WO2015058452A1 - Ailette d'échangeur de chaleur et échangeur de chaleur utilisant l'ailette d'échangeur de chaleur - Google Patents

Ailette d'échangeur de chaleur et échangeur de chaleur utilisant l'ailette d'échangeur de chaleur Download PDF

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Publication number
WO2015058452A1
WO2015058452A1 PCT/CN2013/090647 CN2013090647W WO2015058452A1 WO 2015058452 A1 WO2015058452 A1 WO 2015058452A1 CN 2013090647 W CN2013090647 W CN 2013090647W WO 2015058452 A1 WO2015058452 A1 WO 2015058452A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
exchanger fin
plate
fin
windward
Prior art date
Application number
PCT/CN2013/090647
Other languages
English (en)
Chinese (zh)
Inventor
程志明
徐龙贵
佐藤宪一郎
李丰
吕艳红
Original Assignee
美的集团股份有限公司
程志明
徐龙贵
佐藤宪一郎
李丰
吕艳红
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
Priority claimed from CN201320650570.6U external-priority patent/CN203550718U/zh
Priority claimed from CN201320650075.5U external-priority patent/CN203550715U/zh
Priority claimed from CN201320650096.7U external-priority patent/CN203550716U/zh
Priority claimed from CN201320650072.1U external-priority patent/CN203550713U/zh
Application filed by 美的集团股份有限公司, 程志明, 徐龙贵, 佐藤宪一郎, 李丰, 吕艳红 filed Critical 美的集团股份有限公司
Publication of WO2015058452A1 publication Critical patent/WO2015058452A1/fr

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    • 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
    • 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
    • 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
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing
    • F28F2275/045—Fastening; Joining by brazing with particular processing steps, e.g. by allowing displacement of parts during brazing or by using a reservoir for storing brazing material

Definitions

  • the invention relates to the field of heat exchangers, and in particular to a heat exchanger fin and a heat exchanger using the heat exchanger fin.
  • the microchannel heat exchanger adopts a flat tube with a fine structure as its refrigerant side flow carrier, which can enhance the heat transfer inside the tube, and at the same time, fins are arranged between the flat tubes to enhance the disturbance when the air flows, so as to improve the heat transfer on the air side.
  • the coefficient, therefore, the microchannel heat exchanger is a highly efficient heat exchanger. Since the microchannel heat exchanger can replace the ordinary copper tube finned heat exchanger and reduce the cost, and the compact structure, light weight and less refrigerant charge, the microchannel heat exchanger has been increasingly affected by the air conditioner manufacturer. Pay attention to it.
  • the fins of the microchannel heat exchanger are bonded to the flat tube by the aluminum-silicon solder. In the process of bonding the fins to the flat tube, the existing microchannels are affected to prevent the fins from sticking to each other and affecting the flow of air.
  • the fins of the heat exchanger are provided with a sheet-fixing piece at the windward end of the windward plate, and the chip is fixed on the adjacent fins when the microchannel heat exchanger is brazed, so that the fins are Keep a predetermined distance between them.
  • the microchannel heat exchanger since the microchannel heat exchanger is bonded to the flat tube after the fin is bonded, it needs to be bent further, and the uneven force may cause the partial piece to be separated from the corresponding fin during the bending process, thereby causing the wing.
  • the spacing between the windward plates of the sheet varies, which affects the flow of air and thus the heat transfer effect of the microchannel heat exchanger.
  • the main object of the present invention is to provide a heat exchanger fin and a heat exchanger using the heat exchanger fin, aiming at solving the uneven spacing between the windward plates of the heat exchanger fin caused by the bending heat exchanger. technical problem.
  • the present invention provides a heat exchanger fin for connection to a flat tube, the heat exchanger fin comprising a plurality of fin units, each of the fin units including a windward direction in the air flow direction a plate, a leeward plate, and an intermediate plate between the windward plate and the leeward plate, wherein the leeward plates of each of the fin units are sequentially connected in a longitudinal direction.
  • the heat exchanger fins are bent to extend a first sheet pitch boss for defining a spacing between the windward plates of adjacent heat exchanger fins, and the projection of the first sheet from the boss on the plane of the windward board A connecting line that spans the windward and intermediate plates or is located on one side of the connecting line and adjacent to the connecting line.
  • the windward plates of the respective fin units are spaced apart from each other, and a flat tube slot for inserting the flat tubes is disposed between the intermediate plates of two adjacent fin units .
  • the heat exchanger fin is provided at the edge of the flat tube groove with a flange for adhering to the flat tube.
  • the heat exchanger fin is punched out a first window spanning the windward and intermediate plate connecting lines, and the portion punched out of the first window is bent outward to the first piece from the boss.
  • the first sheet distance boss has a support portion perpendicular to the first window and a connecting portion bent from the support portion.
  • the connecting portion is disposed obliquely with respect to a width direction of the fin unit.
  • the leeward plate is provided with a second sheet pitch boss for defining a spacing between the leeps of adjacent heat exchanger fins, the second sheet distance boss and the first sheet distance boss It is bent and extended to the same side of the heat exchanger fin.
  • the leeward plate is provided with at least two first reinforcing ribs having a V-shaped cross section along a width direction of the heat exchanger fin, and the second sheet distance boss is located at the leeward plate. Between at least two first reinforcing ribs.
  • the leeward plate is provided with at least two first reinforcing ribs having a V-shaped cross section along a width direction of the heat exchanger fin, and a plurality of louvers are disposed on the intermediate plate of each of the fin units.
  • the plurality of first reinforcing ribs overlap the projections of the plurality of louver groups in the width direction of the heat exchanger fins.
  • the intermediate plate is provided with at least one second reinforcing rib having a V-shaped cross section along the width of the heat exchanger fin.
  • the intermediate plate of each of the fin units is provided with a plurality of louver groups, and the plurality of louver groups are symmetrically distributed on opposite sides of the at least one second rib.
  • the intermediate plate of each of the fin units is provided with a plurality of louver groups, and the sum of the widths of the plurality of louver groups is 40% to 70% of the width of the intermediate plate.
  • the first louver and the second louver are symmetrically disposed in a front-rear direction from the windward plate to the leeward, the first louver including a plurality of first wind guides
  • the second louver includes a plurality of second air guiding sheets, and the first air guiding sheet of the first louver and the second air guiding sheet of the second louver form together An "eight"-shaped structure having opposite neck sides and an open side.
  • the first piece is bent from the boss to the constricted side of the "eight" shape structure.
  • a distance between a front end of the louver group and a rear end of the windward plate is at least 3 times a window width between two adjacent first wind guide sheets, and a rear end of the louver group The distance from the front end of the leeward is at least 1.5 times the width of the fenestration between two adjacent second wind deflectors.
  • a window width between two adjacent first wind deflectors of the first louver and between two adjacent second wind guides of the second louver is equal.
  • the windward plate is provided with at least one third reinforcing rib along a width direction of the heat exchanger fin, and the third reinforcing rib extends from the windward plate to a front end portion of the intermediate plate.
  • the louver of the fin unit is bent and formed with two guiding grooves for draining, and the two guiding grooves are arranged to extend in parallel along the longitudinal direction of the heat exchanger fin.
  • the intermediate plate is provided with a plurality of heat transfer grooves, each of the heat transfer grooves extending along a longitudinal direction of the heat exchanger fins, and the plurality of heat transfer grooves are at the heat exchanger fins Arranged in the width direction.
  • the present invention further provides a heat exchanger comprising a first header, a second header, and a plurality of parallelly disposed between the first header and the second header A flat tube and the heat exchanger fins described above, the heat exchanger fins being disposed in parallel spaced perpendicular to the flat tube.
  • connection line of the windward and intermediate plates is located or located at the connecting line One side is adjacent to the connecting line, so that when the heat exchanger is brazed, the windward plates of the adjacent heat exchanger fins can be kept at a predetermined distance to prevent the windward plates from sticking together, and the swapping is performed.
  • the force of each first piece is equal to the convexity of the boss, so that the occurrence of the first piece of the distance from the corresponding heat exchanger fins can be reduced, so that the heat exchanger is bent after the bending
  • the spacing between the windward plates of the heater fins is uniform.
  • FIG. 1 is a schematic perspective view of a heat exchanger according to a first embodiment of the present invention
  • Figure 2 is a schematic view showing the structure of a heat exchanger fin of the heat exchanger of Figure 1;
  • FIG. 3 is a cross-sectional structural view of the heat exchanger fin of Figure 2 taken along line A-A;
  • Figure 4 is a cross-sectional structural view of the heat exchanger fin of Figure 2 taken along line B-B;
  • Figure 5 is a schematic view showing the structure of a heat exchanger fin according to a second embodiment of the present invention.
  • a heat exchanger includes a first header 100 , a second header 200 , and a parallel arrangement of the first header 100 and the first A plurality of flat tubes 300 between the two headers 200.
  • the heat exchanger further includes a plurality of heat exchanger fins 400 spaced apart in parallel, each of the fins 400 being disposed perpendicular to the flat tube 300, and each of the heat exchanger fins 400 is provided with a plurality of flat tube slots 401
  • Each of the flat tubes 300 is inserted into each of the plurality of flat tube grooves 401 of each of the heat exchanger fins 400.
  • each of the heat exchanger fins 400 is used for connection with the flat tube 300.
  • the heat exchanger fin 400 has a plurality of fin units 402.
  • Each of the fin units 402 includes a windward plate 410, an intermediate plate 420, and a leeward plate 430 that are sequentially connected in the air flow direction.
  • the leeward plates 430 of the respective fin units 402 are sequentially connected in the longitudinal direction (in the vertical air flow direction).
  • the intermediate plates 420 of the respective fin units 402 are spaced apart such that the flat tube grooves 401 are formed between the intermediate plates 420 of adjacent fin units 402.
  • the windward plates 410 of each of the fin units 402 are also disposed apart from each other such that an inlet groove 403 communicating with the corresponding flat tube groove 401 is formed between the windward plates 410 of the adjacent fin units 402 for guiding
  • the flat tube 300 is inserted into the flat tube groove 401.
  • the heat exchanger fin 400 provided by the present invention punches out the first window 411 at the joint of the windward plate 410 and the intermediate plate 420, and the portion punched out of the first window 411 is bent outward to the first piece from the boss 412.
  • the first piece from the boss 412 has a support portion 413 perpendicular to the first window 411 and a connecting portion 414 bent from the support portion 413.
  • the connecting portion 414 is opposite to the width direction of the fin unit 402 (ie, the air flow direction) Tilting, and the projection of the connecting portion 414 on the plane of the windward plate 410 spans the connecting line of the windward plate 410 and the intermediate plate 420, or is located adjacent to the connecting line of the intermediate plate 420, or is located adjacent to the windward plate 410
  • the connecting line is preferably adjacent to the point where the projection of the connecting portion 414 is close to the connecting line and the distance from the connecting line is not greater than the maximum length projected by the connecting portion 414, the windward plate 410 and the intermediate plate 420
  • the connecting line is a line passing through the apex of the windward side of the flat tube 300 in the longitudinal direction of the heat exchanger fin 400.
  • the flat tube 300 When the heat exchanger is brazed, the flat tube 300 is inserted into the flat tube groove 401 through the inlet groove 403, and the intermediate plate 23 of the fin 10 is bonded to the flat tube 300 to make a heat exchanger fin 400.
  • the first piece of the connecting portion 414 from the boss 412 is bonded to the windward plate 410 and the intermediate plate 420 of the adjacent heat exchanger fin 400, or the region of the windward plate 410 adjacent to the connecting line, or the intermediate plate 420 is adjacent thereto.
  • the area of the connecting line is bonded to the windward plate 410 and the intermediate plate 420 of the adjacent heat exchanger fin 400, or the region of the windward plate 410 adjacent to the connecting line, or the intermediate plate 420 is adjacent thereto.
  • the heat exchanger fins 400 can be maintained at a predetermined distance between the heat exchangers during brazing furnace welding to prevent the windward plates 410 of the adjacent heat exchanger fins 400 from sticking together.
  • the force of each of the first pieces of the bosses 412 is made uniform during the bending process of the heat exchanger, so that the occurrence of the detachment of the first piece of the bosses 412 from the respective heat exchanger fins 400 can be reduced.
  • the spacing between the windward plates 410 of the heat exchanger fins 400 after the heat exchanger is bent is uniform.
  • a second window 431 is punched out on the leeward plate 430, and a portion punched out of the second window 431 is bent in the same direction as a portion punched out of the first window 411, and the second piece is protruded from the boss 432.
  • the second sheet distance boss 432 is used to define the spacing between the leeward plates 430 of the adjacent heat exchanger fins 400, and the heat exchanger can be ensured by the second sheet pitch boss 432 and the first sheet distance boss 412.
  • the fins 400 are evenly spaced in the direction of air flow.
  • An at least two first reinforcing ribs 433 having a V-shaped cross section are disposed on the leeward plate 430 along a width direction of the heat exchanger fin 400, and the second sheet is spaced from the boss on the leeward plate 430. 432 is located between the corresponding two first reinforcing ribs 433.
  • the intermediate plate 420 is provided with at least one second reinforcing rib 421 having a V-shaped cross section along the width direction of the heat exchanger fin 400.
  • the intermediate plate 420 is further provided with a plurality of louver groups 422 for enhancing the disturbance when the air flows and increasing the air side heat transfer coefficient, and the sum of the widths of the plurality of louver groups 420 is 40 of the width of the intermediate plate 420. % ⁇ 70% to achieve better turbulence effect.
  • the plurality of louver groups 422 are symmetrically distributed on opposite sides of the second reinforcing rib 421. In this embodiment, the plurality of louver groups 422 are adjacent to the junction between the intermediate plate 420 and the leeward plate 430.
  • the windward plate 410 is provided with at least one third reinforcing rib 415 having a V-shaped cross section along the width direction of the heat exchanger fin 400, and the third reinforcing rib 415 extends from the windward plate 410 to the middle
  • the front end portion of the plate 420 extends to the front end portion of the intermediate plate 420 because the third reinforcing rib 415 can not only strengthen the strength of the windward plate 410 but also effectively reduce the vibration of the windward plate 410 to reduce the heat exchanger of the present invention. The noise.
  • a third reinforcing rib 415 is disposed on the windward plate 410 along the width direction of the heat exchanger fin 400, and the second reinforcing rib 421 is disposed on the intermediate plate 420 along the width direction of the heat exchanger fin 400. And the first rib 433 is disposed on the leeward plate 430 along the width direction of the heat exchanger fin 400, which can effectively ensure the strength of the heat exchanger fin 400 after processing and prevent the heat exchanger from being broken during assembly.
  • the heat exchanger fins 400 thereby making assembly of the heat exchanger 100 simple and easy, and the third stiffener 415 on the windward plate 410 and the first stiffener 433 on the leeward 430 can also avoid heat exchanger fins
  • the 400 is deformed by gravity pressing when assembled to the flat tube 300, and the heat exchanger fin 400 is prevented from collapsing and bonding together during the high temperature welding process.
  • the leeward plate 410 of the fin unit 402 is bent to protrude two guiding grooves 404 having a V-shaped cross section.
  • the two guiding grooves 404 are longitudinally disposed in parallel, and the two guiding grooves 404 are respectively located
  • the outer sides of the first reinforcing ribs 433 are both ends.
  • the longitudinally disposed guide groove 404 has a flow guiding effect, the condensed water or the defrosted water on the surface of the heat exchanger fin 400 can be quickly removed along the guide groove 404 under the action of gravity, and the drainage performance is good, on the other hand,
  • the longitudinally disposed flow guiding grooves 404 can increase the longitudinal strength of the heat exchanger fins 400, and the heat exchanger fins 400 are less susceptible to deformation during assembly and transportation.
  • Each of the louver groups 422 includes a first louver 423 and a second louver 424, and the first louver 423 and the second louver 424 are in the windward 410 to the leeward Symmetrical setting in the direction of 430.
  • the first louver 423 includes a plurality of first air guiding sheets 425.
  • the second louver 424 includes a plurality of second air guiding sheets 426.
  • the first air guiding piece 425 of the first louver 423 and the second air guiding piece 426 of the second louver 424 together form an "eight" shape structure.
  • the "eight" shaped structure has opposing constricted sides and open sides.
  • Each of the louver groups 422 can be divided into three zones: a windward zone 427, a diverting zone 428, and a leeward zone 429, and the windward zone 427 and the leeward zone 429 are symmetrically disposed relative to the diverting zone 428.
  • the first louver 423 is located in the windward zone 427
  • the second louver 424 is located in the leeward zone 429
  • the diverting zone 428 is between the first louver 423 and the second louver 424.
  • the distance between the front end of the louver group 422 and the rear end of the windward plate 410 is at least 3 times adjacent to the two
  • the window width d between the first air guiding piece 425 or the second air guiding piece 526 can strengthen the structure of the heat exchanger fin 400, and this part is the most frosty due to actual operation. In such a place, the heat transfer effect can be enhanced, the frosting speed under low temperature heating conditions can be alleviated, and the defrosting water can be smoothly flowed during defrosting.
  • the distance between the rear end of the louver group 422 and the front end of the leeward 430 (between the leeward 430 and the leeward region 429 of the louver group 422) Width is at least 1.5 times the window width d between two adjacent first wind deflectors 425 or second wind deflectors 426, considering the processing feasibility and actual heat transfer effect, d is 1 mm Preferred in ⁇ 2mm.
  • a window width between two adjacent first wind deflectors 425 of the first louver 423 and two adjacent ones of the second louver 424 The window widths between the second air guiding sheets 426 are equal.
  • the orientations of the first sheet guiding boss 412 and the second sheet spacing boss 432 are both formed by the first air guiding piece 425 and the second air guiding piece 426.
  • the shrinkage direction of the "eight" shape structure is consistent.
  • the second reinforcing rib 421, the third reinforcing rib 415, and the guiding groove 404 have the same concave direction, and are formed by the first air guiding piece 425 and the second air guiding piece 426.
  • the open side of the "eight" shape structure is consistent.
  • the projections of the plurality of louver groups 422 and the first reinforcing ribs 433 of the leeward 430 in the width direction of the heat exchanger fins 400 are overlapped one by one.
  • the louver group 422 and the first reinforcing rib 433 are overlapped in the width direction of the heat exchanger fin 400, and the first reinforcing rib 433 and the louver group 422 are viewed from the air flow direction, and the first reinforcing rib 433
  • the overlap with the corresponding louver group 422 can effectively ensure the strength of the heat exchanger fin 400 after processing, thereby preventing the heat exchanger fins 400 from being broken during assembly of the heat exchanger, and the assembly of the heat exchanger is simple and easy.
  • the heat exchanger fins 400 are provided at the edge of the flat tube groove 401 with a flange 405 for fitting with the flat tube 300, and the direction of the folded edge 405 is bent and the "eight
  • the converging sides of the font structure are identical, the flat tube 300 is inserted into the flat tube groove 401 in the heat exchanger fin 400, and the flat tube 300 is brazed after being joined to the flange 405, and the flange 405 is enlarged.
  • the contact area with the flat tube groove 401 thereby enhancing the connection strength between the flat tube groove 401 and the flat tube 300.
  • the heat exchanger fin 400 of the heat exchanger of the present invention solves the problem that water accumulation on the surface of the heat exchanger fin 400 is not easily eliminated, improves the overall heat exchange efficiency of the heat exchanger, and the heat exchanger fin 400 The structural strength is high, and the heat exchanger fin 400 and the flat tube 300 are assembled easily. Moreover, since the heat exchanger of the present invention has high heat exchange efficiency and good drainage performance after using the heat exchanger fins 400, it can also be used as a condenser of a heat pump air conditioner, thereby expanding its application range.
  • the heat exchanger fin 500 used in the heat exchanger according to the second embodiment of the present invention is substantially the same as the heat exchanger fin 400 used in the heat exchanger according to the first embodiment of the present invention.
  • the intermediate plate 520 is provided with a plurality of heat transfer grooves 521, each of the heat transfer grooves 521 extending along the longitudinal direction of the heat exchanger fins 500, and the plurality of heat transfer grooves 521 Arranged in the width direction of the heat exchanger fins 500, the first sheet distance bosses 512 are disposed on the width square of the heat exchanger fins 500.
  • the heat transfer groove 521 replaces the louver group 422 and the second rib 421 of the heat exchanger fin 400 in the first embodiment, and can also effectively enhance heat exchange due to the structure of the heat transfer groove 521 compared to the louver group 422. To smooth, this can further delay the frosting speed of the heat exchanger under low temperature and high humidity.

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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

La présente invention concerne une ailette d'échangeur de chaleur comprenant plusieurs unités d'ailettes de refroidissement (402). Chacune des unités d'ailettes de refroidissement (402) comprend une plaque côté au vent (410), une plaque sous le vent (430), et une plaque médiane (420) qui se trouve entre la plaque côté au vent (410) et la plaque sous le vent (430). Sur l'ailette d'échange de chaleur, un premier bossage de pas de lames (412) destiné à limiter un espace entre les plaques côté au vent est incurvé et s'étend à l'extérieur. La projection du premier bossage de pas de lames (412) sur un plan sur lequel se trouve la plaque côté au vent (410) traverse une ligne de connexion de la plaque côté au vent et de la plaque médiane ou se trouve d'un côté de la ligne de connexion et adjacente à la ligne de connexion, de façon à garder une distance prédéfinie entre les ailettes d'échangeur de chaleur afin d'empêcher que les plaques côté au vent ne se lient entre elles lorsque l'échangeur de chaleur est soudé dans un four de brasage, et à appliquer une force uniforme à chaque premier bossage de pas de lames durant le pliage de l'échangeur de chaleur, de façon à atténuer le problème de la séparation du premier bossage de pas de lames de l'ailette d'échangeur de chaleur correspondante, de sorte que des espaces entre les plaques côté au vent de l'ailette d'échangeur de chaleur après le pliage de l'échangeur de chaleur soient uniformes.
PCT/CN2013/090647 2013-10-21 2013-12-27 Ailette d'échangeur de chaleur et échangeur de chaleur utilisant l'ailette d'échangeur de chaleur WO2015058452A1 (fr)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
CN201320650096.7 2013-10-21
CN201320650570.6U CN203550718U (zh) 2013-10-21 2013-10-21 翅片及采用该翅片的换热器
CN201320650570.6 2013-10-21
CN201320650075.5 2013-10-21
CN201320650075.5U CN203550715U (zh) 2013-10-21 2013-10-21 翅片及采用该翅片的换热器
CN201320650096.7U CN203550716U (zh) 2013-10-21 2013-10-21 翅片及采用该翅片的换热器
CN201320650072.1U CN203550713U (zh) 2013-10-21 2013-10-21 翅片及采用该翅片的换热器
CN201320650072.1 2013-10-21

Publications (1)

Publication Number Publication Date
WO2015058452A1 true WO2015058452A1 (fr) 2015-04-30

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107941067A (zh) * 2017-09-30 2018-04-20 博格思众（常州）热交换器有限公司 一种翅片、冷凝器及翅片的制造方法
CN108645243A (zh) * 2018-07-08 2018-10-12 江西新电汽车空调***有限公司 一种热泵空调用的室外平行流换热器
CN109186304A (zh) * 2018-09-30 2019-01-11 珠海格力电器股份有限公司 一种翅片及具有其的热交换器
CN117858480A (zh) * 2024-03-07 2024-04-09 江苏炳凯富汽车零部件制造有限公司 一种数据中心用散热制冷设备

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