WO2020052485A1 - 换热器扁管及具有其的换热器 - Google Patents

换热器扁管及具有其的换热器 Download PDF

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Publication number
WO2020052485A1
WO2020052485A1 PCT/CN2019/104430 CN2019104430W WO2020052485A1 WO 2020052485 A1 WO2020052485 A1 WO 2020052485A1 CN 2019104430 W CN2019104430 W CN 2019104430W WO 2020052485 A1 WO2020052485 A1 WO 2020052485A1
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WIPO (PCT)
Prior art keywords
heat exchanger
flat tube
curved surface
convex hull
convex
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2019/104430
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English (en)
French (fr)
Inventor
魏文建
马文勇
杨洪亮
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zhejiang Dunan Thermal Technology Co Ltd
Original Assignee
Zhejiang Dunan Thermal Technology Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by Zhejiang Dunan Thermal Technology Co Ltd filed Critical Zhejiang Dunan Thermal Technology Co Ltd
Priority to KR1020217002957A priority Critical patent/KR102496372B1/ko
Priority to US17/057,115 priority patent/US11512911B2/en
Publication of WO2020052485A1 publication Critical patent/WO2020052485A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/424—Means comprising outside portions integral with inside portions
    • F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
    • 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
    • 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
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type 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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F2001/027—Tubular elements of cross-section which is non-circular with dimples
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations

Definitions

  • the invention relates to the technical field of refrigeration and air conditioning, and in particular to a heat exchanger flat tube and a heat exchanger having the same.
  • a convex hull structure is provided in a flat tube of a heat exchanger in the prior art, and a certain turbulent effect can be caused on the fluid medium in the flat tube through the convex hull structure.
  • the convex hull structure in the prior art is mainly a circular convex hull structure.
  • the circular convex hull structure has a limited turbulence effect and cannot improve the heat exchange efficiency of the flat tube of the heat exchanger.
  • the invention provides a heat exchanger flat tube and a heat exchanger having the same to solve the technical problem of low heat exchange efficiency of the heat exchanger flat tube in the prior art.
  • a heat exchanger flat tube includes two oppositely disposed plate bodies, and a fluid passage is formed between the two plate bodies, and a turbulent structure is arranged in the fluid passage.
  • the spoiler structure has a gradually expanding portion and a tapering portion, and the extending direction and the extending direction of the tapered portion are consistent with the flow direction of the fluid, and the tapered portion is located downstream of the gradually expanding portion along the fluid flow direction.
  • the spoiler structure includes a convex hull, and at least one plate body is provided with a convex hull.
  • the convex hull includes a first curved surface, a second curved surface, and a third curved surface.
  • the first curved surface and the second curved surface form a tapered portion
  • the third curved surface forms a tapered portion.
  • both the first curved surface and the second curved surface are convex toward the inner direction of the convex hull.
  • the third curved surface is convex toward the outer direction of the convex hull.
  • first curved surface and the second curved surface are circular arc transitions; and / or, the second curved surface and the third curved surface are circular arc transitions; and / or, the third curved surface and the first curved surface are circular arc transitions.
  • the length of the convex hull is La along the flow direction of the fluid
  • the width of the convex hull is Lb along the flow direction perpendicular to the fluid, where the value of Lb / La ranges from 0.7 to 3.73.
  • a plurality of convex hulls are provided on the plate body.
  • a plurality of convex hulls are arranged on the board in an array.
  • the lateral distance between the convex hulls is Lv
  • the longitudinal distance between the convex hulls is Lh.
  • the distance between two adjacent convex hulls is the longitudinal distance;
  • the distance between two adjacent convex hulls is a lateral distance; wherein, the value of Lv / Lh ranges from 0.7 to 3.73.
  • the convex hull has an incoming flow pressure angle ⁇
  • the first curved surface and the plane on which the plate is located have a first intersection
  • the second curved surface and the plane on which the plate is located have a second intersection
  • the first intersection and the second The intersection line intersects at the first point
  • the end point of the first intersection line far from the first point is the second point
  • the end point of the second intersection line far from the first point is the third point
  • the height of the convex hull is d, and the value of d ranges from 0.5 mm to 1.2 mm.
  • the thickness of the plate is t, and the value of t ranges from 0.3 mm to 1.0 mm.
  • the convex hull has a top surface, and the shape of the top surface is circular or oval.
  • a heat exchanger is provided.
  • the heat exchanger includes a heat exchanger flat tube, and the heat exchanger flat tube is the heat exchanger flat tube provided above.
  • a turbulent structure is provided in the fluid channel, and the turbulent structure has a gradually expanding portion and a tapering portion along the flow direction of the fluid.
  • the turbulent structure When the fluid medium flows in the circulation channel, it will first pass through the gradually expanding portion Passing the tapered portion again, this will increase the velocity of the fluid medium, thereby increasing the disturbance of the fluid medium in the fluid channel, which is beneficial to further improving the heat exchange effect.
  • such a setting will increase the shear forces of the fluid and the turbulent structure, reduce the thickness of the flow boundary layer and the thermal boundary layer, and increase the convective heat transfer coefficient. Therefore, by adopting the heat exchanger flat tube provided by the present invention, the technical problem of low heat exchange efficiency of the heat exchanger flat tube in the prior art can be solved.
  • FIG. 1 is a schematic structural diagram of a board body according to a first embodiment of the present invention
  • FIG. 2 is a schematic structural diagram of a part of a flat tube of a heat exchanger according to a first embodiment of the present invention
  • FIG. 3 is a schematic structural diagram of a flat tube of a heat exchanger according to a first embodiment of the present invention
  • Fig. 4 shows a cross-sectional view taken along the B-B cross section in Fig. 3;
  • Fig. 5 shows a cross-sectional view of the A-A cross section in Fig. 3;
  • FIG. 6 shows a cross-sectional view of the plate along A1-A1, B1-B1, C1-C1;
  • FIG. 7 shows a cross-sectional view of the flat tubes of the heat exchanger along A2-A2, B2-B2, C2-C2;
  • Figure 8 shows the length and width of a single convex hull
  • FIG. 9 shows the lateral distance, longitudinal distance, and incoming pressure angle ⁇ of the convex hull
  • Figure 10 shows the height of the convex hull and the thickness of the plate body
  • Figure 11 shows a schematic diagram of a fluid turbulence around a single convex hull
  • Figure 12 shows a schematic diagram of a fluid turbulent flow around a plurality of convex hulls
  • FIG. 13 is a schematic structural diagram of a convex hull whose top surface is circular;
  • FIG. 14 shows a schematic structural diagram of a convex hull whose top surface is oval
  • FIG. 15 shows a structure diagram of a rectangular convex hull whose top surface is a circular arc transition
  • FIG. 16 is a schematic structural diagram of a convex hull whose top surface is waist-shaped;
  • FIG. 17 is a schematic structural diagram of a heat exchanger provided in Embodiment 2 of the present invention.
  • FIG. 18 shows an enlarged schematic diagram at D in FIG. 17;
  • FIG. 19 shows a side view of a heat exchanger provided by Embodiment 2 of the present invention.
  • FIG. 20 shows an enlarged schematic view at E in FIG. 19.
  • the first embodiment of the present invention provides a flat tube of a heat exchanger.
  • the flat tube of the heat exchanger includes two oppositely disposed plate bodies 10, and a fluid passage is formed between the two plate bodies 10.
  • the fluid channel is provided with a turbulent structure.
  • the turbulent structure has a gradually expanding portion and a tapering portion. The extending direction of the gradually expanding portion and the extending direction of the tapering portion are consistent with the flow direction of the fluid, and the tapered portion flows along the fluid. The direction is located downstream of the gradually expanding portion.
  • a turbulent structure is provided in the fluid channel, and along the flow direction of the fluid, the turbulent structure has a gradually expanding portion and a tapering portion.
  • the fluid medium flows in the flow channel, it will pass through the gradually expanding portion and then the tapering portion. It will increase the velocity of the fluid medium, thereby increasing the disturbance of the fluid medium in the fluid channel, which is conducive to further improving the heat exchange effect.
  • such a setting will increase the shear forces of the fluid and the turbulent structure, reduce the thickness of the flow boundary layer and the thermal boundary layer, and increase the convective heat transfer coefficient. Therefore, by adopting the heat exchanger flat tube provided by the present invention, the technical problem of low heat exchange efficiency of the heat exchanger flat tube in the prior art can be solved.
  • the turbulence structure in this embodiment includes a convex hull 20, and at least one plate body 10 is provided with a convex hull 20, and the convex hull 20 on the plate body 10 is used to turbulent fluid in the fluid channel.
  • a convex hull 20 may be provided on both of the two plate bodies 10 to further improve the effect of turbulence in the fluid channel, so as to further improve the heat exchange efficiency.
  • the convex hull 20 includes a first curved surface, a second curved surface, and a third curved surface.
  • the first curved surface and the second curved surface form an enlarged portion, and the third curved surface forms a tapered portion.
  • the convex hull 20 in this embodiment further includes a top surface, the first curved surface is connected to the second curved surface, the second curved surface is connected to the third curved surface, the third curved surface is connected to the first curved surface, the first curved surface, the second curved surface, and the third curved surface are connected.
  • the curved surfaces are all connected to the top surface, and the first curved surface, the second curved surface, and the third curved surface surround the convex hull 20 in the embodiment.
  • the fluid in the fluid channel will sequentially pass through the gradually expanding portion formed by the first curved surface and the second curved surface and the tapered portion formed by the third curved surface in order to increase the disturbance effect of the fluid in the fluid channel and better improve the heat exchange efficiency.
  • the shear force between the fluid and the wall surface of the convex hull 20 is increased, the thicknesses of the flow boundary layer and the thermal boundary layer are reduced, and the convective heat transfer coefficient is increased.
  • the convex hull 20 in this embodiment has a simple structure and a significant effect, which is convenient for manufacturing.
  • both the first curved surface and the second curved surface are convex toward the inner side of the convex hull 20.
  • the third curved surface is convex toward the outer direction of the convex hull 20.
  • the first curved surface and the second curved surface may be circularly transitioned; or the second curved surface and the third curved surface may be circularly transitioned; or the third curved surface and the first curved surface are circularly transitioned; or
  • the surface and the second surface are arc transitions, and the second and third surfaces are arc transitions; or the first and second surfaces are arc transitions, and the third and first surfaces are arcs Transition; or make the second and third surfaces arc-shaped transitions, and make the first and third surfaces arc-shaped transitions; or make the first, second, and third surfaces all arc-transitions at the same time.
  • the first curved surface, the second curved surface, and the third curved surface all be circular arc transitions, so as to facilitate fluid flow in the fluid channel.
  • the length of the convex hull 20 is La along the flow direction of the fluid
  • the width of the convex hull 20 is Lb along the flow direction perpendicular to the fluid, where the value of Lb / La ranges from 0.7 to 3.73. between. Within this value range, the effects of heat exchange and pressure drop can be made better.
  • a plurality of convex hulls 20 are provided on the plate body 10 in this embodiment.
  • the arrangement of the convex hull 20 is more reasonable and compact.
  • the plurality of convex hulls 20 are arranged on the plate body 10 in an array.
  • the fluid in the fluid channel passes through the array of convex hulls 20, which can further improve the turbulence effect, facilitate convective heat transfer, and better improve the heat exchange effect.
  • the lateral distance between the convex hulls 20 in this embodiment is Lv
  • the vertical distance between the convex hulls 20 is Lh.
  • the distance between two adjacent convex hulls 20 The distance is a longitudinal distance; along the direction perpendicular to the gas flow in the flat tube of the heat exchanger, the distance between two adjacent convex hulls 20 is a lateral distance; wherein, the value of Lv / Lh ranges from 0.7 to 3.73.
  • the convex hull 20 has an incoming flow pressure angle ⁇
  • the first curved surface and the plane where the plate body 10 is located have a first intersection line
  • the second curved surface and the plane where the plate body 10 is located have a second intersection line.
  • An intersection line intersects a second intersection line at a first point
  • an end point of the first intersection line far from the first point is a second point
  • an end point of the second intersection line far from the first point is a third point
  • the height of the convex hull 20 in this embodiment is d, and the value of d ranges from 0.5 mm to 1.2 mm.
  • the thickness of the plate body 10 in this embodiment is t, and the value of t ranges from 0.3 mm to 1.0 mm.
  • the plate body 10 in this embodiment may be made of an aluminum material or a composite aluminum material, and adopts a brazing processing technology.
  • the convex hull 20 has a top surface along a direction perpendicular to the flow direction of the fluid, and the shape of the top surface is circular or oval.
  • the convex hull 20 may also have a rectangular or waist-like shape with a smooth transition.
  • the arrangement of the convex hull 20 in this embodiment is more reasonable, the utilization of the plate body 10 is higher, the clearance is small, the features per unit area are more, and the plate The density of the solder joints on the body 10 is increased, and its withstand voltage is improved.
  • the structure of the convex hull 20 in this embodiment is similar to that of a fish scale, and has the characteristics of efficient heat transfer.
  • the convex hull 20 in this embodiment is processed and formed by a stamping process. Flanges are provided on both sides of the plate body 10, and two oppositely disposed plate bodies 10 are welded together by flanging.
  • a second embodiment of the present invention provides a heat exchanger.
  • the heat exchanger includes a heat exchanger flat tube 30, and the heat exchanger flat tube 30 is the heat exchanger provided in the first embodiment.
  • Flat tube 30 The heat exchanger in this embodiment includes a plurality of heat exchanger flat tubes 30 arranged in parallel and two header pipes 40 arranged vertically, and the plurality of heat exchanger flat tubes 30 are arranged between the two surge tubes, The two ends of each heat exchanger flat tube 30 are in communication with two rapid flow tubes.
  • the heat exchanger provided by this embodiment can improve the heat exchange effect.
  • orientation words such as “front, back, up, down, left, right", “horizontal, vertical, vertical, horizontal”, “top, bottom” and the like indicate the orientation Or the positional relationship is usually based on the orientation or positional relationship shown in the drawings, only for the convenience of describing the present invention and simplifying the description. Unless otherwise stated, these orientation words do not indicate and imply the device or element referred to. It must have a specific orientation or be constructed and operated in a specific orientation, so it cannot be understood as a limitation on the scope of protection of the present invention; the orientation words “inside and outside” refer to the inside and outside relative to the outline of each component itself.
  • spatially relative terms such as “above”, “above”, “above”, “above”, etc. can be used here to describe as shown in the figure Shows the spatial position relationship between one device or feature and other devices or features. It should be understood that spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation of the device as described in the figures. For example, if a device in the figure is turned over, devices described as “above” or “above” other devices or constructions will then be positioned “below the other devices or constructions” or “under Other devices or constructs. " Thus, the exemplary term “above” may include both directions “above” and “below”. The device can also be positioned in other different ways (rotated 90 degrees or at other orientations), and the relative description of space used here is explained accordingly.

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

Abstract

本发明提供了一种换热器扁管及具有其的换热器，换热器扁管包括两个相对设置的板体，两个板体之间形成流体通道，流体通道内设置有扰流结构，扰流结构具有渐扩部和渐缩部，渐扩部的延伸方向和渐缩部的延伸方向均与流体的流动方向一致，且渐缩部沿流体流动方向位于渐扩部的下游。采用本发明提供的换热器扁管，能够解决现有技术中的换热器扁管的换热效率不高的技术问题。

Description

换热器扁管及具有其的换热器 技术领域
本发明涉及制冷空调技术领域，具体而言，涉及一种换热器扁管及具有其的换热器。
背景技术
目前，现有技术中的换热器扁管内设置有凸包结构，通过凸包结构可以对扁管内的流体介质造成一定的扰流作用。但现有技术中的凸包结构主要为圆形凸包结构，该圆形凸包结构的扰流作用有限，并不能很好地提高换热器扁管的换热效率。
发明内容
本发明提供一种换热器扁管及具有其的换热器，以解决现有技术中的换热器扁管的换热效率不高的技术问题。
根据本发明的一个方面，提供了一种换热器扁管，换热器扁管包括两个相对设置的板体，两个板体之间形成流体通道，流体通道内设置有扰流结构，扰流结构具有渐扩部和渐缩部，渐扩部的延伸方向和渐缩部的延伸方向均与流体的流动方向一致，且渐缩部沿流体流动方向位于渐扩部的下游。
进一步地，扰流结构包括凸包，至少一个板体上设置有凸包。
进一步地，凸包包括第一曲面、第二曲面、第三曲面，第一曲面和第二曲面形成渐扩部，第三曲面形成渐缩部。
进一步地，第一曲面和第二曲面均朝向凸包的内侧方向凸起。
进一步地，第三曲面朝向凸包的外侧方向凸起。
进一步地，第一曲面和第二曲面为圆弧过渡；和/或，第二曲面与第三曲面为圆弧过渡；和/或，第三曲面与第一曲面为圆弧过渡。
进一步地，沿流体的流动方向，凸包的长度为La；沿垂直于流体的流动方向，凸包的宽度为Lb，其中，Lb/La的取值范围在0.7至3.73之间。
进一步地，板体上设置有多个凸包。
进一步地，多个凸包呈阵列设置在板体上。
进一步地，凸包的横向间距为Lv，凸包的纵向间距为Lh，沿换热器扁管内的气体流动方向，相邻两个凸包之间的间距为纵向间距；沿垂直于换热器扁管内的气体流动的方向，相邻两个凸包之间的间距为横向间距；其中，Lv/Lh的取值范围在0.7至3.73之间。
进一步地，凸包的具有来流压力角θ，第一曲面与板体所在的平面具有第一交线，第二曲面与板体所在的平面具有第二交线，第一交线与第二交线相交于第一点，第一交线的远离第一点的端点为第二点，第二交线的远离第一点的端点为第三点，第一点与第二点所在的直线与第一点与第三点所在的直线之间的夹角为来流压力角θ，其中，θ＝2arctanLv/Lh。
进一步地，凸包的高度为d，d的取值范围在0.5mm至1.2mm之间。
进一步地，板体的厚度为t，t的取值范围在0.3mm至1.0mm之间。
进一步地，沿垂直于流体的流动方向，凸包具有顶面，顶面的形状为圆形或椭圆形。
根据本发明的另一方面，提供了一种换热器，该换热器包括换热器扁管，换热器扁管为上述提供的换热器扁管。
应用本发明的技术方案，在流体通道内设置有扰流结构，沿流体的流动方向，该扰流结构具有渐扩部和渐缩部，流体介质在流通通道内流动时将先经过渐扩部再经过渐缩部，这样会使得流体介质的速度增大，从而增大了流体通道内流体介质的扰动，有利于进一步提高换热效果。同时，这样的设置将增大流体与扰流结构的剪切力，使得流动边界层和热边界层厚度减薄，增大了对流传热系数。因此，采用本发明提供的换热器扁管，能够解决现有技术中的换热器扁管的换热效率不高的技术问题。
附图说明
构成本申请的一部分的说明书附图用来提供对本发明的进一步理解，本发明的示意性实施例及其说明用于解释本发明，并不构成对本发明的不当限定。在附图中：
图1示出了根据本发明实施例一提供的板体的结构示意图；
图2示出了根据本发明实施例一提供的换热器扁管的部分结构示意图；
图3示出了根据本发明实施例一提供的换热器扁管的结构示意图；
图4示出了图3中B-B截面的剖视图；
图5示出了图3中A-A截面的剖视图；
图6示出了板体沿A1-A1、B1-B1、C1-C1截面的剖视图；
图7示出了换热器扁管沿A2-A2、B2-B2、C2-C2截面的剖视图；
图8示出了单个凸包的长度和宽度；
图9示出了凸包的横向间距、纵向间距以及来流压力角θ；
图10示出了凸包的高度和板体的厚度；
图11示出了流体绕单个凸包扰流的示意图；
图12示出了流体绕多个凸包扰流的示意图；
图13示出了顶面为圆形的凸包的结构示意图；
图14示出了顶面为椭圆形的凸包的结构示意图；
图15示出了顶面为圆弧过渡的矩形的凸包的结构示意图；
图16示出了顶面为腰子形的凸包的结构示意图；
图17示出了本发明实施例二提供的换热器的结构示意图；
图18示出了图17中D处的放大示意图；
图19示出了本发明实施例二提供的换热器的侧视图；
图20示出了图19中E处的放大示意图。
其中，上述附图包括以下附图标记：
10、板体；20、凸包；30、换热器扁管；40、集流管。
具体实施方式
下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本发明一部分实施例，而不是全部的实施例。以下对至少一个示例性实施例的描述实际上仅仅是说明性的，决不作为对本发明及其应用或使用的任何限制。基于本发明中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本发明保护的范围。
如图1至图16所示，本发明实施例一提供了一种换热器扁管，该换热器扁管包括两个相对设置的板体10，两个板体10之间形成流体通道，流体通道内设置有扰流结构，扰流结构具有渐扩部和渐缩部，渐扩部的延伸方向和渐缩部的延伸方向均与流体的流动方向一致，且渐缩部沿流体流动方向位于渐扩部的下游。
在流体通道内设置有扰流结构，沿流体的流动方向，该扰流结构具有渐扩部和渐缩部，流体介质在流通通道内流动时将先经过渐扩部再经过渐缩部，这样会使得流体介质的速度增大，从而增大了流体通道内流体介质的扰动，有利于进一步提高换热效果。同时，这样的设置将增大流体与扰流结构的剪切力，使得流动边界层和热边界层厚度减薄，增大了对流传热系数。因此，采用本发明提供的换热器扁管，能够解决现有技术中的换热器扁管的换热效率不高的技术问题。
具体的，本实施例中的扰流结构包括凸包20，至少一个板体10上设置有凸包20，通过板体10上的凸包20以对流体通道内的流体进行扰流。在本实施例中，可以在两个板体10上均设置有凸包20，以进一步提高流体通道内的扰流效果，以便于进一步提高换热效率。
在本实施例中，凸包20包括第一曲面、第二曲面、第三曲面，第一曲面和第二曲面形成渐扩部，第三曲面形成渐缩部。本实施例中的凸包20还包括顶面，第一曲面与第二曲面连接、第二曲面与第三曲面连接、第三曲面与第一曲面连接，第一曲面、第二曲面和第三曲面均与顶面连接，第一曲面、第二曲面和第三曲面围成本实施例中的凸包20。流体通道内的流体将依次经过第一曲面和第二曲面形成的渐扩部和第三曲面形成的渐缩部，以增加流体通道内流体的扰动效果，并更好地提高换热效率。采用这样的设置，增加了流体与凸包20的壁面之间的剪切力，使得流动边界层和热边界层厚度减薄，增加了对流传热系数。本实施例中的凸包20结构简单，效果显著，便于生产制造。
如图11和图12所示，为了进一步提高换热效果，本实施例中将第一曲面和第二曲面均朝向凸包20的内侧方向凸起。采用这样的设置，流体在流经第一曲面和第二曲面时，将会发生一定的湍流，以强化传热效果。
为了更好地提高换热效果，本实施例中将第三曲面朝向凸包20的外侧方向凸起。
具体的，可以使第一曲面和第二曲面为圆弧过渡；或者可以使第二曲面和第三曲面为圆弧过渡；或者使第三曲面与第一曲面为圆弧过渡；或者使第一曲面和第二曲面为圆弧过渡、并使第二曲面和第三曲面为圆弧过渡；或者使第一曲面和第二曲面为圆弧过渡、并使第三曲面与第一曲面为圆弧过渡；或者使第二曲面和第三曲面为圆弧过渡、并使第一曲面和第三曲面为圆弧过渡；或者同时使第一曲面、第二曲面、第三曲面均为圆弧过渡。
在本实施例中，优选的，使第一曲面、第二曲面、第三曲面均为圆弧过渡，以便于流体通道内流体的流动。
如图8所示，沿流体的流动方向，凸包20的长度为La；沿垂直于流体的流动方向，凸包20的宽度为Lb，其中，Lb/La的取值范围在0.7至3.73之间。在该取值范围内，能够使得换热和压降的效果较好。
为了进一步提高换热效果，本实施例中在板体10上设置有多个凸包20。使得凸包20的布置更加合理紧凑。
优选的，多个凸包20呈阵列设置在板体10上。流体通道内的流体经过阵列式的凸包20，能够进一步提高扰流效果，便于对流传热，以更好地提高换热效果。
如图9所示，本实施例中的凸包20的横向间距为Lv，凸包20的纵向间距为Lh，沿换热器扁管内的气体流动方向，相邻两个凸包20之间的间距为纵向间距；沿垂直于换热器扁管内的气体流动的方向，相邻两个凸包20之间的间距为横向间距；其中，Lv/Lh的取值范围在0.7至3.73之间。采用这样的设置，能够使凸包20结构的排列更加紧凑，减小余隙，在两相流动工况下，改善了气相旁通造成的气液分离。
如图9所示，凸包20的具有来流压力角θ，第一曲面与板体10所在的平面具有第一交线，第二曲面与板体10所在的平面具有第二交线，第一交线与第二交线相交于第一点，第一交线的远离第一点的端点为第二点，第二交线的远离第一点的端点为第三点，第一点与第二点所 在的直线与第一点与第三点所在的直线之间的夹角为来流压力角θ，其中，θ＝2arctanLv/Lh。通过调节来流压力角θ，能够调整换热效果和压降系数。具体的，增大来流压力角θ可使介质在通道内横向分配，以便于调节换热和压降的最优匹配。
如图10所示，本实施例中的凸包20的高度为d，d的取值范围在0.5mm至1.2mm之间。通过将凸包20高度设置在该范围内，能够更好地对流体进行扰流作用，从而更好地提高换热效果。
如图10所示，为了保证板体10的整体结构强度，本实施例中的板体10的厚度为t，t的取值范围在0.3mm至1.0mm之间。本实施例中的板体10可以采用铝材或复合铝材制成，并采用钎焊加工技术。
如图13至图16所示，沿垂直于流体的流动方向，凸包20具有顶面，顶面的形状为圆形或椭圆形。凸包20还可以为具有圆滑过渡的矩形或腰子形等形状。相比于现有技术中的圆点凸包20而言，本实施例中的凸包20布置更加合理，板体10利用率更高，余隙小，单位面积上的特征更多，且板体10上的焊点密度增大，其耐压能力提高。
本实施例中的凸包20结构类似于鱼鳞形，具有高效传热的特点。本实施例中的凸包20采用冲压成型工艺加工成型，在板体10的两侧设置有翻边，两个相对设置的板体10通过翻边拼焊起来。
如图17至图20所示，本发明实施例二提供了一种换热器，该换热器包括换热器扁管30，换热器扁管30为实施例一中提供的换热器扁管30。本实施例中的换热器包括多个平行设置的换热器扁管30以及两个竖直设置的集流管40，多个换热器扁管30均设置在两个激流管之间，且每个换热器扁管30的两端均与两个急流管连通。采用本实施例提供的换热器能够提高换热效果。
需要注意的是，这里所使用的术语仅是为了描述具体实施方式，而非意图限制根据本申请的示例性实施方式。如在这里所使用的，除非上下文另外明确指出，否则单数形式也意图包括复数形式，此外，还应当理解的是，当在本说明书中使用术语“包含”和/或“包括”时，其指明存在特征、步骤、操作、器件、组件和/或它们的组合。
除非另外具体说明，否则在这些实施例中阐述的部件和步骤的相对布置、数字表达式和数值不限制本发明的范围。同时，应当明白，为了便于描述，附图中所示出的各个部分的尺寸并不是按照实际的比例关系绘制的。对于相关领域普通技术人员已知的技术、方法和设备可能不作详细讨论，但在适当情况下，所述技术、方法和设备应当被视为授权说明书的一部分。在这里示出和讨论的所有示例中，任何具体值应被解释为仅仅是示例性的，而不是作为限制。因此，示例性实施例的其它示例可以具有不同的值。应注意到：相似的标号和字母在下面的附图中表示类似项，因此，一旦某一项在一个附图中被定义，则在随后的附图中不需要对其进行进一步讨论。
在本发明的描述中，需要理解的是，方位词如“前、后、上、下、左、右”、“横向、竖向、垂直、水平”和“顶、底”等所指示的方位或位置关系通常是基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，在未作相反说明的情况下，这些方位词并不指示和暗示所指的装置或元件必须具有特定的方位或者以特定的方位构造和操作，因此不能理解为对本发明保护范围的限制；方位词“内、外”是指相对于各部件本身的轮廓的内外。
为了便于描述，在这里可以使用空间相对术语，如“在……之上”、“在……上方”、“在……上表面”、“上面的”等，用来描述如在图中所示的一个器件或特征与其他器件或特征的空间位置关系。应当理解的是，空间相对术语旨在包含除了器件在图中所描述的方位之外的在使用或操作中的不同方位。例如，如果附图中的器件被倒置，则描述为“在其他器件或构造上方”或“在其他器件或构造之上”的器件之后将被定位为“在其他器件或构造下方”或“在其他器件或构造之下”。因而，示例性术语“在……上方”可以包括“在……上方”和“在……下方”两种方位。该器件也可以其他不同方式定位(旋转90度或处于其他方位)，并且对这里所使用的空间相对描述作出相应解释。
此外，需要说明的是，使用“第一”、“第二”等词语来限定零部件，仅仅是为了便于对相应零部件进行区别，如没有另行声明，上述词语并没有特殊含义，因此不能理解为对本发明保护范围的限制。
以上所述仅为本发明的优选实施例而已，并不用于限制本发明，对于本领域的技术人员来说，本发明可以有各种更改和变化。凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。

Claims (15)

  1. 一种换热器扁管，其特征在于，所述换热器扁管包括两个相对设置的板体(10)，两个所述板体(10)之间形成流体通道，所述流体通道内设置有扰流结构，所述扰流结构具有渐扩部和渐缩部，所述渐扩部的延伸方向和所述渐缩部的延伸方向均与所述流体的流动方向一致，且所述渐缩部沿流体流动方向位于所述渐扩部的下游。
  2. 根据权利要求1所述的换热器扁管，其特征在于，所述扰流结构包括凸包(20)，至少一个所述板体(10)上设置有所述凸包(20)。
  3. 根据权利要求2所述的换热器扁管，其特征在于，所述凸包(20)包括第一曲面、第二曲面、第三曲面，所述第一曲面和所述第二曲面形成渐扩部，所述第三曲面形成渐缩部。
  4. 根据权利要求3所述的换热器扁管，其特征在于，所述第一曲面和所述第二曲面均朝向所述凸包(20)的内侧方向凸起。
  5. 根据权利要求3所述的换热器扁管，其特征在于，所述第三曲面朝向所述凸包(20)的外侧方向凸起。
  6. 根据权利要求3所述的换热器扁管，其特征在于，
    所述第一曲面和所述第二曲面为圆弧过渡；和/或，
    所述第二曲面与所述第三曲面为圆弧过渡；和/或，
    所述第三曲面与所述第一曲面为圆弧过渡。
  7. 根据权利要求2所述的换热器扁管，其特征在于，沿所述流体的流动方向，所述凸包(20)的长度为La；沿垂直于所述流体的流动方向，所述凸包(20)的宽度为Lb，其中，Lb/La的取值范围在0.7至3.73之间。
  8. 根据权利要求3所述的换热器扁管，其特征在于，所述板体(10)上设置有多个所述凸包(20)。
  9. 根据权利要求8所述的换热器扁管，其特征在于，多个所述凸包(20)呈阵列设置在所述板体(10)上。
  10. 根据权利要求9所述的换热器扁管，其特征在于，所述凸包(20)的横向间距为Lv，所述凸包(20)的纵向间距为Lh，沿所述换热器扁管内的气体流动方向，相邻两个所述凸包(20)之间的间距为所述纵向间距；沿垂直于所述换热器扁管内的气体流动的方向，相邻两个所述凸包(20)之间的间距为所述横向间距；其中，Lv/Lh的取值范围在0.7至3.73之间。
  11. 根据权利要求10所述的换热器扁管，其特征在于，所述凸包(20)的具有来流压力角θ，所述第一曲面与所述板体(10)所在的平面具有第一交线，所述第二曲面与所述板体(10)所在的平面具有第二交线，所述第一交线与所述第二交线相交于第一点，所述第一交线的远离所述第一点的端点为第二点，所述第二交线的远离所述第一点的端点为第三点， 所述第一点与所述第二点所在的直线与所述第一点与所述第三点所在的直线之间的夹角为所述来流压力角θ，其中，θ＝2arctanLv/Lh。
  12. 根据权利要求2所述的换热器扁管，其特征在于，所述凸包(20)的高度为d，d的取值范围在0.5mm至1.2mm之间。
  13. 根据权利要求1所述的换热器扁管，其特征在于，所述板体(10)的厚度为t，t的取值范围在0.3mm至1.0mm之间。
  14. 根据权利要求2所述的换热器扁管，其特征在于，沿垂直于所述流体的流动方向，所述凸包(20)具有顶面，所述顶面的形状为圆形或椭圆形。
  15. 一种换热器，其特征在于，包括换热器扁管(30)，所述换热器扁管(30)为权利要求1至14中任一项所述的换热器扁管(30)。
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