WO2018099086A1 - Tube d'échange de chaleur et échangeur de chaleur comprenant celui-ci - Google Patents

Tube d'échange de chaleur et échangeur de chaleur comprenant celui-ci Download PDF

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Publication number
WO2018099086A1
WO2018099086A1 PCT/CN2017/092168 CN2017092168W WO2018099086A1 WO 2018099086 A1 WO2018099086 A1 WO 2018099086A1 CN 2017092168 W CN2017092168 W CN 2017092168W WO 2018099086 A1 WO2018099086 A1 WO 2018099086A1
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WO
WIPO (PCT)
Prior art keywords
heat exchange
outer wing
wing
exchange tube
tube according
Prior art date
Application number
PCT/CN2017/092168
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English (en)
Chinese (zh)
Inventor
颜家桃
王晨光
谢镇洲
蔺维君
何国栋
谢蓉
韩中
Original Assignee
珠海格力电器股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Publication of WO2018099086A1 publication Critical patent/WO2018099086A1/fr

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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
    • F28F1/124—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 being formed of pins

Definitions

  • the invention relates to the technical field of heat exchange, in particular to a heat exchange tube.
  • the invention also relates to a heat exchanger having the heat exchange tubes.
  • Heat exchange is involved in many industrial productions and in daily life, such as condensers for air conditioning.
  • the performance of the condenser depends largely on the heat transfer performance of the heat exchange tubes.
  • the working process of the heat exchange tube is a condensation heat exchange process, which specifically includes: flowing a low temperature fluid inside the tube, flowing a refrigerant gas outside the tube, contacting the refrigerant gas with the tube wall, and performing a phase change after heat exchange with the low temperature fluid in the tube. Condensation into a liquid, the refrigerant liquid flows along the outer wall of the tube to form a liquid film; and the subsequent refrigerant gas must be exchanged through the liquid film. The thicker the liquid film, the larger the thermal resistance and the worse the heat exchange performance.
  • heat transfer performance is generally improved by increasing the heat exchange area or thinning the thickness of the liquid film.
  • some prior art designs reduce the thickness of the liquid film by designing pyramidal fins on the outer surface of the tube, especially when the heat exchange tube is used vertically, and improve the heat transfer coefficient; some prior art techniques By adding a number of drainage fins on the outer fins, the heat exchange area is increased, the liquid film thickness is reduced, and the heat exchange effect is improved.
  • the heat exchange tube needs to be straightened, and the straightening process easily causes damage to the outer wing, which is not conducive to effectively pierce the liquid film by the tip of the wing.
  • the straightening process easily causes damage to the outer wing, which is not conducive to effectively pierce the liquid film by the tip of the wing.
  • the main object of the present invention is to provide a heat exchange tube which can effectively overcome the problem of a decrease in heat exchange performance caused by damage of the outer wing during production and installation.
  • a condensation heat exchange tube comprising a tube body, and a plurality of pointed corners on an outer wall surface of the tube body
  • An outer wing the outer wing including a first outer wing and a second outer wing, the first outer wing having a height greater than a height of the second outer wing, and at least a portion of the first outer wing At least a portion of the number of the second outer wings are staggered.
  • the first outer wing and the second outer wing are alternately arranged in the axial and/or circumferential direction of the tubular body.
  • the adjacent first outer wing and the second outer wing constitute one outer wing unit, and the interval between adjacent outer wing units is greater than between the first outer wing and the second outer wing in the same outer wing unit Interval.
  • the first outer wing and the second outer wing are disposed on a common outer wing root.
  • At least one of the first side surface of the first outer wing and the first side surface of the second outer wing is a curved surface, wherein the first side of the first outer wing faces the second outer wing The first side of the second outer wing faces the first outer wing.
  • At least a portion of the outer fin unit is gradually contracted in the height direction, wherein the height direction is a direction from the outer wall surface of the tube to the tip end of the outer fin unit.
  • a first groove is formed between the first outer wing and the second outer wing, and a height difference from a bottom of the first groove to a top end of the second outer wing is 0.2-0.5 mm.
  • the outer fin unit has a total width of 0.2 to 0.6 mm and a total height of 0.5 to 1.5 mm;
  • the distance between two adjacent outer fin units is 0.2 to 0.5 mm;
  • the distance between adjacent two outer fin units is 0.3 to 0.8 mm.
  • the first outer fin and the second outer fin are juxtaposed in the circumferential direction of the tubular body.
  • the first outer fin and the second outer fin have the same root size in the circumferential direction of the tubular body.
  • a second groove is formed between the adjacent two outer fin units, and the groove bottom of the second groove is curved.
  • a drainage channel is formed between adjacent outer fin units.
  • the height difference between the first outer wing and the second outer wing is 0.05 to 0.5 mm.
  • the top end of the first outer wing and/or the second outer wing has a sharp edge extending in the axial direction of the tubular body.
  • Another object of the present invention is to provide a heat exchanger comprising the heat exchange tubes previously described.
  • the outer wall of the tube of the heat exchange tube of the present invention is provided with different height outer fins, so that when the outer wing is damaged during straightening and/or installation, it is ensured that only a part of the outer outer wing is damaged, and the outer part is short.
  • the wings can be protected from damage, so that the liquid film can be effectively pierced to ensure heat exchange efficiency.
  • a drainage channel between the outer fins it is also possible to effectively reduce the thickness of the liquid film and further improve the heat exchange performance.
  • FIG. 1 is a schematic cross-sectional view of a heat exchange tube in accordance with a preferred embodiment of the present invention
  • FIG. 2 is a schematic end view of a heat exchange tube in accordance with a preferred embodiment of the present invention.
  • FIG. 3 is a partial perspective view of a heat exchange tube in accordance with a preferred embodiment of the present invention.
  • Figure 4 is a partial enlarged view of the area A in Figure 3.
  • the first aspect of the present invention provides a heat exchange tube, preferably a condensing heat exchange tube.
  • the condensing heat exchange tube will be exemplified below.
  • the heat exchange tube of the present invention comprises a tubular body 1, and a plurality of outer corners having sharp corners are provided on the outer wall surface of the tubular body 1, and the outer wing includes a first outer wing. 11 and the second outer wing 12, the height of the first outer wing 11 is greater than the height of the second outer wing 12, and at least a portion of the first outer wing 11 and the second outer wing 12 At least a portion of the arrangement is staggered.
  • the outer wall surface of the heat exchange tube of the present invention is provided with at least two outer fins of different heights, and at least a part of the outer fins of different heights are alternately arranged on the outer wall surface, so that the shorter outer wings can be made (ie, the second outer wing 12) is hidden between the upper outer fins (ie, the first outer fins 11), such that even due to the straightening process in the production process or the friction between the support plate and the support plate during the installation process.
  • causes damage to some of the outer wings and also ensures that only the outer wings are injured, but shorter
  • the outer wing can still ensure that its sharp corners are complete, so that the liquid film and/or air bubbles can be pierced smoothly during the working process, and the heat exchange efficiency is improved.
  • first outer wing 11 and the second outer wing 12 are alternately arranged in the axial and/or circumferential direction of the tubular body 1. That is, these outer wings can be alternately arranged in accordance with the regularity of one first outer wing 11, one second outer wing 12, one first outer wing 11, ... so that the shorter outer wing can be better protected.
  • the adjacent first outer wing 11 and the second outer wing 12 constitute one outer wing unit, and the interval between adjacent outer wing units is larger than the first outer wing 11 and the second outer one of the same outer wing unit.
  • a higher outer wing and a shorter outer wing may be combined (two or more) to form an outer wing unit, and preferably a liquid is formed between adjacent outer fin units.
  • the flow path ensures better protection of the shorter outer wings and enhances the drainage efficiency, thereby reducing the liquid film thickness.
  • the first outer wing 11 and the second outer wing 12 are disposed on a common outer wing root.
  • the roots of each outer wing are integrally connected, and the integrated root extends a certain height from the outer wall surface of the tube, and then Bifurcation into a first outer wing and a second outer wing.
  • the outer wing root has a large size, the overall strength of the outer wing unit can be ensured, and it is not easy to be broken from the root, and the bifurcation of each outer wing can be ensured after bifurcation into two (or more) outer wings. Sharpness to facilitate puncture of the liquid film.
  • At least one of the first side surface of the first outer wing 11 and the first side surface of the second outer wing 12 is a curved surface, wherein the first side surface is defined in the following manner: the first outer wing
  • the first side of the first outer wing 12 faces the second outer wing 12, and the first side of the second outer wing 12 faces the first outer wing 11.
  • the first side surface of the first outer wing 11 is a convex curved surface
  • the first side surface of the second outer wing 12 is a concave curved surface.
  • This arrangement is sufficient to ensure the first shape in addition to being easily formed.
  • the strength of the outer wing 11 is such that it is not easily damaged, and the sharpness of the angle between the two outer wings can be made similar.
  • the outer fin units are gradually contracted in the height direction, wherein the height direction is a direction from the outer wall surface of the tube body 1 to the tip end of the outer fin unit.
  • the gradually shrinking structure can also strongly guarantee the strength of the outer wing unit and the sharp angle of each outer wing.
  • the sharpness of the part may not be limited to a certain direction, for example, the two side walls of the outer fin unit in the axial (and/or circumferential) direction of the tubular body may be inclined to each other to assume a gradually contracted configuration.
  • the taper angle ⁇ is determined according to the above principle, and the strength of the outer wing unit and the sharpness of the outer wing can be ensured.
  • a first groove 14 is formed between the first outer wing 11 and the second outer wing 12, and the bottom of the first groove 14 is to the bottom
  • the height difference of the tips of the second outer wings 12 is 0.2 to 0.5 mm, for example, 0.3 mm.
  • the first groove 14 also functions as a drain flow path.
  • the outer fin unit has a total width of 0.2 to 0.6 mm, for example 0.4 mm, and a total height of 0.5 to 1.5 mm, for example 1.0 mm.
  • the total width of the outer fin unit refers to the dimension of the root portion of the outer fin unit in the circumferential direction of the tube body.
  • the first outer fin 11 and the second outer fin 12 are juxtaposed in the circumferential direction of the tubular body 1. And preferably, in the same outer fin unit, the first outer fin 11 and the second outer fin 12 have the same root dimension (i.e., root width dimension) in the circumferential direction of the tubular body 1.
  • a second groove 15 (which is a part of the drainage channel) is formed between the adjacent two outer fin units, and the groove of the second groove 15
  • the bottom is curved, such as a circular arc.
  • the curved groove bottom can reduce the stress concentration between the outer fin unit and the outer wall surface of the tube, thereby ensuring the strength of the outer fin unit.
  • the height difference between the first outer wing 11 and the second outer wing 12 is 0.05 to 0.5 mm.
  • the height of the second outer wing 12 may be 0.8 mm.
  • the tips of the first outer fins 11 and/or the second outer fins 12 have sharp edges extending in the axial direction of the tubular body 1. That is, in the present invention, each outer wing The sharp corner portion is provided with a sharp edge having a certain length, so that the strength of the sharp corner portion is effectively ensured while maintaining the sharpness, so that the probability of damage during the straightening process and during the installation is lowered. In particular, the sharply extending sharp edges also better maintain strength and shape during the mounting of the support plate.
  • internal teeth 13 extending in a spiral shape are further provided on the inner wall surface of the tubular body 1.
  • the main function of the internal teeth 13 is to block and agitate the cryogenic fluid flowing inside the tubular body, thereby improving the efficiency of heat exchange.
  • the number of the internal teeth is 50-80.
  • the ends of the tube body of the condensing heat exchange tube of the present invention are, for example, light segments, so that when the heat exchange tubes pass through the tube sheets on both sides of the condenser, they can be tightly fixed with the tube sheets, and the length of the light segments is preferably not greater than the thickness of the tube sheets. .
  • the contact portion of the heat exchange tube and the support plate may be formed into a light segment or a structure with an outer wing. Since the condensing heat transfer tube of the present invention has the preferred structure as described above, it can still ensure better heat exchange performance after the support plate is mounted.
  • the outer wall of the tube of the heat exchange tube of the present invention is provided with different height outer fins, so that when the outer wing is damaged during straightening and/or installation, it is ensured that only a part of the outer outer wing is damaged, and The short outer wing can be protected from damage, which can effectively puncture the liquid film and ensure heat exchange efficiency.
  • a drainage channel between the outer fins it is also possible to effectively reduce the thickness of the liquid film and further improve the heat exchange performance.
  • another aspect of the present invention provides a heat exchanger, preferably a condenser, comprising the heat exchange tubes previously described herein. Since the heat exchange performance of the heat exchange tube of the present invention is remarkably improved, the performance of the heat exchanger of the present invention is also remarkably improved.

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

Abstract

La présente invention concerne un tube d'échange de chaleur et un échangeur de chaleur comprenant celui-ci. Le tube d'échange de chaleur comprend un corps de tube (1). Une surface de paroi externe du corps de tube (1) est pourvue d'une pluralité d'ailettes externes ayant des coins aigus. Les ailettes externes comprennent une première ailette externe (11) et une seconde ailette externe (12). La hauteur de la première ailette externe (11) est supérieure à la hauteur de la seconde ailette externe (12). Au moins certaines des premières ailettes externes (11) et au moins certaines des secondes ailettes externes (12) sont disposées en alternance. La surface de paroi externe du corps de tube du tube d'échange de chaleur est pourvue d'ailettes externes ayant différentes hauteurs, de telle sorte que si des ailettes externes sont endommagées pendant l'alignement et/ou l'installation, il peut être garanti que seules certaines des ailettes externes supérieures sont endommagées, et que les ailettes externes inférieures sont protégées. Par conséquent, un film liquide est efficacement percé, et l'efficacité d'échange de chaleur est garantie.
PCT/CN2017/092168 2016-12-02 2017-07-07 Tube d'échange de chaleur et échangeur de chaleur comprenant celui-ci WO2018099086A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201611100601.5 2016-12-02
CN201611100601.5A CN106767095A (zh) 2016-12-02 2016-12-02 一种换热管及具有其的换热器

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WO2018099086A1 true WO2018099086A1 (fr) 2018-06-07

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WO (1) WO2018099086A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4086560A1 (fr) * 2021-05-05 2022-11-09 Diehl Metall Stiftung & Co. KG Dissipateur thermique destiné à la fabrication d'un refroidisseur rond

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106767095A (zh) * 2016-12-02 2017-05-31 珠海格力电器股份有限公司 一种换热管及具有其的换热器
CN107560479A (zh) * 2017-09-04 2018-01-09 珠海格力电器股份有限公司 一种换热管及具有其的换热器
CN110425778A (zh) * 2019-07-26 2019-11-08 江苏萃隆精密铜管股份有限公司 一种高低翅强化冷凝换热管

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CN101813433A (zh) * 2010-03-18 2010-08-25 金龙精密铜管集团股份有限公司 冷凝用强化传热管
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CN106767095A (zh) * 2016-12-02 2017-05-31 珠海格力电器股份有限公司 一种换热管及具有其的换热器
CN206247931U (zh) * 2016-12-02 2017-06-13 珠海格力电器股份有限公司 一种换热管及具有其的换热器

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Publication number Priority date Publication date Assignee Title
JP2004301446A (ja) * 2003-03-31 2004-10-28 Kobe Steel Ltd 凝縮器用伝熱管
CN101813433A (zh) * 2010-03-18 2010-08-25 金龙精密铜管集团股份有限公司 冷凝用强化传热管
CN201787852U (zh) * 2010-08-11 2011-04-06 烟台恒辉铜业有限公司 一种y型翅片换热管
CN204830966U (zh) * 2015-08-26 2015-12-02 航天海鹰(哈尔滨)钛业有限公司 一种火力发电凝汽器用高效冷凝管
CN204854446U (zh) * 2015-08-26 2015-12-09 航天海鹰(哈尔滨)钛业有限公司 一种凝汽器用钛合金m翅型冷凝管
CN106767095A (zh) * 2016-12-02 2017-05-31 珠海格力电器股份有限公司 一种换热管及具有其的换热器
CN206247931U (zh) * 2016-12-02 2017-06-13 珠海格力电器股份有限公司 一种换热管及具有其的换热器

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4086560A1 (fr) * 2021-05-05 2022-11-09 Diehl Metall Stiftung & Co. KG Dissipateur thermique destiné à la fabrication d'un refroidisseur rond

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