WO2017050237A1 - 翅片和具有它的换热器 - Google Patents

翅片和具有它的换热器 Download PDF

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Publication number
WO2017050237A1
WO2017050237A1 PCT/CN2016/099628 CN2016099628W WO2017050237A1 WO 2017050237 A1 WO2017050237 A1 WO 2017050237A1 CN 2016099628 W CN2016099628 W CN 2016099628W WO 2017050237 A1 WO2017050237 A1 WO 2017050237A1
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WO
WIPO (PCT)
Prior art keywords
section
heat exchange
fin
main heat
leeward
Prior art date
Application number
PCT/CN2016/099628
Other languages
English (en)
French (fr)
Inventor
王雷雷
何延
梁欣
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 US15/761,689 priority Critical patent/US10578375B2/en
Publication of WO2017050237A1 publication Critical patent/WO2017050237A1/zh

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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
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/30—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being attachable to the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/08—Fins with openings, e.g. louvers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits

Definitions

  • the present invention relates to the field of heat exchanger technology, and in particular to a fin and a heat exchanger having the same.
  • the microchannel heat exchanger in the related art is composed of a collecting tube, a flat tube and fins, and the fins are arranged between adjacent flat tubes, and the fin surface is open with a large number of louvers occupying the fins, and the fins are windy
  • the heat exchange intensity at the end is large, resulting in more condensed water or frost on the windward end of the fin.
  • Frosting on the fin surface will reduce the effective heat exchange area of the heat exchanger, and the system such as the air conditioner using the heat exchanger will frequently enter the defrosting process, which affects the stability of the temperature.
  • the condensed water on the surface of the fin is removed by gravity. However, due to the long flow path of the condensed water, it is difficult to remove, and the heat transfer resistance of the heat exchanger is increased, which affects the heat exchange capacity of the heat exchanger.
  • the present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention needs to provide a fin having a fast condensing water removal rate and a slow frosting speed, which can improve the heat exchange performance of the heat exchanger and improve the temperature stability of the heat exchange system.
  • the present invention also needs to provide a heat exchanger.
  • a fin according to an embodiment of the first aspect of the present invention includes a sheet body including a plurality of fin units arranged in a longitudinal direction of the sheet body, each fin unit including a windward direction arranged along a lateral direction of the sheet body a section, a leeward section, and a main heat exchange section between the windward section and the leeward section, the windward sections of adjacent fin units are connected to each other, and a flat fin is formed between adjacent fin units a tube groove extending between a leeward section and a main heat exchange section of one of the adjacent fin units and a leeward section and a main heat exchange section of the other fin unit;
  • Each of the fin units is provided with a plurality of protrusions protruding from the surface of the fin unit and spaced apart from each other.
  • the fin according to the embodiment of the invention can sufficiently dehumidify the air, slow down the frosting speed of the windward section of the fin, thereby improving the heat exchange efficiency of the heat exchanger and the temperature stability of the heat exchange system, and more The bulges also speed up the removal of condensate, thereby improving the overall performance of the heat exchange system.
  • the protrusion has a flow guiding surface or a flow guiding slope.
  • the protrusion is a spherical shape, a cylindrical shape or a conical shape, or a cylinder or a cone having a polygonal cross section.
  • the plurality of protrusions are divided into groups, each group of protrusions being arranged in a straight line, a triangle or a polygon.
  • the projections are only disposed within the main heat exchange section and the leeward section.
  • the sheet body has a corrugated portion located within the windward section, the crests and troughs of the corrugated portion extending in the longitudinal direction of the sheet body, respectively.
  • a corrugated portion in the windward section is spaced apart from the main heat exchange section by a planar section.
  • an area ratio of the area of the planar section to the windward section is 20%.
  • the main heat exchange section is further provided with a louver, the louver being adjacent to the leeward section.
  • the protrusion is only disposed in the main heat exchange section and the leeward section, and the louver is located on the protrusion on the main heat exchange section and the leeward section Between the bumps.
  • the louver includes a first louver and a second louver arranged along a lateral interval of the sheet, the second louver being closer to the first louver than the first louver a leeward section, the first louver having a plurality of first air guides extending obliquely from the main heat exchange section to the leeward section, the second louver having a change from the main a plurality of second air guiding fins extending obliquely to the windward section.
  • the spacing between adjacent first air guiding sheets is greater than the spacing of adjacent second air guiding sheets.
  • a projection of the protrusion on a plane of the sheet is circular, and in the main heat exchange section, a rim of the flat tube groove and a circumference of the circle The minimum spacing between the edges is not less than the radius of the circle.
  • the diameter of the circle is 20%-30% of the height of the fin unit in the longitudinal direction.
  • the projected area of the protrusion in the leeward section on the plane of the sheet body is not greater than the protrusion in the main heat exchange section on the plane of the sheet body. The area of the projection.
  • the edge of the flat tube groove is provided with a flange.
  • the bending direction of the flange is consistent with the protrusion direction of the protrusion.
  • the width of the portion of the flat tube groove between the adjacent leeward sections in the longitudinal direction gradually increases in a direction from the windward section to the leeward section.
  • a heat exchanger comprising: a first header and a second header; a plurality of fins, the fins being fins according to the first aspect of the invention, The fins are spaced apart from each other between the first header and the second header; a flat tube, the two ends of the flat tube are respectively associated with the first header and the second The headers are connected and the flat tubes are respectively fitted in the flat tube slots.
  • the condensed water is quickly removed, the frosting speed is slow, and the heat exchange efficiency is high.
  • FIG. 1 is a schematic structural view of a heat exchanger according to an embodiment of the present invention.
  • FIG. 2 is a schematic view showing the structure of a fin body according to an embodiment of the present invention.
  • FIG 3 is a transverse cross-sectional view of a sheet of fins in accordance with an embodiment of the present invention.
  • FIG. 4 is a longitudinal cross-sectional view of a sheet of fins in accordance with an embodiment of the present invention.
  • Figure 5 is a schematic view showing the structure of a fin of a fin according to a first alternative embodiment of the present invention.
  • Figure 6 is a schematic view showing the structure of a fin body according to a second alternative embodiment of the present invention.
  • Figure 7 is a schematic view showing the structure of a fin body according to a third alternative embodiment of the present invention.
  • Figure 8 is a schematic view showing the structure of a fin body according to a fourth alternative embodiment of the present invention.
  • Figure 9 is a schematic view showing the structure of a fin body according to a fifth alternative embodiment of the present invention.
  • Heat exchanger 100 first header 1, second header 2, fin 3, flat tube 4, sheet 5,
  • Heat sink unit 31 windward section 311, main heat exchange section 312, leeward section 313, flat tube groove 314, protrusion 315, corrugated portion 316 in the windward section, plane section 317, louver 318, The louver 318a, the first air guiding piece 318c, the second louver 318b, the second air guiding piece 318d, and the flange 319.
  • a fin 3 according to an embodiment of the first aspect of the present invention which is suitable for a microchannel heat exchanger, has a high speed of elimination of condensed water and a slow frosting speed, and can be described with reference to Figs. Improve the heat transfer performance of the heat exchanger.
  • a fin 3 according to an embodiment of the present invention includes a sheet 5.
  • the sheet body 5 includes a plurality of fin units 31 arranged in the longitudinal direction of the sheet body 5 (ie, the up and down direction of the drawing), and each fin unit 31 includes a lateral direction along the sheet body 5 (ie, the front and rear directions of the drawing)
  • a plurality of fin units 31 are arranged in the up and down direction, and the windward section 311, the leeward section 313, and the main heat exchange section 312 of each fin unit 31 are forward and backward.
  • the direction is arranged, wherein the windward section 311 is located at the front end of the heat sink unit 31, the leeward section 313 is located at the rear end of the heat sink unit 31, and the main heat exchange section 312 is located in the windward section 311 and the leeward area. Between segments 313. As shown in the drawing, the windward sections 311 of the adjacent fin units 31 are connected to each other such that the plurality of fin units 31 are connected to each other to form the sheet body 5, so that the structure of the sheet body 5 is reliable.
  • a flat tube groove 314 is formed between the adjacent fin units 31, and the flat tube groove 314 is adapted to accommodate the flat tube of the heat exchanger, so that the fitting fins 3 of the flat tube and the flat tube groove 314 can be fixed on the heat exchanger. .
  • the flat tube groove 314 extends in the leeward section 313 and the main heat exchange section 312 of one of the adjacent fin units 31 and the leeward section 313 and the main heat exchange section 312 of the other fin unit 31. Therefore, the heat exchange effect between the fin 3 and the flat tube is better. For example, as shown in FIG. 2 and FIG. 4 to FIG.
  • the flat tube groove 314 extends in the front-rear direction, and the flat tube groove 314 penetrates the leeward section 313 of the upper fin unit 31 and the leeward area of the lower fin unit 31. Between the segments 313, and the flat tube groove 314 is penetrated between the main heat exchange section 312 of the upper fin unit 31 and the main heat exchange section 312 of the lower fin unit 31.
  • Each of the fin units 31 is provided with a plurality of protrusions 315 spaced apart from each other, and each of the protrusions 315 protrudes from the surface of the fin unit 31 (as shown in FIG. 3, each of the protrusions 315 is constituted by the fin unit 31).
  • the left side surface protrudes to the left, such that, on the one hand, the plurality of protrusions 315 turbulize the air flowing therethrough, so that the air can flow around to enhance the turbulence effect of the air flow, and the flow of the air
  • the degree of change in direction is small, so that the heat exchange intensity of the fin unit 31 is concentrated at the plurality of protrusions 315, so that the heat exchange of the windward section 311 can be alleviated by setting the number, arrangement, position and spacing of the protrusions 315.
  • the strength enhances the heat exchange effect of the fins 3.
  • the projections 315 do not repeatedly bounce the air, the repeated change of the airflow is small, thereby facilitating the reduction of the noise of the air flow.
  • the plurality of protrusions 315 can also block the penetration of dust or foreign objects and prevent the fins 3 from being blocked.
  • the plurality of protrusions 315 are spaced apart from each other, there is a planar area between the adjacent two protrusions 315, which reduces the wind resistance through which air flows.
  • the flow of air can be controlled to control the heat exchange intensity of the windward section 311, and the wind resistance can be controlled within a suitable range. It is also possible to improve the elimination of condensed water on the fins 3.
  • the windward section 311, the main heat exchange section 312, the leeward section 313 and the plurality of protrusions 315 which are connected to each other can effectively alleviate the windwardness of the fins 3.
  • the heat exchange intensity of the section 311 can sufficiently dehumidify the air, slow down the frosting speed of the windward section 311 of the fin 3, thereby improving the heat exchange efficiency of the heat exchanger and the temperature stability of the heat exchange system, and
  • the plurality of projections 315 also speed up the removal of condensed water, thereby improving the overall performance of the heat exchange system.
  • the protrusion 315 may have a flow guiding surface or a guiding slope so that the condensed water can flow along the guiding surface or the guiding slope Conducive to the condensate flowing out of the wings faster Slice 3.
  • the protrusion 315 may be spherical, cylindrical or conical, such that the protrusion 315 has a flow guiding surface, or the protrusion 315 may also be a cylinder or cone having a polygonal cross section.
  • the projection 315 has a flow guiding ramp.
  • the plurality of protrusions 315 may have the same shape or different shapes (ie, may be a combination of the above various shapes).
  • the projections 315 are all spherically shaped.
  • the partial protrusion 315 is a cylinder having a polygonal cross section
  • the other portion of the protrusion 315 is a spherical shape
  • the remaining protrusion 315 is a cone having a triangular cross section.
  • the plurality of protrusions 315 may be divided into groups, each group of protrusions 315 being arranged in a straight line, a triangle or a polygon.
  • a set of protrusions 315 located in the leeward section 313 are arranged in a triangle
  • a set of protrusions 315 located in the main heat exchange section 312 are arranged in a diamond shape.
  • each set of protrusions 315 is arranged in a straight line shape.
  • FIG. 1 As another example, as shown in FIG.
  • a set of protrusions 315 located in the leeward section 313 are arranged in a straight line, and a set of protrusions 315 located in the main heat exchange section 312 are arranged in a triangle shape.
  • the plurality of sets of protrusions 315 may be arranged in a combination of a straight line, a triangle, and a polygon.
  • the projection of the protrusion 315 on the sheet 5 is circular, and in the main heat exchange section 312, the edge of the flat tube groove 314 and the outer circumference of the protrusion 315
  • the minimum spacing between them is not less than (in the description of the present invention, "not less than” includes a case of greater than or equal to) the radius of the protrusion 315. That is to say, the protrusions 315 in the main heat exchange section 312 are spaced apart from the flat tubes, so that the airflow of the main heat exchange section 312 can be effectively disturbed, thereby enhancing the heat exchange effect, and the main heat exchange section
  • the condensed water of 312 converges to the vicinity of the flat tube under the action of gravity.
  • the protrusion 315 Since the protrusion 315 is not arranged close to the flat tube, the condensed water is not affected, and the frost layer near the flat tube is prevented from increasing after the long-term operation of the heat exchanger, and further The performance of the heat exchanger is guaranteed.
  • the distance between the two protrusions 315 of the main heat exchange section 312 which are furthest apart in the up and down direction accounts for 20%-80% of the height of the main heat exchange section 312 in the up and down direction, so that the main The projections 315 in the heat exchange section 312 are dispersedly arranged to each other, thereby preventing the discharge of the condensed water attached to the surface of the projection 315 from being affected due to the distance between the projections 315 being too close to each other.
  • the pitch X of the center of the two protrusions 315 adjacent in the front-rear direction in the front-rear direction is greater than or equal to the diameter of the protrusion 315, or in the up and down direction.
  • the pitch Y of the centers of the adjacent two protrusions 315 in the up and down direction is greater than or equal to the diameter of the protrusions 315, so that the distribution of the protrusions 315 in the main heat exchange section 312 is more dispersed.
  • the distance between the protrusions 315 is such that X is greater than or equal to the diameter of the protrusion 315, and Y is greater than or equal to The diameter of the protrusion 315.
  • the diameter of the projection 315 is 20% to 30% of the height of the fin unit 31 in the longitudinal direction, so that the projection 315 can effectively disturb the air flow without affecting the elimination of the condensed water.
  • each bulge within the leeward section 313 is in accordance with some embodiments of the present invention.
  • the projected area of the 315 on the sheet 5 is no greater than the projected area of each of the projections 315 in the main heat exchange section 312 on the sheet 5.
  • the heat exchange intensity of the fins 3 is concentrated in the main heat exchange section 312, and the elimination of the condensed water in the main heat exchange section 312 is accelerated, and the frosting speed in the main heat exchange section 312 is slowed down.
  • the edge of the flat tube groove 314 is provided with a flange 319, and the flange 319 is adapted to fit the flat tube to facilitate the brazing of the flat tube and the fin 3.
  • the joint is welded, and since the flange 319 increases the contact area of the fin 3 with the flat tube, the joint strength between the fin 3 and the flat tube is enhanced.
  • the bending direction of the flange 319 coincides with the protrusion direction of the protrusion 315, for example, the flange 319 is bent to the left and the protrusion 315 is convex to the left.
  • the width of the portion of the flat tube groove 314 between the adjacent leeward sections 313 in the longitudinal direction is from the windward section 311 to the leeward zone.
  • the direction of the segment 313 gradually increases. That is, the width of the flat tube groove 314 in the up and down direction gradually increases from the front to the back, thereby facilitating the smooth insertion of the flat tube into the flat tube groove 314.
  • FIG. 2 shows a schematic structural view of two adjacent fin units 31 of the fin 3.
  • the sheet body 5 has a corrugated portion 316 located in the windward section 311, and the crests and troughs of the corrugated portion 316 extend in the longitudinal direction of the sheet body 5 (i.e., the up and down direction shown in the drawing).
  • the condensed water from the main heat exchange section 312 can flow along the corrugated portion 316 under the action of gravity, speeding up the removal of the condensed water and reducing the accumulation of the condensed water in the windward section 311.
  • the corrugated portion 316 can dehumidify the flowing air for the first time to reduce the humidity of the air entering the main heat exchange section 312.
  • the corrugated portion 316 can also increase the structural strength of the fin unit 31, thereby reducing the amount of deformation of the windward section 311.
  • the cross section of the corrugated portion 316 has a substantially "V" shape, and the width of the corrugated portion 316 in the front-rear direction accounts for 70% of the width of the windward section 311 in the front-rear direction, thereby condensing The water removal effect is good.
  • the corrugated portion 316 in the windward section 311 is spaced apart from the main heat exchange section 312 by a planar section 317 such that condensation from the main heat exchange section 312 is achieved.
  • the water can be concentrated to the plane section 317 under the guidance of the protrusions 315, and flows downward along the plane section 317 under gravity to discharge the fins 3, thereby further speeding up the elimination of the condensed water, further reducing The degree of accumulation of condensed water in the windward section 311.
  • the area of the planar section 317 occupies 20% of the area of the windward section 311, so that a faster elimination speed of the condensed water can be ensured.
  • a plurality of spherically shaped projections 315 are provided only in the front section of the main heat exchange section 312 of the fin unit 31 and the leeward section 313, thus reducing the heat exchange intensity of the windward section 311, and the condensed water can be along
  • the arcuate surface of the projection 315 facilitates the condensate to flow out of the fin 3 more quickly.
  • the plurality of protrusions 315 are divided into two groups, and a group of protrusions located in the main heat exchange section 312
  • the 315 is arranged in a diamond shape, and a set of protrusions 315 located in the leeward section 313 are arranged in a triangle shape, which reduces the wind resistance of the front section of the main heat exchange section 312, and increases the heat exchange intensity of the leeward section 313, and strengthens The structure of the leeward section 313.
  • the main heat exchange section 312 is further provided with a louver 318 adjacent to the leeward section 313 and located between the protrusion 315 on the main heat exchange section 312 and the protrusion 315 on the leeward section 313, that is, the louver 318 Located in the rear section of the main heat exchange section 312, a plurality of protrusions 315 on the main heat exchange section 312 are provided in the front section of the main heat exchange section 312.
  • the width of the louver 318 in the front-rear direction accounts for 40% of the width of the main heat exchange section 312 in the front-rear direction, and accordingly, the plurality of protrusions 315 of the main heat exchange section 312 occupy in the front-rear direction.
  • the width occupies 60% of the width of the main heat exchange section 312 in the front-rear direction, such that the plurality of protrusions 315 of the main heat exchange section 312 and the louver 318 are arranged one behind the other in the direction of air flow, so that the main heat exchange section 312 is entered.
  • the air can be first dehumidified through the plurality of protrusions 315, and then heat exchanged through the louvers 318, thereby enhancing the heat exchange effect of the fins 3.
  • the louver 318 includes a first louver 318a and a second louver 318b disposed along the lateral spacing of the sheet 5, the second louver 318b being further relative to the first louver 318a Close to the leeward section 313, that is, the first louver 318a and the second louver 318b are spaced apart from each other, and the first louver 318a is located in front of the second louver 318b, thereby further enhancing the fin 3 Heat transfer effect. As shown in FIG.
  • the first louver 318a has a plurality of first air guiding fins 318c extending obliquely to the right from the main heat exchange section 312 to the leeward section 313, and the second louver 318b has a heat exchange from the main
  • the section 312 is inclined to the windward section 311 by a plurality of second air guiding pieces 318d extending to the right, that is, the first air guiding piece 318c is inclined obliquely to the right from the front to the rear, and the second air guiding piece 318d is inclined to the right from the back to the front.
  • the first air guiding piece 318c and the second air guiding piece 318d form a substantially "eight" shape structure, which facilitates air flowing in from the first air guiding piece 318c and then flowing out from the second air guiding piece 318d, further enhancing the blinds. 318 heat transfer effect.
  • the spacing d2 of the adjacent first air guiding fins 318c is greater than the spacing d1 of the adjacent second air guiding fins 318d, that is, d2>d1, so that most of the frost layer can be prevented from being concentrated on the first louver 318a, ensuring the first The heat transfer of the two louvers 318b.
  • the opening direction of the first louver 318a is the same as the protrusion direction of the protrusion 315 of the main heat exchange section 312, whereby the air flowing through the protrusion 315 of the main heat exchange section 312 can smoothly enter the first direction.
  • the one-leaf window 318a performs heat exchange.
  • the fins 3 shown in Figures 2 - 4 are suitable for use in a microchannel heat exchanger by providing a corrugated portion 316 in the windward section 311, a louver 318 in the main heat exchange section 312, a main heat exchange section 312 and
  • the leeward section 313 is provided with protrusions 315 which can ensure the strength of the fins 3 in the lateral and longitudinal directions, and reduce the degree of deformation of the fins 3 during assembly and transportation.
  • the amount of frost on the fins 3 can be reasonably distributed, and the frosting speed of the heat exchanger can be slowed down.
  • FIG. 5 shows a schematic structural view of two adjacent fin units 31 of the fin 3.
  • the windward section 311, the main heat exchange section 312, and the leeward section 313 of the fin unit 31 are shown in FIG.
  • a plurality of spherical protrusions 315 are respectively provided.
  • the plurality of protrusions 315 are divided into five groups, and the two sets of protrusions 315 located in the windward section 311 are respectively arranged in a straight line shape, and the two sets of protrusions 315 located in the main heat exchange section 312 are respectively arranged in a rhombus shape and the two groups have a common convex shape.
  • a set of protrusions 315 located in the leeward section 313 are arranged in a triangle shape, so that the wind resistance of the main heat exchange section 312 is small, and the heat exchange intensity of the leeward section 313 is increased, and the windward section 311 and the leeward zone are strengthened.
  • the fin 3 shown in FIG. 5 is suitable for the microchannel heat exchanger, and can effectively reduce the heat exchange intensity of the windward section 311 of the fin 3, has a good dehumidifying effect on the air, and can slow down the windward section 311 of the fin 3.
  • the frosting speed so that the heat exchange efficiency of the heat exchanger is high, the temperature of the heat exchange system is more stable, and the plurality of protrusions 315 make the condensed water removal speed faster, and the overall performance of the heat exchange system is better.
  • FIG. 6 shows a schematic structural view of two adjacent fin units 31 of the fin 3.
  • the sheet body 5 has a corrugated portion 316 located in the windward section 311, and the crests and troughs of the corrugated portion 316 respectively extend in the up and down direction of the sheet body 5, the corrugated portion 316 and the main heat exchange region. Segments 312 are spaced apart by a planar section 317.
  • the width of the corrugated portion 316 in the front-rear direction accounts for 70% of the width of the windward section 311 in the front-rear direction, so that the condensed water is effectively removed, and the area of the planar section 317 occupies the area of the windward section 311. 20%, thus ensuring faster removal of condensate.
  • a plurality of spherically shaped protrusions 315 are provided only in the main heat exchange section 312 and the leeward section 313 of the fin unit 31, and the plurality of protrusions 315 are divided into two groups, and a group of protrusions located in the main heat exchange section 312.
  • the 315 is arranged in a diamond shape, and a set of protrusions 315 located in the leeward section 313 are arranged in a triangle shape, so that the heat exchange intensity of the windward section 311 is small, the wind resistance of the main heat exchange section 312 is small, and the leeward section 313 is added.
  • the heat exchange strength enhances the structure of the leeward section 313.
  • the main heat exchange section 312 is further provided with a louver 318.
  • the louver 318 is located at a rear portion of the main heat exchange section 312, and a plurality of protrusions 315 on the main heat exchange section 312 are disposed at a front section of the main heat exchange section 312.
  • the width of the louver 318 in the front-rear direction accounts for 40% of the width of the main heat exchange section 312 in the front-rear direction. Accordingly, the width of the plurality of protrusions 315 of the main heat exchange section 312 occupies the front-rear direction.
  • the hot section 312 is 60% of the width in the front-rear direction.
  • the fin 3 shown in Fig. 6 is suitable for a microchannel heat exchanger, which can effectively reduce the heat exchange intensity of the windward section 311 of the fin 3, increase the elimination speed of the condensed water, and slow the knot of the windward section 311 of the fin 3.
  • the frost speed, and thus the heat exchange efficiency of the heat exchanger is high.
  • FIG. 7 shows a schematic structural view of two adjacent fin units 31 of the fin 3.
  • the windward section 311, the main heat exchange section 312, and the leeward section 313 of the fin unit 31 are shown in FIG.
  • a plurality of spherical protrusions 315 are respectively provided, and the plurality of protrusions 315 are divided into three groups, and a group of protrusions 315 located in the windward section 311 are arranged in a triangle shape, and a group of protrusions 315 located in the main heat exchange section 312.
  • a set of protrusions 315 located in the leeward section 313 are arranged in a triangular shape such that the wind resistance of the main heat exchange section 312 is small, and the structural strength of the windward section 311 and the leeward section 313 is high.
  • the main heat exchange section 312 is further provided with a louver 318, the louver 318 is adjacent to the leeward section 313, and is located between the protrusion 315 on the main heat exchange section 312 and the protrusion 315 on the leeward section 313, and the louver 318 includes
  • the first louver 318a and the second louver 318b are spaced apart in the front-rear direction, and the first louver 318a is located in front of the second louver 318b.
  • the specific structures of the first louver 318a and the second louver 318b are the same as those described above, and are not described herein again.
  • the fin 3 shown in FIG. 7 is suitable for a microchannel heat exchanger, and the condensed water is quickly removed, has a good dehumidifying effect on the air, can slow down the frosting speed of the windward section 311 of the fin 3, and improves the heat exchanger.
  • the heat exchange efficiency is high, and the temperature stability of the heat exchange system is ensured.
  • the sheet body 5 has a corrugated portion 316 located in the windward section 311, and the crests and troughs of the corrugated portion 316 respectively extend in the up and down direction of the sheet body 5, the corrugated portion 316 and the main heat exchange region.
  • the segments 312 are spaced apart by a planar section 317, the width of the corrugated portion 316 in the front-rear direction occupies 70% of the width of the windward section 311 in the front-rear direction, and the area of the planar section 317 occupies the windward section 311. 20% of the area.
  • a plurality of spherical protrusions 315 are provided only in the main heat exchange section 312 and the leeward section 313 of the fin unit 31, and the plurality of protrusions 315 are divided into four groups, three of which are disposed in the main heat exchange section 312. And a set is disposed in the leeward section 313, and each set of protrusions 315 are arranged in a straight line in the up and down direction, thereby reducing the wind resistance on the main heat exchange section 312 and the leeward section 313.
  • the main heat exchange section 312 is further provided with a louver 318, the louver 318 is adjacent to the leeward section 313, and is located between the protrusion 315 on the main heat exchange section 312 and the protrusion 315 on the leeward section 313, and the louver 318 includes
  • the first louver 318a and the second louver 318b are spaced apart in the front-rear direction, and the first louver 318a is located in front of the second louver 318b.
  • the specific structures of the first louver 318a and the second louver 318b are the same as those described above, and are not described herein again.
  • the fin 3 shown in Fig. 8 is suitable for a microchannel heat exchanger, which can effectively improve the heat exchange efficiency of the heat exchanger and improve the overall performance of the heat exchange system.
  • FIG. 9 shows a schematic structural view of two adjacent fin units 31 of the fin 3.
  • the sheet 5 has a corrugated portion 316 located in the windward section 311, the corrugated portion 316 The crests and troughs respectively extend in the up and down direction of the sheet body 5, and the corrugated portion 316 is spaced apart from the main heat exchange portion 312 by a plane section 317, and the width of the corrugated portion 316 in the front and rear direction occupies the windward section.
  • 311 is 70% of the width in the front-rear direction, and the area of the planar section 317 accounts for 20% of the area of the windward section 311.
  • the plurality of protrusions 315 are disposed only in the main heat exchange section 312 and the leeward section 313 of the fin unit 31, and the plurality of protrusions 315 are divided into two groups, wherein a group of protrusions 315 located in the leeward section 313 are arranged.
  • the protrusions 315 are cylindrical with a rectangular cross section, and a set of protrusions 315 located in the main heat exchange section 312 are arranged in a diamond shape, and a part of the protrusions 315 are spherical and the other part is 315. It is a cone with a triangular cross section.
  • the main heat exchange section 312 is further provided with a louver 318 adjacent to the leeward section 313 and located between the protrusion 315 on the main heat exchange section 312 and the protrusion 315 on the leeward section 313, and the louver 318 includes
  • the first louver 318a and the second louver 318b are spaced apart in the front-rear direction, and the first louver 318a is located in front of the second louver 318b.
  • the specific structures of the first louver 318a and the second louver 318b are the same as those described above, and are not described herein again.
  • the fin 3 shown in FIG. 9 is suitable for a microchannel heat exchanger, which can improve the removal speed of the condensed water and slow down the frosting speed of the fin 3, thereby effectively improving the heat exchange efficiency of the heat exchanger and improving the overall heat exchange system. performance.
  • a heat exchanger 100 includes a first header 1, a second header 2, a plurality of fins, and a flat tube 4.
  • the fins are fins 3 according to the above-described embodiment of the present invention, and the fins 3 are disposed between the first header 1 and the second header 2 at a distance from each other. Both ends of the flat tube 4 are connected to the first header tube 1 and the second header tube 2, respectively, and the flat tube tube 4 is fitted in the flat tube groove 314, respectively.
  • the fins 3 extend in the up and down direction
  • the flat tubes 4 extend in the left-right direction
  • the fins 3 are disposed perpendicularly to the flat tubes 4 such that each fin 3 is connected to a plurality of flat tubes 4, each The flat tube 4 is connected to a plurality of fins 3, and the fins 3 and the flat tubes 4 are reliably connected.
  • the condensed water is quickly removed, the frosting speed is slow, and the heat exchange efficiency is high.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, features defining “first” and “second” may include one or more of the features either explicitly or implicitly. In the description of the present invention, "a plurality” means two or more unless otherwise stated.
  • connection In the description of the present invention, it should be noted that the terms “installation”, “connected”, and “connected” are to be understood broadly, and may be fixed or detachable, for example, unless otherwise explicitly defined and defined.
  • Connect, Or integrally connected may be mechanical connection or electrical connection; may be directly connected, or may be indirectly connected through an intermediate medium, and may be internal communication between the two elements.
  • the specific meaning of the above terms in the present invention can be understood in a specific case by those skilled in the art.

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  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

一种翅片（3）和具有该翅片（3）的换热器（100），翅片（3）包括片体（5），片体（5）包括沿该片体（5）的纵向排列的多个散热片单元（31），每个散热片单元（31）包括沿该片体（5）的横向排列的迎风区段（311）、主换热区段（312）和背风区段（313），相邻散热片单元（31）的迎风区段（311）彼此相连，扁管槽（314）延伸在相邻散热片单元（31）中的一个散热片单元（31）的背风区段（313）和主换热区段（312）与另一个散热片单元（31）的背风区段（313）和主换热区段（312）之间，每个散热片单元（31）上设有彼此间隔开的多个凸起（315）。

Description

翅片和具有它的换热器 技术领域
本发明涉及换热器技术领域，具体而言，涉及一种翅片和具有所述翅片的换热器。
背景技术
相关技术中的微通道换热器由集流管、扁管和翅片组成，翅片设置在相邻扁管之间，翅片表面开设有占据翅片的绝大部分的百叶窗，翅片迎风端的换热强度较大，导致翅片迎风端的冷凝水或结霜量较多。翅片表面结霜会减小换热器的有效换热面积，且应用该换热器的空调器等系统会频繁进入除霜程序，影响温度的稳定性。翅片表面的冷凝水靠重力作用下流排除，但由于冷凝水的流动路径较长，排除困难，增加了换热器的换热热阻，影响换热器的换热能力。
发明内容
本发明旨在至少解决现有技术中存在的技术问题之一。为此，本发明需要提供一种翅片，所述翅片的冷凝水排除速度快且结霜速度慢，能够提高换热器的换热性能，提高换热系统温度的稳定性。
本发明还需要提供一种换热器。
根据本发明第一方面实施例的翅片，包括片体，所述片体包括沿该片体的纵向排列的多个散热片单元，每个散热片单元包括沿该片体的横向排列的迎风区段、背风区段和位于所述迎风区段与所述背风区段之间的主换热区段，相邻散热片单元的迎风区段彼此相连，相邻散热片单元之间形成有扁管槽，所述扁管槽延伸在相邻散热片单元中的一个散热片单元的背风区段和主换热区段与另一个散热片单元的背风区段和主换热区段之间，每个散热片单元上设有从该散热片单元的表面突起且彼此间隔开的多个凸起。
根据本发明实施例的翅片，能够对空气进行充分的除湿，减缓翅片的迎风区段的结霜速度，从而提高换热器的换热效率以及换热系统温度的稳定性，而且，多个凸起还加快了冷凝水的排除速度，从而提高了换热系统的整体性能。
根据本发明的一些实施例，所述凸起具有导流曲面或导流斜面。
根据本发明的一些实施例，所述凸起为球缺形、圆柱形或圆锥形，或为横截面为多边形的柱体或锥体。
根据本发明的一些实施例，多个所述凸起分成多组，每一组凸起排列成直线形、三角形或多边形。
根据本发明的一个实施例，所述凸起仅设置在所述主换热区段和所述背风区段内。
根据本发明的一个实施例，所述片体具有位于所述迎风区段内的波纹状部分，所述波纹状部分的波峰和波谷分别沿该片体的纵向延伸。
进一步地，所述迎风区段内的波纹状部分与所述主换热区段之间通过一平面区段间隔开。
可选地，所述平面区段的面积与所述迎风区段的面积比为20％。
根据本发明的一个实施例，所述主换热区段上进一步设有百叶窗，所述百叶窗邻近所述背风区段。
可选地，所述凸起仅设在所述主换热区段和所述背风区段内，且所述百叶窗位于所述主换热区段上的凸起与所述背风区段上的凸起之间。
可选地，所述百叶窗包括沿所述片体的横向间隔布置的第一百叶窗和第二百叶窗，所述第二百叶窗相对于所述第一百叶窗更靠近所述背风区段，所述第一百叶窗具有从所述主换热区段向所述背风区段倾斜延伸的多个第一导风片，所述第二百叶窗具有从所述主换热区段向所述迎风区段倾斜延伸的多个第二导风片。
优选地，相邻第一导风片的间距大于相邻第二导风片的间距。
根据本发明的一些实施例，所述凸起在所述片体所在平面上的投影为圆形，在所述主换热区段内，所述扁管槽的边沿与所述圆形的外周缘之间的最小间距不小于所述圆形的半径。
可选地，所述圆形的直径为所述散热片单元在所述纵向上的高度的20％-30％。
根据本发明的一些实施例，所述背风区段内的凸起在所述片体所在平面上的投影的面积不大于所述主换热区段内的凸起在所述片体所在平面上的投影的面积。
根据本发明的一个实施例，所述扁管槽的边沿设有翻边。
进一步地，所述翻边的弯折方向与所述凸起的突起方向一致。
根据本发明的一些实施例，所述扁管槽的位于相邻背风区段之间的部分在所述纵向上的宽度沿从所述迎风区段到所述背风区段的方向逐渐增大。
根据本发明第二方面实施例的换热器，包括：第一集流管和第二集流管；多个翅片，所述翅片为根据本发明上述第一方面实施例的翅片，所述翅片彼此间隔开地设在所述第一集流管和所述第二集流管之间；扁管，所述扁管的两端分别与所述第一集流管和第二集流管相连且所述扁管分别配合在所述扁管槽内。
根据本发明实施例的换热器，利用如上所述的翅片，冷凝水的排除速度快，结霜速度缓慢，换热效率高。
本发明的附加方面和优点将在下面的描述中部分给出，部分将从下面的描述中变 得明显，或通过本发明的实践了解到。
附图说明
图1是根据本发明实施例的换热器的结构示意图。
图2是根据本发明实施例的翅片的片体的结构示意图。
图3是根据本发明实施例的翅片的片体的横向剖视图。
图4是根据本发明实施例的翅片的片体的纵向剖视图。
图5是根据本发明第一可选实施例的翅片的片体的结构示意图。
图6是根据本发明第二可选实施例的翅片的片体的结构示意图。
图7是根据本发明第三可选实施例的翅片的片体的结构示意图。
图8是根据本发明第四可选实施例的翅片的片体的结构示意图。
图9是根据本发明第五可选实施例的翅片的片体的结构示意图。
附图标记：
换热器100，第一集流管1，第二集流管2，翅片3，扁管4，片体5，
散热片单元31，迎风区段311，主换热区段312，背风区段313，扁管槽314，凸起315，迎风区段内的波纹状部分316，平面区段317，百叶窗318，第一百叶窗318a，第一导风片318c，第二百叶窗318b，第二导风片318d，翻边319。
具体实施方式
下面详细描述本发明的实施例，所述实施例的示例在附图中示出，其中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，仅用于解释本发明，而不能理解为对本发明的限制。
下面参考图1-图9描述根据本发明第一方面实施例的翅片3，所述翅片3适用于微通道换热器，具有冷凝水的排除速度快和结霜速度慢等优点，能够提高换热器的换热性能。
如图1-图9所示，根据本发明实施例的翅片3，包括片体5。
具体地，片体5包括沿该片体5的纵向(即图示上下方向)排列的多个散热片单元31，每个散热片单元31包括沿该片体5的横向(即图示前后方向)排列的迎风区段311、背风区段313和位于迎风区段311与背风区段313之间的主换热区段312。例如，如图2和图5-图9所示，多个散热片单元31沿上下方向排列，每个散热片单元31的迎风区段311、背风区段313和主换热区段312沿前后方向排列，其中迎风区段311位于散热片单元31的前端，背风区段313位于散热片单元31的后端，主换热区段312位于迎风区段311和背风区 段313之间。如附图中，相邻散热片单元31的迎风区段311彼此相连，这样多个散热片单元31彼此相连形成为片体5，使得片体5的结构可靠。
相邻散热片单元31之间形成有扁管槽314，扁管槽314适于容纳换热器的扁管，这样利用扁管与扁管槽314的配合翅片3能够固定在换热器上。扁管槽314延伸在相邻散热片单元31中的一个散热片单元31的背风区段313和主换热区段312与另一个散热片单元31的背风区段313和主换热区段312之间，从而翅片3与扁管的换热效果更好。例如，如图2和图4-图9所示，扁管槽314沿前后方向延伸，扁管槽314贯穿在上方的散热片单元31的背风区段313与下方的散热片单元31的背风区段313之间，且扁管槽314贯穿在上方的散热片单元31的主换热区段312与下方的散热片单元31的主换热区段312之间。
每个散热片单元31上设有彼此间隔开的多个凸起315，每个凸起315从该散热片单元31的表面突起(如图3所示，每个凸起315由散热片单元31的左侧表面向左突起)，这样，一方面，多个凸起315对流动至该处的空气进行扰流，使得空气能够发生绕流，以增强空气流动的紊流效果，且空气的流动方向改变程度小，从而使得散热片单元31的换热强度集中在多个凸起315处，这样通过设置凸起315的数量、排列方式、位置和间距大小，可以减轻迎风区段311的换热强度，加强翅片3的换热效果。而且，由于凸起315没有对空气进行反复折流，气流的反复变向小，从而有利于减小空气流动的噪音。
另一方面，当散热片单元31表面的霜层融化时，由于冷凝水在重力和凸起315的双重作用下能够沿着凸起315的外表面向下流动，由此，多个凸起315加快了冷凝水的排除速度，且能够降低空气的湿度，减缓翅片3的结霜速度。
同时，多个凸起315还可以阻拦灰尘或者外来物的深入，避免翅片3被堵塞。此外，由于多个凸起315彼此间隔设置，相邻的两个凸起315之间会有平面区域，这样减小了空气流经此处的风阻。
可以理解的是，通过设置凸起315的数量、位置、排列方式和间距大小，既可以控制空气的流动情况以控制迎风区段311的换热强度，又可以将风阻控制在合适的范围内，还能够改善翅片3上冷凝水的排除情况。
综上所述，根据本发明实施例的翅片3，利用相互连接的迎风区段311、主换热区段312、背风区段313以及多个凸起315，可以有效减轻翅片3的迎风区段311的换热强度，能够对空气进行充分的除湿，减缓翅片3的迎风区段311的结霜速度，从而提高换热器的换热效率以及换热系统温度的稳定性，而且，多个凸起315还加快了冷凝水的排除速度，从而提高了换热系统的整体性能。
根据本发明的一些实施例，如图2-图3和图5-图9所示，凸起315可以具有导流曲面或导流斜面，这样冷凝水能够沿着导流曲面或导流斜面流动，有利于冷凝水更快地流出翅 片3。
根据本发明的一些实施例，凸起315可以为球缺形、圆柱形或圆锥形，这样凸起315具有导流曲面，或者凸起315还可以是横截面为多边形的柱体或锥体，这样凸起315具有导流斜面。可以理解的是，多个凸起315可以形状相同，也可以形状不同(即可以是上述各种形状的组合)。例如，如图2-图3和图5-图8所示，凸起315全部为球缺形。又如，如图9所示，部分凸起315是横截面为多边形的柱体，另一部分凸起315是球缺形，剩余凸起315是横截面为三角形的锥体。
根据本发明的一些实施例，多个凸起315可以分成多组，每一组凸起315排列成直线形、三角形或多边形。例如，如图2和图6-图7所示，位于背风区段313的一组凸起315排列成三角形，位于主换热区段312的一组凸起315排列成菱形。又如，如图8所示，每一组凸起315均排列成直线形。再如，如图9所示，位于背风区段313的一组凸起315排列成直线形，位于主换热区段312的一组凸起315排列成三角形。当然，如图5所示，多组凸起315的排列方式还可以是直线形、三角形和多边形的组合。
在如图2-图8所示的实施例中，凸起315在片体5上的投影为圆形，在主换热区段312内，扁管槽314的边沿与凸起315的外周缘之间的最小间距不小于(本发明的描述中，“不小于”包括大于或者等于的情形)凸起315的半径。也就是说，主换热区段312内的凸起315与扁管间隔开，这样能够对主换热区段312的气流进行有效地扰动，从而加强换热效果，而且，主换热区段312的冷凝水在重力作用下汇聚到扁管附近，由于凸起315不靠近扁管布置，从而不影响冷凝水的排放，避免换热器长时间运行后扁管附近的霜层大量增加，进而保证了换热器的使用性能。可选地，主换热区段312在上下方向上的相距最远的两个凸起315之间的距离占主换热区段312在上下方向上的高度的20％-80％，这样主换热区段312内的凸起315彼此分散布置，从而防止由于凸起315彼此间距离过近而影响凸起315表面附着的冷凝水的排放。
进一步地，如图2和图5-图8所示，在前后方向上相邻的两个凸起315的圆心在前后方向上的间距X大于或者等于凸起315的直径，或者在上下方向上相邻的两个凸起315的圆心在上下方向上的间距Y大于或者等于凸起315的直径，这样主换热区段312内的凸起315的分布更加分散。特殊地，如图2和图5-图7所示，当凸起315排列成三角形或多边形时，凸起315彼此间的距离满足：X大于或者等于凸起315的直径，且Y大于或者等于凸起315的直径。
作为优选，凸起315的直径为散热片单元31在纵向上的高度的20％-30％，这样凸起315能够有效地扰动气流，且不影响冷凝水的排除。
如图2-图3和图5-图9所示，根据本发明的一些实施例，背风区段313内的每个凸起 315在片体5上的投影的面积不大于主换热区段312内的每个凸起315在片体5上的投影的面积。这样，翅片3的换热强度集中在主换热区段312内，且加快了主换热区段312内冷凝水的排除，减缓了主换热区段312内的结霜速度。
如图2和图4所示，根据本发明的一些实施例，扁管槽314的边沿设有翻边319，翻边319适于与扁管贴合，以便于扁管与翅片3的钎焊连接，且由于翻边319增加了翅片3与扁管的接触面积，从而增强了翅片3与扁管之间的连接强度。进一步地，如图4所示，翻边319的弯折方向与凸起315的突起方向一致，例如，翻边319向左弯折且凸起315向左凸起。
如图2和图5-图9所示，根据本发明的一些实施例，扁管槽314的位于相邻背风区段313之间的部分在纵向上的宽度沿从迎风区段311到背风区段313的方向逐渐增大。也就是说，扁管槽314在上下方向上的宽度从前向后逐渐增大，从而方便扁管顺利地插入扁管槽314内。
下面参考图2-图4详细描述根据本发明的一个具体实施例的翅片3，值得理解的是，下述描述只是示例性说明，而不能理解为对本发明的限制。需要说明的是，图2中仅示出翅片3的相邻两个散热片单元31的结构示意图。
如图2所示，片体5具有位于迎风区段311内的波纹状部分316，波纹状部分316的波峰和波谷分别沿该片体5的纵向(即图中所示的上下方向)延伸，这样来自主换热区段312的冷凝水可以在重力作用下沿着波纹状部分316流动，加快了冷凝水的排除速度，减小了冷凝水在迎风区段311的积聚程度。而且，波纹状部分316可以对流过的空气进行第一次除湿，以减小进入主换热区段312的空气的湿度。另外，波纹状部分316还能够增加散热片单元31的结构强度，从而减小了迎风区段311的变形量。优选地，如图3所示，波纹状部分316的横截面呈大体“V”形，波纹状部分316在前后方向上的宽度占迎风区段311在前后方向上的宽度的70％，从而冷凝水的排除效果好。
进一步地，如图2-图3所示，迎风区段311内的波纹状部分316与主换热区段312之间通过一平面区段317间隔开，这样来自主换热区段312的冷凝水可以在凸起315的引导下汇聚至平面区段317，并在重力作用下沿着平面区段317向下流动而排出翅片3，从而进一步加快了冷凝水的排除速度，进一步减小了冷凝水在迎风区段311的积聚程度。优选地，平面区段317的面积占迎风区段311的面积的20％，从而能够保证冷凝水的较快的排除速度。
多个球缺形的凸起315仅设在散热片单元31的主换热区段312的前段和背风区段313内，这样减轻了迎风区段311的换热强度，且冷凝水能够沿着凸起315的弧面流动，有利于冷凝水更快地流出翅片3。多个凸起315分成两组，位于主换热区段312的一组凸 起315排列成菱形，位于背风区段313的一组凸起315排列成三角形，这样减小了主换热区段312的前段的风阻，且增加了背风区段313的换热强度，强化了背风区段313的结构。
主换热区段312上还设有百叶窗318，百叶窗318邻近背风区段313，且位于主换热区段312上的凸起315与背风区段313上的凸起315之间，即百叶窗318位于主换热区段312的后段，主换热区段312上的多个凸起315设在主换热区段312的前段。可选地，百叶窗318在前后方向上的宽度占主换热区段312在前后方向上的宽度的40％，相应地，主换热区段312的多个凸起315在前后方向上占据的宽度占主换热区段312在前后方向上的宽度的60％，这样主换热区段312的多个凸起315与百叶窗318沿空气流动的方向前后布置，使得进入主换热区段312的空气能够先经过多个凸起315进行第二次除湿后，再通过百叶窗318进行换热，从而增强了翅片3的换热效果。
进一步地，如图2所示，百叶窗318包括沿片体5的横向间隔布置的第一百叶窗318a和第二百叶窗318b，第二百叶窗318b相对于第一百叶窗318a更靠近背风区段313，即第一百叶窗318a与第二百叶窗318b前后间隔开，且第一百叶窗318a位于第二百叶窗318b的前方，由此进一步增强了翅片3的换热效果。如图3所示，第一百叶窗318a具有从主换热区段312向背风区段313倾斜向右延伸的多个第一导风片318c，第二百叶窗318b具有从主换热区段312向迎风区段311倾斜向右延伸的多个第二导风片318d，即第一导风片318c从前向后倾斜向右延伸，第二导风片318d从后向前倾斜向右延伸，第一导风片318c与第二导风片318d形成大体“八”字形结构，有利于空气由第一导风片318c流入再从第二导风片318d流出，更进一步地增强了百叶窗318的换热效果。
优选地，相邻第一导风片318c的间距d2大于相邻第二导风片318d的间距d1，即d2>d1，这样能够避免大部分霜层集中在第一百叶窗318a，保证第二百叶窗318b的换热作用。可以理解的是，第一百叶窗318a的开口方向与主换热区段312的凸起315的突起方向相同，由此流过主换热区段312的凸起315的空气能够顺利进入第一百叶窗318a进行换热。
图2-图4所示的翅片3适用于微通道换热器，通过在迎风区段311设置波纹状部分316、在主换热区段312设置百叶窗318、在主换热区段312和背风区段313设置凸起315，可以保证翅片3在横向和纵向方向上的强度，减小翅片3在组装和运送过程中的变形程度。而且，通过在翅片3上控制不同区段的换热强度，能够合理分布翅片3上的结霜量，减缓换热器的结霜速度。
下面参考图5详细描述根据本发明第一可选实施例的翅片3，值得理解的是，下述描述只是示例性说明，而不能理解为对本发明的限制。需要说明的是，图5中仅示出翅片3的相邻两个散热片单元31的结构示意图。
如图5所示，散热片单元31的迎风区段311、主换热区段312和背风区段313内 分别设有多个球缺形的凸起315。多个凸起315分成五组，位于迎风区段311的两组凸起315分别排列成直线形，位于主换热区段312的两组凸起315分别排列成菱形且两组具有共同的凸起315，位于背风区段313的一组凸起315排列成三角形，这样主换热区段312的风阻小，且增加了背风区段313的换热强度，强化了迎风区段311和背风区段313的结构。
图5所示的翅片3适用于微通道换热器，能够有效减轻翅片3的迎风区段311的换热强度，对空气的除湿效果好，可以减缓翅片3的迎风区段311的结霜速度，从而换热器的换热效率高，换热系统的温度更加稳定，而且，多个凸起315使得冷凝水的排除速度更快，换热系统的整体性能更好。
下面参考图6详细描述根据本发明的第二可选实施例的翅片3，值得理解的是，下述描述只是示例性说明，而不能理解为对本发明的限制。需要说明的是，图6中仅示出翅片3的相邻两个散热片单元31的结构示意图。
如图6所示，片体5具有位于迎风区段311内的波纹状部分316，波纹状部分316的波峰和波谷分别沿该片体5的上下方向延伸，波纹状部分316与主换热区段312之间通过一平面区段317间隔开。优选地，波纹状部分316在前后方向上的宽度占迎风区段311在前后方向上的宽度的70％，从而冷凝水的排除效果好，平面区段317的面积占迎风区段311的面积的20％，从而能够保证冷凝水的较快的排除速度。
多个球缺形的凸起315仅设在散热片单元31的主换热区段312和背风区段313内，多个凸起315分成两组，位于主换热区段312的一组凸起315排列成菱形，位于背风区段313的一组凸起315排列成三角形，这样迎风区段311的换热强度小，主换热区段312的风阻小，且增加了背风区段313的换热强度，强化了背风区段313的结构。
主换热区段312上还设有百叶窗318，百叶窗318位于主换热区段312的后段，主换热区段312上的多个凸起315设在主换热区段312的前段，百叶窗318在前后方向上的宽度占主换热区段312在前后方向上的宽度的40％，相应地，主换热区段312的多个凸起315在前后方向上占据的宽度占主换热区段312在前后方向上的宽度的60％。
图6所示的翅片3适用于微通道换热器，能够有效减轻翅片3的迎风区段311的换热强度，提高冷凝水的排除速度，减缓翅片3的迎风区段311的结霜速度，从而换热器的换热效率高。
下面参考图7详细描述根据本发明的第三可选实施例的翅片3，值得理解的是，下述描述只是示例性说明，而不能理解为对本发明的限制。需要说明的是，图7中仅示出翅片3的相邻两个散热片单元31的结构示意图。
如图7所示，散热片单元31的迎风区段311、主换热区段312和背风区段313内 分别设有多个球缺形的凸起315，多个凸起315分成三组，位于迎风区段311的一组凸起315排列成三角形，位于主换热区段312的一组凸起315排列成菱形，位于背风区段313的一组凸起315排列成三角形，这样主换热区段312的风阻小，迎风区段311和背风区段313的结构强度高。
主换热区段312上还设有百叶窗318，百叶窗318邻近背风区段313，且位于主换热区段312上的凸起315与背风区段313上的凸起315之间，百叶窗318包括沿前后方向间隔布置的第一百叶窗318a和第二百叶窗318b，且第一百叶窗318a位于第二百叶窗318b的前方。其中第一百叶窗318a和第二百叶窗318b的具体结构同上所述，这里不再赘述。
图7所示的翅片3适用于微通道换热器，冷凝水的排除速度快，对空气的除湿效果好，可以减缓翅片3的迎风区段311的结霜速度，提高换热器的换热效率高，保证换热系统温度的稳定性。
下面参考图8详细描述根据本发明的第四可选实施例的翅片3，值得理解的是，下述描述只是示例性说明，而不能理解为对本发明的限制。需要说明的是，图8中仅给出翅片3的相邻两个散热片单元31的结构示意图。
如图8所示，片体5具有位于迎风区段311内的波纹状部分316，波纹状部分316的波峰和波谷分别沿该片体5的上下方向延伸，波纹状部分316与主换热区段312之间通过一平面区段317间隔开，波纹状部分316在前后方向上的宽度占迎风区段311在前后方向上的宽度的70％，平面区段317的面积占迎风区段311的面积的20％。
多个球缺形的凸起315仅设在散热片单元31的主换热区段312和背风区段313内，多个凸起315分成四组，其中三组设置在主换热区段312且一组设置在背风区段313，每一组凸起315沿上下方向排列成直线形，从而减小了主换热区段312和背风区段313上的风阻。
主换热区段312上还设有百叶窗318，百叶窗318邻近背风区段313，且位于主换热区段312上的凸起315与背风区段313上的凸起315之间，百叶窗318包括沿前后方向间隔布置的第一百叶窗318a和第二百叶窗318b，且第一百叶窗318a位于第二百叶窗318b的前方。其中第一百叶窗318a和第二百叶窗318b的具体结构同上所述，这里不再赘述。
图8所示的翅片3适用于微通道换热器，能够有效提高换热器的换热效率，提高换热系统的整体性能。
下面参考图9详细描述根据本发明的第五可选实施例的翅片3，值得理解的是，下述描述只是示例性说明，而不能理解为对本发明的限制。需要说明的是，图9中仅示出翅片3的相邻两个散热片单元31的结构示意图。
如图9所示，片体5具有位于迎风区段311内的波纹状部分316，波纹状部分316的 波峰和波谷分别沿该片体5的上下方向延伸，波纹状部分316与主换热区段312之间通过一平面区段317间隔开，波纹状部分316在前后方向上的宽度占迎风区段311在前后方向上的宽度的70％，平面区段317的面积占迎风区段311的面积的20％。
多个凸起315仅设在散热片单元31的主换热区段312和背风区段313内，多个凸起315分成两组，其中，位于背风区段313内的一组凸起315排列成直线形，且凸起315为横截面为长方形的柱体，位于主换热区段312内的一组凸起315排列成菱形，且一部分凸起315为球缺形，另一部分凸起315为横截面为三角形的锥体。
主换热区段312上还设有百叶窗318，百叶窗318邻近背风区段313且位于主换热区段312上的凸起315与背风区段313上的凸起315之间，百叶窗318包括沿前后方向间隔布置的第一百叶窗318a和第二百叶窗318b，且第一百叶窗318a位于第二百叶窗318b的前方。其中第一百叶窗318a和第二百叶窗318b的具体结构同上所述，这里不再赘述。
图9所示的翅片3适用于微通道换热器，能够提高冷凝水的排除速度，减缓翅片3的结霜速度，从而有效提高换热器的换热效率，提高换热系统的整体性能。
如图1所示，根据本发明第二方面实施例的换热器100，包括第一集流管1、第二集流管2、多个翅片以及扁管4。
翅片为根据本发明上述实施例的翅片3，翅片3彼此间隔开地设在第一集流管1和第二集流管2之间。扁管4的两端分别与第一集流管1和第二集流管2相连且扁管4分别配合在扁管槽314内。例如，如图1所示，翅片3沿上下方向延伸，扁管4沿左右方向延伸，翅片3与扁管4垂直设置，这样每个翅片3与多个扁管4相连，每个扁管4与多个翅片3相连，翅片3与扁管4可靠地连接在一起。
根据本发明实施例的换热器100，利用如上所述的翅片3，冷凝水的排除速度快，结霜速度缓慢，换热效率高。
在本发明的描述中，需要理解的是，术语“纵向”、“横向”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括一个或者更多个该特征。在本发明的描述中，除非另有说明，“多个”的含义是两个或两个以上。
在本发明的描述中，需要说明的是，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”应做广义理解，例如，可以是固定连接，也可以是可拆卸连接， 或一体地连接；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通。对于本领域的普通技术人员而言，可以具体情况理解上述术语在本发明中的具体含义。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“可选实施例”、“具体实施例”等的描述意指结合该实施例描述的具体特征、结构、材料或者特点包含于本发明的至少一个实施例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例。而且，描述的具体特征、结构、材料或者特点可以在任何的一个或多个实施例中以合适的方式结合。
尽管已经示出和描述了本发明的实施例，本领域的普通技术人员可以理解：在不脱离本发明的原理和宗旨的情况下可以对这些实施例进行多种变化、修改、替换和变型，本发明的范围由权利要求及其等同物限定。

Claims (19)

  1. 一种翅片，其特征在于，包括片体，所述片体包括沿该片体的纵向排列的多个散热片单元，每个散热片单元包括沿该片体的横向排列的迎风区段、背风区段和位于所述迎风区段与所述背风区段之间的主换热区段，相邻散热片单元的迎风区段彼此相连，相邻散热片单元之间形成有扁管槽，所述扁管槽延伸在相邻散热片单元中的一个散热片单元的背风区段和主换热区段与另一个散热片单元的背风区段和主换热区段之间，每个散热片单元上设有从该散热片单元的表面突起且彼此间隔开的多个凸起。
  2. 根据权利要求1所述的翅片，其特征在于，所述凸起具有导流曲面或导流斜面。
  3. 根据权利要求1-2中任一项所述的翅片，其特征在于，所述凸起为球缺形、圆柱形或圆锥形，或为横截面为多边形的柱体或锥体。
  4. 根据权利要求1-3中任一项所述的翅片，其特征在于，多个所述凸起分成多组，每一组凸起排列成直线形、三角形或多边形。
  5. 根据权利要求1-4中任一项所述的翅片，其特征在于，所述凸起仅设置在所述主换热区段和所述背风区段内。
  6. 根据权利要求1-5中任一项所述的翅片，其特征在于，所述片体具有位于所述迎风区段内的波纹状部分，所述波纹状部分的波峰和波谷分别沿该片体的纵向延伸。
  7. 根据权利要求6所述的翅片，其特征在于，所述迎风区段内的波纹状部分与所述主换热区段之间通过一平面区段间隔开。
  8. 根据权利要求7所述的翅片，其特征在于，所述平面区段的面积与所述迎风区段的面积比为20％。
  9. 根据权利要求1-8任一项所述的翅片，其特征在于，所述主换热区段上进一步设有百叶窗，所述百叶窗邻近所述背风区段。
  10. 根据权利要求9所述的翅片，其特征在于，所述凸起仅设在所述主换热区段和所述背风区段内，且所述百叶窗位于所述主换热区段上的凸起与所述背风区段上的凸起之间。
  11. 根据权利要求9所述的翅片，其特征在于，所述百叶窗包括沿所述片体的横向间隔布置的第一百叶窗和第二百叶窗，所述第二百叶窗相对于所述第一百叶窗更靠近所述背风区段，所述第一百叶窗具有从所述主换热区段向所述背风区段倾斜延伸的多个第一导风片，所述第二百叶窗具有从所述主换热区段向所述迎风区段倾斜延伸的多个第二导风片。
  12. 根据权利要求11所述的翅片，其特征在于，相邻第一导风片的间距大于相邻第二导风片的间距。
  13. 根据权利要求1-12中任一项所述的翅片，其特征在于，所述凸起在所述片体所在 平面上的投影为圆形，在所述主换热区段内，所述扁管槽的边沿与所述圆形的外周缘之间的最小间距不小于所述圆形的半径。
  14. 根据权利要求13所述的翅片，其特征在于，所述圆形的直径为所述散热片单元在所述纵向上的高度的20％-30％。
  15. 根据权利要求1-14中任一项所述的翅片，其特征在于，所述背风区段内的凸起在所述片体所在平面上的投影的面积不大于所述主换热区段内的凸起在所述片体所在平面上的投影的面积。
  16. 根据权利要求1-15中任一项所述的翅片，其特征在于，所述扁管槽的边沿设有翻边。
  17. 根据权利要求16所述的翅片，其特征在于，所述翻边的弯折方向与所述凸起的突起方向一致。
  18. 根据权利要求1-17中任一项所述的翅片，其特征在于，所述扁管槽的位于相邻背风区段之间的部分在所述纵向上的宽度沿从所述迎风区段到所述背风区段的方向逐渐增大。
  19. 一种换热器，其特征在于，包括：
    第一集流管和第二集流管；
    多个翅片，所述翅片为根据权利要求1-18中任一项所述的翅片，所述翅片彼此间隔开地设在所述第一集流管和所述第二集流管之间；
    扁管，所述扁管的两端分别与所述第一集流管和第二集流管相连且所述扁管分别配合在所述扁管槽内。
PCT/CN2016/099628 2015-09-21 2016-09-21 翅片和具有它的换热器 WO2017050237A1 (zh)

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