WO2022011570A1 - 换热器 - Google Patents

换热器 Download PDF

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Publication number
WO2022011570A1
WO2022011570A1 PCT/CN2020/101966 CN2020101966W WO2022011570A1 WO 2022011570 A1 WO2022011570 A1 WO 2022011570A1 CN 2020101966 W CN2020101966 W CN 2020101966W WO 2022011570 A1 WO2022011570 A1 WO 2022011570A1
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WO
WIPO (PCT)
Prior art keywords
tube
heat exchange
cross
channel
channels
Prior art date
Application number
PCT/CN2020/101966
Other languages
English (en)
French (fr)
Inventor
蒋建龙
高强
钟笑鸣
蒋皓波
黄宁杰
Original Assignee
杭州三花微通道换热器有限公司
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 杭州三花微通道换热器有限公司 filed Critical 杭州三花微通道换热器有限公司
Priority to CN202090000336.7U priority Critical patent/CN215491193U/zh
Priority to EP20945496.6A priority patent/EP4184084A4/en
Priority to PCT/CN2020/101966 priority patent/WO2022011570A1/zh
Publication of WO2022011570A1 publication Critical patent/WO2022011570A1/zh
Priority to US17/823,536 priority patent/US20220412660A1/en

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Classifications

    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates

Definitions

  • the embodiments of the present application relate to the technical field of heat exchange, and more particularly, to a heat exchanger.
  • the multi-channel heat exchanger adopts a plurality of multi-channel heat exchange tubes for heat exchange, and the multi-channel heat exchange tubes are spaced with multiple channels in the width direction. It is distributed among the heat exchanger tubes, and then distributed between the various channels of the heat exchange tubes. The distribution of the refrigerant in the heat exchange tubes and each channel affects the heat exchange performance of the heat exchanger. The heat exchange performance of the multi-channel heat exchanger is improved.
  • the embodiments of the present application propose a heat exchanger, which can adjust the distribution of refrigerant in the heat exchanger, which is beneficial to improve the heat exchange performance of the heat exchanger.
  • the first pipe includes a peripheral wall and a main channel surrounded by the peripheral wall
  • the heat exchanger further includes an inlet and outlet pipe, and the inlet and outlet pipes communicate with the first pipe
  • a plurality of heat exchange tubes communicate with the first tube and the second tube
  • the heat exchange tubes include a plurality of channels arranged at intervals, and the channels communicate with the first tube and the second tube.
  • the cross-sectional area of the first channel is larger than the cross-sectional area of the remaining channels in the plurality of channels except the first channel
  • the cross-sectional area of the second channel is smaller than the cross-sectional area of the plurality of channels except the second channel
  • a first piece the first piece is located in the main channel of the first pipe, the first piece extends a certain distance along the length direction of the first pipe, and the main channel includes a first flow channel and a second A flow channel, the first piece is located between the first flow channel and the second flow channel, the first flow channel is communicated with the inlet and outlet pipes, and the second flow channel is connected with the heat exchange tube communication, the first piece includes a plurality of through holes, the through holes communicate with the first flow channel and the second flow channel,
  • the cross-sectional area of the first channel on the cross section of the heat exchange tube is A1
  • the cross-sectional area of the second channel on the cross section of the heat exchange tube is A2
  • the A1 and A2 satisfy the following relationship Formula: 0.15 ⁇ (A1-A2)*N/A3 ⁇ 3.8, where A3 is the sum of the flow cross-sectional areas of the plurality of through holes of the first piece, and N is the heat exchange tube connected to the main channel number of.
  • the first piece is arranged in the main channel of the first tube to define the first flow channel and the second flow channel in the main channel, and the cut-off of the plurality of channels in the heat exchange tube is arranged.
  • the areas are inconsistent, so that the cross-sectional area A1 of the first channel on the cross section of the heat exchange tube, the cross-sectional area A2 of the second channel on the cross section of the heat exchange tube, and the number N of heat exchange tubes connected to the second flow channel satisfy : 0.15 ⁇ (A1-A2)*N/A3 ⁇ 3.8, the distribution of refrigerant in the heat exchanger can be adjusted, the heat exchange performance of the heat exchanger can be improved, and the superheat degree at the outlet of the heat exchanger can be adjusted to reduce the The opening degree fluctuates to improve the stability of the refrigeration and air-conditioning system.
  • the first piece is a third tube
  • the third tube includes a third peripheral wall
  • the third peripheral wall is located between the first flow channel and the second flow channel
  • the first The three peripheral walls have the through holes penetrating the peripheral walls, the through holes communicate with the first flow channel and the second flow channel
  • the third pipe communicates with the inlet and outlet pipes, or the third pipe includes all the Describe the inlet and outlet pipes.
  • the side of the heat exchanger located upstream of the wind direction during heat exchange is defined as the windward side
  • the side of the heat exchanger downstream of the wind direction is defined as the leeward side
  • the first channel is located on the Windward side
  • the side of the heat exchanger located upstream in the wind direction is defined as the windward side
  • the side downstream of the heat exchanger in the wind direction is defined as the leeward side
  • the channels located on the windward side of the plurality of channels are defined as the windward side.
  • the sum of the flow cross-sectional areas is greater than the sum of the flow cross-sectional areas of the channels located on the leeward side of the plurality of channels.
  • a part of the through holes in the distribution pipe is located on the windward side, and another part of the through holes in the distribution pipe is located on the leeward side, and the through holes on the windward side are located on the windward side.
  • the sum of the cross-sectional areas of the through holes is smaller than the sum of the cross-sectional areas of the through holes on the leeward side.
  • the distance I between at least two adjacent through holes satisfies: 20mm ⁇ I ⁇ 150mm.
  • the first pipe includes a first end face, and in the length direction of the first pipe, a through hole adjacent to the first end face of the first pipe among the plurality of through holes is the first a through hole, the heat exchange tube adjacent to the first end face of the first tube among the plurality of heat exchange tubes is the first heat exchange tube, and the plurality of heat exchange tubes includes a second heat exchange tube, In the length direction of the first tube, the number of the heat exchange tubes located between the first heat exchange tube and the second heat exchange tube is greater than or equal to 10 and less than 30, and the first through hole is connected to the second heat exchange tube.
  • the minimum distance of the first end face in the length direction of the first tube is smaller than the minimum distance between the second heat exchange tube and the first end face in the length direction of the first tube.
  • the distance between two adjacent channels in the width direction of the heat exchange tube is equal, and the distance between the two adjacent channels is equal.
  • the cross-sectional areas are not equal.
  • the outer peripheral contour of the cross section of the heat exchange tube is substantially quadrilateral, and the inner diameter of the second tube is 1.1 times or more the width of the heat exchange tube.
  • a heat exchanger includes a first tube including a peripheral wall and a main channel surrounded by the peripheral wall, and a second tube, one end in the length direction of the first tube is the first end, the first end of the first pipe includes a first end surface, the heat exchanger further includes an inlet and outlet pipe, and the inlet and outlet pipes are communicated with the first pipe; a plurality of heat exchange pipes are The heat exchange tube communicates with the first tube and the second tube, the heat exchange tube includes a plurality of channels arranged at intervals, at least three of the channels have unequal cross-sectional areas, and the channels communicate with the first tube.
  • the tube and the second tube, in the cross section of the heat exchange tube, the cross-sectional area of the plurality of channels varies along the spacing direction of the plurality of channels, and the plurality of channels includes a first channel and a second channel A channel, in the cross section of the heat exchange tube, the cross-sectional area of the first channel is larger than the cross-sectional area of the remaining channels in the plurality of channels except the first channel, and the cross-sectional area of the second channel is smaller than the cross-sectional area of the plurality of channels
  • the main channel includes a first flow channel and a second flow channel, the first piece is located between the first flow channel and the second flow channel, the first flow channel and the inlet and outlet pipes
  • the second flow channel communicates with the heat exchange tube, the first piece includes a plurality of through holes
  • the minimum distance in the length direction is d3, and d3 ⁇ (10d1+9d2)*A1/A2, where d1 is the thickness of the heat exchange tube, and d2 is the adjacent heat exchange tube in the length direction of the first tube.
  • the first piece having a plurality of through holes is arranged in the main channel of the first tube to define the first flow channel and the second flow channel in the main channel, and the heat exchange tube is arranged in the main channel.
  • the cross-sectional areas of the multiple channels are inconsistent, the cross-sectional area A1 of the first channel on the cross-section of the heat exchange tube, the cross-sectional area A2 of the second channel on the cross-section of the heat exchange tube, and the thickness d1 of the heat exchange tube.
  • the minimum distance d2 between adjacent heat exchange tubes in the length direction of a tube and the distance d3 from the first through hole of the first piece to the end of the first tube satisfy: d3 ⁇ (10d1+9d2)*A1/A2,
  • the superheat degree of the heat exchange tubes can be adjusted, so that the refrigerant distribution between the heat exchange tubes is beneficial to improve the performance of the heat exchanger.
  • the first piece is a third tube
  • the third tube includes a third peripheral wall
  • the third peripheral wall is located between the first flow channel and the second flow channel
  • the first The three peripheral walls have a plurality of the through holes penetrating the peripheral walls.
  • the side located upstream of the heat exchanger along the wind direction is defined as the windward side
  • the side located downstream of the heat exchanger along the wind direction is defined as the leeward side
  • the first channel is located on the windward side
  • At least part of the plurality of through holes are located on the leeward side.
  • the side of the heat exchanger located upstream in the wind direction is defined as the windward side
  • the side downstream of the heat exchanger in the wind direction is defined as the leeward side
  • the channels located on the windward side of the plurality of channels are defined as the windward side.
  • the sum of the flow cross-sectional areas is the sum of the flow cross-sectional areas of the channels located on the leeward side of the plurality of channels, and at least part of the plurality of through holes are located on the leeward side.
  • a part of the through holes in the plurality of through holes are located on the windward side, and another part of the through holes in the plurality of through holes are located on the leeward side, and the transverse direction of the through holes on the windward side is located on the windward side.
  • the sum of the cross-sectional areas is smaller than the sum of the cross-sectional areas of the through holes on the leeward side.
  • one end of the third pipe communicates with the inlet and outlet pipes, and the other end of the third pipe has an orifice, and the flow area of the orifice is smaller than the flow cross-sectional area of the third pipe .
  • the hydraulic diameter of the second tube is equal to or equal to 1.1 times the hydraulic diameter of the first tube.
  • the outer peripheral contour of the cross section of the heat exchange tube is substantially quadrilateral, and the inner diameter of the second tube is 1.1 times or more the width of the heat exchange tube.
  • FIG. 1 is a front view of a heat exchanger according to an embodiment of the present application.
  • FIG. 2 is a schematic diagram of a heat exchanger according to an embodiment of the present application, wherein the first piece is shown.
  • FIG. 3 is an enlarged view of part A in FIG. 2 .
  • FIG 4 is a side view of a heat exchanger according to one embodiment of the present application.
  • FIG. 5 is a cross-sectional view of a heat exchange tube of a heat exchanger according to an embodiment of the present application.
  • FIG. 6 is a cross-sectional view of a heat exchange tube of a heat exchanger according to another embodiment of the present application.
  • FIG. 7 is a cross-sectional view of a heat exchange tube of a heat exchanger according to still another embodiment of the present application.
  • FIG. 8 is a schematic diagram of a partial structure of a heat exchanger according to an embodiment of the present application.
  • FIG. 9 is a cross-sectional view taken along the A-A direction in FIG. 8 .
  • FIG. 10 is a cross-sectional view of a heat exchanger according to an embodiment of the present application.
  • FIG. 11 is a cross-sectional view taken along the direction B-B in FIG. 10 .
  • FIG. 12 is a cross-sectional view in the direction B-B of FIG. 10, and shows ⁇ 1 and ⁇ 2.
  • FIG. 13 is a schematic diagram of the fit of the first tube and the first piece in the heat exchanger according to an embodiment of the present application.
  • FIG. 14 is a graph of the heat exchange performance of the heat exchanger according to an embodiment of the present application as a function of the value of (A1-A2)*N/A3.
  • 15 is a graph comparing the degree of superheat of a heat exchanger (with a third tube) and a heat exchanger (without a third tube) according to one embodiment of the present application.
  • 16 is a graph comparing the heat exchange performance of a heat exchanger (with a third tube) and a heat exchanger (without a third tube) according to an embodiment of the present application.
  • 17 is a graph of the heat exchange performance of the heat exchanger according to an embodiment of the present application as a function of the value of (A1-A2)/A4
  • FIG. 18 is a graph showing the heat exchange performance of heat exchange tubes (heat exchange tubes with non-uniform flow channel cross-sectional areas) and heat exchange tubes (heat exchange tubes with uniform flow channel cross-sectional areas) of a heat exchanger according to an embodiment of the present application Comparison chart.
  • FIG. 19 is a schematic diagram of a refrigeration and air conditioning system including a heat exchanger according to an embodiment of the present application.
  • the first tube 10 the main channel 101; the first flow channel 1011; the second flow channel 1012;
  • heat exchange tube 30 channel 301;
  • Compressor 100 Compressor 100 , first heat exchanger 200 , throttle 300 , second heat exchanger 400 , fan 500 .
  • the refrigerant flows through the inner channel of the multi-channel heat exchanger, and the airflow passes through the surface of the heat exchanger to exchange heat with the refrigerant in the heat exchanger. As shown in FIG.
  • the refrigeration and air-conditioning system includes a compressor 100, a first heat exchanger 200, a throttle 300, a second heat exchanger 400 and a fan 500, wherein the compressor 100, the first heat exchanger 200, the throttle The device 300 and the second heat exchanger 400 are connected in series to form a circulation loop, one fan 500 is aligned with the first heat exchanger 200 to blow air to the first heat exchanger 200, and the other fan 500 is aligned with the second heat exchanger 400 to blow air to the first heat exchanger 200.
  • the second heat exchanger 400 blows air. Either or each of the heat exchanger 200 and the heat exchanger 400 may be the heat exchanger 1 in this application.
  • a heat exchanger 1 according to an embodiment of an aspect of the present application is described below with reference to FIGS. 1-18 .
  • the heat exchanger 1 includes a first tube 10 , a second tube 20 , a plurality of heat exchange tubes 30 and a first piece 40 .
  • the first pipe 10 includes a peripheral wall and a main channel 101 surrounded by the peripheral wall.
  • the heat exchanger 1 further includes an inlet and outlet pipe 60 that communicates with the first pipe 10 .
  • both the first pipe 10 and the second pipe 20 extend in the left-right direction, and the first pipe 10 and the second pipe 20 are spaced apart in the front-rear direction, and the inlet and outlet pipes 60 are located in the first pipe 10 and the right end of the first pipe 10 communicates with the left end of the inlet and outlet pipes 60 .
  • One end of the heat exchange tube 30 is communicated with the first tube 10, the other end of the heat exchange tube 30 is communicated with the second tube 20, the heat exchange tube 30 is communicated with the first tube 10 and the second tube 20, and the heat exchange tube 30 includes A plurality of channels 301 (two or more channels 301), the channels 301 communicate with the first tube 10 and the second tube 20, on the cross section of the heat exchange tube 30, at least three channels 301 in the plurality of channels 301
  • the cross-sectional areas are not equal to each other, and the plurality of channels 301 include a first channel and a second channel.
  • the cross-sectional area of the first channel is larger than the rest of the plurality of channels 301 except the first channel.
  • the cross-sectional area of the channel 301, the cross-sectional area of the second channel is smaller than the cross-sectional area of the other channels 301 in the plurality of channels 301 except the second channel.
  • each heat exchange tube 30 extends in the front-rear direction, and a plurality of heat exchange tubes 30 are arranged at intervals between the first tube 10 and the second tube 20 in the left-right direction. In communication with the first tube 10 , the rear end of the heat exchange tube 30 is in communication with the second tube 20 . As shown in FIG. 4 and FIG. 5 , each heat exchange tube 30 is formed with a plurality of channels 301 arranged at intervals in the up-down direction, and the channels 301 extend in the front-rear direction, and the front end of the channel 301 communicates with the first tube 10 .
  • the rear end of 301 communicates with the second pipe 20 , the channel 301 with the largest cross-sectional area among the plurality of channels 301 is the first channel, and the channel 301 with the smallest cross-sectional area among the plurality of channels 301 is the second channel.
  • both the first channel and the second channel may be multiple, and the cross-sectional areas of the multiple channels 301 may be all different or partially the same.
  • the first piece 40 is located in the main channel 101 of the first tube 10 , the first piece 40 extends for a certain distance along the length direction of the first tube 10 , and the length of the first piece 40 in the main channel 101 of the first tube 10 is less than or equal to
  • the length of the first tube 10 includes a first flow channel 1011 and a second flow channel 1012, the first piece 40 is located between the first flow channel 1011 and the second flow channel 1012, and the first flow channel 1011 communicates with the inlet and outlet pipes 60 , the second flow channel 1012 communicates with the heat exchange tube 30 , the first piece 40 includes a plurality of through holes 401 , and the through holes 401 communicate with the first flow channel 1011 and the second flow channel 1012 .
  • the first piece 40 penetrates the main channel 101 in the left-right direction, the first piece 40 has through holes 401 spaced along the left-right direction, the first flow channel 1011 and the second flow channel 1012 Both extend in the left-right direction and the first piece 40 separates the first flow channel 1011 and the second flow channel 1012, the right end of the first flow channel 1011 communicates with the inlet and outlet pipes, and the second flow channel 1012 is connected with the front ends of the plurality of heat exchange tubes 30. Connected.
  • the refrigerant is suitable for flowing into the first flow channel 1011 along the inlet and outlet pipes, and the refrigerant in the first flow channel 1011 flows into the second flow channel 1012 through the through hole 401 on the first piece 40 , and passes through the second flow channel 1012
  • the communication with the heat exchange tubes 30 flows into the heat exchange tubes 30 for further heat exchange.
  • the cross-sectional area of the first channel on the cross section of the heat exchange tube 30 is A1
  • the cross-sectional area of the second channel on the cross section of the heat exchange tube 30 is A2, where A1 and A2 satisfy the following relationship: 0.15 ⁇ (A1- A2)*N/A3 ⁇ 3.8, where A3 is the sum of the flow cross-sectional areas of the plurality of through holes 401 of the first piece 40 , and N is the number of heat exchange tubes 30 connected to the main channel 101 .
  • the first piece 40 (such as a distribution pipe) is not provided in the main channel, and the cross-sectional areas of the multiple channels in the heat exchange pipe are consistent.
  • the problem As shown in Fig. 15, Fig. 16 and Fig. 18, the applicant found that when the first piece is provided in the main channel and the cross-sectional areas of the multiple channels in the heat exchange tube are inconsistent, it is beneficial to improve the heat exchange performance of the heat exchanger and to uniformly exchange the heat. The degree of superheat at the heater outlet.
  • the applicant also found that the greater the difference in the flow area between the multiple channels of the heat exchange tube, for example, the greater the cross-sectional area difference between the channel with the largest cross-sectional area and the channel with the smallest cross-sectional area, the greater the cross-sectional area difference between the channels of the refrigerant heat exchanger.
  • the total area of the through holes on the first piece is related to the distribution of the refrigerant among the heat exchange tubes. At the same time, the area of the through holes affects the flow rate of the refrigerant flowing out of the first piece. The larger the flow rate, the better the two-phase refrigerant.
  • the total area of the through holes is too large, it is not conducive to the mixing of two-phase refrigerants, resulting in aggravated gas-liquid separation and reduced heat exchange performance. If the total area of the through holes is too small, the pressure drop will be large when the refrigerant circulates, which will also affect the heat transfer performance. Therefore, the area of the through hole on the first piece needs to be designed according to the condition of the heat exchanger.
  • the distribution of the refrigerant in each heat exchange tube and each channel of the heat exchange tube affects each other. If there is no more refrigerant entering the channel with the largest cross-sectional area or evenly distributed among the various channels of the heat exchange tube, it is detrimental to the heat exchange performance. On the contrary, if the distribution of the refrigerant in the first tube is not balanced, through the design of each channel of the heat exchange tube, the distribution of the refrigerant in each channel of the heat exchange tube can adjust the superheat degree of the refrigerant at the outlet of the heat exchanger and reduce the exchange rate. Influence of thermal performance.
  • the applicant found that, on the cross section of the heat exchange tube, the channel with the largest cross-sectional area is taken as the first channel, and the cross-sectional area of the first channel is defined as A1, and the channel with the smallest cross-sectional area is taken as the second channel.
  • the cross-sectional area of the second channel is defined as A2
  • the number of heat exchange tubes connected to the main channel is N
  • the sum of the flow cross-sectional areas of the multiple through holes of the first piece is A3, there is a design relationship: (A1-A2 )*N/A3, as shown in Figure 14, when (A1-A2)*N/A3 ⁇ 0.15 or (A1-A2)*N/A3>3.8, the heat exchange performance of the heat exchanger decreases, when When 0.15 ⁇ (A1-A2)*N/A3 ⁇ 3.8, the design of the heat exchanger adjusts the distribution of the refrigerant between each heat exchange tube and each channel of the same heat exchange tube, which is beneficial to the performance of heat exchanger 1. Heat transfer performance is improved.
  • the first piece is arranged in the main channel of the first tube to define the first flow channel and the second flow channel in the main channel, and a plurality of heat exchange tubes are arranged in the main channel.
  • the cross-sectional areas of the channels are inconsistent, so that the cross-sectional area A1 of the first channel on the cross-section of the heat exchange tube, the cross-sectional area A2 of the second channel on the cross-section of the heat exchange tube, and the number of heat exchange tubes connected to the second flow channel.
  • the number N satisfies: 0.15 ⁇ (A1-A2)*N/A3 ⁇ 3.8, which can adjust the distribution of refrigerant in the heat exchanger, improve the heat exchange performance of the heat exchanger, and at the same time adjust the superheat at the outlet of the heat exchanger to reduce
  • the opening degree of the expansion valve fluctuates to improve the stability of the refrigeration and air-conditioning system.
  • the first piece 40 is a third pipe (distribution pipe), the third pipe includes a third peripheral wall, and the third peripheral wall is located in the first flow channel 1011 and the second flow channel 1012 In between, the third peripheral wall has a plurality of through holes 401 penetrating the peripheral wall, the through holes 401 communicate with the first flow channel 1011 and the second flow channel 1012, the third pipe communicates with the inlet and outlet pipes 60, or the third pipe includes an inlet and outlet Tube.
  • the third pipe includes a third pipe (distribution pipe)
  • the third pipe includes a third peripheral wall
  • the third peripheral wall is located in the first flow channel 1011 and the second flow channel 1012
  • the third peripheral wall has a plurality of through holes 401 penetrating the peripheral wall, the through holes 401 communicate with the first flow channel 1011 and the second flow channel 1012, the third pipe communicates with the inlet and outlet pipes 60, or the third pipe includes an inlet and outlet Tube.
  • the third pipe is a round pipe and is inserted into the main channel 101 along the left-right direction.
  • a second flow channel 1012 is formed between the peripheral wall of the third tube and the inner peripheral wall of the first tube 10, and a first flow channel 1011 (the third channel of the third tube is formed in the third tube). ), the first flow channel 1011 and the second flow channel 1012 are communicated through the through hole 401 .
  • the refrigerant flows into the first flow channel 1011 along the inlet and outlet pipes 60, the refrigerant in the first flow channel 1011 flows into the second flow channel 1012 through the through holes 401 on the third tube, and passes through the second flow channel 1012 and the heat exchange tube.
  • the communication of 30 flows into the heat exchange tube 30, and the refrigerant is in the heat exchanger 1 for heat exchange.
  • the side of the heat exchanger 1 located upstream in the wind direction during heat exchange is defined as the windward side
  • the side of the heat exchanger 1 downstream of the wind direction is defined as the leeward side.
  • the side where the through holes 401 located upstream are located is the windward side
  • the side where the through holes 401 located downstream are located is the leeward side.
  • the angle between the through hole 401 located upstream and the inlet direction of the channel 301 of the heat exchange tube 30 is a1, and the through hole 401 located downstream and the channel of the heat exchange tube 30 are 0 degrees.
  • the angle formed by the entrance direction of 301 is a2, wherein the angle range of a1 is 0-180 degrees (including 0 degrees and 180 degrees), and the angle range of a2 is 180-360 degrees.
  • a first channel of the plurality of channels 301 is located on the windward side, and at least part of the plurality of through holes are located on the leeward side. Therefore, the flow resistance of the refrigerant passing through the first channel is small, so that more refrigerant can flow to the windward side, and the temperature difference between the air flow on the windward side and the refrigerant is large, thereby improving the heat exchange performance.
  • the sum of the flow cross-sectional areas of the channels located on the windward side of the plurality of channels 301 is greater than the sum of the flow cross-sectional areas of the channels located on the leeward side of the plurality of channels 301 , and at least part of the plurality of through holes 401 are located on the leeward side. Leeward side.
  • the wind is suitable for blowing through the heat exchange tubes 30 from upstream to downstream.
  • the first passage is located on the upstream windward side, and parts of the plurality of through holes 401 are located on the downstream leeward side.
  • a part of the channels with a smaller sum of flow areas can be arranged on the leeward side of the heat exchange tube, and another part of the channels with a larger sum of flow areas can be arranged on the windward side of the heat exchange tubes, and at least part of the through holes are arranged Located on the leeward side of the heat exchange tube, the inner wall of the first tube can be used to rebound, which is conducive to more refrigerant flowing to the windward side, adjusting the superheat degree of the outlet of the heat exchanger, and improving the heat exchange performance of the heat exchanger.
  • all the through holes 401 are located on the leeward side, and the heat exchange performance of the heat exchanger is better.
  • a part of the through holes 401 of the third pipe are located on the windward side, and another part of the through holes 401 of the third pipe are located on the leeward side, and the cross-sectional areas of the through holes 401 on the windward side are combined.
  • the sum is smaller than the sum of the cross-sectional areas of the through holes 401 on the leeward side.
  • a part of the through holes with a smaller sum of cross-sectional areas can be arranged on the leeward side of the heat exchange tube, and another part of the through holes with a larger sum of cross-sectional areas can be arranged on the windward side of the heat exchange tube, so that the The through-hole area on the windward side reduces the through-hole area on the leeward side, thereby allowing more refrigerant to flow to the windward side, reducing the difference between the refrigerant superheat on the windward side and the leeward side, improving the refrigerant distribution of the heat exchanger, and improving the exchange rate. Heat transfer performance of the heater.
  • (A1-A2)/A4 ⁇ 0.09 where A4 is the maximum flow cross-sectional area of the third tube.
  • A4 is the maximum flow cross-sectional area of the third tube.
  • the heat exchange performance of the heat exchanger 1 gradually increases with the increase of (A1-A2)/A4.
  • the heat exchange performance of the heat exchanger 1 is greatly improved.
  • the distance I between at least two adjacent through holes 401 satisfies: 20mm ⁇ I ⁇ 150mm. Therefore, the number of the through holes 401 can be reasonably set, so as to prevent the total area of the through holes from being too large or too small, and improve the reliability and uniformity of the refrigerant distribution by the third tube. Preferably, when 20mm ⁇ I ⁇ 150mm, the distribution effect of the refrigerant is better.
  • the first piece 40 is not limited to the third tube shown in FIGS. 2 and 3 .
  • the first piece 40 may also be a plate body passing through the main channel 101 in the left-right direction, and the plate body has through holes 401 arranged at intervals in the left-right direction and penetrating the plate body,
  • the plate body defines a second flow channel 1012 on the rear side of the plate body and a first flow channel 1011 on the front side of the plate body in the main channel 101.
  • the refrigerant flows into the first flow channel 1011 through the inlet and outlet pipes 60.
  • the refrigerant flows into the second flow channel 1012 on the rear side of the plate body through the through hole 401 on the plate body.
  • the first tube 10 includes a first end surface, and in the length direction of the first tube 10 (the left-right direction in FIG. 2 ), the plurality of through holes 401 are adjacent to the first end surface.
  • the through hole 401 of the first end face of a tube 10 (the right end face of the first tube 10 in FIG. 2 ) is the first through hole, and the heat exchange tube 30 adjacent to the first end face of the first tube 10 among the plurality of heat exchange tubes 30 for the first heat exchange tube.
  • the plurality of heat exchange tubes 30 include second heat exchange tubes.
  • the number of heat exchange tubes 30 located between the first heat exchange tube and the second heat exchange tube is greater than or equal to 10 and less than or equal to 10.
  • the minimum distance between the first through hole and the first end surface 50 of the first tube 10 in the length direction of the first tube 10 is smaller than that between the second heat exchange tube 30 and the first end surface 50 of the first tube 10 in the first tube 10 .
  • the minimum distance in the length direction of the tube 10 is the minimum distance in the length direction of the tube 10 .
  • the rightmost heat exchange tube 30 among the plurality of heat exchange tubes 30 is the first heat exchange tube, and counted from right to left from the first heat exchange tube, And the first heat exchange tube is used as the first heat exchange tube 30 until the 10th heat exchange tube 30 or the 30th heat exchange tube 30 is counted as the second heat exchange tube, and the rightmost among the plurality of through holes 401
  • the through hole 401 is a first through hole, and the distance between the right edge of the outer peripheral wall of the first through hole and the right end face of the first tube 10 in the left-right direction is smaller than that between the right side of the second heat exchange tube and the first tube 10 The distance in the left-right direction of the right end face of .
  • the cross-sectional areas of the plurality of channels 301 gradually change along the width direction of the heat exchange tube 30 (up and down direction in FIG. 5 ). Therefore, the difference in the cross-sectional area of multiple channels can be used to increase the cross-sectional area of the channel on the windward side and reduce the cross-sectional area of the channel on the leeward side, so that more refrigerant flows to the windward side, and the holes between the heat exchange tubes are optimized. distribution to improve heat transfer performance.
  • the spacing distance between two adjacent channels 301 in the width direction of the heat exchange tube 30 (up and down direction in FIG. 5 ) If they are equal, the cross-sectional areas of the two adjacent channels 301 are not equal. In other words, in the width direction of the heat exchange tubes 30 , the channels 301 are evenly spaced, that is, the thicknesses of the partition walls between the through holes are equal, so as to further optimize the distribution of the refrigerant in the heat exchange tubes 30 .
  • the outer peripheral contour of the cross section of the heat exchange tube 30 is substantially quadrilateral, and the inner diameter of the second tube 20 is 1.1 times or more than the width of the heat exchange tube 30 . Therefore, when the refrigerant in each channel flows into the second pipe, the pressure of the refrigerant can be reduced, so as to adjust the distribution of the refrigerant in each channel, and at the same time, the pressure on the suction side of the air conditioning and refrigeration system can be reduced, and the performance of the air conditioning and refrigeration system can be improved.
  • the heat exchange tube 30 includes a first side surface and a second side surface arranged side by side in the thickness direction (the left-right direction in FIG. 3 ) of the heat exchange tube 30 , and the channel 301 is connected to the heat exchange tube 30 .
  • the minimum distance between the first side of the tube 30 in the thickness direction of the heat exchange tube 30 is the first distance, and the first distances of the plurality of channels 301 are equal.
  • the minimum distance in the thickness direction is the second distance, and the second distances of the plurality of channels 301 are equal.
  • the edges of the plurality of channels 301 are aligned in the thickness direction of the heat exchange tube 30 , so that the channels 301 with different cross-sectional areas can be formed only by setting the dimensions of the plurality of channels 301 in the width direction of the heat exchange tube 30 to be different. , which is convenient for non-uniform design of multiple channels 301 .
  • the first distance of the channel 301 is equal to the second distance of the channel 301 .
  • a heat exchanger 1 according to an embodiment of another aspect of the present application is described below with reference to FIGS. 1-18 .
  • the heat exchanger 1 includes a first tube 10, a second tube 20, a plurality of heat exchange tubes 30 and a first piece 40.
  • the first tube 10 includes a peripheral wall and a main channel 101 surrounded by the peripheral wall. One end in the length direction of a tube 10 is the first end (the right end of the first tube 10 in FIG. 2 ).
  • the first end of the first tube 10 includes a first end face 50
  • the heat exchanger 1 further includes an inlet and outlet tube 60 .
  • the outlet pipe 60 communicates with the first pipe 10 .
  • both the first tube 10 and the second tube 20 extend in the left-right direction, and the first tube 10 and the second tube 20 are spaced apart in the front-rear direction, and the right end of the first tube 10 includes the first tube 10
  • the inlet and outlet pipes are located on the right side of the first pipe 10 , and the right end of the first pipe 10 communicates with the left end of the inlet and outlet pipes 60 .
  • One end of the heat exchange tube 30 is communicated with the first tube 10, the other end of the heat exchange tube 30 is communicated with the second tube 20, the heat exchange tube 30 is communicated with the first tube 10 and the second tube 20, and the heat exchange tube 30 includes A plurality of channels 301, the channels 301 communicate with the first tube 10 and the second tube 20, in the cross section of the heat exchange tube 30, the cross-sectional areas of at least three channels 301 are not equal, and the plurality of channels 301 include a first channel and a second channel On the cross section of the heat exchange tube 30, the cross-sectional area of the first channel is larger than the cross-sectional area of the remaining channels in the plurality of channels except the first channel, and the cross-sectional area of the second channel is smaller than the cross-sectional area of the second channel in the plurality of channels except the second channel. Cross-sectional area of channels other than channels.
  • each heat exchange tube 30 extends in the front-rear direction, and a plurality of heat exchange tubes 30 are arranged at intervals between the first tube 10 and the second tube 20 in the left-right direction. In communication with the first tube 10 , the rear end of the heat exchange tube 30 is in communication with the second tube 20 . As shown in FIG. 4 and FIG. 5 , each heat exchange tube 30 is formed with a plurality of channels 301 arranged at intervals in the up-down direction, and the channels 301 extend in the front-rear direction, and the front end of the channel 301 communicates with the first tube 10 .
  • the rear end of 301 communicates with the second pipe 20 , the channel 301 with the largest cross-sectional area among the plurality of channels 301 is the first channel, and the channel 301 with the smallest cross-sectional area among the plurality of channels 301 is the second channel.
  • the cross-sectional areas of the multiple channels 301 are different, and the multiple channels 301 may include a large channel and a small channel (as shown in FIG. 6 ), or may include a group of large channels A channel and a group of small channels (as shown in FIG. 7 ), or the cross-sectional area of the multiple channels 301 gradually changes along the width direction of the heat exchange tube 30 (as shown in FIG.
  • the cross-sectional area of the channels 301 can also be varied along the width direction of the heat exchange tube 30 according to a specific rule, such as a polynomial rule or an exponential rule.
  • the first piece 40 is located in the main channel 101 of the first tube 10, the first piece 40 extends for a certain distance along the length direction of the first tube 10, the main channel 101 includes a first flow channel 1011 and a second flow channel 1012, the first piece 40 is located between the first flow channel 1011 and the second flow channel 1012, the first flow channel 1011 is communicated with the inlet and outlet pipes 60, and the second flow channel 1012 is communicated with the heat exchange tube 30.
  • the first piece 40 includes a plurality of through holes 401. 401 communicates with the first flow channel 1011 and the second flow channel 1012 .
  • the first piece 40 penetrates the main channel 101 in the left-right direction, the first piece 40 has through holes 401 spaced along the left-right direction, the first flow channel 1011 and the second flow channel 1012 Both extend in the left-right direction and the first piece 40 separates the first flow channel 1011 and the second flow channel 1012, the right end of the first flow channel 1011 is communicated with the inlet and outlet pipes 60, and the second flow channel 1012 is connected with the plurality of heat exchange tubes 30. Front-end connectivity.
  • the refrigerant is suitable for flowing into the first flow channel 1011 along the inlet and outlet pipes 60, and the refrigerant in the first flow channel 1011 flows into the second flow channel 1012 through the through hole 401 on the first piece 40, and passes through the second flow channel
  • the communication between 1012 and the heat exchange tube 30 flows into the heat exchange tube 30 for further heat exchange.
  • the through hole 401 adjacent to the first end face 50 of the first tube 10 among the plurality of through holes 401 is the first through hole.
  • the hole 401 is a first through hole, and the minimum distance between the first through hole and the first end face 50 of the first tube 10 in the length direction of the first tube 10 is d3, and d3 ⁇ (10d1+9d2)*A1/A2,
  • d1 is the thickness of the heat exchange tubes 30
  • d2 is the minimum distance between adjacent heat exchange tubes 30 in the length direction of the first tubes 10
  • A1 is the cross-sectional area of the first channel on the cross section of the heat exchange tubes 30
  • A2 is the cross-sectional area of the second channel on the cross-section of the heat exchange tube 30 .
  • the rightmost through hole 401 among the plurality of through holes 401 is the first through hole, and the right edge of the outer peripheral wall of the first through hole is connected to the right end surface of the first tube 10 .
  • the distance in the left-right direction is smaller than the distance between the right side of the second heat exchange tube and the right end surface of the first tube 10 in the left-right direction. Minimum distance d3 in the direction.
  • the distance exceeds the set value the refrigerant accumulates at the end, which affects the superheat degree of the heat exchange tubes near the inlet and outlet pipes, resulting in a serious imbalance in the distribution of refrigerant between the heat exchange tubes and a decrease in heat exchange performance.
  • the inventor found that the thickness d1 of the heat exchange tube, the minimum distance d2 between adjacent heat exchange tubes in the length direction of the first tube, and the cross-sectional area of the first channel on the cross section of the heat exchange tube There is a relationship between A1 and the cross-sectional area A2 of the second channel on the cross-section of the heat exchange tube: (10d1+9d2)*A1/A2, when d3 ⁇ (10d1+9d2)*A1/A2, the heat exchanger exchanges heat High performance.
  • the first piece having a plurality of through holes is arranged in the main channel of the first pipe to define the first flow channel and the second flow channel in the main channel, and the The cross-sectional areas of the multiple channels in the heat exchange tube are inconsistent, the cross-sectional area A1 of the first channel on the cross section of the heat exchange tube, the cross-sectional area A2 of the second channel on the cross section of the heat exchange tube, and the thickness of the heat exchange tube d1 , the minimum distance d2 between adjacent heat exchange tubes in the length direction of the first tube and the distance d3 from the first through hole of the first piece to the end of the first tube satisfy: d3 ⁇ (10d1+9d2)*A1 /A2, the superheat degree of each heat exchange tube can be made uniform, so that the refrigerant distribution between the heat exchange tubes is reasonable and the performance of the heat exchanger is improved.
  • one end of the third pipe communicates with the inlet and outlet pipes 60, and the other end of the third pipe has an orifice, and the flow area of the orifice is smaller than the flow cross-sectional area of the third pipe. In this way, the internal flow of the first tube is promoted, the refrigerant distribution between the tubes is more uniform, and the heat exchange performance is improved.
  • the hydraulic diameter of the second tube 20 is greater than or equal to 1.1 times the hydraulic diameter of the first tube 10 . Therefore, the pressure drop in the heat exchange tube and the first tube can be balanced, the refrigerant distribution of the heat exchange tube can be more uniform, and the pressure drop on the suction side of the refrigeration system can be reduced to improve the performance of the refrigeration system.
  • the outer peripheral contour of the cross section of the heat exchange tube 30 is substantially quadrilateral, and the inner diameter of the second tube 20 is 1.1 times or more the width of the heat exchange tube 30 . Therefore, the pressure drop in the heat exchange tube and the first tube can be balanced, the refrigerant distribution of the heat exchange tube can be more uniform, and the pressure drop on the suction side of the refrigeration system can be reduced to improve the performance of the refrigeration system.
  • a heat exchanger 1 according to some examples of the present application is described below with reference to FIGS. 1-13 .
  • the heat exchanger 1 includes a first tube 10 , a second tube 20 , a third tube, an inlet and outlet tube 60 and a plurality of heat exchange tubes 30 .
  • Both the first tube 10 and the first tube 10 extend in the left-right direction, and the first tube 10 and the second tube 20 are spaced apart in the front-rear direction, and a plurality of heat exchange tubes 30 are communicated between the first tube 10 and the second tube 20 .
  • the plurality of heat exchange tubes 30 are arranged at intervals along the left-right direction, the front ends of the plurality of heat exchange tubes 30 communicate with the first tube 10 , and the rear ends of the plurality of heat exchange tubes 30 communicate with the second tube 20 .
  • the first pipe 10 includes a first end surface 50 and a main channel extending in the left-right direction.
  • the third pipe is inserted into the main channel in the left-right direction.
  • a first flow channel 1011 is formed in the third pipe.
  • a second flow channel 1012 is formed between the inner peripheral walls of the heat exchange tubes 30, and the front end of the heat exchange tube 30 communicates with the second flow channel 1012.
  • the peripheral wall of the third tube is provided with a plurality of spaced apart along the length direction of the third tube and passing through the third tube. Through holes 401 in the peripheral wall.
  • the right end of the third pipe is open, and the opening of the third pipe is communicated with the inlet of the first pipe 10 , the refrigerant is suitable for flowing into the first flow through the inlet of the first pipe 10 , and the refrigerant in the second flow channel 1012 passes through the through hole 401 Flowing into the second flow channel 1012, the refrigerant in the second flow channel 1012 can flow into the heat exchange tube 30 for heat exchange.
  • the heat exchange tube 30 has a plurality of channels 301 spaced in the up-down direction, the plurality of channels 301 extend in the front-rear direction, the cross-sectional area of the plurality of channels 301 gradually changes along the up-down direction, and a through hole 401 with a larger sum of cross-sectional areas
  • the through hole 401 with the smaller sum of cross-sectional areas is arranged on the upper side (leeward side) of the heat exchange tube 30, and the edges of the plurality of channels 301 are located in the heat exchange tube 30.
  • 30 are aligned in the thickness direction, and the minimum distances of adjacent channels 301 in the vertical direction among the plurality of channels 301 are equal.
  • the heat exchange tube 30 located on the far right is the first heat exchange tube 30, and the plurality of heat exchange tubes 30 include the second heat exchange tube.
  • the number of heat exchange tubes 30 located between the first heat exchange tube and the second heat exchange tube is greater than or equal to 10 and less than 30, and the rightmost through hole 401 is located.
  • the through hole 401 is a first through hole, and the first through hole is located between the first heat exchange tube 30 and the second heat exchange tube 30 .
  • the first piece 40 is a plate body passing through the main channel 101 in the left-right direction. Hole 401, the plate body defines a second flow channel 1012 on the rear side of the plate body and a first flow channel 1011 on the front side of the plate body in the main channel 101, the refrigerant flows into the first flow channel 1011 through the inlet and outlet pipes 60, the first flow channel The refrigerant in 1011 flows into the second flow channel 1012 on the rear side of the plate body through the through hole 401 on the plate body.
  • the terms “installed”, “connected”, “connected”, “fixed” and other terms should be understood in a broad sense, for example, it may be a fixed connection or a detachable connection , or integrated; it can be a mechanical connection or an electrical connection or can communicate with each other; it can be directly connected or indirectly connected through an intermediate medium, it can be the internal connection of two components or the interaction relationship between the two components, unless otherwise expressly qualified.
  • installed installed
  • connected connected
  • fixed a detachable connection
  • it can be a mechanical connection or an electrical connection or can communicate with each other
  • it can be directly connected or indirectly connected through an intermediate medium, it can be the internal connection of two components or the interaction relationship between the two components, unless otherwise expressly qualified.
  • the specific meanings of the above terms in this application can be understood according to specific situations.
  • a first feature "on” or “under” a second feature may be in direct contact with the first and second features, or the first and second features indirectly through an intermediary get in touch with.
  • the first feature being “above”, “over” and “above” the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is level higher than the second feature.
  • the first feature being “below”, “below” and “below” the second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature has a lower level than the second feature.

Abstract

本申请的实施例公开了一种换热器，所述换热器包括第一管、第二管、多个换热管、进出口管和第一件，第一管具有主通道，换热管连接在第一管与第二管之间，换热管包括间隔布置的多个通道，至少三个通道的截面积两两不同，多个通道包括截面积最大的第一通道和截面积最小的第二通道；第一件位于第一管的主通道内以限定出第一流道和第二流道，第一流道与进出口管连通，第二流道与换热管连通，第一件包括通孔，第一通道在换热管的横截面上的截面积为A1，第二通道在所述换热管的横截面上的截面积为A2，A1，A2满足以下关系式：0.15≤(A1-A2)*N/A3≤3.8，其中，A3为第一件的多个通孔的流通截面积之和，N为换热管的个数。本申请的实施例的换热器，换热器中冷媒分配得以调节，换热性能高。

Description

换热器 技术领域
本申请的实施例涉及换热技术领域，更具体地，涉及一种换热器。
背景技术
目前，多通道换热器广泛应用在各空调领域。相关技术中，多通道换热器采用多个多通道换热管进行换热，多通道换热管的宽度方向上间隔分布有多个通道，冷媒流入换热器时会在多个换热管之间进行分配，之后又在换热管的各个通道之间进行分配，冷媒在换热管以及各通道之内的分配情况影响了换热器的换热性能，在某些应用中，不利于多通道换热器换热性能的提高。
发明内容
为此，本申请的实施例提出了一种换热器，该换热器可调节换热器中冷媒的分配情况，有利于提高换热器的换热性能。
根据本申请的第一方面的实施例的换热器包括：
第一管和第二管，所述第一管包括周壁和由周壁包围形成的主通道，所述换热器还包括进出口管，所述进出口管与所述第一管连通；
多个换热管，所述换热管连通所述第一管和所述第二管，所述换热管包括间隔布置的多个通道，所述通道连通所述第一管和所述第二管，在所述换热管的横截面上，多个所述通道中至少三个通道的截面积两两不相等，多个所述通道包括第一通道和第二通道，在所述换热管的横截面上，所述第一通道的截面积大于多个通道中除第一通道之外的其余通道的截面积，所述第二通道的截面积小于多个通道中除第二通道之外的其他通道的截面积；
第一件，所述第一件位于所述第一管的主通道内，所述第一件沿所述第一管的长度方向延伸一定的距离，所述主通道包括第一流道和第二流道，所述第一件位于所述第一流道和所述第二流道之间，，所述第一流道与所述进出口管连通，所述第二流道与所述换热管连通，所述第一件包括多个通孔，所述通孔连通所述第一流道和所述第二流道，
所述第一通道在所述换热管的横截面上的截面积为A1，所述第二通道在所述换热管的横截面上的截面积为A2，所述A1，A2满足以下关系式：0.15≤(A1-A2)*N/A3≤3.8，其中，A3为所述第一件的多个所述通孔的流通截面积之和，N为所述主通道连通的换热管的个数。
根据本申请实施例的换热器，通过在第一管的主通道内设置第一件以在主通道内限定出第一流道和第二流道，且设置换热管内的多个通道的截面积不一致，使第一通道在换热管的横截面上的截面积A1、第二通道在换热管的横截面上的截面积A2和第二流道连通的 换热管的个数N满足：0.15≤(A1-A2)*N/A3≤3.8，可调节换热器中冷媒的分配，提升换热器的换热性能，同时可以调节换热器出口的过热度，减小膨胀阀的开度波动，提升制冷空调系统的稳定性。
在一些实施例中，所述第一件为第三管，所述第三管包括第三周壁，所述第三周壁位于所述第一流道和所述第二流道之间，所述第三周壁上具有贯穿该周壁的所述通孔，所述通孔连通所述第一流道和第二流道，所述第三管与所述进出口管连通，或者所述第三管包括所述进出口管。
在一些实施例中，定义所述换热器在换热时位于风向上游的一侧为迎风侧，且定义所述换热器风向下游的一侧为背风侧，所述第一通道位于所述迎风侧。
在一些实施例中，定义所述换热器位于风向上游的一侧为迎风侧，且定义所述换热器风向下游的一侧为背风侧，多个通道中位于所述迎风侧的通道的流通截面积之和大于多个通道中位于所述背风侧的通道的流通截面积之和。
在一些实施例中，所述分配管多个所述通孔中的一部分通孔位于所述迎风侧，多个所述通孔中的另一部分通孔位于所述背风侧，所述迎风侧的通孔的横截面积之和小于所述背风侧的通孔的横截面积之和。
在一些实施例中，(A1-A2)/A4≤0.09，其中，A4是所述第三管的最大流通截面积。
在一些实施例中，在所述第三管的长度方向上，至少两个相邻所述通孔之间的距离I满足：20mm≤I≤150mm。
在一些实施例中，所述第一管包括第一端面，在所述第一管的长度方向上，多个所述通孔中邻近所述第一管的第一端面的通孔为第一通孔，多个所述换热管中邻近所述第一管的第一端面的换热管为第一换热管，多个所述换热管中包括第二换热管，在所述第一管的长度方向上，位于所述第一换热管与所述第二换热管之间的所述换热管的数量大于等于10个且小于30个，所述第一通孔与所述第一端面在所述第一管的长度方向上的最小距离小于所述第二换热管与所述第一端面在所述第一管的长度方向上的最小距离。
在一些实施例中，在所述换热管的横截面上，在所述换热管的宽度方向上两个相邻所述通道之间的间隔距离相等，该两个相邻所述通道的截面积不相等。
在一些实施例中，所述换热管的横截面的外周轮廓大体为四边形，所述第二管的内径是所述换热管的宽度的1.1倍及以上。
根据本申请的第二方面的实施例的换热器包括：第一管和第二管，所述第一管包括周壁和由周壁包围形成的主通道，所述第一管长度方向上的一端为第一端，所述第一管的第一端包括第一端面，所述换热器还包括进出口管，所述进出口管与所述第一管连通；多个换热管，所述换热管连通所述第一管和所述第二管，所述换热管包括间隔布置的多个通道， 至少三个所述通道的截面积不相等，所述通道连通所述第一管和所述第二管，在所述换热管的横截面上，多个所述通道的截面积沿多个所述通道的间隔方向变化，多个所述通道包括第一通道和第二通道，在所述换热管的横截面上，所述第一通道的截面积大于多个通道中除第一通道之外的其余通道的截面积，所述第二通道的截面积小于多个通道中除第二通道之外的其他通道的截面积；第一件，所述第一件位于所述第一管的主通道内，所述第一件沿所述第一管的长度方向延伸一定的距离，所述主通道包括第一流道和第二流道，所述第一件位于所述第一流道和所述第二流道之间，所述第一流道与所述进出口管连通，所述第二流道与所述换热管连通，所述第一件包括多个通孔，所述通孔连通所述第一流道和所述第二流道，多个所述通孔中，与所述第一管的第一端面之间的距离最小的通孔为第一通孔，所述第一通孔与所述第一管的第一端面在所述第一管的长度方向上的最小距离为d3，且d3＜(10d1+9d2)*A1/A2，其中d1为所述换热管的厚度，d2为在所述第一管的长度方向上相邻所述换热管之间的最小距离，A1为所述第一通道在所述换热管的横截面上的截面积，A2为所述第二通道在所述换热管的横截面上的截面积。
根据本申请实施例的换热器，通过在第一管的主通道内设置具有多个通孔的第一件以在主通道内限定出第一流道和第二流道，且设置换热管内的多个通道的截面积不一致，第一通道在换热管的横截面上的截面积A1、第二通道在换热管的横截面上的截面积A2，换热管的厚度d1，在第一管的长度方向上相邻换热管之间的最小距离d2与第一件的第一通孔到第一管的端部的距离d3满足：d3＜(10d1+9d2)*A1/A2，可调节换热管的过热度，从而使各换热管之间的冷媒分配有利于提高换热器性能。
在一些实施例中，所述第一件为第三管，所述第三管包括第三周壁，所述第三周壁位于所述第一流道和所述第二流道之间，所述第三周壁上具有贯穿该周壁的多个所述通孔。
在一些实施例中，定义沿风向位于所述换热器的上游的一侧为迎风侧，且定义沿风向位于所述换热器的下游的一侧为背风侧，所述第一通道位于迎风侧，多个所述通孔中的至少部分位于背风侧。
在一些实施例中，定义所述换热器位于风向上游的一侧为迎风侧，且定义所述换热器风向下游的一侧为背风侧，多个通道中位于所述迎风侧的通道的流通截面积之和多个通道中位于所述背风侧的通道的流通截面积之和，多个所述通孔中的至少部分位于所述背风侧。
在一些实施例中，多个所述通孔中的一部分通孔位于所述迎风侧，多个所述通孔中的另一部分通孔位于所述背风侧，所述迎风侧的通孔的横截面积之和小于所述背风侧的通孔的横截面积之和。
在一些实施例中，所述第三管的一端与所述进出口管连通，所述第三管的另一端具有孔口，所述孔口的流通面积小于所述第三管的流通截面积。
在一些实施例中，所述第二管的水力直径等于或等于所述第一管的水力直径的1.1倍。
在一些实施例中，所述换热管的横截面的外周轮廓大体为四边形，所述第二管的内径是所述换热管的宽度1.1倍及以上。
附图说明
图1是根据本申请的一个实施例的换热器的主视图。
图2是根据本申请的实施例的换热器的示意图，其中，第一件示出。
图3是图2中A部分的放大图。
图4是根据本申请的一个实施例的换热器的侧视图。
图5是根据本申请的一个实施例的换热器的换热管的剖视图。
图6是根据本申请的另一个实施例的换热器的换热管的剖视图。
图7是根据本申请的再一个实施例的换热器的换热管的剖视图。
图8是根据本申请的实施例的换热器的局部结构示意图。
图9是图8中沿A-A方向的剖视图。
图10根据本申请的实施例的换热器的剖视图。
图11是图10中沿B-B方向的剖视图。
图12是图10中沿B-B方向的剖视图,且示出了α1和α2。
图13是根据本申请的实施例的换热器中第一管和第一件配合的示意图。
图14是根据本申请的一个实施例的换热器的换热性能随(A1-A2)*N/A3的数值变化的曲线图。
图15是根据本申请的一个实施例的换热器(带第三管)与换热器(不带第三管)的过热度的曲线对比图。
图16是根据本申请的一个实施例的换热器(带第三管)与换热器(不带第三管)的换热性能的曲线对比图。
图17是根据本申请的一个实施例的换热器的换热性能随(A1-A2)/A4的数值变化的曲线图
图18是根据本申请的一个实施例的换热器的换热管(流通通道截面积不一致的换热管)与换热管(流通通道截面积一致的换热管)的换热性能的曲线对比图。
图19是包括根据本申请的实施例的换热器的制冷空调系统的示意图。
附图标记：
换热器1；
第一管10；主通道101；第一流道1011；第二流道1012；
第二管20；
换热管30；通道301；
第一件40；通孔401；
第一端面50；
进出口管60，
压缩机100，第一换热器200，节流件300，第二换热器400，风机500。
具体实施方式
下面详细描述本申请的实施例，所述实施例的示例在附图中示出。下面通过参考附图描述的实施例是示例性的，旨在用于解释本申请，而不能理解为对本申请的限制。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”、“轴向”、“径向”、“周向”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本申请和简化描述，而不是指示或暗示所指的装置或元夹具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。
多通道换热器在制冷空调系统中工作换热时，冷媒在多通道换热器的内部通道流过，气流通过换热器的表面与换热器里面的冷媒进行换热。如图19所示，制冷空调系统包括压缩机100、第一换热器200、节流件300、第二换热器400和风机500，其中压缩机100、第一换热器200、节流件300和第二换热器400串联形成循环回路，一个风机500对准第一换热器200以向第一换热器200吹风，另一个风机500对准第二换热器400以向第二换热器400吹风。换热器200和换热器400中的任一个或每一个可以为本申请中的换热器1。
下面参考图1-图18描述根据本申请的一个方面的实施例的换热器1。
如图1-图18所示，根据本申请实施例的换热器1包括第一管10、第二管20、多个换热管30和第一件40。
第一管10包括周壁和由周壁包围形成的主通道101，换热器1还包括进出口管60，进出口管60与第一管10连通。如图1和图2所示，第一管10和第二管20均沿左右方向延伸，且第一管10和第二管20在前后方向上间隔开，进出口管60位于第一管10的右侧，且第一管10的右端与进出口管60的左端连通。
换热管30的一端与第一管10连通，换热管30的另一端与第二管20连通，换热管30连通第一管10和第二管20，换热管30包括间隔布置的多个通道301(两个及两个以上通道301)，通道301连通第一管10和第二管20，在换热管30的横截面上，多个通道301中的至少三个通道301的截面积两两不相等，多个通道301包括第一通道和第二通道，在换热管30的横截面上，第一通道的截面积大于多个通道301中除第一通道之外的其余通道 301的截面积，第二通道的截面积小于多个通道301中除第二通道之外的其他通道301的截面积。
如图1和图2所示，换热管30沿前后方向延伸，且多个换热管30沿左右方向间隔排布在第一管10与第二管20之间，换热管30的前端与第一管10连通，换热管30的后端与第二管20连通。如图4和图5所示，每个换热管30内形成有多个沿上下方向间隔排布的通道301，且通道301沿前后方向延伸，通道301的前端与第一管10连通，通道301的后端与第二管20连通，多个通道301中截面积最大的通道301为第一通道，多个通道301中截面积最小的通道301为第二通道。需要说明的是，在该技术方案中，第一通道和第二通道均可以为多个，多个通道301的截面积可以全部不同也可以部分相同。
第一件40位于第一管10的主通道101内，第一件40沿第一管10的长度方向延伸一定的距离，第一件40在第一管10的主通道101内的长度小于等于第一管10的长度，主通道101包括第一流道1011和第二流道1012，第一件40位于第一流道1011和第二流道1012之间，第一流道1011与进出口管60连通，第二流道1012与换热管30连通，第一件40包括多个通孔401，通孔401连通第一流道1011和第二流道1012。
如图2和图3所示，第一件40沿左右方向穿设于主通道101内，第一件40上具有沿左右方向间隔布置的通孔401，第一流道1011和第二流道1012均沿左右方向延伸且第一件40将第一流道1011和第二流道1012间隔开，第一流道1011的右端与进出口管连通，第二流道1012与多个换热管30的前端连通。可以理解的是，冷媒适于沿进出口管流入第一流道1011，第一流道1011内的冷媒通过第一件40上的通孔401流入第二流道1012内，并通过第二流道1012与换热管30的连通流入换热管30内以进行进一步换热。
第一通道在换热管30的横截面上的截面积为A1，第二通道在换热管30的横截面上的截面积为A2，其中A1，A2满足以下关系式：0.15≤(A1-A2)*N/A3≤3.8，其中，A3为第一件40的多个通孔401的流通截面积之和，N为主通道101连通的换热管30的个数。
相关技术中，主通道内不设置第一件40(例如分配管)，换热管内多个通道的截面积一致，相关技术中的换热器存在换热管冷媒分布不均匀，换热效率低的问题。如图15、图16和图18所示，申请人发现，当主通道内设置第一件，且换热管内多个通道截面积不一致时，有利于提高换热器的换热性能，以及均匀换热器出口的过热度。
在此基础上，申请人还发现，换热管的多个通道之间的流通面积差异越大，例如最大截面积通道和最小截面积通道的截面积差越大，冷媒换热器的通道间分配越有利于换热性能的提升。另外，第一件上的通孔的总面积与冷媒在各换热管之间的分配相关，同时，通孔的面积影响冷媒流出第一件的流速，流速越大，越利于两相态冷媒的汽液混合均匀，越有利于换热性能提升。但是如果通孔的总面积太大，不利于两相态的冷媒混合，导致气液 分离加剧，换热性能降低。如果通孔的总面积太小，冷媒流通时压降大，同样影响换热性能。因此，第一件上通孔的面积需要根据换热器的情况进行设计。
当多个通道面积不同的换热管与第一件配合使用时，冷媒在各个换热管以及换热管的各个通道之内的分配互相影响，比如第一件管将冷媒在第一管之内进行分配，没有较多的冷媒进入到最大截面积的通道或者在换热管的各个通道之间分配均匀，对换热性能反而不利。反之，如果冷媒在第一管之内的分布不均衡，通过对换热管各个通道的设计，冷媒在换热管的各个通道中的分配可以调节换热器出口冷媒的过热度，减少对换热性能的影响。
基于上述分析，申请人发现，在换热管的横截面上，取截面积最大的通道为第一通道，且将第一通道的截面积定义为A1，取截面积最小的通道为第二通道，且将第二通道的截面积定义为A2，主通道连通的换热管的个数为N，第一件的多个通孔的流通截面积之和A3，存在设计关系：(A1-A2)*N/A3，如图14所示，当(A1-A2)*N/A3＜0.15或(A1-A2)*N/A3＞3.8时，换热器的换热性能有所降低，当0.15≤(A1-A2)*N/A3≤3.8时，换热器的设计调整了冷媒在各换热管之间以及同一换热管的各通道之间的分配，有利于换热器1的换热性能提高。
由此，根据本申请实施例的换热器，通过在第一管的主通道内设置第一件以在主通道内限定出第一流道和第二流道，且设置换热管内的多个通道的截面积不一致，使第一通道在换热管的横截面上的截面积A1、第二通道在换热管的横截面上的截面积A2和第二流道连通的换热管的个数N满足：0.15≤(A1-A2)*N/A3≤3.8，可以调节换热器中冷媒的分配，提升换热器的换热性能，同时可以调节换热器出口的过热度，减小膨胀阀的开度波动，提升制冷空调系统运行的稳定性。
在一些实施例中，如图2和图3所示，第一件40为第三管(分配管)，第三管包括第三周壁，第三周壁位于第一流道1011和第二流道1012之间，第三周壁上具有贯穿该周壁的多个通孔401，通孔401连通第一流道1011和第二流道1012，第三管与进出口管60连通，或者第三管包括进出口管。
如图2所示，第三管为圆管且沿左右方向穿设于主通道101内，第三管的一段的长度与第一管10的长度相等，第三管的周壁上具有沿左右方向间隔布置且贯通周壁的通孔401，第三管的周壁与第一管10的内周壁之间形成有第二流道1012，第三管内形成有第一流道1011(第三管的第三通道)，第一流道1011和第二流道1012通过通孔401连通。
具体地，冷媒沿进出口管60流入第一流道1011，第一流道1011内的冷媒通过第三管上的通孔401流入第二流道1012内，并通过第二流道1012与换热管30的连通流入换热管30，冷媒在换热器1内以进行换热。
在一些实施例中，如图4和图5所示，定义换热器1在换热时位于风向上游的一侧为 迎风侧，且定义换热器1风向下游的一侧为背风侧。例如图10-12所示，位于上游的通孔401所在的一侧为迎风侧，位于下游的通孔401所在的一侧为背风侧。以正对换热管1通道入口为0度，位于上游的通孔401与换热管30的通道301的入口方向所成的角度为a1，位于下游的通孔401与换热管30的通道301的入口方向所成角度为a2，其中a1角度范围为0-180度(包括0度和180度)，a2角度范围为180-360度。
多个通道301中的第一通道位于迎风侧，多个通孔中的至少部分位于背风侧。由此，冷媒通过第一通道流阻较小，从而可以使更多的冷媒流向迎风侧，且迎风侧气流与冷媒温差大，进而可以提升换热性能。
在一些实施例中，多个通道301中位于迎风侧的通道的流通截面积之和大于多个通道301中位于背风侧的通道的流通截面积之和，多个通孔401中的至少部分位于背风侧。
具体地，风适于从上游到下游的方向吹过换热管30，如图4所示，第一通道位于上游迎风侧，多个通孔401的部分位于下游背风侧。
由此，可以将流通面积之和较小的一部分通道设置在换热管的背风侧，将流通面积之和较大的另一部分通道设置在换热管的迎风侧，且通过设置至少部分通孔位于换热管的背风侧，可以利用第一管的内壁反弹，有利于更多的冷媒流向迎风侧，调节换热器的出口的过热度，提升换热器的换热性能。优选地，所有通孔401位于背风侧，换热器的换热性能更好。
在一些实施例中，第三管的多个通孔401中的一部分通孔位于迎风侧，多个通孔401中的另一部分通孔位于背风侧，迎风侧的通孔401的横截面积之和小于背风侧的通孔401的横截面积之和。
由此，可以将横截面积之和较小的一部分通孔设置在换热管的背风侧，将横截面积之和较大的另一部分通孔设置在换热管的迎风侧，从而可以增加迎风侧的通孔面积，减少背风侧的通孔面积，进而让更多的冷媒流向迎风侧，减小迎风侧和背风侧的冷媒过热度的差值，改善换热器的冷媒分配，提升换热器的换热性能。
在一些实施例中，(A1-A2)/A4≤0.09，其中，A4是第三管的最大流通截面积。如图17所示，(A1-A2)/A4≤0.09时，换热器1的换热性能随着(A1-A2)/A4的增大逐步升高。优选地，(A1-A2)/A4＝0.09时，换热器1的换热性能提升量大。
在一些实施例中，如图3所示，在第三管的长度方向上，至少两个相邻通孔401之间的距离I满足：20mm≤I≤150mm。由此，可以合理设置通孔401数量，避免通孔总面积过大或过小，提高第三管分配冷媒的可靠性和均匀性。优选地，20mm≤I≤150mm时，冷媒的分配效果更好。
需要说明的是，第一件40不限于为图2和图3所示的第三管。例如，如图8和图9所 示，第一件40还可以为沿左右方向穿设于主通道101内的板体，板体上具有沿左右方向间隔布置且贯穿板体的通孔401，板体在主通道101内限定出位于板体后侧的第二流道1012和位于板体前侧的第一流道1011，冷媒通过进出口管60流入第一流道1011，第一流道1011内的冷媒通过板体上的通孔401流入板体后侧的第二流道1012内。
在一些实施例中，如图1和图2所示，第一管10包括第一端面，在第一管10的长度方向上(图2中的左右方向)，多个通孔401中邻近第一管10的第一端面(图2中第一管10的右端面)的通孔401为第一通孔，多个换热管30中邻近第一管10的第一端面的换热管30为第一换热管。
多个换热管30包括第二换热管，在第一管10的长度方向上，位于第一换热管和第二换热管之间的换热管30的数量大于等于10个且小于30个，第一通孔的与第一管10的第一端面50在第一管10的长度方向上的最小距离小于第二换热管30与第一管10的第一端面50在第一管10的长度方向上的最小距离。
如图2、图3和图13所示，多个换热管30中最右侧的换热管30为第一换热管，从该第一换热管沿从右向左的方向数，且该第一换热管作为第一个换热管30，直至数到第10个换热管30或第30个换热管30为第二换热管，多个通孔401中最右侧的通孔401为第一通孔，第一通孔的外周壁的右侧边缘与第一管10的右端面在左右方向上的距离小于第二换热管的右侧面与第一管10的右端面在左右方向上的距离。
在一些实施例中，如图5所示，在换热管30的横截面上，多个通道301的截面积沿换热管30的宽度方向(图5中的上下方向)逐渐变化。由此，可以利用多个通道的截面积的差异，增大迎风侧的通道的截面积，减小背风侧的通道的截面积，使更多的冷媒流向迎风侧，优化换热管的孔间分配，提高换热性能。
在一些实施例中，如图5所示，在换热管30的横截面上，在换热管30的宽度方向上(图5中的上下方向)两个相邻通道301之间的间隔距离相等，该两个相邻通道301的截面积不相等。换言之，在换热管30的宽度方向上，多个通道301均匀间隔布置，即通孔与通孔之间的间隔壁的厚度相等，从而进一步优化换热管30内的冷媒分配。
在一些实施例中，如图8所示，换热管30的横截面的外周轮廓大体为四边形，第二管20的内径是换热管30的宽度的1.1倍及以上。由此，可以在各通道内的冷媒流入第二管时，降低冷媒压力，从而调节各通道内的冷媒的分配，同时可以降低空调制冷系统吸气侧压力，提升空调制冷系统性能。
在一些实施例中，如图3所示，换热管30包括在换热管30的厚度方向(图3中的左右方向)上并列布置的第一侧面和第二侧面，通道301与换热管30的第一侧面在换热管30的厚度方向上的最小距离为第一距离，多个通道301的第一距离相等，通道301与换热 管30的第二侧面在换热管30的厚度方向上的最小距离为第二距离，多个通道301的第二距离相等。
换言之，多个通道301的边缘在换热管30的厚度方向上对齐，由此只需要设置多个通道301在换热管30的宽度方向上的尺寸不同，即可形成不同截面积的通道301，便于多个通道301的非一致性设计。优选地，通道301的第一距离与通道301的第二距离相等。
下面参考图1-图18描述根据本申请的另一个方面的实施例的换热器1。
根据本发明实施例的换热器1包括第一管10、第二管20、多个换热管30和第一件40，第一管10包括周壁和由周壁包围形成的主通道101，第一管10长度方向上的一端为第一端(图2中第一管10的右端)，第一管10的第一端包括第一端面50，换热器1还包括进出口管60，进出口管60与第一管10连通。
如图1和图2所示，第一管10和第二管20均沿左右方向延伸，且第一管10和第二管20在前后方向上间隔开，第一管10的右端包括第一端面，进出口管位于第一管10的右侧，且第一管10的右端与进出口管60的左端连通。
换热管30的一端与第一管10连通，换热管30的另一端与第二管20连通，换热管30连通第一管10和第二管20，换热管30包括间隔布置的多个通道301，通道301连通第一管10和第二管20，在换热管30的横截面上，至少三个通道301的截面积不相等，多个通道301包括第一通道和第二通道，在换热管30的横截面上，第一通道的截面积大于多个通道中除第一通道之外的其余通道的截面积，第二通道的截面积小于多个通道中除第二通道之外的其他通道的截面积。
如图1和图2所示，换热管30沿前后方向延伸，且多个换热管30沿左右方向间隔排布在第一管10与第二管20之间，换热管30的前端与第一管10连通，换热管30的后端与第二管20连通。如图4和图5所示，每个换热管30内形成有多个沿上下方向间隔排布的通道301，且通道301沿前后方向延伸，通道301的前端与第一管10连通，通道301的后端与第二管20连通，多个通道301中截面积最大的通道301为第一通道，多个通道301中截面积最小的通道301为第二通道。
需要说明的是，如图6和图7所示，多个通道301的截面积不同，多个通道301可以包括一个大通道和一个小通道(如图6所示)，也可以包括一组大通道和一组小通道(如图7所示)，或者，多个通道301的截面积沿着换热管30的宽度方向逐渐变化(如图5所示)，也可以是通道301的截面积沿换热管30的宽度方向以一定的比例变化，当然也可以是通道301的截面积沿着换热管30的宽度方向以特定的规则，比如多项式规则，指数规则进行变化。
第一件40位于第一管10的主通道101内，第一件40沿第一管10的长度方向延伸一 定的距离，主通道101包括第一流道1011和第二流道1012，第一件40位于第一流道1011和第二流道1012间，第一流道1011与进出口管60连通，第二流道1012与换热管30连通，第一件40包括多个通孔401，通孔401连通第一流道1011和第二流道1012。
如图2和图3所示，第一件40沿左右方向穿设于主通道101内，第一件40上具有沿左右方向间隔布置的通孔401，第一流道1011和第二流道1012均沿左右方向延伸且第一件40将第一流道1011和第二流道1012间隔开，第一流道1011的右端与进出口管60连通，第二流道1012与多个换热管30的前端连通。可以理解的是，冷媒适于沿进出口管60流入第一流道1011，第一流道1011内的冷媒通过第一件40上的通孔401流入第二流道1012内，并通过第二流道1012与换热管30的连通流入换热管30内以进行进一步换热。
多个通孔401中邻近第一管10的第一端面50的通孔401为第一通孔，多个通孔401中，与第一管10的第一端面50之间的距离最小的通孔401为第一通孔，第一通孔与第一管10的第一端面50在第一管10的长度方向上的最小距离为d3，且d3＜(10d1+9d2)*A1/A2，其中d1为换热管30的厚度，d2为在第一管10的长度方向上相邻换热管30之间的最小距离，A1为第一通道在换热管30的横截面上的截面积，A2为第二通道在换热管30的横截面上的截面积。
如图2、图3和图13所示，多个通孔401中最右侧的通孔401为第一通孔，第一通孔的外周壁的右侧边缘与第一管10的右端面在左右方向上的距离小于第二换热管的右侧面与第一管10的右端面在左右方向上的距离为第一通孔与第一管10的右端面(第一端面)在左右方向上的最小距离d3。
发明人发现，第一件的第一通孔到第一管的端部的距离d3会影响冷媒的管间分配，第一管的端部与进出口管邻近，当该距离超过设定值之后，冷媒在端部积聚，影响进出口管附近的换热管的过热度，导致换热管间冷媒分配严重不平衡，换热性能下降。
在此基础上，发明人发现，换热管的厚度d1，在第一管的长度方向上相邻换热管之间的最小距离d2，第一通道在换热管的横截面上的截面积A1和第二通道在换热管的横截面上的截面积A2存在关系式：(10d1+9d2)*A1/A2，当d3＜(10d1+9d2)*A1/A2时，换热器换热性能高。
由此，根据本发明实施例的换热器，通过在第一管的主通道内设置具有多个通孔的第一件以在主通道内限定出第一流道和第二流道，且设置换热管内的多个通道的截面积不一致，第一通道在换热管的横截面上的截面积A1、第二通道在换热管的横截面上的截面积A2，换热管的厚度d1，在第一管的长度方向上相邻换热管之间的最小距离d2与第一件的第一通孔到第一管的端部的距离d3满足：d3＜(10d1+9d2)*A1/A2，可以使各换热管的过热度均匀，从而使换热管间冷媒分配合理，提高换热器性能。
在一些实施例中，第三管的一端与进出口管60连通，第三管的另一端具有孔口，孔口的流通面积小于第三管的流通截面积。由此，促进第一管的内部流动，使管间冷媒分配更均匀，提升换热性能。
在一些实施例中，第二管20的水力直径大于或等于第一管10的水力直径的1.1倍。由此，可以平衡换热管内和第一管内的压降，保证换热管件的冷媒分配更均匀，同时可以减小制冷系统吸气侧压降，提升制冷系统性能。
在一些实施例中，换热管30的横截面的外周轮廓大体为四边形，第二管20的内径是换热管30的宽度的1.1倍及以上。由此，可以平衡换热管内和第一管内的压降，保证换热管件的冷媒分配更均匀，同时可以减小制冷系统吸气侧压降，提升制冷系统性能。
下面参考图1-图13描述根据本申请的一些示例的换热器1。
示例1
如图1-图13所示，换热器1包括第一管10、第二管20、第三管、进出口管60和多个换热管30。
第一管10和第一管10均沿左右方向延伸，且第一管10与第二管20在前后方向上间隔开，多个换热管30连通在第一管10与第二管20之间，多个换热管30沿左右方向间隔布置，多个换热管30的前端与第一管10连通，多个换热管30的后端与第二管20连通。
第一管10包括第一端面50和沿左右方向延伸的主流道，第三管沿左右方向穿设于主流道内，第三管内形成有第一流道1011，第三管的周壁与第一管10的内周壁之间形成有第二流道1012，换热管30的前端与第二流道1012连通，第三管的周壁上设有多个沿第三管长度方向间隔布置且贯穿第三管周壁的通孔401。
第三管的右端开口，且第三管的开口与第一管10的进口连通，冷媒适于经过第一管10的进口流入第一流到内，第二流道1012内的冷媒通过通孔401流入第二流道1012内，第二流道1012内的冷媒可以流入换热管30以进行换热。
换热管30内具有多个沿上下方向间隔排布的通道301，多个通道301沿前后方向延伸，多个通道301的截面积沿上下方向逐渐变化，截面积之和较大的通孔401设置在换热管30内的下侧(迎风侧)，截面积之和较小的通孔401设置在换热管30内的上侧(背风侧)，多个通道301的边缘在换热管30的厚度方向上对齐，且多个通道301中相邻通道301在上下方向上的最小距离相等。
在左右方向上，最靠近第一端面50的10个换热管30中位于最右侧的换热管30为第一换热管30，多个换热管30包括第二换热管，在第一管10的长度方向上，位于第一换热管和第二换热管之间的换热管30的数量大于等于10个且小于30个，多个通孔401中位于最右侧的通孔401为第一通孔，第一通孔位于第一换热管30与第二换热管30之间。
示例2
如图8和图9所示，与示例1不同的是，第一件40为沿左右方向穿设于主通道101内的板体，板体上具有沿左右方向间隔布置且贯穿板体的通孔401，板体在主通道101内限定出位于板体后侧的第二流道1012和位于板体前侧的第一流道1011，冷媒通过进出口管60流入第一流道1011，第一流道1011内的冷媒通过板体上的通孔401流入板体后侧的第二流道1012内。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本申请的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不必须针对的是相等的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任一个或多个实施例或示例中以合适的方式结合。此外，在不相互矛盾的情况下，本领域的技术人员可以将本说明书中描述的不同实施例或示例以及不同实施例或示例的特征进行结合和组合。
在本申请的描述中，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。在本申请的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
在本申请中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接或彼此可通讯；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系，除非另有明确的限定。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本申请中的具体含义。
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“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
尽管上面已经示出和描述了本申请的实施例，可以理解的是，上述实施例是示例性的，不能理解为对本申请的限制，本领域的普通技术人员在本申请的范围内可以对上述实施例进行变化、修改、替换和变型。

Claims (18)

  1. 一种换热器，其特征在于，包括：
    第一管和第二管，所述第一管包括周壁和由周壁包围形成的主通道，所述换热器还包括进出口管，所述进出口管与所述第一管连通；
    多个换热管，所述换热管连通所述第一管和所述第二管，所述换热管包括间隔布置的多个通道，所述通道连通所述第一管和所述第二管，在所述换热管的横截面上，多个所述通道中的至少三个通道的截面积两两不相等，多个所述通道包括第一通道和第二通道，在所述换热管的横截面上，所述第一通道的截面积大于多个通道中除第一通道之外的其余通道的截面积，所述第二通道的截面积小于多个通道中除第二通道之外的其他通道的截面积；
    第一件，所述第一件位于所述第一管的主通道内，所述第一件沿所述第一管的长度方向延伸一定的距离，所述主通道包括第一流道和第二流道，所述第一件位于所述第一流道和所述第二流道之间，所述第一流道与所述进出口管连通，所述第二流道与所述换热管连通，所述第一件包括多个通孔，所述通孔连通所述第一流道和所述第二流道，
    所述第一通道在所述换热管的横截面上的截面积为A1，所述第二通道在所述换热管的横截面上的截面积为A2，所述A1，A2满足以下关系式：0.15≤(A1-A2)*N/A3≤3.8，其中，A3为所述第一件的多个所述通孔的流通截面积之和，N为所述主通道连通的换热管的个数。
  2. 根据权利要求1所述的换热器，其特征在于，所述第一件为第三管，所述第三管包括第三周壁，所述第三周壁位于所述第一流道和所述第二流道之间，所述第三周壁上具有贯穿该周壁的所述通孔，所述通孔连通所述第一流道和第二流道，所述第三管与所述进出口管连通，或者所述第三管包括所述进出口管。
  3. 根据权利要求2所述的换热器，其特征在于，定义所述换热器在换热时位于风向上游的一侧为迎风侧，且定义所述换热器风向下游的一侧为背风侧，所述第一通道位于所述迎风侧。
  4. 根据权利要求2所述的换热器，其特征在于，定义所述换热器在换热时位于风向上游的一侧为迎风侧，且定义所述换热器风向下游的一侧为背风侧，所述换热管的多个所述通道中位于所述迎风侧的通道的流通截面积之和大于多个通道中位于所述背风侧的通道的流通截面积之和。
  5. 根据权利要求3或4所述的换热器，其特征在于，所述分配管的多个所述通孔中的一部分通孔位于所述迎风侧，多个所述通孔中的另一部分通孔位于所述背风侧，所述迎风侧的通孔的横截面积之和小于所述背风侧的通孔的横截面积之和。
  6. 根据权利要求2-5中任一项所述的换热器，其特征在于，(A1-A2)/A4≤0.09，其中，A4是所述第三管的最大流通截面积。
  7. 根据权利要求2-5中任一项所述的换热器，其特征在于，在所述第三管的长度方向上，至少两个相邻所述通孔之间的距离I满足：20mm≤I≤150mm。
  8. 根据权利要求2-5中任一项所述的换热器，其特征在于，所述第一管包括第一端面，在所述第一管的长度方向上，多个所述通孔中邻近所述第一管的第一端面的通孔为第一通孔，多个所述换热管中邻近所述第一管的第一端面的换热管为第一换热管，多个所述换热管中包括第二换热管，在所述第一管的长度方向上，位于所述第一换热管与所述第二换热管之间的所述换热管的数量大于等于10个且小于30个，所述第一通孔与所述第一端面在所述第一管的长度方向上的最小距离小于所述第二换热管与所述第一端面在所述第一管的长度方向上的最小距离。
  9. 根据权利要求1-8中任一项所述的换热器，其特征在于，在所述换热管的横截面上，在所述换热管的宽度方向上两个相邻所述通道之间的间隔距离相等，该两个相邻的所述通道的截面积不相等。
  10. 根据权利要求1-9中任一项所述的换热器，其特征在于，所述换热管的横截面的外周轮廓大体为四边形，所述第二管的内径是所述换热管的宽度的1.1倍计及以上。
  11. 一种换热器，其特征在于，包括：
    第一管和第二管，所述第一管包括周壁和由周壁包围形成的主通道，所述第一管长度方向上的一端为第一端，所述第一管的第一端包括第一端面，所述换热器还包括进出口管，所述进出口管与所述第一管连通；
    多个换热管，所述换热管连通所述第一管和所述第二管，所述换热管包括间隔布置的多个通道，所述通道连通所述第一管和所述第二管，在所述换热管的横截面上，至少三个所述通道的截面积不相等，多个所述通道包括第一通道和第二通道，在所述换热管的横截面上，所述第一通道的截面积大于多个通道中除第一通道之外的其余通道的截面积，所述第二通道的截面积小于多个通道中除第二通道之外的其他通道的截面积；
    第一件，所述第一件位于所述第一管的主通道内，所述第一件沿所述第一管的长度方向延伸一定的距离，所述主通道包括第一流道和第二流道，所述第一件位于所述第一流道和所述第二流道之间，所述第一流道与所述进出口管连通，所述第二流道与所述换热管连通，所述第一件包括多个通孔，所述通孔连通所述第一流道和所述第二流道，
    在所述第一管长度方向上，多个所述通孔中，与所述第一管的第一端面之间的距离最小的通孔为第一通孔，所述第一通孔与所述第一端面在所述第一管的长度方向上的最小距离为d3，且d3＜(10d1+9d2)*A1/A2，其中d1为所述换热管的厚度，d2为在所述第一管 的长度方向上相邻所述换热管之间的最小距离，A1为所述第一通道在所述换热管的横截面上的截面积，A2为所述第二通道在所述换热管的横截面上的截面积。
  12. 根据权利要求11所述的换热器，其特征在于，所述第一件为第三管，所述第三管包括第三周壁，所述第三周壁位于所述第一流道和所述第二流道之间，所述第三周壁上具有贯穿该周壁的多个所述通孔。
  13. 根据权利要求12所述的换热器，其特征在于，定义沿风向位于所述换热器的上游的一侧为迎风侧，且定义沿风向位于所述换热器的下游的一侧为背风侧，所述第一通道位于迎风侧，多个所述通孔中的至少部分位于背风侧。
  14. 根据权利要求12所述的换热器，其特征在于，定义所述换热器位于风向上游的一侧为迎风侧，且定义所述换热器风向下游的一侧为背风侧，多个通道中位于所述迎风侧的通道的流通截面积之和多个通道中位于所述背风侧的通道的流通截面积之和，多个所述通孔中的至少部分位于所述背风侧。
  15. 根据权利要求13或14所述的换热器，其特征在于，多个所述通孔中的一部分通孔位于所述迎风侧，多个所述通孔中的另一部分通孔位于所述背风侧，所述迎风侧的通孔的横截面积之和小于所述背风侧的通孔的横截面积之和。
  16. 根据权利要求12所述的换热器，其特征在于，所述第三管的一端与所述进出口管连通，所述第三管的另一端具有孔口，所述孔口的流通面积小于所述第三管的流通截面积。
  17. 根据权利要求11-16中任一项所述的换热器，其特征在于，所述第二管的水力直径大于或等于所述第一管的水力直径的1.1倍。
  18. 根据权利要求11-17中任一项所述的换热器，其特征在于，所述换热管的横截面的外周轮廓大体为四边形，所述第二管的内径是所述换热管的宽度的1.1倍及以上。
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