EP2379977B1 - Échangeur de chaleur comprenant des tubes a ailettes rainurées - Google Patents

Échangeur de chaleur comprenant des tubes a ailettes rainurées Download PDF

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Publication number
EP2379977B1
EP2379977B1 EP09716192A EP09716192A EP2379977B1 EP 2379977 B1 EP2379977 B1 EP 2379977B1 EP 09716192 A EP09716192 A EP 09716192A EP 09716192 A EP09716192 A EP 09716192A EP 2379977 B1 EP2379977 B1 EP 2379977B1
Authority
EP
European Patent Office
Prior art keywords
fin
tube
tubes
grooves
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP09716192A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2379977A1 (fr
Inventor
Herveline Robidou
Jérôme GOUMONDIE
Rémy TINTILLIER
François CLUNET
Serge Chacun
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kelvion Thermal Solutions SAS
Original Assignee
GEA Batignolles Technologies Thermiques
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 GEA Batignolles Technologies Thermiques filed Critical GEA Batignolles Technologies Thermiques
Priority to PL09716192T priority Critical patent/PL2379977T3/pl
Publication of EP2379977A1 publication Critical patent/EP2379977A1/fr
Application granted granted Critical
Publication of EP2379977B1 publication Critical patent/EP2379977B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • 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
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • the invention relates to a tube heat exchanger comprising finned tubes, in which the tubes extend in a certain axial direction and are provided with heat exchange fins, each fin having a heat exchange surface. surrounding a tube which extends in a certain radial direction relative to the tube and which is structured in relief to form grooves spaced relative to each other in the radial direction.
  • a tube heat exchanger is known from the document US 2008/0023180 A1 , see in particular the Figures 5 and 6 .
  • Such an exchanger corresponds to the preamble of claim 1.
  • the invention applies more particularly to a tube heat exchanger using air as a secondary exchange fluid such as aero-refrigerant, aero-condenser, aero-heater or aero-evaporator type equipment, used respectively for cooling, condensing, reheating and evaporation of a fluid, in particular in refining processes, gas treatment and compression plants, gas liquefaction units, coal synthesis units and gas, power generation facilities, regasification units, or any other fluid treatment facility.
  • a secondary exchange fluid such as aero-refrigerant, aero-condenser, aero-heater or aero-evaporator type equipment, used respectively for cooling, condensing, reheating and evaporation of a fluid, in particular in refining processes, gas treatment and compression plants, gas liquefaction units, coal synthesis units and gas, power generation facilities, regasification units, or any other fluid treatment facility.
  • such equipment comprises a main heat exchanger equipped with a bundle of external finned tubes in which circulates the fluid to be cooled, condensed, heated or evaporated, as well as distribution and distribution manifolds. fluid between the tubes.
  • the fluid is cooled in the outer finned tubes by heat exchange with a second fluid circulating around the external tubes and fins, including ambient air.
  • a circulation or forced ventilation of ambient air is provided by fans positioned either below (what is called a forced draft) or above (so-called induced draft) tubes exchanger .
  • the ambient air is pulsed through the finned tube bundle at a relatively low frontal speed of between 1.5 and 4 meters per second (m / s).
  • the flow regime of the ambient air is generally laminar with some local turbulence.
  • the areas of the heat exchanger where heat exchange is most important are the leading edges of the fins and tubes in the direction of the flow of air.
  • Patent document is known US-2008023180 a fin for aero-refrigerant tube which has on the surface a relief with cavities or grooves formed by mechanical deformation of the fins. Such cavities or grooves make it possible to increase the heat exchange between the air and the fin thanks to creating turbulence while increasing pressure losses.
  • concentric grooves 42 of semi-cylindrical section are formed on each fin.
  • Patent document is also known WO 2007/147754 a fin for a heat exchanger tube equipped with airflow deflectors in the form of projecting surfaces which modify the structure of the air flow in order to improve heat exchanges between the air and the fin .
  • These surfaces are in the form of rectangular or triangular cutouts in the fin.
  • the heat exchangers being mostly outside and the ambient air not being filtered, the cuts made in the fin can be sources of fouling due to dust, insects, etc ... that come to obstruct the cuts.
  • the object of the invention is to provide a grooved fin structure for a heat exchanger tube which makes it possible to obtain an increase in the heat exchange between the air and the fluid circulating in the tube, without deteriorating the loss of heat. charge.
  • the subject of the invention is a tube heat exchanger comprising finned tubes, in which the tubes extend in a certain axial direction and are provided with heat exchange fins, each fin having a heat exchange surface surrounding a tube which extends in a certain radial direction relative to the tube and which is structured in relief to form grooves spaced from each other in the radial direction, and wherein the grooves of a fin have dimensions different that decrease as one moves away from the tube in the radial direction so as to provide a guide for a fluid around the tube.
  • the main advantage of such a staggered conformation of the relief of the fins is that it makes it possible to better guide the flow of air at the rear of the tubes in the radial direction of the tubes (according to the direction of the flow which arrives on the tubes ).
  • tubes with external fins according to the invention it is thus possible to greatly reduce an air recirculation zone at the rear of the tubes in the direction of the flow of air, which is normally important when uses flat-profiled (flat-profile) finned tubes.
  • the stepped relief surface guiding the air at the rear of the tubes reduces the areas of recirculation where the heat exchange is bad and therefore to take better advantage of the surface of the fins. In this way with a fin according to the invention, the gain obtained in terms of thermal performance can be very important.
  • the grooves of a fin may have different depths and widths which decrease as one moves away from the tube in said radial direction.
  • Each fin may have a thickness which decreases as one moves away from the tube in said radial direction.
  • the grooves of a fin may be spaced from each other in a concentric shape pattern or in an elliptical shape pattern.
  • the grooves of a fin may be very close to one another, that is to say joined.
  • the grooves may be disposed on both sides of the fin.
  • Each fin can be rolled up helically around the tube or where the fins may be in the form of disc.
  • a heat exchanger 1 comprising a tube bundle 2 with finned circular section disposed in several substantially parallel superimposed rows extending in an axial direction A in which circulates a fluid to be cooled between an inlet B and an outlet C fluid, and around which circulates a flow of pulsed ambient air from the bottom upwards in the direction indicated by the arrows D, transversely to the tubes 2, by fans 3 positioned above the heat exchanger 1.
  • the flow of fluid is here divided into three passage sections or passes 2a, 2b, 2c successive schematically represented on the figure 1 to improve the cooling of the fluid.
  • a heat exchanger 1 thus generally comprises between three and eight rows of superposed tubes 2 arranged staggered or aligned with respect to the fluid flow direction in the tubes 2 as indicated by the arrows F.
  • the tubes 2 are provided with outer radial annular fins 4 substantially perpendicular to the tube 2 and substantially parallel to each other, favoring the heat exchange between the ambient air and the fluid, as well as guiding the flow of air towards the rear of the tubes. tubes 2 in the axial direction, as this will be described below.
  • the outer fins 4 make it possible to increase the external heat exchange area by a factor of between 15 and 25 with respect to the surface of a similar tube 2 without fins. Such a surface increase makes it possible to increase the heat exchange, but also generates losses which are in particular compensated by the use of efficient fans.
  • fins 4 are preferably arranged all along all the tubes 2 of the exchanger 1.
  • shape and size of the outer fins 4 may vary from one tube to another of the bundle of tubes 2.
  • the configurations of tubes 2 outer fins 4 are not necessarily homogeneous within a bundle of tubes 2, in particular the diameters of the tubes 2 may vary.
  • a fin 4 according to the invention with a radial surface structured in relief 5 to form grooves 5a, 5b, 5c spaced from each other in a certain radial direction E by a fin portion 8 substantially flat annular.
  • the grooves 5a, 5b, 5c of the fin 4 have different dimensions which decrease as one moves away from the tube 2 in such a way as to guide the flow of ambient air around the tube 2 in the axial direction A. More precisely, the grooves 5a, 5b, 5c of a fin 4 have respective respective depths p1, p2, p3 in the axial direction A and respective widths 11, 12, 13 in the radial direction E, respectively.
  • the innermost groove 5a is the uppermost and widest of the grooves
  • the outermost groove 5c is the lowest and the smallest
  • the middle groove 5b is of intermediate height and width.
  • the number of grooves 5a, 5b, 5c on a fin 4 is between two and four, but other grooves may be added depending on the application.
  • the raised surface 5 consists of three circular grooves 5a, 5b, 5c arranged in a concentric pattern and centered around the tube 2.
  • Adjacent fins 4 may have concentric grooves 5a, 5b, 5c which are respectively in alignment axial (the fins 4 have the same raised surface 5 and thus a groove 5a, 5b, 5c of a fin 4 is in axial alignment with the corresponding groove of the other fins 4 on the tube 2).
  • the concentric adjacent grooves 5a, 5b, 5c of a fin 4 are separated (disjoint) radially from each other by annular planar flat portions 8.
  • These annular portions 8 may have in the radial direction E the same width d1, d2 or different widths d1, d2 according to a variable diagram, d1, d2 being for example between 1 and 5 mm.
  • the portion widths decreases going from the tube 2 to the outer peripheral edge 4A or vice versa. It is also possible to provide adjacent grooves which are contiguous and in this case the width of the separation portions 8 is very small (less than 1 mm).
  • a tube 2 has fins 4 of the same configuration over its entire length.
  • tubes 2 with different configurations of fins 4.
  • the grooves 5a, 5b, 5c are formed on the same face 4c of the fin 4, that is to say oriented in the same direction relative to the fin 4.
  • the figure 4 shows another embodiment of a fin 4 according to the invention in which grooves 5d, 5e, 5f are oriented on either side of the fin 4, that is to say they are arranged alternately on two faces 4c, 4d of the blade 4 opposite, which can confer a better mechanical strength with respect to the grooves 5a, 5b, 5c.
  • FIG. 5 another embodiment of a fin 4 according to the invention in which the concentric grooves 5a, 5b, 5c have been replaced by grooves 6a, 6b, 6c arranged according to an elliptical shape diagram 4.
  • Such grooves 6a, 6b 6c elliptical make it possible to take advantage of the phenomenon of guiding the air through the grooves while limiting the increase in the associated pressure drop.
  • the advantage of this solution is an increase in performance gain for similar conditions of use, ie iso speed and even pressure drop.
  • the outer fins 4 can be made from an aluminum strip 7, or even another heat-conducting material, helically wound in the axial direction A around each tube 2, as shown schematically in FIG. figure 6 .
  • the fins 4 are here very slightly inclined relative to the tube 2 and the direction A, as indicated by the arrow 4e, this inclination being small because the fins 4 are very close to each other, so that we can consider that the fins 4 are almost perpendicular to the tube 2. It is also possible to make a tube 2 with fins 4 more inclined relative to the axial direction A of the tube 2.
  • Another embodiment of an outer fin 4 is formed by means of a series of rotating disks.
  • the attachment between the fin 4 and the tube 2 may be made by embedding the fin 4, for example in a groove previously made on the periphery of the tube 2 (not shown), or by winding the fin 4 to the base of which a folding is achieved and crimping on the tube 2 for example knurled.
  • the fin 4 can also be obtained by forming or deformation of an aluminum tube attached to the tube 2.
  • the fin 4 can also be made using stacked disks.
  • the fin 4 has a thickness which decreases as one moves away from the tube from the inner edge 4b the fin 4 towards its outer edge 4a.
  • the thickness e1 of the fin 4 at its outer edge 4a may be between about 0.15 and 0.4 millimeters (mm) and the thickness e2 of the fin 4 at its inner edge 4b can be between about 0.4 and 1 mm.
  • the grooves 5a, 5b, 5c have respective depths p1, p2, p3 of between approximately 0.4 and 1.5 mm, as well as respective widths 11, 12, 13 at the base of the groove of between approximately 1 and 4. mm, the grooves 5a, 5b, 5c having different heights and widths so as to obtain the stepped relief decreasing away from the tube 2 such that p1> p2> p3 and 11> 12> 13.
  • the fin 4 according to the invention has a length H of between approximately 10 and 20 mm and preferably between approximately 12 and 18 mm.
  • the pitch P between two consecutive fins along the tube 2 is between about 2.2 and 3.5 mm and preferably between about 2.5 and 3.2 mm, or generally less than the conventional spacing between two blades profiled consecutive dish.
  • a heat exchanger 1 comprises a bundle of tubes 2 resting on a steel structure (not shown) and formed of about 50 to 300 tubes 2 of diameter between about 15 millimeters and 55 millimeters, the width of the exchanger heat 1 being between 0.3 meters and 5 meters, and its length between 8 meters and 18 meters.
  • the tubes 2 may be composed of steel, for example stainless steel or carbon steel or a high-alloy steel, such as incoloy, the choice of the material of the tubes 2 being a function of the transported fluid which may be aggressive. , and operating conditions.
  • the outer fins 4 are generally made of aluminum, but may also be stainless steel, or any other heat conducting material.
  • the Figures 7 and 8 present current lines (obtained by numerical simulation) of the ambient air flowing in the direction D around several tubes 2 of the heat exchanger 1 in a plane M substantially perpendicular to the tubes 2 and located centrally between two fins 4 consecutive as indicated on the figure 1 and on the figure 3 . More specifically, the figure 7 presents the case of a flat-profile fin and the figure 8 presents the case of a fin 4 according to the invention having concentric grooves 5a, 5b, 5c. As can be seen on the figure 7 , a fluid recirculation zone Z1 is located at the rear of the tubes 2 in the direction of the flow D of the air in which the heat exchange is bad.
  • the pressure drop is represented as a function of the frontal air speed on the tubes 2 for flat-profile tubes 2 (curve 9A) and for tubes 2 with fins 4 according to the invention with grooves 5a , 5b, 5c concentric (curve 9B).
  • curve 9A flat-profile tubes 2
  • curve 9B tubes 2 with fins 4 according to the invention with grooves 5a , 5b, 5c concentric
  • This increase in the pressure drop can be compensated by spacing the fins 4 each other along the tube 2.
  • the pitch P between two consecutive fins is different according to whether the surface of the fins is raised or not: 2.54 mm in the case of the flat profile vane and 3 mm for the fin 4 according to the invention with grooves 5a, 5b, 5c concentric. In this way, as can be seen on the figure 9 the increase in pressure drop caused by the raised surface 5 remains very low.
  • the spacing of the fins 4 along the tube 2 reduces the amount of material used to make the fins, which compensates for the increase in material caused by the realization of the raised surface 5 on the fin 4 by modifying the surface of the fin, and decreases the amount of material used to achieve a saving of the order of 3 to 6% per meter.

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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)
EP09716192A 2008-12-19 2009-05-05 Échangeur de chaleur comprenant des tubes a ailettes rainurées Active EP2379977B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL09716192T PL2379977T3 (pl) 2008-12-19 2009-05-05 Wymiennik ciepła zawierający rury żebrowe rowkowane

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0858864A FR2940422B1 (fr) 2008-12-19 2008-12-19 Echangeur de chaleur comprenant des tubes a ailettes rainurees
PCT/FR2009/050832 WO2010070216A1 (fr) 2008-12-19 2009-05-05 Échangeur de chaleur comprenant des tubes a ailettes rainurées

Publications (2)

Publication Number Publication Date
EP2379977A1 EP2379977A1 (fr) 2011-10-26
EP2379977B1 true EP2379977B1 (fr) 2012-10-17

Family

ID=40627684

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09716192A Active EP2379977B1 (fr) 2008-12-19 2009-05-05 Échangeur de chaleur comprenant des tubes a ailettes rainurées

Country Status (12)

Country Link
US (1) US8376033B2 (es)
EP (1) EP2379977B1 (es)
KR (1) KR101177726B1 (es)
CN (1) CN101861506B (es)
BR (1) BRPI0906068B1 (es)
CA (1) CA2747353C (es)
ES (1) ES2399504T3 (es)
FR (1) FR2940422B1 (es)
HK (1) HK1149073A1 (es)
PL (1) PL2379977T3 (es)
RU (1) RU2494330C2 (es)
WO (1) WO2010070216A1 (es)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015188812A1 (de) 2014-06-11 2015-12-17 GEA Luftkühler GmbH Wärmetauscher

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CN102322761A (zh) * 2011-09-19 2012-01-18 无锡市冠云换热器有限公司 一种具有球形凹凸的锯齿波状翅片
CN102322765A (zh) * 2011-09-19 2012-01-18 无锡市冠云换热器有限公司 一种具有球形凹凸的矩形波状翅片
US9938935B2 (en) 2012-07-12 2018-04-10 General Electric Company Exhaust gas recirculation system and method
US10508621B2 (en) 2012-07-12 2019-12-17 Ge Global Sourcing Llc Exhaust gas recirculation system and method
US9360258B2 (en) 2013-03-15 2016-06-07 Ormat Technologies, Inc. Fin configuration for air cooled heat exchanger tubes
EP2784426A1 (en) 2013-03-27 2014-10-01 GEA Batignolles Technologies Thermiques Tube heat exchanger with optimized thermo-hydraulic characteristics
KR101321708B1 (ko) * 2013-09-12 2013-10-28 주식회사 두발 열교환기
CN103884220B (zh) * 2014-04-15 2016-03-23 重庆大学 适用于结霜工况下的翅片管式制冷换热器用椭圆穿孔翅片
NO20141176A1 (no) 2014-09-30 2016-03-31 Global Lng Services As Fremgangsmåte og anlegg for fremstilling av LNG
CA2930827A1 (en) 2016-05-25 2017-11-25 Nova Chemicals Corporation Furnace coil modified fins
US20180372413A1 (en) 2017-06-22 2018-12-27 Rheem Manufacturing Company Heat Exchanger Tubes And Tube Assembly Configurations
GB2575015B (en) * 2018-05-23 2023-02-22 Veragon Srl Atmospheric water generator using a finned heat exchanger
RU188272U1 (ru) * 2018-11-14 2019-04-04 Наиль Закуанович Галиванов Теплообменная труба с профилированными рёбрами
WO2023053319A1 (ja) * 2021-09-30 2023-04-06 三菱電機株式会社 熱交換器および冷凍サイクル装置
KR102599087B1 (ko) 2021-12-08 2023-11-07 전주대학교 산학협력단 난류발생을 이용한 핀튜브 열교환기

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015188812A1 (de) 2014-06-11 2015-12-17 GEA Luftkühler GmbH Wärmetauscher
DE102014108209A1 (de) 2014-06-11 2015-12-17 GEA Luftkühler GmbH Wärmetauscher

Also Published As

Publication number Publication date
FR2940422A1 (fr) 2010-06-25
KR20100103777A (ko) 2010-09-28
WO2010070216A1 (fr) 2010-06-24
RU2494330C2 (ru) 2013-09-27
CA2747353A1 (fr) 2010-06-24
EP2379977A1 (fr) 2011-10-26
CA2747353C (fr) 2015-08-11
RU2011129831A (ru) 2013-01-27
CN101861506A (zh) 2010-10-13
CN101861506B (zh) 2012-01-11
ES2399504T3 (es) 2013-04-01
BRPI0906068B1 (pt) 2019-12-03
KR101177726B1 (ko) 2012-08-28
HK1149073A1 (en) 2011-09-23
FR2940422B1 (fr) 2010-12-03
BRPI0906068A2 (pt) 2015-06-30
US8376033B2 (en) 2013-02-19
PL2379977T3 (pl) 2013-03-29
US20100155041A1 (en) 2010-06-24

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