WO2021018126A1 - 换热器和换热系统 - Google Patents

换热器和换热系统 Download PDF

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Publication number
WO2021018126A1
WO2021018126A1 PCT/CN2020/105114 CN2020105114W WO2021018126A1 WO 2021018126 A1 WO2021018126 A1 WO 2021018126A1 CN 2020105114 W CN2020105114 W CN 2020105114W WO 2021018126 A1 WO2021018126 A1 WO 2021018126A1
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WO
WIPO (PCT)
Prior art keywords
heat exchange
header
heat exchanger
exchange tube
tube
Prior art date
Application number
PCT/CN2020/105114
Other languages
English (en)
French (fr)
Inventor
杨振波
祁照岗
许伟东
黄宁杰
Original Assignee
浙江三花智能控制股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 浙江三花智能控制股份有限公司 filed Critical 浙江三花智能控制股份有限公司
Priority to EP20848620.9A priority Critical patent/EP3982054B1/en
Publication of WO2021018126A1 publication Critical patent/WO2021018126A1/zh
Priority to US17/552,888 priority patent/US12111122B2/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B60H1/00278—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit for the battery
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00899—Controlling the flow of liquid in a heat pump system
    • B60H1/00907—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant changes and an evaporator becomes condenser
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00899—Controlling the flow of liquid in a heat pump system
    • B60H1/00921—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant does not change and there is an extra subcondenser, e.g. in an air duct
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3228—Cooling devices using compression characterised by refrigerant circuit configurations
    • B60H1/32281—Cooling devices using compression characterised by refrigerant circuit configurations comprising a single secondary circuit, e.g. at evaporator or condenser side
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/323—Cooling devices using compression characterised by comprising auxiliary or multiple systems, e.g. plurality of evaporators, or by involving auxiliary cooling devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/05308—Assemblies of conduits connected side by side or with individual headers, e.g. section type radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/22—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0207—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions the longitudinal or transversal partitions being separate elements attached to header boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0243—Header boxes having a circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B60H2001/00307—Component temperature regulation using a liquid flow
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00935—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising four way valves for controlling the fluid direction
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/01—Heaters
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2515—Flow valves

Definitions

  • This application relates to the field of heat exchange, specifically, to heat exchangers and heat exchange systems.
  • the heat exchange industry is developing rapidly, and as one of the main components of air conditioners, heat exchangers also need to be improved and optimized.
  • the heat exchanger consists of a header and a heat exchange tube. When the refrigerant flows into the heat exchanger, it is distributed through the header into the heat exchange tube. However, when the refrigerant is a gas-liquid two-phase in the related heat exchanger, its distribution uniformity needs to be improve.
  • a heat exchanger includes a first header, a heat exchange tube, and a baffle.
  • the first header has a tube wall and a first inner cavity.
  • the first header has a first end and a second end in its length direction, and the partition is disposed in the first inner cavity and extends from the first end along the length of the first header Extend so as to divide the first inner cavity into a first sub-cavity and a second sub-cavity parallel in the length direction of the first header;
  • the heat exchange tube has a tube wall and a refrigerant channel for the refrigerant to flow, so
  • the heat exchange tube has a first end and a second end in its extending direction, and the refrigerant passage extends along the first end to the second end and penetrates the heat exchange tube;
  • the first header The wall of the tube is also provided with a first insertion hole, the partition plate is provided with a second insertion hole corresponding to the first insertion hole, and the first end of the heat
  • a heat exchange system has a compressor, at least one first heat exchanger, a throttling device, and at least one second heat exchanger.
  • the heat exchanger and/or the second heat exchanger are the heat exchangers as described above.
  • the heat exchanger can relatively improve the uniformity of refrigerant distribution during system operation, thereby increasing its heat exchange efficiency.
  • the refrigerant flows into the first heat exchanger through the compressor, and flows into the throttling device after heat exchange occurs in the first heat exchanger, and then the refrigerant flows into the second heat exchanger.
  • the heat exchanger flows into the compressor again after heat exchange occurs in the second heat exchanger.
  • a partition is provided in the first header, and the partition divides the first inner cavity of the first header into two sub-cavities parallel in the length direction of the first header (the first sub-cavity). Cavity and second subcavity), when the gas-liquid two-phase refrigerant flows into the first header, it first enters one of the subcavities (second subcavity) and then enters through the other subcavity (first subcavity) Heat exchange tubes, thereby improving the uniformity of distribution.
  • Fig. 1 is a schematic structural diagram of a heat exchanger according to an embodiment of the present application.
  • Fig. 2 is a schematic cross-sectional view of the heat exchanger along the A-A direction of an embodiment of the application in Fig. 9.
  • Fig. 3 is a schematic cross-sectional view of the heat exchanger along the A-A direction of another embodiment of the present application.
  • FIG. 4 is a schematic cross-sectional view of the assembly structure of heat exchange tubes and fins of the present application.
  • Fig. 5 is a schematic diagram of the structure of the heat exchange tube and the fins in zone B in Fig. 1.
  • Fig. 6 is a schematic cross-sectional view of the assembly of the heat exchange tube and the header in the present application.
  • Fig. 7 is a schematic cross-sectional view of an assembly method of the heat exchange tube and the partition plate of the present application.
  • Fig. 8 is a schematic cross-sectional view of another assembly method of the heat exchange tube and the partition plate of the present application.
  • Fig. 9 is a schematic structural view of the heat exchanger of the embodiment of Figs. 1 to 3 along the height direction of the heat exchange tube.
  • Fig. 10 is a schematic diagram of an exemplary heat exchange system of the present application.
  • Heat exchanger 100, 200 header 10, first header 11, second header 12; first inner cavity 101; second inner cavity 102; baffle 103; partition 104; first jack 105; first end 113; second end 114; third end 213; fourth end 214; first branch 111; second branch 112; first sub-cavity 1110; second sub-cavity 1120; first Subcavity 1111; second subcavity 1112; second insertion hole 1041; first through hole 1042; first surface 1043; second surface 1044;
  • Heat exchange tube 20 first heat exchange tube 21; second heat exchange tube 22; first ends 211, 221; second ends 212, 222; ribs 231; circulation channels 232; protrusions 233; first end surface 2111 2211; second end surface 2121, 2221; first side wall 215; second side wall 216; first top wall 217; first bottom wall 218; third side wall 225; fourth side wall 226; second top wall 227 ; The second bottom wall 228;
  • Fin 30 crest portion 31; trough portion 32; side wall portion 33; crest 311; trough 321;
  • Heat exchange system 1000 compressor 1; first heat exchanger 2; throttling device 3; second heat exchanger 4; reversing device 5.
  • first and second are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features. Thus, the features defined with “first” and “second” may explicitly or implicitly include one or more of these features. In the description of this application, “multiple” means two or more than two, unless otherwise specifically defined.
  • connection should be interpreted broadly unless otherwise clearly specified and limited.
  • it can be a fixed connection or a detachable connection.
  • Connected or integrally connected it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the internal communication between two components or the interaction between two components.
  • connection should be interpreted broadly unless otherwise clearly specified and limited.
  • it can be a fixed connection or a detachable connection.
  • Connected or integrally connected it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the internal communication between two components or the interaction between two components.
  • the "on" or “under” of the first feature of the second feature may include the first and second features in direct contact, or may include the first and second features Not in direct contact but through other features between them.
  • “above”, “above” and “above” the second feature of the first feature include the first feature being directly above and obliquely above the second feature, or it simply means that the level of the first feature is higher than the second feature.
  • the “below”, “below” and “below” the first feature of the second feature include the first feature directly below and obliquely below the second feature, or it simply means that the level of the first feature is smaller than the second feature.
  • the heat exchanger includes a header and a heat exchange tube
  • the header has a tube wall and an inner cavity
  • the heat exchange tube has a tube wall and a refrigerant channel
  • the One end of the heat exchange tube is inserted into the header through a heat exchange tube insertion hole arranged on the tube wall of the header
  • the refrigerant channel of the heat exchange tube is in communication with the inner cavity of the header.
  • the heat exchanger when the heat exchanger is used as an evaporator, the refrigerant entering it may be in a gas-liquid two-phase state, so that the uniformity of the refrigerant entering the heat exchange tube after being distributed through the header is not high.
  • the uniform distribution of the refrigerant in the heat exchanger needs to be improved.
  • the embodiment of the present application provides a heat exchanger that can relatively improve the uniformity of refrigerant distribution when used in a heat exchange system.
  • the heat exchanger can be used as an evaporator in a heat pump system to improve the uniformity of refrigerant distribution. It is easy to understand that in addition to being used in heat pump systems as outdoor heat exchangers, this heat exchanger can also be used in other air treatments. There is no restriction here.
  • the collector tube used in the heat exchanger is one or more of a circular collector tube, a D-shaped collector tube, an oval tube or a square tube, and the heat exchange tube is a heat exchange flat tube.
  • the headers all have a length direction.
  • the section perpendicular to its length is defined as a cross section, the cross section of the circular header is a ring structure, and its inner diameter is d 1 ;
  • the cross section of the D-shaped header includes a circular arc segment and a straight Section, the cross-section of which is roughly D-shaped, the width of the straight section is d 2 ;
  • the cross-section of the elliptical tube is roughly elliptical, the longer diameter of the ellipse is d 3 ; similarly, the The cross section of the square tube is roughly square, and the length of the wider side of the square is d 4 .
  • the width d of the heat exchange tube satisfies one of the following conditions:
  • the width d of the heat exchange tube is smaller than the inner diameter d 1 of the cross section of the header;
  • the header When the header is a D-shaped tube, the header includes an arc-shaped wall and a straight wall, and the width of the heat exchange tube is smaller than the width d 2 of the straight section of the header;
  • the width of the heat exchange tube is smaller than the inner diameter d 3 of the cross section of the collecting tube;
  • the width of the heat exchange tube is at least smaller than the wider side d 4 of the square tube
  • FIG. 1 is a schematic structural diagram of a heat exchanger according to an embodiment of the present application.
  • Fig. 9 is a schematic structural view of the heat exchanger in Fig. 1 along the height direction of the heat exchange tube.
  • Fig. 2 is a schematic cross-sectional view of the heat exchanger along the A-A direction of an embodiment of the application in Fig. 9. The details are as follows.
  • the heat exchanger 100 of an embodiment of the present application may include a header 10, a plurality of heat exchange tubes 20 and fins 30.
  • the header 10 has an inner cavity (not shown in the figure) for the flow of refrigerant, and the shape of the header is a circular tube.
  • the length direction is the axial direction.
  • the header 10 has two headers, namely a first header 11 and a second header 12, and the first header 11 and the second header 12 are arranged substantially in parallel.
  • the heat exchanger 100 and air generally only undergo heat exchange once, which is often referred to as a single-layer heat exchanger in the industry.
  • the header 10 may also be a D-shaped or square tube, and its specific shape is not limited, as long as its burst pressure meets the needs of the system.
  • the relative position of the header 10 is also not limited, as long as it meets actual installation requirements.
  • the number of the header 10 can also be only one, as long as it meets the heat exchange requirement, and it is not limited here.
  • the header 10 in the embodiment of the present application is a round tube as an example.
  • the heat exchange tube 20 has a plurality of heat exchange tubes 20 each having a length direction, a width direction and a height direction.
  • the heat exchange tubes 20 are arranged along the axial direction of the collecting tube 10 and are arranged substantially in parallel.
  • Each of the plurality of heat exchange tubes 20 has a first end and a second end.
  • the heat exchange tube 20 includes a first heat exchange tube 21 and a second heat exchange tube 22 arranged side by side.
  • the first heat exchange tube 21 has a first end 211 and a second end 212, and the direction in which the first end 211 of the heat exchange tube 21 extends to the second end 212 is the length direction of the heat exchange tube (the X direction in the figure) .
  • the first heat exchange tube 21 has a first top wall 217 and a first bottom wall 218, and the first top wall 217 and the first bottom wall 218 are substantially parallel
  • the height direction of the heat exchange tube may also be referred to as the thickness direction of the heat exchange tube.
  • the first heat exchange tube 21 has a first side wall 215 and a second side wall 216, and the first side wall 215 and the second side wall 216 are substantially opposite to each other. .
  • the first end 211 of the first heat exchange tube 21 has a first end face 2111
  • the second end 212 of the first heat exchange tube 21 has a second end face 2121
  • the first end face 2111 and the second end face 2121 are approximately the same and approximately parallel
  • the first heat exchange tube 21 also has a channel 232 for the flow of refrigerant inside.
  • the second heat exchange tube 22 has a first end 221, a second end 222, a first end surface 2211, and a second end surface 2221.
  • the second heat exchange tube 22 also has a corresponding first side wall 215
  • the first end 211 of the first heat exchange tube 21 is connected to the first header 11, and the second end 212 of the first heat exchange tube 21 is connected to the second header 12 is connected.
  • the first end 221 of the second heat exchange tube 22 is connected to the first header 11, and the second end 222 of the second heat exchange tube 22 is connected to The second header 12 is connected.
  • the first heat exchange tube 21 and the second heat exchange tube 22 are arranged substantially in parallel.
  • the heat exchange tube 20 has an inner cavity (not marked in the figure) for the flow of refrigerant, and is connected so that the inner cavity of the heat exchange tube 20 communicates with the inner cavity of the header 10 to form a heat exchanger
  • the refrigerant circulation channel 100 (not shown in the figure), the refrigerant can circulate in the heat exchange channel, and the heat exchange is realized through the heat exchanger 100.
  • the heat exchange tube 20 also called a flat tube in the industry, has an inner cavity for the flow of refrigerant inside.
  • the inner cavity of the heat exchange tube 20 (not shown in the figure) is usually separated by a rib 231 into a plurality of refrigerant circulation channels 232.
  • This arrangement not only increases the heat exchange area of the heat exchange tube 20, and improves the heat exchange efficiency, but also, the inner surface of the heat exchange tube 20 can also be provided with tiny protrusions 233, which can form capillary The effect enhances heat transfer.
  • the protrusion 233 can be sawtooth, wave, triangle, etc. (not marked in the figure), and its shape can be set as required.
  • Adjacent channels 232 are isolated from each other.
  • a plurality of channels 232 are arranged in a row to jointly affect the width of the heat exchange tube 20.
  • the heat exchange tube 20 is flat as a whole, and its length is greater than its width, and its width is greater than its thickness.
  • the heat exchange tube mentioned here is not limited to this type, and may be of other forms. For example, adjacent channels may not be completely isolated. For another example, all channels can be arranged in two rows, as long as the width is still greater than the thickness.
  • the first header 11 and the second header 12 both have tube walls (not labeled), the first header 11 has a first inner cavity 101, and the second header 12 has a second Internal cavity 102.
  • the axial direction defining the first header 11 and the second header 12 is the length direction of the header (ie the Z direction in the figure), and the first header 11 has a lengthwise direction
  • the first end 113 and the second end 114 of the second header 21 are provided with third ends 213 corresponding to the first end 113 of the first header 11 at both ends in the length direction of the second header 21 And the fourth end 214 corresponding to the second end 114 of the first header 11.
  • the first inner cavity 101 of the first header 11 is provided with a baffle 103 and a partition 104.
  • the baffle 103 is substantially perpendicular to the axial direction of the first header 11, and the number of the baffle 103 is at least one. In some other embodiments, the number of the baffle 103 may be multiple. In other embodiments, as shown in FIG. 3, the baffle 103 may not be provided. In other words, the baffle 103 is set according to the requirements of the process. Just set it, so I won’t repeat it here.
  • the baffle 103 divides the first header 11 into a first branch 111 and a second branch 112, and divides the first inner cavity 101 of the first header 11 into a first branch.
  • the partition 104 is provided in the first sub-cavity 1110.
  • the partition 104 extends from the first end 113 of the first header 11 along the axial direction of the first header 11 toward the baffle 103, and the partition 104 connects the first
  • the sub-cavity 1110 is divided into a first sub-cavity 1111 and a second sub-cavity 1112.
  • One end of the partition 104 is connected to the first end 113, and the other end of the partition 104 is connected to the baffle 103.
  • the partition 104 is provided with a through hole 1042, and the through hole 1042 communicates with the first subcavity 1111 and the second subcavity 1112.
  • the tube walls of the first header 11 and the second header 12 are also provided with a first insertion hole 105 for inserting the heat exchange tube 20, and the first insertion hole 105 penetrates the first collector.
  • the flow tube 11 and the tube wall of the second header 12, the first insertion hole 105 has a plurality of and are arranged parallel to each other, the first ends 211, 221 of the heat exchange tube 20 can pass through the first
  • the insertion hole 105 is inserted into the first header 11.
  • the first inner cavity 101 of the first header 11 is in communication with the refrigerant channel 232 of the heat exchange tube 20.
  • the partition 104 is provided with a second insertion hole 1041 for inserting the heat exchange tube 20, the second insertion hole 1041 has a plurality of and is arranged parallel to each other, and the second insertion hole 1041 is arranged through the partition 104 ,
  • the first ends 211, 221 of the heat exchange tube 20 pass through the first insertion hole 105 and are inserted into the second insertion hole 1041, along the insertion direction of the heat exchange tube (ie the X direction in the figure),
  • the projection of the first jack 105 is substantially the same as and overlaps with the projection of the second jack 1041, and the projection of the second jack 1041 does not overlap with the projection of the through hole 1042.
  • the The two jacks 1041 are staggered from the through holes.
  • the refrigerant passage 232 of the heat exchange tube 20 is in communication with the first subcavity 1111 and the second subcavity 1112 of the first header 11, wherein the heat exchange tube 20
  • the communicating part between the refrigerant channel 232 and the first subcavity 1111 of the first header 11 refers to the communication with the first subcavity 1111.
  • the heat exchanger 100 further includes a first inlet and outlet 1071 and a second inlet and outlet 1072.
  • the first inlet and outlet 1071 are arranged at the first end 113 of the first header 11,
  • the second inlet and outlet 1072 are arranged at the second end 114 of the first header 11.
  • the first inlet and outlet 1071 are in communication with the second sub-cavity 1112.
  • the refrigerant flows into the second sub-chamber 1112 through the first inlet and outlet 1071, and then passes through the partition plate 104.
  • the through hole 1042 flows into the first sub-chamber 1111, and then flows into the refrigerant passage 232 of the heat exchange tube 20.
  • the walls of the first branch 111 and the second branch 112 are each provided with a plurality of the first insertion holes 105, and the first ends 211, 221 of the heat exchange tube 20 are inserted into the first set.
  • the first insertion hole 105 of the flow tube 11 is inserted into the second insertion hole 1041.
  • the partition 104 has a first surface 1043 and a second surface 1044 that are oppositely disposed, and the first surface 1043 is the partition 104 facing the first sub The surface of the cavity 1111, the second surface 1044 is the surface of the partition 104 facing the second sub-cavity 1112.
  • a gap 106 is formed between a part of the inner wall surface of the first header 11 and the second surface 1044 of the partition 104.
  • the heat exchange tube 20 is inserted into the outer side wall portion of the second sub-cavity 1112, the first header 11 forms the inner wall surface portion of the second sub-cavity 1112, and the partition wall 104
  • a gap 106 is formed between the second surfaces 1044.
  • the heat exchange tube 20 connected to the first branch pipe 111 is the first process heat exchange tube 201
  • the heat exchange tube 20 connected to the second branch pipe 112 is the second process heat exchange tube 202.
  • the heat exchanger When a refrigerant flows in 100, the refrigerant flows into the second sub-cavity 1112 through the first inlet and outlet 1071. After encountering the resistance of the heat exchange tube 20, it passes through the gaps on both sides of the heat exchange tube 20 under pressure. Due to the limited width of the gap 106, the turbulence effect of the two-phase refrigerant in the second sub-cavity 1112 can be intensified, so that the two-phase refrigerant is uniformly mixed, and then passes through the partition 104.
  • the hole 1042 flows into the inside of the first sub-cavity 1111.
  • the refrigerant flows into the refrigerant passage 232 through the first end 211 of the first process heat exchange tube 201 and then flows into the second header 12, then flows into the refrigerant circulation channel 232 of the second process heat exchange tube 202, and then enters the second sub-cavity 1120 of the first header 11, and passes through the second inlet
  • the outlet 1072 flows out of the heat exchanger 100.
  • the refrigerant exchanges heat with the heat exchanger 100.
  • the heat exchange of the refrigerant in the heat exchanger 100 is a two-process heat exchange.
  • the The heat exchanger 100 is a dual-process heat exchanger.
  • the heat exchanger 100 may also be a heat exchanger with more than two processes, which can be designed according to actual needs.
  • FIG. 3 is a schematic cross-sectional view of a heat exchanger 200 according to another embodiment.
  • the structure of the heat exchanger 200 and the heat exchanger 100 are substantially the same, and the heat exchanger 200 also includes the first set.
  • the difference between the flow tube 11 and the second header 12 is that the first header 11 is not provided with the baffle 103 as shown in FIG. 2, and the partition 104 separates the first
  • the first inner cavity 102 of the header 11 is divided into the parallel first sub-cavity 1111 and the second sub-cavity 1112, and the first ends 211, 221 of the heat exchange tube 20 pass through the tube wall.
  • the first insertion hole 105 on the upper part is inserted into the first header 11, it is then inserted into the second insertion hole 1041 of the partition 104, and the first inlet and outlet 1071 are provided in the first
  • the first end 113 of the header 11 is in communication with the second sub-cavity 1112, the second inlet and outlet 1072 are provided at the fourth end 214 of the second header 12, when the refrigerant flows in In the heat exchanger, the refrigerant flows into the second sub-cavity 1112 through the first inlet and outlet 1071, and the multiple turbulence occurs in the second sub-cavity 1112, and then passes through the partition 104
  • the through hole 1042 flows into the first sub-cavity 1111, and then flows into the refrigerant channel 232 of the heat exchange tube 20 through the first ends 211, 221 of the heat exchange tube 20, and then flows into the refrigerant channel 232 of the heat exchange tube 20.
  • the heat exchanger 200 flows out through the second inlet and outlet 1072.
  • the heat exchanger 200 and the air generally undergo only one heat exchange, which is often referred to as a single-layer heat exchanger in the industry.
  • the distribution structure in the embodiment of the present invention is not limited to single-layer heat exchangers, but can also be used in other multi-layer heat exchangers.
  • the multi-layer heat exchanger can be a heat exchanger with a bent heat exchange tube or
  • the heat exchangers that connect the adjacent collector pipes through the connection module have roughly the same structure, and will not be repeated here. It should be noted that when the multi-layer heat exchanger is a heat exchanger with a bent heat exchange tube, the length direction of the heat exchange tube is the extension direction of the heat exchange tube. In other words, the length direction is not limited to a straight line. direction.
  • FIG. 6 shows a schematic cross-sectional view of the assembly of the first heat exchange tube 21 and the first header 11.
  • FIG. 8 shows a schematic cross-sectional view in which the first heat exchange tube 21 is inserted into the second insertion hole 1041 of the partition 104 of the first header 11. 6 and 8, after the first end 211 of the first heat exchange tube 21 is inserted into the first cavity 101 of the first header 11 through the first insertion hole 105, it passes through the partition
  • the second insertion hole 1041 of the plate 104 is inserted into the partition 104, the first end surface 2111 of the first heat exchange tube 21 penetrates the partition 104, and the first heat exchange tube 21
  • the distance between the first end surface 2111 and the first surface 1043 of the partition 104 is a first distance H 1 , and the first distance H 1 is less than 2 mm. In some other embodiments, the first distance H 1 The size is 1mm. In some other embodiments, the size of the first distance H 1 is 0.5 mm.
  • FIG. 7 is a schematic cross-sectional view of another assembly method of the first heat exchange tube 21 and the partition 104 of this application. 6 and 7, after the first end 211 of the first heat exchange tube 21 is inserted into the first header 11 through the first insertion hole 105, it passes through the second end of the partition 104 The two insertion holes 1042 are inserted into the partition 104, but the first end surface 2111 of the first heat exchange tube 21 does not penetrate the partition 104.
  • the distance between the first end surface 2111 of the first heat exchange tube 21 and the first surface 1043 of the partition 104 is a second distance H 2 , and the second distance H 2 is smaller than the thickness of the partition 104
  • the thickness of the partition 104 may be 1 to 3 mm, and the second distance H 2 may be 2 mm.
  • the size of the second distance H 2 is 1 mm. In some other embodiments, the size of the second distance H 2 is 0.5 mm.
  • the heat exchanger 100 and the heat exchanger 200 of the embodiment of the present application further include fins 30.
  • the surface of the heat exchanger in the related art is coated with functional materials, such as corrosion-resistant materials. Specifically, it is coated on all or part of the outer surface of the entire heat exchanger.
  • the functional material may be Corrosion-resistant materials or moisture-absorbing materials, etc., can be set as required, and will not be repeated here.
  • the fin 30 is a window fin. To illustrate, in other embodiments, the fins may also be fins without opening windows.
  • the shape of the fin can be roughly wave-shaped or profiled.
  • the cross-section of the fin can be a sine wave or an approximate sine wave, or a sawtooth wave, as long as it meets the requirements, and the specific structure is not limited.
  • the fin 30 can be coated with functional materials as required, which is not limited here.
  • the fin 30 in the embodiment of the present application is a corrugated fin, and the fin 30 has a crest portion 31, a trough portion 32, and a side wall portion 33 connecting the crest portion 31 and the trough portion 32.
  • the wave crest portion 31 and the wave trough portion 32 are arranged at intervals in the longitudinal direction of the fin 30, and the side wall portion 33 has a plurality of them.
  • the multiple in the present invention refers to two and more than two, unless otherwise specified.
  • the side wall portion 33 can be provided with or without opening windows, which can be provided according to heat exchange requirements.
  • the shape of the fin 30 can be roughly wavy or profiled.
  • the cross section of the fin can be a sine wave or an approximate sine wave, or a sawtooth wave, as long as it meets the requirements.
  • the specific structure is not limited.
  • the fin 30 has a waveform as a whole, the crest portion 31 and the trough portion 32 are spaced apart, and the fin 30 is disposed between two adjacent heat exchange tubes 20.
  • the crest portion 31 is at least partially in contact with the first heat exchange tube 21, and the trough portion 32 is at least partially in contact with the second heat exchange tube 22.
  • the highest point of the wave crest portion 31 is a wave crest 311, and the lowest point of the wave trough portion 32 is a wave trough 321. That is, the crest part 31 is in contact with the first bottom wall 218 of the first heat exchange tube 21, and the trough part 32 is in contact with the first top wall 227 of the second heat exchange tube 22.
  • the extending direction of the crest portion 31 and the trough portion 32 defining the fin 30 at intervals is the length direction of the fin 30 (the X direction in the figure), which defines the vertical direction between the plane where the crest 311 is located and the plane where the trough 321 is located. It is the height direction of the fin (the Z direction in the figure). It can be seen that the length direction of the fin 30 is the same as the length direction of the heat exchange tube 20 (X direction in the figure), and the width direction of the fin 30 is the same as the width direction of the heat exchange tube 20 ( Figure In the Y direction), the distance between the heat exchange tubes 20 is the height direction of the fin 30 (the Z direction in the drawing).
  • the heat exchange system 1000 at least includes a compressor 1, a first heat exchanger 2, a throttling device 3, and a second heat exchange system. ⁇ 4 ⁇ 5 ⁇ 4 and reversing device 5.
  • the compressor 1 of the heat exchange system 1000 may be a horizontal compressor or a vertical compressor.
  • the throttling device 3 may be an expansion valve.
  • the throttling device 3 may also be other components that have the function of reducing pressure and adjusting the flow rate of the refrigerant. This application does not specifically limit the types of throttling devices. It can be selected according to the actual application environment and will not be repeated here.
  • the heat exchanger 100 described in the present invention can be used in the heat exchange system 1000 as the first heat exchanger 2 and/or the second heat exchanger 4.
  • the compressor 1 compresses the refrigerant, the temperature of the compressed refrigerant rises, and then enters the first heat exchanger 2, and transfers heat to the first heat exchanger 2 through heat exchange with the outside world Outside, the refrigerant passing through the throttling device 3 becomes liquid or gas-liquid two-phase state.
  • the temperature of the refrigerant decreases, and then the lower temperature refrigerant flows to the second heat exchanger 4, and in the second heat exchanger 4 After heat exchange with the outside, it enters the compressor 1 again to realize the refrigerant circulation.
  • the second heat exchanger 4 is used as an outdoor heat exchanger to exchange heat with the air, refer to the above-mentioned examples, and arrange the heat exchanger as needed.

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Abstract

一种换热器（100，200），包括第一集流管（11）、多个换热管（20）和隔板（104），多个所述换热管（20）大致平行设置且沿第一集流管（11）的轴向分布并插置于所述第一集流管（11）。所述隔板（104）将所述第一集流管（11）的第一内腔（101）分隔为第一子腔（1111）和第二子腔（1112），所述换热管（20）的一端与所述第一子腔（1111）连通，所述冷媒进入第一集流管（11）先流入第二子腔（1112），与插入第二子腔（1112）中的换热管（20）作用后形成剧烈的湍流效应，然后通过设置于隔板（104）的通孔（1042）流入所述第一子腔（1111），进而流入换热管（20），从而可相对提高两相冷媒分配的均匀性。

Description

换热器和换热系统
相关申请的交叉引用
本申请要求于2019年8月1日申请的、申请号为201910708413.8、发明名称为“换热器和换热系统”的中国发明专利申请的优先权，该专利申请的相关内容以引用的形式并入本文中。
技术领域
本申请涉及换热领域，具体而言，涉及换热器和换热系统。
背景技术
换热行业迅猛发展，而换热器作为空调的主要组成部分之一，也需要改进和优化设计。换热器包含有集流管和换热管，当冷媒流入换热器时，经集流管分配进入换热管，但是相关换热器中当冷媒为气液两相时其分配均匀性有待提高。
发明内容
根据本申请的一个方面，提供一种换热器，所述换热器包括第一集流管、换热管以及隔板，所述第一集流管具有管壁和第一内腔，所述第一集流管具有于其长度方向的第一端部和第二端部，所述隔板设置于所述第一内腔内且自第一端部沿第一集流管的长度方向延伸从而将所述第一内腔分隔为在第一集流管的长度方向上并行的第一子腔和第二子腔；所述换热管具有管壁和供冷媒流动的冷媒通道，所述换热管具有于其延伸方向的第一端和第二端，所述冷媒通道沿所述第一端向所述第二端延伸并贯穿所述换热管；所述第一集 流管的管壁还设置有第一插孔，所述隔板设有与第一插孔对应的第二插孔，所述换热管的第一端贯穿通过所述第一插孔并插入所述第二插孔；所述隔板设置有通孔，所述通孔与所述第二插孔错位设置，所述通孔连通所述第一子腔和所述第二子腔；所述换热器还包括第一进出口，所述第一进出口设置于所述第一集流管的所述第一端部且与所述第二子腔连通所述第一子腔与冷媒通道连通。
根据本申请的另一方面，提供一种换热系统，所述换热系统具有压缩机、至少一个第一换热器、节流装置和至少一个第二换热器，所述第一换热器和/或所述第二换热器为如上所述的换热器，所述换热器在系统运行时能相对提高冷媒分配的均匀性，进而提高其换热效率，当所述换热系统有冷媒流动时，所述冷媒经所述压缩机流入所述第一换热器，并在所述第一换热器发生热交换之后流入节流装置，而后所述冷媒流入所述第二换热器并在所述第二换热器发生热交换后再次流入所述压缩机。
本申请通过在第一集流管内设置隔板，所述隔板将第一集流管具有的第一内腔分隔为在第一集流管的长度方向上并行的两个子腔(第一子腔和第二子腔)，当气液两相的冷媒流入所述第一集流管时先进入其中一个子腔(第二子腔)再经由另外一个子腔(第一子腔)而进入换热管，从而提高了分配的均匀性。
附图说明
图1是本申请一实施例换热器的结构示意图。
图2是图9中本申请一实施例换热器沿A-A方向的剖面示意图。
图3是本申请又一实施例换热器沿A-A方向的剖面示意图。
图4是本申请换热管与翅片装配结构的截面示意图。
图5是图1中B区的换热管与翅片配合的结构示意图。
图6是本申请换热管与集流管装配的截面示意图。
图7是本申请换热管与隔板的一种装配方式的截面示意图。
图8是本申请换热管与隔板另一种装配方式的截面示意图。
图9是图1至图3实施例的换热器的沿换热管的高度方向的结构示意图。
图10是本申请示例性的一种换热系统示意图。
附图标记：
换热器100、200；集流管10、第一集流管11、第二集流管12；第一内腔101；第二内腔102；挡板103；隔板104；第一插孔105；第一端部113；第二端部114；第三端部213；第四端部214；第一分管111；第二分管112；第一分腔1110；第二分腔1120；第一子腔1111；第二子腔1112；第二插孔1041；第一通孔1042；第一面1043；第二面1044；
换热管20；第一换热管21；第二换热管22；第一端211、221；第二端212、222；凸筋231；流通通道232；凸起233；第一端面2111、2211；第二端面2121、2221；第一侧壁215；第二侧壁216；第一顶壁217；第一底壁218；第三侧壁225；第四侧壁226；第二顶壁227；第二底壁228；
翅片30；波峰部31；波谷部32；侧壁部33；波峰311；波谷321；
换热系统1000；压缩机1；第一换热器2；节流装置3；第二换热器4；换向装置5。
具体实施方式
这里将详细地对示例性实施例进行说明，其示例表示在附图中。下面的描述涉及附图时，除非另有表示，不同附图中的相同数字表示相同或相似的要素。以下示例性实施例中所描述的实施方式并不代表与本申请相一致的所有实施方式。相反，它们仅是与如所附权利要求书中所详述的、本申请的一些方面相一致的装置和方法的例子。
在本申请使用的术语是仅仅出于描述特定实施例的目的，而非旨在限制本申请。在本申请的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”、“顺时针”、“逆时针”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本申请和简化描述，而不是指示或暗示所指的 装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本申请的限制。此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括一个或者更多个该特征。在本申请的描述中，“多个”的含义是两个或两个以上，除非另有明确具体的限定。
在本申请的描述中，需要说明的是，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或一体地连接；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本申请中的具体含义。
在本申请中，除非另有明确的规定和限定，第一特征在第二特征之“上”或之“下”可以包括第一和第二特征直接接触，也可以包括第一和第二特征不是直接接触而是通过它们之间的另外的特征接触。而且，第一特征在第二特征“之上”、“上方”和“上面”包括第一特征在第二特征正上方和斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”包括第一特征在第二特征正下方和斜下方，或仅仅表示第一特征水平高度小于第二特征。下面结合附图，对本申请示例性实施例进行详细说明。在不冲突的情况下，下述的实施例及实施方式中的特征可以相互补充或相互组合。
在本申请使用的术语是仅仅出于描述特定实施例的目的，而非旨在限制本申请。在本申请和所附权利要求书中所使用的单数形式的“一种”、“所述”和“该”也旨在包括多数形式，除非上下文清楚地表示其他含义。
下面结合附图，对本申请示例性实施例进行详细说明。在不冲突的情况下，下述的实施例及实施方式中的特征可以相互组合。
相关换热器，尤其是空调系统中，换热器包含有集流管和换热管，所述 集流管具有管壁和内腔，所述换热管具有管壁和冷媒通道，所述换热管的一端通过设置在集流管管壁的换热管插孔插入所述集流管，所述换热管的冷媒通道与所述集流管的内腔连通。当冷媒流入换热器时，首先流入集流管内腔分配后进入换热管。在换热系统中，当换热器作为蒸发器使用时，进入其的冷媒可能是气液两相状态，如此容易使得冷媒经集流管分配后进入换热管时的均匀性不高，相关换热器中的冷媒均匀分配性有待提高。本申请实施例提供在换热系统中使用可相对提高冷媒分配均匀性的换热器。所述换热器可在热泵系统中作为蒸发器使用，提高冷媒的分配均匀性。容易理解，本换热器除可以应用于热泵系统作为室外换热器外，该换热器也可以用于其他空气处理等。此处不作限制。
相关技术中，换热器使用的集流管为圆形集流管、D型集流管、椭圆形管或者方形管中的一种或几种，换热管为换热扁管。所述集流管均具有长度方向。定义与其长度方向相垂直的面为横截面，所述圆形集流管的横截面为圆环结构，其内直径为d 1；所述D型集流管的横截面包括圆弧段和平直段，其截面大致呈D型，所述平直段的宽度为d 2；所述椭圆形管的横截面大致呈椭圆环形，所述椭圆形的较长直径为d 3；类似的，所述方形管的横截面大致呈方形，所述方形较宽的一边长为d 4。其中，所述换热管的宽度d满足以下条件之一：
(1)当所述集流管为圆形管时，所述换热管的宽度d小于所述集流管横截面的内直径d 1；
(2)当所述集流管为D型管时，所述集流管包括弧形壁和平直壁，所述换热管的宽度小于所述集流管平直段的宽d 2；
(3)当所述集流管为椭圆形管时，所述换热管的宽度小于所述集流管横截面较宽内直径d 3；
(4)当所述集流管为方形管时，所述换热管的宽度至少小于所述方形管较宽的一边d 4；
如图1和图2所示、必要时结合其它附图，对本申请换热器的具体实施 方式进行说明。图1是本申请一实施例换热器的结构示意图。图9是图1中换热器的沿换热管的高度方向的结构示意图。图2是图9中本申请一实施例换热器沿A-A方向的剖面示意图。具体说明如下。
本申请一实施例换热器100可包括集流管10、多个换热管20以及翅片30。所述集流管10具有供冷媒流动的内腔(图中未标示)，其形状为圆管。其长度方向即为轴向方向。所述集流管10具有两个，即第一集流管11和第二集流管12，所述第一集流管11和所述第二集流管12大致平行设置。说明一点，所述换热器100和空气一般只经过一次换热，业内常称之为单层换热器。当然，在其他一些实施例中，所述集流管10也可以是D型或者方形管，其具体形状不受限制，只要其爆破压力满足系统需要即可。所述集流管10的相对位置也不受限制，满足实际安装需要即可。所述集流管10的数量也可以只有一个，只要其满足换热需要即可，此处不受限制。本申请实施例中的集流管10以圆管为例。
所述换热管20具有多个，所述换热管20均具有长度方向、宽度方向和高度方向，多个换热管20沿所述集流管10的轴向排布且大致平行设置。多个换热管20均具有第一端和第二端。如图1所示，换热管20包括并列设置的第一换热管21和第二换热管22。所述第一换热管21具有第一端211和第二端212，界定换热管21的第一端211向第二端212延伸的方向为换热管的长度方向(图中X方向)。沿所述换热管高度方向的两端，所述第一换热管21具有第一顶壁217和第一底壁218，所述第一顶壁217和所述第一底壁218大致平行设置，其中所述换热管的高度方向也可以称为换热管的厚度方向。沿换热管的宽度方向的两端，所述第一换热管21具有第一侧壁215和第二侧壁216，所述第一侧壁215和所述第二侧壁216大致相对设置。所述第一换热管21的第一端211具有第一端面2111，所述第一换热管21的第二端212具有第二端面2121，所述第一端面2111和所述第二端面2121大致相同且大致平行，所述第一换热管21内部还具有供冷媒流动的通道232。同样的，所述第二换热管22具有第一端221、第二端222、第一端面2211和第二端面 2221，所述第二换热管22还具有与第一侧壁215对应的第三侧壁225、与第二侧壁216对应的第四侧壁226、与第一顶壁217对应的第二顶壁227、与第一底壁218对应的第二底壁228以及冷媒流通通道232。
所述第一换热管21的所述第一端211与所述第一集流管11相连接，所述第一换热管21的所述第二端212与所述第二集流管12相连接，同样的，所述第二换热管22的所述第一端221与所述第一集流管11相连接，所述第二换热管22的所述第二端222与所述第二集流管12相连接。第一换热管21和第二换热管22大致相平行设置。所述换热管20具有供冷媒流动的内腔(图中未标示)，如此连接，使得所述换热管20的内腔与所述集流管10的内腔相连通，形成换热器100的冷媒流通通道(图中未标示)，冷媒可在换热通道内进行流通，并通过换热器100实现换热。
需要说明的是，所述换热管20，业内也称为扁管，其内部具有供冷媒流动的内腔。如图4所示，换热管20内腔(图中未标示)通常会用凸筋231隔开成多个冷媒流通通道232。如此设置，不仅增加了换热管20的换热面积，使得换热效率得以提升，而且，在换热管20的内表面还可以设置有微小的凸起233，所述凸起233可以形成毛细效应强化换热。所述凸起233可以是锯齿形、波形、三角形等(图中未标示)，其形状可以根据需要设定。相邻的通道232彼此隔离。多个通道232排成一列，共同影响换热管20的宽度。换热管20整体呈扁平状，其长度大于宽度，宽度又大于其厚度。这里所说的换热管并不局限于此种类型，也可以是其它形态。比如，相邻的通道可不完全隔离。又比如，所有的通道可以排成两列，只要其宽度仍大于厚度即可。
所述第一集流管11和所述第二集流管12均具有管壁(未标号)，所述第一集流管11具有第一内腔101，第二集流管12具有第二内腔102。界定所述第一集流管11和第二集流管12的轴向方向为所述集流管的长度方向(即图中Z方向)，所述第一集流管11具有于其长度方向的第一端部113和第二端部114，所述第二集流管21于其长度方向的两端设有与第一集流管11的第一端部113对应的第三端部213和与第一集流管11的第二端部114对应 的第四端部214。所述第一集流管11的第一内腔101中设有挡板103和隔板104。所述挡板103大致与所述第一集流管11的轴向方向垂直设置，所述挡板103的数量为至少一个。在其他一些实施例中，所述挡板103的数量可以为多个，在另外一些实施例中，如图3所示，也可以不设置挡板103，换言之，挡板103根据流程设置的需要设置即可，在此不做赘述。
本申请实施例中所述挡板103将所述第一集流管11分为第一分管111和第二分管112，且将第一集流管11的第一内腔101分隔为第一分腔1110和第二分腔1120，所述第一分管111具有所述第一分腔1110，所述第二分管112具有所述第二分腔1120，沿所述集流管的轴向方向所述第一分腔1110内设有所述隔板104。所述隔板104由所述第一集流管11的第一端部113沿所述第一集流管11的轴向方向朝所述挡板103延伸设置且所述隔板104将第一分腔1110分隔为第一子腔1111和第二子腔1112。其中所述隔板104的一端与所述第一端部113相接，所述隔板104的另一端与所述挡板103相接。所述隔板104设置有通孔1042，所述通孔1042连通所述第一子腔1111和所述第二子腔1112。
所述第一集流管11和所述第二集流管12的管壁还设置有供换热管20插设的第一插孔105，所述第一插孔105贯穿所述第一集流管11和所述第二集流管12的管壁，所述第一插孔105具有多个且相互平行设置，所述换热管20的第一端211、221可通过所述第一插孔105插入所述第一集流管11。所述第一集流管11的第一内腔101与所述换热管20的所述冷媒通道232连通。所述隔板104设有供换热管20插设的第二插孔1041，所述第二插孔1041具有多个且相互平行设置，所述第二插孔1041贯穿所述隔板104设置，所述换热管20的第一端211、221贯穿通过所述第一插孔105并插入所述第二插孔1041，沿所述换热管的插入方向(即图中X方向)，所述第一插孔105的投影大致与所述第二插孔1041的投影大致相同且重叠，所述第二插孔1041的投影与所述通孔1042的投影不重叠，换言之，所述第二插孔1041与通孔错开设置。具体的，所述换热管20的所述冷媒通道232与所述第一集流管11 的第一子腔1111和第二子腔1112均连通，其中，所述换热管20的所述冷媒通道232与所述第一集流管11的所述第一子腔1111的连通部分，指的是与第一子腔1111连通。
如图2所示，所述换热器100还包括第一进出口1071和第二进出口1072，所述第一进出口1071设置于所述第一集流管11的第一端部113，所述第二进出口1072设置于所述第一集流管11的第二端部114。所述第一进出口1071与所述第二子分腔体1112连通。当所述换热器100用于换热系统时，在换热系统运行中所述冷媒经所述第一进出口1071流入所述第二子分腔1112后经过所述隔板104的所述通孔1042流入所述第一子分腔1111，进而流入所述换热管20的所述冷媒通道232。
所述第一分管111和所述第二分管112的管壁处均设有多个所述第一插孔105，所述换热管20的第一端211、221贯穿插入所述第一集流管11的所述第一插孔105后插入所述第二插孔1041。
如图1至图3并结合图6所示，所述隔板104具有相对设置的第一面1043和第二面1044，所述第一面1043为所述隔板104朝向所述第一子腔1111的面，所述第二面1044为所述隔板104朝向所述第二子腔1112的面。所述第一集流管11的部分内壁面与所述隔板104的第二面1044之间具有缝隙部106。具体的，所述换热管20插入所述第二子腔1112的外侧壁部分、所述第一集流管11形成所述第二子腔1112的内壁面部分、以及所述隔板104的所述第二面1044之间具有缝隙部106。与所述第一分管111相连的换热管20为第一流程换热管201，与所述第二分管112相连的换热管20为第二流程换热管202，当所述换热器100中有冷媒流入时，所述冷媒经过所述第一进出口1071流入所述第二子腔1112后，遇到换热管20的阻力后在压力的作用下经换热管20两边的缝隙部106流动，由于所述缝隙部106的宽度有限，如此可加剧两相的冷媒在第二子腔1112中的湍流效应，使两相冷媒混合均匀，而后经过所述隔板104的所述通孔1042流入所述第一子腔1111内部，在压力的作用下，所述冷媒经所述第一流程换热管201的第一端211流入其冷媒通道232 而后流入所述第二集流管12的第二内腔102中，接着流入所述第二流程换热管202的冷媒流通通道232中，而后进入所述第一集流管11的第二分腔1120中，并经由第二进出口1072流出所述换热器100。上述过程中冷媒与所述换热器100实现热交换，需要说明的是，上述换热过程中，所述冷媒在换热器100中的换热为两个流程的换热，换言之，所述换热器100为双流程换热器。在其他一些实施例中，所述换热器100也可以是两个流程以上的换热器，根据实际需要设计即可。
如图3所示为又一实施例的换热器200的剖面示意图，所述换热器200和所述换热器100的结构大致相同，所述换热器200也包括所述第一集流管11和所述第二集流管12，不同之处在于，所述第一集流管11中不设置如图2中的所述挡板103，所述隔板104将所述第一集流管11的所述第一内腔102整个儿分为并行的所述第一子腔1111和所述第二子腔1112，所述换热管20的第一端211、221通过管壁上的所述第一插孔105插入所述第一集流管11后，再插入所述隔板104所述的第二插孔1041中，所述第一进出口1071设于所述第一集流管11的所述第一端部113且与第二子腔1112连通，所述第二进出口1072设于所述第二集流管12的所述第四端部214，当冷媒流入所述换热器时，所述冷媒经所述第一进出口1071流入所述第二子腔1112，在所述第二子腔1112中发生所述多次湍流，而后经过所述隔板104的所述通孔1042流入所述第一子腔1111中，而后经过所述换热管20的第一端211、221流入所述换热管20的所述冷媒通道232，而后又流入所述第二集流管12的第二内腔102中，通过第二进出口1072流出所述换热器200。说明一点，所述换热器200和空气一般只经过一次换热，业内常称之为单层换热器。
本发明实施例中的分配结构不仅限于用于单层换热器，在其他多层换热器中也可以使用，多层换热器可以是换热管折弯的换热器，也可以是通过连接模块将相邻的集流管连接起来的换热器，结构大致相同，在此不再赘述。需要说明一点，当多层换热器为换热管折弯的换热器时，所述换热管的长度方向即为换热管的延伸方向，换言之，所述长度方向并局限于为直线方向。
如图6所示为第一换热管21与第一集流管11装配的截面示意图。
如图8所示为所述第一换热管21插入所述第一集流管11的隔板104的第二插孔1041中的一种截面示意图。结合图6和图8，所述第一换热管21的第一端211经所述第一插孔105插入所述第一集流管11的第一内腔101后，又经所述隔板104的所述第二插孔1041插入所述隔板104，所述第一换热管21的所述第一端面2111穿出所述隔板104，且所述第一换热管21的第一端面2111距所述隔板104的所述第一面1043的距离为第一距离H 1，所述第一距离H 1小于2mm，在其他一些实施例中，所述第一距离H 1的大小为1mm。在另外一些实施例中，所述第一距离H 1的大小为0.5mm。
如图7所示为本申请第一换热管21与所述隔板104的另外一种装配方式的截面示意图。结合图6和图7，所述第一换热管21的第一端211经所述第一插孔105插入所述第一集流管11后，又经所述隔板104的所述第二插孔1042插入所述隔板104，但是所述第一换热管21的第一端面2111不穿出所述隔板104。所述第一换热管21的第一端面2111距所述隔板104的所述第一面1043的距离为第二距离H 2，所述第二距离H 2小于所述隔板104的厚度，所述隔板104的厚度可以为1～3mm，所述第二距离H 2可以为2mm，在其他一些实施例中，所述第二距离H 2的大小为1mm。在另外一些实施例中，所述第二距离H 2的大小为0.5mm。
如图1至图5所示，本申请实施例的换热器100和换热器200还包括翅片30。值得注意的是，相关技术中的换热器表面涂覆有功能材料，如耐腐蚀材料等，具体的，是在整个换热器的外表面的全部或部分涂覆，所述功能材料可以是耐腐蚀材料或吸湿材料等，根据需要设置即可，在此不做赘述。所述翅片30为窗型翅片。说明一点，在其他实施例中，翅片也可以是不开窗翅片。翅片的形状可以是大致呈波形，也可以是型材，翅片的截面可以是正弦波或近似正弦波，也可以是锯齿波，只要满足需要即可，其具体结构不受限制。当然，翅片30可以根据需要涂覆功能材料，在此不予限制。
本申请实施例中的翅片30为波形翅片，所述翅片30具有波峰部31、波 谷部32以及连接所述波峰部31和所述波谷部32的侧壁部33。所述波峰部31、波谷部32在所述翅片30的长度方向一一间隔设置，所述侧壁部33具有多个。说明一点，本发明中所述的多个指的是两个以及两个以上，除非另有说明。所述侧壁部33可设置开窗或者不设置开窗，根据换热需要设置即可。在其他一些实施例中，所述翅片30的形状可以是大致呈波形，也可以是型材，翅片的截面可以是正弦波或近似正弦波，也可以是锯齿波，只要满足需要即可，其具体结构不受限制。
本申请的实施例中所述翅片30整体呈波形，所述波峰部31与所述波谷部32间隔设置，所述翅片30设置于相邻的两个换热管20之间，所述波峰部31至少部分与第一换热管21相接触，所述波谷部32至少部分与第二换热管22相接触。其中，所述波峰部31的最高点为波峰311，所述波谷部32的最底点为波谷321。即，所述波峰部31与所述第一换热管21的第一底壁218接触，所述波谷部32与所述第二换热管22的第一顶壁227接触。界定翅片30的波峰部31和波谷部32一一间隔设置的延伸方向为翅片30的长度方向(如图中的X方向)，界定波峰311所在平面与波谷321所在平面之间的垂直方向为翅片的高度方向(如图中的Z方向)。如此可知，所述翅片30的长度方向与所述换热管20的长度方向相同(图中X方向)，所述翅片30的宽度方向与所述换热管20的宽度方向相同(图中Y方向)，换热管20之间的间距即为翅片30的高度方向(附图中Z方向)。
如图10所示，是本申请一示例性实施例示出的一种换热系统1000，该换热系统1000至少包括压缩机1、第一换热器2、节流装置3、第二换热器4以及换向装置5。可选的，该换热系统1000的压缩机1可以是卧式压缩机或立式压缩机。可选的，节流装置3可以是膨胀阀，此外，节流装置3还可以是其它对冷媒具有降压及调节流量作用的零部件，本申请文件对节流装置的种类不做具体限制，可根据实际应用环境进行选取，在此不再赘述。需要说明的是，在有些系统中，可以没有换向装置5。本发明中所述的换热器100、可以用于该换热系统1000中作为第一换热器2和/或第二换热器4。在该换 热系统1000中，压缩机1对冷媒进行压缩，压缩后的冷媒温度升高，而后进入第一换热器2中，经过第一换热器2和外界的热交换将热量传递给外界，之后经过节流装置3的冷媒变成液态或气液两相的状态，此时冷媒的温度降低，而后较低温度的冷媒流向第二换热器4，并在第二换热器4与外界热交换后再次进入压缩机1中，实现冷媒循环。当第二换热器4作为室外换热器与空气发生热交换使用时，参照上述事实例，根据需要布置所述换热器。
以上所述仅是本申请的较佳实施例而已，并非对本申请做任何形式上的限制，虽然本申请已以较佳实施例揭露如上，然而并非用以限定本申请，任何熟悉本专业的技术人员，在不脱离本申请技术方案的范围内，当可利用上述揭示的技术内容做出些许更动或修饰为等同变化的等效实施例，但凡是未脱离本申请技术方案的内容，依据本申请的技术实质对以上实施例所作的任何简单修改、等同变化与修饰，均仍属于本申请技术方案的范围内。

Claims (16)

  1. 一种换热器，其特征在于，所述换热器包括第一集流管、换热管以及隔板，所述第一集流管具有管壁和第一内腔，所述第一集流管具有于其长度方向的第一端部和第二端部，所述隔板设置于所述第一内腔内且自第一端部沿第一集流管的长度方向延伸从而将所述第一内腔分隔为在第一集流管的长度方向上并行的第一子腔和第二子腔；
    所述换热管具有管壁和供冷媒流动的冷媒通道，所述换热管具有于其延伸方向的第一端和第二端，所述冷媒通道沿所述第一端向所述第二端延伸并贯穿所述换热管；
    所述第一集流管的管壁还设置有第一插孔，所述隔板设有与第一插孔对应的第二插孔，所述换热管的第一端贯穿通过所述第一插孔并插入所述第二插孔；
    所述隔板设置有通孔，所述通孔与所述第二插孔错位设置，所述通孔连通所述第一子腔和所述第二子腔；
    所述换热器还包括第一进出口，所述第一进出口设置于所述第一集流管的所述第一端部且与所述第二子腔连通所述第一子腔与冷媒通道连通。
  2. 如权利要求1所述的换热器，其特征在于，所述换热器包括设置于所述第一集流管内的挡板，所述挡板大致与所述第一集流管的长度方向垂直设置，所述挡板将所述第一集流管分为具有第一分腔的第一分管和具有第二分腔的第二分管，所述隔板设置于所述第一分腔内且沿所述第一集流管的长度方向自所述第一端部延伸至所述挡板，其中，所述隔板与所述第一端部和所述挡板均连接，所述隔板将第一分腔分隔为所述第一子腔和所述第二子腔；
    所述第一分管的管壁和所述第二分管的管壁均设有所述第一插孔，所述第一分管内设有具有所述第二插孔的所述隔板，所有换热管的第一端贯穿插入所述第一分管和第二分管的所述第一插孔，部分换热管的第一端插入所述第一分管的所述第二插孔，剩余部分换热管的第一端仅延伸入所述第二分管 的第二分腔内，所述第二分管内无所述隔板故无所述第二插孔供剩余部分换热管的第一端插设。
  3. 如权利要求1所述的换热器，其特征在于，所述第一内腔内仅具有沿第一集流管长度方向延伸的隔板而没有与所述第一集流管长度方向垂直的挡板，所述隔板自所述第一端部延伸至所述第二端部从而所述隔板与所述第一端部和所述第二端部均连接，所述换热管的第一端贯穿插入所述第一集流管的所述第一插孔且所有换热管的第一端均插入所述隔板的所述第二插孔。
  4. 如权利要求2或3所述的换热器，其特征在于，还包括第二集流管，所述第二集流管与所述第一集流管大致相互平行设置，所述第二集流管包括管壁和第二内腔，所述第二集流管于其长度方向的两端设有与第一集流管的第一端部对应的第三端部和与第一集流管的第二端部对应的第四端部，所述第二集流管设置有与所述第一插孔相对应的第三插孔，所述第三插孔贯穿所述第二集流管的管壁设置，所述换热管的第二端通过所述第三插孔插入所述第二集流管，所述换热管的所述冷媒通道与所述第二集流管的第二内腔连通；
    所述换热器还包括第二进出口，所述第二进出口设置于所述第二集流管的第四端部或所述第一集流管的第二端部。
  5. 如权利要求1所述的换热器，其特征在于，所述第一集流管为圆管、椭圆管、D型管或方形管中的一种。
  6. 如权利要求1或5所述的换热器，其特征在于，所述隔板具有相对设置的第一面和第二面，所述第一面为所述隔板朝向所述第一子腔的面，所述第二面为所述隔板朝向所述第二子腔的面，所述换热管固定密封于所述第二子腔的管壁，所述第一集流管的部分内壁面与所述隔板的第二面之间具有缝隙部。
  7. 如权利要求6所述的换热器，其特征在于，所述缝隙部位于所述第一集流管形成所述第二子腔的内壁面部分、所述换热管插入所述第二子腔内的外侧壁部分以及所述隔板的第二面之间。
  8. 如权利要求6所述的换热器，其特征在于，所述换热管的第一端具 有第一端面，所述换热管的第一端插入所述第二插孔并穿过所述第一面，所述换热管的第一端面距所述隔板的第一面的距离小于2mm。
  9. 如权利要求8所述的换热器，其特征在于，所述换热管的第一端面距所述隔板的第一面的距离为0.5mm。
  10. 如权利要求6所述的换热器，其特征在于，所述换热管的第一端插入所述第二插孔且不超出所述第一隔板的第一面，所述换热管的第一端面距所述隔板的第一面的距离不大于隔板的厚度。
  11. 如权利要求10所述的换热器，其特征在于，所述换热管的第一端面距所述隔板的第一面的距离为所述隔板的厚度的一半。
  12. 如权利要求1所述的换热器，其特征在于，所述换热管内设有凸筋，所述凸筋将所述换热管的所述冷媒流通通道分隔为多个子冷媒通道。
  13. 如权利要求12所述的换热器，其特征在于，所述换热管于面向每一个子冷媒通道的内表面设有多个凸起。
  14. 如权利要求1所述的换热器，其特征在于，所述换热管为多个，相邻的所述换热管之间设置有翅片，所述翅片的至少部分表面与所述换热器接触。
  15. 如权利要求14所述的换热器，其特征在于，所述翅片沿所述换热管的长度方向延伸且大体呈波形，所述翅片具有波峰部和波谷部，所述波峰部与所述波峰部间隔设置，所述翅片设置于相邻的所述第一换热管和第二换热管之间；所述第一换热管具有位于其高度方向两侧的第一顶壁和第一底壁，所述第二换热管具有位于其高度方向两侧的第二顶壁和第二底壁，所述波峰部与所述第一换热管的第一底壁接触，所述波谷部与所述第二换热管的第二顶壁接触。
  16. 一种换热系统，其特征在于，所述换热系统具有压缩机、至少一个第一换热器、节流装置和至少一个第二换热器，所述第一换热器和/或所述第二换热器为如权利要求1～15任一权利要求所述的换热器，当所述换热系统有冷媒流动时，所述冷媒经所述压缩机流入所述第一换热器，并在所述第一 换热器发生热交换之后流入节流装置，而后所述冷媒流入所述第二换热器并在所述第二换热器发生热交换后再次流入所述压缩机。
PCT/CN2020/105114 2019-08-01 2020-07-28 换热器和换热系统 WO2021018126A1 (zh)

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EP3982054A1 (en) 2022-04-13
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CN112303886A (zh) 2021-02-02
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