅片65可以延伸到电控盒7的外侧，例如在盒体72上开设装配口，换热主体61设置在盒体72内，并与电子元件71导热连接，而散热翅片65的一侧与换热主体61导热连接，并经装配口延伸到盒体72的外侧，并可以进一步通过风冷辅助来提高换热主体61的散热能力。
6.电子元件设置在散热器温度较高的位置
请参阅图34，本实施例中的电控盒7包括盒体72、散热器6和电子元件71，盒体72设有安装腔721，散热器6至少部分设置于安装腔721内，电子元件71设于安装腔721内。其中，盒体72和散热器6的结构与上述实施例中的大致相同，请参照上述实施例中的描述。
可选地，换热主体61可以全部设置于电控盒7的安装腔721内，换热主体61也可以部分设置于电控盒7的安装腔721内，部分凸伸出电控盒7外，以用于与集流管组件62和外部管路连接。
冷媒流的流动使得散热器6的温度较低，由于电控盒7内电子元件71发热使得电控盒7的安装腔721内的温度较高，当电控盒7内温度较高的空气接触到散热器6时容易冷凝，进而在散热器6的表面形成冷凝水。如果生成的冷凝水流动至电子元件71的位置处，容易使得电子元件71短路或者损坏，更严重的会产生火灾隐患。
故而，如图34所示，可以将换热主体61沿冷媒流的流向划分为第一端61a和第二端61b，换热主体61工作时，换热主体61的温度在从第一端61a到第二端61b的方向上逐渐降低，即第一端61a的温度高于第二端61b的温度。电子元件71设置在靠近第一端61a的位置处，并将电子元件71与换热主体61导热连接。需要注意的是，由于换热主体61需要与电控盒7的内部环境或其内部元件进行换热，因 此上文以及下文描述的换热主体61的温度是指换热主体61的表面温度。具体来说，换热主体61的表面温度变化由与表面相邻的换热通道决定。例如，当换热主体61的表面所相邻的换热通道为主路通道时，由于主路通道的冷媒流随着流动不断被辅路通道的冷媒流吸热，因此换热主体61的表面温度沿主路通道的冷媒流向逐渐降低，此时第一端61a沿主路通道的冷媒流向位于第二端61b的上游。当换热主体61的表面所相邻的换热通道为辅路通道时，换热主体61的表面温度沿辅路通道的冷媒流向逐渐降升高，此时第一端61a沿辅路通道的冷媒流向位于第二端61b的下游。
因此，通过根据工作时换热主体61上温度的变化，将换热主体61划分为温度较高的第一端61a和温度较低的第二端61b，由于温度较高的第一端61a与热空气之间的温差较小，不会产生冷凝水或者产生的冷凝水的量较少，通过将电子元件71设置在靠近第一端61a的位置处，可以降低电子元件71与冷凝水接触的几率，进而保护电子元件71。
值得注意的是，由于空调一般存在制冷模式和制热模式，而在这两种模式下可能存在冷媒流动方向相反的情况。此时，换热主体61的温度在第一端61a到第二端61b存在相反的变化趋势，即在一种模式下，换热主体61的温度在第一端61a到第二端61b逐渐降低，而在另外一种模式下换热主体61的温度在第一端61a到第二端61b逐渐升高。在本实施例中，优先确保在制冷模式下，换热主体61的温度在第一端61a到第二端61b逐渐降低，理由如下：
当环境温度较低时，例如，当空调装置在冬天工作进行制热时，电控盒7内的空气的温度较低，此时，电控盒7内的空气与散热器6之间的温差较小，空气不容易冷凝形成冷凝水。而当环境温度较高，例如，当空调装置在夏天工作进行制冷时，电控盒7内的空气的温度较高，电控盒7内的空气与散热器6之间的温差较大，空气容易冷凝形成冷凝水。故而，在本实施例中，可以设置至少在空调装置的制冷模式下，换热主体61的温度在从第一端61a到第二端61b的方向上逐渐降低，以避免散热器6在制冷模式下产生冷凝水。
进一步地，将电子元件71设置在靠近第一端61a的位置处指的是，电子元件71在换热主体61上的导热连接位置与第一端61a之间具有第一距离，与第二端61b之间具有第二距离，第一距离小于第二距离。
具体来说，由于换热主体61的温度在从第一端61a到第二端61b的方向上逐渐降低，故而，第一端61a的温度最高，第二端61b的温度最低，换热主体61的温度越高，与电控盒7内的空气之间的温差越小，冷凝水越不容易凝聚。换热主体61的温度越低，与热空气之间的温差越大，冷凝水越容易凝聚。即，在从换热主体61的第一端61a到第二端61b的方向上，产生冷凝水的几率逐渐增大。故而，通过将电子元件71设置的靠近换热主体61温度较高的一端，即设置在冷凝水不易积聚的位置处，可以降低电子元件71与冷凝水接触的风险，进而保护电子元件71。
进一步，如图34所示，可以将换热主体61的延伸方向沿竖直方向设置，并将第一端61a设置在第二端61b的上部，如此，当换热主体61靠近第二端61b的位置处产生冷凝水时，冷凝水会沿竖直方向下流，即冷凝水会向背离电子元件71的方向流动，避免电子元件71与冷凝水接触。
或者，还可以根据需要将换热主体61的延伸方向沿水平方向设置，以便于靠近第二端61b位置处产生的冷凝水在重力的作用下迅速与换热主体61分离，避免与电子元件71接触。或者，在其它实施例中，还可以将换热主体61的延伸方向相对水平方向倾斜设置，本申请实施例不做具体限定。
可以理解地，本实施例中的散热器6的结构可以设置得与上述实施例中的相同，即采用折弯的换热主体61。或者，本实施例中的散热器6的结构也可以采用直条形的换热主体61。或者，除了可以采用上述的设有微通道的散热器6外，还可以采用其他种类的散热器，本申请实施例不对散热器6的具体结构进行限定。此外，在本申请的其他将散热器应用于电控盒的实施例可以采用本申请所公开的各种散热器，或者本领域公知的其他散热器。
7.冷凝水防护
请参阅图35所示，本实施例中的电控盒7包括盒体72、安装板76、电子元件71和散热器6。
其中，盒体72设有安装腔721，安装板76设于安装腔721内，以使得安装腔721形成位于安装板76两侧的第一腔室7212和第二腔室7214，电子元件71设于第二腔室7214内，换热主体61的至少部分设于第一腔室7212内，且与电子元件71导热连接，安装板76用于隔挡散热器6上的冷凝水流入第二腔室7214。
通过在电控盒7内设置将安装腔721间隔开的安装板76，并分别将换热主体61和电子元件71分别设于彼此独立的第一腔室7212和第二腔室7214内，可以将电子元件71与冷凝水完全隔绝，进而避免电子元件71接触冷凝水而发生短路或者损坏。
进一步地，可以采用散热固定板74将电子元件71与换热主体61间接连接。
具体来说，可以在安装板76与散热固定板74对应的位置处开设避让孔762，散热固定板74连接于换热主体61并封堵避让孔762，电子元件71设于散热固定板74背离换热主体61的一侧。如此，可 以利用散热固定板74将电子元件71和换热主体61导热连接，并可以利用散热固定板74将第一腔室7212和第二腔室7214间隔开，以避免冷凝水经避让孔762流动至设有电子元件71的第二腔室7214内，进而可以防止冷凝水与电子元件71接触。
进一步地，如果换热主体61上产生了较多的冷凝水，冷凝水积聚后会在重力的作用下下落，滴落的冷凝水容易溅射，进而为电控盒7内的电路带来隐患，而且较为分散的冷凝水也不利于排出电控盒7。
因此，如图35所示，可以在电控盒7内设置导流板77，导流板77设置于散热器6的下侧，用于收集自散热器6滴落的冷凝水。导流板77的设置，不仅可以缩小冷凝水滴落的高度，避免冷凝水滴溅射，而且导流板77也对冷凝水具有一定的积聚作用，便于将冷凝水汇流后一起排出电控盒7。
如图35所示，导流板7固定于电控盒7的底板723上，导流板77的一端连接于底板723，导流板77的另一端向第一腔室7212内部延伸，且散热器6沿竖直方向的投影落在导流板77的内部。如此，可以保证自散热器6上滴落的冷凝水均位于导流板77上，避免冷凝水滴落至电控盒7的其他位置处。
可以理解地，散热器6还可以设置于安装板76上，此时，导流板77的一端连接于安装板76，导流板77的另一端向第一腔室7212内部延伸，且散热器6沿竖直方向的投影落在导流板77的内部。
进一步地，如图36所示，为了便于导流板77上的冷凝水及时排出电控盒7，还可以在盒体72的底壁上开设排水口725，并将导流板77相对盒体72的底壁倾斜设置，冷凝水经导流板77导流后经排水口725排出盒体72。
具体来说，可以在电控盒7的周向侧板724上开设排水口725，导流板77连接于安装板76或者盒体72的底板723，并向排水口725的方向倾斜设置，冷凝水滴落在导流板77上以后，会沿倾斜的导流板77汇聚至排水口725的位置处，进而自排水口725排出电控盒7。
其中，排水口725的数量和大小可以根据冷凝水的多少灵活设置，本申请实施例不做具体限定。
在本实施例中，可以将换热主体61中的冷媒流的流向沿水平方向设置，即换热主体61的延伸方向沿水平方向设置，一方面可以缩短冷凝水在换热主体61上的流动路径，使得冷凝水在重力的作用下尽快滴落至导流板77上，以便于冷凝水及时排出电控盒7，避免与设于安装腔721内的电子元件71接触；另一方面也可以避免导流板77与换热主体61产生干涉，从而可以设置相对较长的换热主体61，提升散热器6的换热效率。
在另一个实施例中，如图37所示，在从导流板77的中部区域到两端的方向上，导流板77沿竖直方向的高度逐渐变低，以使得滴落在导流板77上的冷凝水向导流板77的两端流动。即导流板77设置成倒V形，此种方式，能够降低导流板77沿竖直方向的整体高度，避免导流板77与电控盒7内的其他部件产生干涉，而且也能够快速排出散热器6滴落在导流板77上的冷凝水。
进一步地，如图37所示，盒体72设置有分别与导流板77两端位置对应的第一排水口771和第二排水口772，以排出流动至导流板77两端的冷凝水。滴落在导流板77上的冷凝水向导流板77的两端流动，并经第一排水口771和第二排水口772排出盒体72。
在又一个实施例中，如图38所示，在从导流板77的中部区域到两端的方向上，导流板77沿竖直方向的高度逐渐变高，以使得滴落在导流板77上的冷凝水向导流板77的中部区域流动。即导流板77可以呈V形设置，此种方式，能够使冷凝水通过导流板77汇聚到导流板的中部区域，并从中部区域排出。
进一步地，如图38所示，盒体72设置有与导流板77的中部区域位置对应的排水口725，以排出流动至导流板77的中部区域的冷凝水，此种方式，利于冷凝水的收集与排放。
上述排水口725、第一排水口771和第二排水口772的数量和大小可以根据冷凝水的多少灵活设置，本申请实施例不做具体限定。
值得注意的是，上述导流板77可以设置在以其他安装方式安装于电控盒7且用于对电控盒7内的电子元件71进行散热的散热器6的下方，而并不局限于上文描述的实施例。
8.散热器上游设置电子元件，下游设置散热翅片
如图39所示，盒体72设有安装腔721，换热主体61的至少部分设于安装腔721内；电子元件71于第一位置处与换热主体61导热连接，散热翅片65于第二位置处与换热主体61导热连接，其中第一位置和第二位置沿换热主体61的冷媒流的流向彼此间隔设置。如上文所描述的，此处所提到的冷媒流可以是图1-4所示的空调系统中主路冷媒流，也可以是辅路冷媒流。
本实施例通过将电子元件71和散热翅片65沿换热主体61的冷媒流的流向彼此间隔设置，可以充分利用换热主体61上的空间，不仅可以利用换热主体61对电子元件71进行散热，而且也可以利用散热翅片65降低电控盒7的安装腔721内的温度，进而保护设置于安装腔721内的电子元件71。
进一步地，换热主体61包括沿冷媒流的流向彼此间隔设置的第一端61a和第二端61b，其中换热主体61的温度在从第一端61a到第二端61b的方向上逐渐降低，即第一端61a的温度大于第二端61b的温度。第一位置相较于第二位置靠近第一端61a设置。
具体来说，由于换热主体61工作的过程中，换热主体61表面的温度会随着冷媒流的流动方向产生变化，进而形成温度较高的第一端61a和温度较低的第二端61b，由于温度较高的第一端61a与安装腔721内的热空气之间的温差较小，不容易产生冷凝水，故而，可以将电子元件71靠近第一端61a设置，即，将第一位置设置在靠近第一端61a的位置处。由于温度较低的第二端61b与安装腔721内的热空气之间的温差较大，容易产生冷凝水，故而，可以将散热翅片65靠近第二端61b设置，一方面温度较低的散热翅片65可以保证散热翅片65与热空气具有足够大的温差，便于对电控盒7进行散热，另一方面散热翅片65上冷凝形成的冷凝水也会在热空气的作用下蒸发，冷凝水蒸发吸热，以进一步降低冷媒流的温度，提升散热器6的换热效果。
8.1加速散热气流的流动速度
进一步地，如图40所示，还可以在电控盒7内设置散热风扇78，散热风扇78用于在电控盒7内形成作用于散热翅片65上的散热气流，如此，可以加速散热气流的流动速度，进而提升换热效果。
可选地，散热风扇78可以设置在靠近散热翅片65的位置处，以直接作用于散热翅片65。
或者，如图40所示，还可以在电控盒7内设置安装板76，安装板76设于安装腔721内，以使得安装腔721形成位于安装板76两侧的第一腔室7212和第二腔室7214，安装板76上间隔开设有第一通风口764和第二通风口766，以使得第一腔室7212内的气体经第一通风口764流入第二腔室7214，第二腔室7214内的气体经第二通风口766流入第一腔室7212，换热主体61的至少部分位于第一腔室7212内，电子元件71和散热风扇78设于第二腔室7214内。
通过采用安装板76将安装腔721分隔形成两个相互独立的第一腔室7212和第二腔室7214，可以在第一腔室7212和第二腔室7214内形成循环流动的气流，以增大与设于第一腔室7212内的散热翅片65接触的风量，并且可以便于降温后的气流为设置于第二腔室7214内的电子元件71散热，避免气体混流，以提升散热翅片65的散热效率。
其中，设置于第二腔室7214内的散热风扇78用于加速第二腔室7214内的空气的流动速度，进而加快空气在第一腔室7212和第二腔室7214之间的循环速度，提升电控盒7的散热效率。
进一步地，可以设置散热气流流经散热翅片65时的流动方向垂直于冷媒流的流向。
如图39和图40所示，当换热主体61中的冷媒流沿水平方向时，可以设置散热气流沿竖直方向流动，以避免散热气流流动至电子元件71的位置处。
具体来说，可以将第一通风口764和第二通风口766沿竖直方向间隔设置于散热翅片65的相对两侧。其中，第一通风口764和第二通风口766的数量和排布密度可以根据需要进行设置。
或者，当换热主体61中的冷媒流沿竖直方向时，可以设置散热气流沿水平方向流动，以避免散热气流流动至电子元件71的位置处。或者，散热气流的流向还可以与冷媒流的流向设置为沿其他两个相互垂直的方向，本申请实施例不做具体限定。
进一步地，当采用竖直方向设置的第一通风口764和第二通风口766时，可以将第一通风口764设置在第二通风口766的上部，以使得经第二通风口766进入第一腔室7212中的热空气自动上升至换热主体61的位置处，并与换热主体61进行热交换。
可选地，可以将散热风扇78设置在靠近第一通风口764的位置处，以便于位于第一腔室7212顶部的冷空气及时进入第二腔室7214，并且散热风扇78可以为冷空气加速，以提升电子元件71的散热效率。
9.内部环流
通常情况下，为了对电控盒7进行降温，通常在电控盒7的盒体72上开设与安装腔721连通的散热孔，以通过散热孔与外界空气自然对流进行换热，进而对电控盒7进行降温。但是采用在盒体72上开设散热孔的方式，会降低电控盒7的密封性，外界的水份、灰尘等杂质会经散热孔进入安装腔721内，进而损坏设置于安装腔721内的电子元件。
本实施例为了解决上述问题，可以将电控盒7的盒体72设置为密封结构。具体来说，请参阅图41，电控盒7包括盒体72、安装板76、散热器6、电子元件71以及散热风扇78。
其中，盒体72设有安装腔721，安装板76设于安装腔721内，以使得安装腔721形成位于安装板76两侧的第一腔室7212和第二腔室7214，安装板76上设有间隔的第一通风口764和第二通风口766，第一通风口764和第二通风口766连通第一腔室7212和第二腔室7214；散热器6至少部分设于第一腔室7212内；电子元件71设于第二腔室7214内，并与散热器6导热连接；散热风扇78用于送风，以使得第一腔室7212内的气体经第一通风口764流入第二腔室7214。
本实施例通过将散热器6的至少部分设于第一腔室7212内，将电子元件71和散热风扇78设于第二腔室7214内，并在安装板76上开设间隔的连通第一腔室7212和第二腔室7214的第一通风口764和第二通风口766，如此，电子元件71发热使得第二腔室7214内的空气的温度较高，散热风扇78将热空气送入第二通风口766，由于热空气的密度较小，热空气自然上升以与设于第一腔室7212内的散 热器6接触，散热器6用于对热空气进行降温形成冷空气，冷空气自第一通风口764流入第二腔室7214内，散热风扇78用于对冷空气加速，以利用冷空气对设于第二腔室7214内的电子元件71进行降温，与电子元件71热交换后的冷空气的温度升高，温度升高后的冷空气进一步在散热风扇78的作用下继续进入第二通风口766，以此循环，进而通过内循环的方式为设于电控盒7内的电子元件71进行降温，相比于采用在电控盒7上开设散热孔的方式进行降温，本申请中的电控盒7为全密闭电控盒7，可以有效解决防水、防虫、防尘、防潮等问题，进而提升电控盒7的电控可靠性。
在另一实施例中，如图42所示，散热风扇78所在的平面与安装板76所在的平面垂直，散热风扇78的背风侧朝向第一通风口764设置。
具体来说，散热风扇78可以设置于安装板76朝向第二腔室7214的一侧，散热风扇78的转轴方向与安装板76所在的平面平行，散热风扇78的背风侧指的是散热风扇78的进风侧。在本实施例中，可以将散热风扇78设置于第一通风口764和电子元件71之间，经第一通风口764进入第二腔室7214内的冷空气经散热风扇78加速后流出，以提升冷空气的流动速度，提升电控盒7的散热效率。
在另一实施例中，如图43所示，散热风扇78还可以设置为离心风扇。
其中，离心风扇是依靠输入的机械能，提高气体压力并排送气体的机械。离心风扇的工作原理是利用高速旋转的叶轮将气体加速。故而，在本实施例中，通过将散热风扇78设置为离心风扇，一方面可以获得高速的冷空气，提升电子元件71的散热效率，另一方面，离心风扇也可以简化散热风扇78的结构，并提升安装效率。
还可以在安装板76上间隔设置导风板(图中未示出)，并在导风板之间形成导风流道，以用于为散热风扇78吹出的空气导向。
例如，可以在分散设置的电子元件71之间设置两个平行间隔的导风板，导风板的延伸方向沿电子元件71的间隔方向，以在两个导风板之间限定出沿电子元件71的间隔方向的导风流道。散热风扇78吹出的冷空气首先流动至部分电子元件71的位置处，以对电子元件71进行散热，经过部分电子元件71后的空气进一步经导风流道流动至另一部分电子元件71的位置处，以用于对另一部分电子元件71进行散热，如此，可以使得电子元件71热量散失的更加均衡，避免局部电子元件71的温度过高，发生损坏。
其中，可以将散热器6设置于电控盒7的内部，即，可以将换热主体61设于第一腔室7212内，以用于对第一腔室7212中的空气进行降温。
或者，还可以将散热器6设置于电控盒7的外部，并将散热器6的至少部分延伸设置于第一腔室7212内。例如，在散热器6包括换热主体61、集成管路组件62以及散热翅片65的情况下，可以在盒体72上开设有与第一腔室7212连通的装配口(未图示)。此时，将换热主体61连接于盒体72的外侧壁，散热翅片65连接于换热主体61上，并经装配口插置于第一腔室7212内。
其中，本实施例中的散热器6与电控盒7的配合方式与上述实施例中的相同，请参照上述实施例中的描述，此处不再赘述。
如图43所示，可以将电子元件71设置在散热风扇78的送风范围内，以便于散热风扇78直接作用于电子元件71以进行降温。
其中，电子元件71例如可以包括共模电感711、电抗712和电容713等发热量较大的主发热元件，以及风机模块714等发热量较小的次发热元件。为了提升主发热元件的散热效率，可以设置主发热元件与第一通风口764之间的距离小于次发热元件与第一通风口764之间的距离，即可以将发热量较大的主发热元件设置在靠近第一通风口764的位置处，将发热量较小的次发热元件设置在远离第一通风口764的位置处，以使得经第一通风口764进入的温度较低的空气首先作用于发热量较大的主发热元件，以提升发热量较大的主发热元件的散热效率。
可选地，可以将第二通风口766开设在散热风扇78送风的末端，并开设在靠近发热量较大的电子元件71的位置处，一方面可以扩大散热风扇78的辐射范围，提升第二腔室7214内空气的循环效率，另一方面也可以使得与发热量较大的电子元件71换热后的热空气及时排出第二腔室7214，避免提升整个第二腔室7214的温度。
进一步地，可以将第二通风口766设置在靠近第一通风口764的位置处，以缩短空气在第二腔室7214内的循环路径，降低空气流动阻力，提升空气的循环效率，进而提升电控盒7的散热效率。
进一步地，第一通风口764和第二通风口766的尺寸大小也可以根据电子元件71的排布情况进行设置。
具体来说，第二通风口766的数量可以具有多个，多个第二通风口766分别设于安装板76的不同位置处。设于发热量较大的电子元件71位置处的第二通风口766的尺寸可以设置的相对较大，第二通风口766的数量也可以设置的相对较多，且多个第二通风口766的分布密度可以设置的相对较大。设于发热量较小的电子元件71位置处的第二通风口766的尺寸可以设置的相对较小，第二通风口766的数 量也可以设置的相对较少，且多个第二通风口766的分布密度可以设置的相对较小。
进一步地，可以设置第一通风口764的尺寸大于第二通风口766的尺寸，以提升回风风量，提高散热风扇78的效率。
10.自然对流
请参阅图44和图45，在本实施例中，电控盒7包括盒体72、安装板76、散热器6和主发热元件715。
其中，盒体72设有安装腔721，安装板76设于安装腔721内，以使得安装腔721形成位于安装板76两侧的第一腔室7212和第二腔室7214，安装板76上设有沿竖直方向间隔的第一通风口764和第二通风口766；散热器6至少部分设于第一腔室7212内；主发热元件715设于第二腔室7214内；第一通风口764和第二通风口766连通第一腔室7212和第二腔室7214，以利用主发热元件715和散热器6的温差在第一腔室7212和第二腔室7214之间形成循环流动的散热气流。
具体来说，主发热元件715设于第二腔室7214内，主发热元件715工作产生的热量导致第二腔室7214内的温度升高，由于热空气的密度较小，热空气自然上升并经第二腔室7214顶部的第一通风口764进入第一腔室7212内，热空气接触到散热器6后与散热器6进行热交换，热空气的温度降低，密度增大，在重力的作用下自然下沉至第一腔室7212的底部，并经第二通风口766进入第二腔室7214内，用于对设于第二腔室7214中的主发热元件715降温，与主发热元件715热交换后的热空气进一步上升至第一通风口764的位置处，以此形成在第一腔室7212和第二腔室7214之间的内循环气流。
本实施例通过在安装板76上开设连通第一腔室7212和第二腔室7214的第一通风口764和第二通风口766，并将第一通风口764和第二通风口766沿竖直方向设置，可以利用空气的自身重力在第一腔室7212和第二腔室7214之间循环流动，以用于对设于第二腔室7214内的电子元件71降温，并可以降低电控盒7的整体温度，相比于采用散热风扇78进行送风的方案，本实施例中的电控盒7的结构更加简洁，进而可以提升电控盒7的装配效率并降低电控盒7的生产成本。
进一步地，可以将散热器6沿重力方向设于主发热元件715的上侧，即将散热器6设置在靠近第一腔室7212顶部的位置处，将主发热元件715设置在靠近第二腔室7214底部的位置处。通过此种设置方式，可以缩小散热器6与第一通风口764之间的距离，使得经第一通风口764进入第一腔室7212的热空气快速与散热器6接触进行降温，并在重力的作用下自然下沉。通过缩小主发热元件715与第二通风口766之间的距离，使得经第二通风口766进入第二腔室7214的热空气快速与主发热元件715接触进行升温，并在浮力的作用下自然上升，如此，可以提升电控盒7内的气流的循环速度，提升散热效率。
进一步地，如图45所示，还可以在电控盒7内设置次发热元件716，次发热元件716设于第二腔室7214内，并与换热主体61导热连接，其中，次发热元件716的发热量小于主发热元件715的发热量。
具体来说，在本实施例中，可以将发热量较大的主发热元件715设置在靠近第二通风口766的位置处，一方面可以使得经第一腔室7212进入的冷空气首先与发热量较大的电子元件71接触，提升电子元件71的散热效率，另一方面也可以使得冷空气和发热量较大的电子元件71之间具有较大的温差，使得冷空气可以迅速升温，进而在浮力的作用下迅速上升。将发热量较小的次发热元件716设置在换热主体61上，并与换热主体61接触，可以利用换热主体61直接对发热量较小的电子元件71进行降温。如此，通过将发热量较大的主发热元件715和发热量较小的次发热元件716分区域设置，可以使得电子元件71的分布合理，并可以充分利用电控盒7的内部空间。
可选地，次发热元件716通过散热固定板74连接于换热主体61上，以提升次发热元件716的装配效率。
其中，次发热元件716与换热主体61的连接方式可以与上述实施例中的相同，具体参照上述实施例中的描述，此处不再赘述。
或者，还可以将散热器6设置于电控盒7的外部，并将散热器6的至少部分延伸设置于第一腔室7212内。
其中，散热器6与电控盒7的配合方式与上述实施例中的相同，请参照上述实施例中的描述。
11.管路上设置引流套
如图46和图47所示，本实施例的空调系统1包括散热器6、管路710和引流套79。
管路710用于连接散热器6，以向散热器6提供冷媒流或者收集散热器6内流出的冷媒流。具体地而言，管路710连接散热器6的集流管组件。
其中，管路710可以包括输入管路和输出管路，输入管路用于向散热器6提供冷媒流，输出管路用于收集散热器6内冷媒流。
引流套79套设于管路710上，用于对管路710上形成的冷凝水或者流经管路的冷凝水进行引流。通过该引流套79能够对管路710上的冷凝水进行导流，且具有保护管路710的作用，提高空调系统1的可靠性。
具体地，如图48所示，引流套79包括套体791和凸缘792。
套体791上设置有插置孔793和排水槽708，插置孔793用于容纳管路710。插置孔793的数量和尺寸可以根据管路710的分布及尺寸情况进行设置。比如，在图46所示的实施例中，插置孔793的数量可以为2个，在其他实施例中，插置孔793的数量可以为1个或者3个等。
套体791可以采用柔性材质，例如，热塑性聚氨酯弹性体橡胶，以对管路710进行保护，防止管路710在振动时与电控盒钣金相接触磨损。
凸缘792设置于套体791的端面，并位于插置孔793外围，进而与套体791配合形成集水槽794，集水槽794用于收集管路710上的冷凝水，排水槽708与集水槽794连通，用于排出集水槽794内的冷凝水。空调系统在运行时，冷凝水顺管路710流到引流套79的集水槽794内，再通过套体791上的排水槽708排出。
如图48所示，凸缘793的外侧壁与套体791的外侧壁平齐，以增大集水槽794的体积，从而更有利于冷凝水的收集。
管路710可以沿重力方向设置，套体791包括相背设置的上端面和下端面，凸缘792和集水槽794设置于套体791的上端面，排水槽708连通套体791的上端面和下端面。管路710上的冷凝水能够在重力的作用下流到集水槽794中，然后通过与集水槽794连通的排水槽708将冷凝水排出。此种方式，能够对管路710上的冷凝水实现自动排放。在其他实施例中，管路710也可以倾斜设置，以适应不同的应用场景。
如图48所示，排水槽708开设于套体791的侧壁上，并进一步连通插置孔793和套体791的外侧面，以允许管路710经排水槽708嵌入插置孔793。此种设计，一方面，可以通过排水槽708将引流套79套设于管路710上，便于引流套79与管路710的装配，另一方面，还可以通过排水槽708排出集水槽794内的冷凝水，简化引流套79的结构。其中，排水槽708的大小可以根据冷凝水的数量进行选择设置，在此不做具体限定。
可选地，凸缘792在排水槽708所在一侧具有一开口，以允许管路710经开口进入集水槽794，此种方式，便于引流套79的装配。
如图46和50所示，空调系统1进一步包括电控盒7，电控盒7包括盒体72，散热器6设置于盒体72内。可选地，盒体72上设置排水口725，引流套79嵌设于排水口725内。电控盒7内的冷凝水可以收集至引流套79的集水槽794内，并通过排水槽708排出。如此，不仅能够利于冷凝水的排放，而且可以通过该引流套79对电控盒7进行密封，以提高电控盒7的可靠性。
套体791和凸缘792与盒体72抵接，排水槽708和凸缘792上的开口位于套体791和凸缘792与盒体72相抵接一侧，以使得盒体72从引流套79的侧向封堵排水槽708和开口。此种方式，能够提高电控盒7的密封性，减少与电控盒7与外界连通的面积。
在另一个实施例中，如图49所示，本实施例与图48所示的实施例的区别在于，插置孔793的内部可以设置还有多个凸肋796，多个凸肋796绕管路710间隔设置，并与管路710抵接，以在凸肋796之间进一步形成排水槽709。集水槽794连通排水槽709，且集水槽794内收集的冷凝水也可以通过此排水槽709排出。图49所示实施例中，引流套79同时设置排水槽708和排水槽709，通过此种方式，更利于集水槽794内冷凝水的排出，防止集水槽794内的冷凝水外溢。其中，凸肋796可以连接套体791的上端面和下端面，凸肋796的数量可以为2个、3个、4个或者5个等，凸肋796的延伸方向与管路710的延伸方向相同，以利于冷凝水的排放。
凸肋796可以与套体791一体成型设置，以方便加工，且使引流套79的结构更加可靠。在其他实施例中，凸肋796也可以粘接于插置孔793的内表面，凸肋796的数量可以根据实际需要排放冷凝水的数量进行选择设置，本申请中不做具体限定。
可以理解的是，在其他实施例中，引流套79可以只设置排水槽709，而不设置排水槽708。此种方式，也能够实现集水槽794内冷凝水的排放，且使引流套79的结构更加简单。
如图49所示，套体791上还可以设置有固定槽797，固定槽797用于与盒体72卡合，以固定引流套79。可选地，固定槽797可以设置于套体791设置有排水槽708的一侧，以便于引流套79的安装。通过固定槽797可以实现对引流套79的固定，防止引流套79在管路710上滑动，同时，引流套79可以对管路710进行固定，防止管路710在外力的作用下发生倾斜，提高空调系统1的可靠性。
上述实施例中，空调系统1的管路710上套设有引流套79，能够对管路710上的冷凝水进行引流，对管路710进行保护，且可对电控盒7进行密封，提高空调系统1的可靠性。
以上各实施例中的结构可以相互组合使用，并且，可以理解地，上述实施例中的方案除了可以采用前文所述的散热器6外，还可以采用其它种类的散热器6，本申请实施例不做具体限定。
以上所述仅为本申请的实施方式，并非因此限制本申请的专利范围，凡是利用本申请说明书及附图内容所作的等效结构或等效流程变换，或直接或间接运用在其他相关的技术领域，均同理包括在本申 请的专利保护范围内。

Claims (15)

  1. 一种换热器，其特征在于，所述换热器包括：
    换热主体及集流管组件，所述集流管组件用于向所述换热主体提供冷媒流，所述换热主体包括并列且间隔设置的至少两个板体组件；
    散热翅片，设置于至少两个所述板体组件上，所述散热翅片与所述换热主体导热连接；
    固定板，同时覆盖于至少两个所述板体组件上的散热翅片背离所述板体组件的一侧，以形成散热风道。
  2. 根据权利要求1所述的换热器，其特征在于，所述固定板包括顶面板和至少一侧面板，所述顶面板同时覆盖于至少两个所述板体组件上的散热翅片背离所述板体组件的一侧，所述侧面板与所述顶面板弯折连接，且向所述板体组件延伸。
  3. 根据权利要求2所述的换热器，其特征在于，所述侧面板的数量为两个，两个所述侧面板沿所述至少两个板体组件的间隔方向的垂直方向间隔设置，所述顶面板分别连接两个所述侧面板，以形成容置空间，所述散热翅片位于所述容置空间内。
  4. 根据权利要求2所述的换热器，其特征在于，所述散热翅片的数量为至少两个，每个所述散热翅片设置于对应的所述板体组件上，所述至少两个散热翅片沿所述至少两个板体组件的间隔方向彼此间隔分布。
  5. 根据权利要求4所述的换热器，其特征在于，所述散热翅片的数量与所述板体组件的数量相等，每个所述散热翅片设置于对应的一个所述板体组件上。
  6. 根据权利要求1所述的换热器，其特征在于，所述散热翅片为一体式设置，并设置于所述至少两个板体组件上。
  7. 根据权利要求6所述的换热器，其特征在于，所述散热翅片沿所述板体组件延伸方向的垂直方向上的宽度大于或者等于所述换热主体的宽度。
  8. 根据权利要求1所述的换热器，其特征在于，所述固定板的沿所述至少两个板体组件的间隔方向的两端开放，以使得所述散热风道内的气流沿所述至少两个板体组件的间隔方向流动。
  9. 根据权利要求8所述的换热器，其特征在于，所述冷媒流的流动方向垂直于所述至少两个板体组件的间隔方向。
  10. 根据权利要求1所述的换热器，其特征在于，每个所述板体组件包括层叠设置的第一板体和第二板体，所述第一板体上设置供第一冷媒流流动的多个第一微通道，所述第二板体上设置有供第二冷媒流流动的多个第二微通道，所述第二冷媒流从所述第一冷媒流吸热，以使得所述第一冷媒流过冷，或者所述第一冷媒流从所述第二冷媒流吸热，以使得所述第二冷媒流过冷。
  11. 根据权利要求10所述的换热器，其特征在于，所述换热器还包括连接片，所述连接片夹置于所述第一板体和所述第二板体之间，所述连接片的两侧设置有焊料，所述焊料用于将所述连接片与所述连接片两侧的所述第一板体和所述第二板体焊接固定。
  12. 根据权利要求11所述的换热器，其特征在于，所述连接片为金属箔片。
  13. 根据权利要求1所述的换热器，其特征在于，所述换热主体内设置有至少两组微通道，所述微通道用于供冷媒流流动；
    所述集流管组件包括总集流管和隔流板，所述隔流板设置于所述总集流管内，以使得所述总集流管形成与所述至少两组微通道对应的至少两组集流管；
    其中，所述至少两组微通道贯穿所述总集流管的管壁并与对应的所述集流管连通。
  14. 一种电控盒，其特征在于，所述电控盒包括盒体和如权利要求1-13任意一项所述的换热器，所述换热器与所述电控盒相连，所述换热器用于为所述电控盒进行散热。
  15. 一种空调系统，其特征在于，所述空调系统包括压缩机、室外换热器、室内换热器和如权利要求1-13任意一项所述的换热器，所述压缩机通过所述连接管路在所述室外换热器和所述室内换热器之间提供循环流动的冷媒流，所述换热器设置在所述室外换热器和所述室内换热器之间，并与所述连接管路相连通。
PCT/CN2021/122412 2021-02-08 2021-09-30 换热器、电控盒及空调系统 Ceased WO2022166235A1 (zh)

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