EP2784426A1 - Échangeur de chaleur de tube à caractéristiques thermo-hydrauliques optimisées - Google Patents

Échangeur de chaleur de tube à caractéristiques thermo-hydrauliques optimisées Download PDF

Info

Publication number
EP2784426A1
EP2784426A1 EP13161435.6A EP13161435A EP2784426A1 EP 2784426 A1 EP2784426 A1 EP 2784426A1 EP 13161435 A EP13161435 A EP 13161435A EP 2784426 A1 EP2784426 A1 EP 2784426A1
Authority
EP
European Patent Office
Prior art keywords
tube
dimples
heat exchanger
groove
rib
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.)
Withdrawn
Application number
EP13161435.6A
Other languages
German (de)
English (en)
Inventor
Jean El Hajal
Karine Brand
Xavier Guerif
Brigitte Ploix
Daniel Bougeard
Serge Russeil
Nicolas Bariteau
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.)
Wieland Werke AG
Kelvion Thermal Solutions SAS
Technip Energies France SAS
Original Assignee
Wieland Werke AG
Technip France SAS
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 Wieland Werke AG, Technip France SAS, GEA Batignolles Technologies Thermiques filed Critical Wieland Werke AG
Priority to EP13161435.6A priority Critical patent/EP2784426A1/fr
Priority to PCT/EP2014/053142 priority patent/WO2014154398A1/fr
Priority to US14/777,579 priority patent/US20160273840A1/en
Publication of EP2784426A1 publication Critical patent/EP2784426A1/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • F28F1/34—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 obliquely
    • F28F1/36—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 obliquely the means being helically wound fins or wire spirals
    • 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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation

Definitions

  • the invention relates to a tube heat exchanger comprising at least a tube extending along a certain axial direction, each tube being provided with heat exchange fins spaced apart from one another along the axial direction and extending radially from the tube, each fin being relief structured to form a groove/rib arranged at a first distance from the tube.
  • the invention applies to a tube heat exchanger employing air as secondary exchange fluid such as air cooled heat exchangers used for the cooling or condensing of fluids in the oil and gas, power, petrochemical industries.
  • such equipment comprises a main heat exchanger provided with a bundle of finned tubes in which the fluid to be cooled or condensed circulates.
  • These heat exchangers are generally equipped with 50 to 300 finned tubes and have as geometrical characteristics a length of 8 to 18 m and width of 0.3 to 5 m.
  • These heat exchangers are supported by a steel structure.
  • the cooling or condensing of the internal fluid is ensured by a forced circulation of ambient air crossing the external fins.
  • the air circulation is generally ensured by fans that are located either below (forced draft) or above (induced draft) the finned tube of the heat exchanger.
  • the internal fluid circulation can be divided into passes, the heat exchanger comprising generally between three to eight rows of tubes.
  • the finned tubes consist of bare tubes or inner grooved tubes, having a diameter between 15 and 55 mm, generally composed of steel or steel alloy with aluminum fins on the outside of the tube.
  • the selection of the bare tube material is a function of the internal fluid in respect to corrosion and safety issues.
  • the aluminum fins around for example the bare tubes have the advantage of increasing the external heat exchange surface by a factor between 15 and 25 compared to the bare tube external surface. This surface increase allows the increase of the heat transfer but generates pressure losses that are overcame by performing fan system.
  • Aluminum fins can be realized through different manufacturing processes. In most of the known configurations, the fin profile along the tube is helicoidal. Moreover, the fins are independent from one tube to the other, each tube being therefore equipped with its own fin that is spirally wound around it.
  • the air is blown on the outside of the finned tubes at a face velocity between 1 and 4 m/s.
  • the air flow regime is overall laminar with some local turbulences, and characterized by relatively low heat exchange coefficients with the external fins.
  • the areas of high heat exchange coefficients are the leading edge of the fins and the tube to fins junctions in the upstream zone.
  • the downstream areas of the tubes located behind the tubes in the flow direction show very poor heat transfer capacities.
  • Said downstream areas, known as recirculation zones of the heat exchanger are characterized by a recirculation of the air, which generates pressure drops and which does not enable a good cooling of the fins.
  • Some tube heat exchangers are provided with serrated fin with partial cutting performed along the fin periphery and enabling to locally increase the heat transfer through local turbulences created in the air flow.
  • the Patent documents EP 0 854 344 and US 2010/0 282 456 disclose such serrated fins in which the cut parts are bent to allow higher heat transfer rate and guidance of the air flow. However this fin design shows a very poor resistance to fouling phenomena.
  • Patent document KR 2010/0 102 937 discloses a tube heat exchanger with fin provided with holes formed on the downstream side of the fins to minimize the flow separation and increase the heat transfer coefficient. Nevertheless, this fin design does not solve the issues related to the low heat transfer that occurs in the downstream area of the finned tubes due to recirculation. In addition, the effective exchange surface area for transferring heat is decreased because of the holes.
  • Patent document US 7,743,821 discloses a tube heat exchanger with fin having on its surface a relief with dimples or grooves formed by mechanical deformation of the fins. Such dimples or grooves make it possible to increase the heat exchange between the air and the fin thanks to the creation of turbulences while increasing the pressure drop.
  • Patent document FR 2 940 422 discloses a tube heat exchanger with fin provided with grooves having different dimensions that progressively decrease on moving radially away from the tube so as to form a guide for a fluid around the tube.
  • An object of the invention is to provide a tube heat exchanger with optimized thermo-hydraulic characteristics enabling to reach an increase in heat exchanges between the air and the fluid circulating in the tube, without deteriorating the pressure drop and with good resistance to fouling phenomena.
  • the invention provides a tube heat exchanger comprising at least one tube extending along a certain axial direction, each tube being provided with heat exchange fins spaced apart from one another along the axial direction and extending radially from the tube, each fin being relief structured to form a groove/rib arranged at a first distance from the tube, characterized in that each fin further comprises dimples arranged in at least one line at a second distance from the tube, the second distance being greater than the first distance.
  • the main advantage of such a design is that the dimples placed on the outside of the groove/rib create local turbulences in the air flow, that, by guidance of the air flow and in particular in the downstream area of the finned tube to prevent air recirculation, contribute to the heat transfer increase coefficient with reasonable pressure losses increase.
  • the tube heat exchanger of the invention may have the following features :
  • the heat exchanger 1 is represented comprising a bundle of tubes 2 of circular section with a diameter between 15 and 55 mm.
  • the tubes 2 are arranged in several substantially parallel superimposed rows extending in an axial direction A and in which a fluid to be cooled circulates between an inlet B and an outlet C of the fluid, and around which circulates a flow of drafted ambient air drawn from the bottom upwards in the direction indicated by the arrows D, in a transversal manner to the tubes 2, by fans 3 positioned above the heat exchanger 1.
  • a heat exchanger 1 generally comprises between three and eight rows of superimposed tubes 2 laid out in a staggered manner, six in the illustrated example.
  • the tubes 2 may be composed of steel, for example stainless steel or carbon steel or a highly alloyed steel, such as Incoloy, the choice of the material of the tubes 2 being dependent on the transported fluid, which may be aggressive, and the operating conditions.
  • the external fins 4 are generally made of aluminum, but can also be made of stainless steel, or any other heat conducting material. The fins 4 are attached to the bare tube 2 by any commonly known manufacturing process.
  • each tube 2 is provided with external radial fins 4 substantially perpendicular to the tube 2 and substantially parallel to each other favoring heat exchange between the ambient air and the fluid, as well as guiding the flow of air towards the rear of the tubes 2, as will be described hereafter.
  • the pitch between two fins 4 is usually between 2 and 3.5 mm and preferably between 2.3 and 3 mm. In the range of velocities concerned by the application (between 1 and 4 m/s), this distance allows for a maximal ratio between the heat transfer and the associated pressure losses on the air side.
  • FIG 1 For better clarity, several fins 4 spaced apart from each other on a tube 2 are shown on figure 1 . It is obvious that the fins 4 are arranged preferably along the whole length of all of the tubes 2.
  • the shape and the dimension of the external fins 4 may vary from one tube 2 to the next tube 2.
  • the configurations of tube 2 with external fins 4 are not necessarily uniform within a bundle of tubes 2, particularly the diameters of the tubes 2 can vary.
  • the fin 4 is helicoidally wound around the tube 2.
  • the fins may also have disc shapes, the discs being independent and arranged parallel to each other. In both case, viewed in the axial direction A, the fins 4 have a height between 8 and 20 mm and preferably between 12 and 18 mm.
  • the fin 4 according to the invention is relief structured to form a groove/rib 5 and a line of dimples 6.
  • the groove/rib 5 and the line of dimples 6 are concentric and radially spaced apart from each other with the line of dimples 6 surrounding the groove/rib 5.
  • the groove/rib 5 and the line of dimples 6 are manufactured by mechanical deformation of the fins 4.
  • the groove and the rib of the groove/rib 5 are corresponding to each other, the groove being visible on one side of the fin 4, the rib being visible on the other side of the fin 4.
  • the groove and the rib of the groove/rib 5 have a depth, along the axial direction A, between 0.6 and 1.6 mm and preferably between 0.8 and 1.4 mm.
  • the distance D1 between the tube 2 and the groove/rib 5 is between 3 and 7 mm and preferably between 4 mm and 6 mm.
  • the width of the groove/rib 5 is between 1.2 and 3.2mm.
  • the groove/rib 5 preferably has, in the axial plane P, a round shape.
  • the dimples 6 are aligned to each other at a distance D2 from the tube 2 between 8.5 and 12.5 mm and preferably between 9.5 mm and 11.5 mm. Distances D1 and D2 are measured from the outside diameter of the tube 2 to the middle of the groove/dimple 6.
  • the dimples 6 can be equally spaced along the line with a pitch D3 between of two adjacent dimples6 between 4 and 10 mm and preferably between 5 and 8 mm.
  • Each dimple 6 can have a hemispherical, a pyramidal, a truncated shape or any similar suitable smooth shape.
  • the dimples 6 have a depth P2 between 0.4 and 1.4 mm and preferably between 0.6 and 1.2 mm.
  • each dimple 6 is between 1.2 and 2.4 mm.
  • the pitch D3 between two adjacent dimples 6 is between 4 and 10 mm and preferably between 5 and 8 mm.
  • the dimples 6 have the same orientation than the groove/rib 5. It is also possible to provide dimples following an opposite orientation or have dimples 6 located on both sides of the fin 4 and following two opposed orientations.
  • each tube 2 has fins 4 of the same configuration over its whole length. But tubes 2 may also be provided with different configurations of fins 4.
  • This fin 4 design allows a subsequent increase of the global heat transfer and is associated with reasonable increase of the air side pressure loss.
  • the groove/rib 5 close to the tube 2 allows for guidance of the air flow and in particular in the downstream area of the finned tube 2 which is known to be inefficient.
  • the depth P1 of the groove/rib 5 is optimized to get the maximum effect of the air flow guidance. Such guidance effect is visible on figures 5 and 6 on which the velocity fields in the plane located between two adjacent fins 4, 40 is illustrated.
  • the dimples 6 placed on the outside of the groove/rib 5 create local turbulences in the air flow, which contribute to the heat transfer increase coefficient with reasonable pressure losses increase. If there are only grooves 5, the heat exchange is mainly improve in the downstream area of the tubes 2. If there are only dimples 6, the heat exchange is improved all around the fins 4 except in the downstream of the tubes 2. That is why the combination of the groove 5 and the dimples 6 is efficient because the heat exchange is improved all around the tubes 2 thanks to the guidance of the air done with the groove/rib 5.
  • the previously detailed dimensions have been found to be optimal for the application concerned by the invention.
  • the depth P2 of the dimples 6 is optimized to increase the heat transfer without important increase of the pressure losses on the air side.
  • Such fin 4 design is optimized in regards to different phenomenon impacting the air flow topology such as the creation of local turbulences and air guidance.
  • the dimples 6 depth P2 smaller than the groove/rib 5 depth P1 allows the creation of local horseshoe vortices accounting for high heat transfer coefficients in the upstream part of the tube 4. If the pitch D3 between two dimples 6 is too small, the dimples 6 have a negative impact on each others. Indeed, behind each dimple 6, a small recirculation area is created. If the dimples 6 are too close to each others, the recirculation areas will combine together and obstruct the air flow. If the distance between two dimples 6 is too important the local contribution of each dimple 6 will not sufficiently increase the heat transfer.
  • the graph of figure 7 shows the heat transfer coefficients reached with a compound fin 4 according to the invention and a conventional plain fin, as a function of the ventilation power used to push or pull the air flow through the tube heat exchanger 1.
  • the heat transfer coefficient is clearly increased by the new fin 4 design.
  • This new fin 4 design also increase the pressure drop on the air side. As the fan power consumption is directly proportional to the air flow multiplied by the air pressure losses, the air side pressure drop increase results in a higher power consumption of the fan system if the comparison is done for the same air flow rate.
  • the new fin 4 design can also be performing at lower air flow rates and compared to conventional fin designs at the same fan power consumption. In that case, the heat transfer coefficient between the fin 4 and the air can be increased by up to 30% for the same power consumption of the fan system as shown in figure 7 .
  • the graph of figure 8 shows the heat transfer coefficients reached with a compound fin 4 according to the invention and a fin equipped with two grooves and no dimple, as a function of the ventilation power used to push or pull the air flow through the tube heat exchanger 1.
  • the grooved fin has similar dimensions as the compound fin 4.
  • the groove of the grooved fin close to the tube is the same as the one of the compound fin 4 (same position, depth and width), and the other groove of the grooved fin and close to the fin tip has the same position, depth and width than the dimples 6 of the compound fin 4.
  • the heat transfer coefficient is clearly increased by the new fin 4 design due to the dimple 6 contribution for optimized geometrical range of parameters.
  • the graph of figure 9 shows the heat transfer coefficients reached with a compound fin 4 having dimensions as detailed previously and a compound fin 4 having dimensional parameters out of the range described. Optimal heat transfer coefficient is clearly reached thanks to the optimized dimensions.
  • the result of the performance increase of the Air Cooled Heat Exchanger can be turned in two different ways ; either a global increase of the system performance to which the tube heat exchanger 1 is connected to, or a reduction of the tube heat exchanger 1 size. The latter will result in less material used for the same service as for conventional design.

Landscapes

  • 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)
EP13161435.6A 2013-03-27 2013-03-27 Échangeur de chaleur de tube à caractéristiques thermo-hydrauliques optimisées Withdrawn EP2784426A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP13161435.6A EP2784426A1 (fr) 2013-03-27 2013-03-27 Échangeur de chaleur de tube à caractéristiques thermo-hydrauliques optimisées
PCT/EP2014/053142 WO2014154398A1 (fr) 2013-03-27 2014-02-18 Échangeur de chaleur à tubes avec caractéristiques thermohydrauliques optimisées
US14/777,579 US20160273840A1 (en) 2013-03-27 2014-02-18 Tube heat exchanger with optimized thermo-hydraulic characteristics

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13161435.6A EP2784426A1 (fr) 2013-03-27 2013-03-27 Échangeur de chaleur de tube à caractéristiques thermo-hydrauliques optimisées

Publications (1)

Publication Number Publication Date
EP2784426A1 true EP2784426A1 (fr) 2014-10-01

Family

ID=48050459

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13161435.6A Withdrawn EP2784426A1 (fr) 2013-03-27 2013-03-27 Échangeur de chaleur de tube à caractéristiques thermo-hydrauliques optimisées

Country Status (3)

Country Link
US (1) US20160273840A1 (fr)
EP (1) EP2784426A1 (fr)
WO (1) WO2014154398A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110726323A (zh) * 2019-11-19 2020-01-24 广东美的暖通设备有限公司 用于换热器的散热翅片、换热器和制冷设备

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10508621B2 (en) 2012-07-12 2019-12-17 Ge Global Sourcing Llc Exhaust gas recirculation system and method
US9938935B2 (en) 2012-07-12 2018-04-10 General Electric Company Exhaust gas recirculation system and method
US10465492B2 (en) 2014-05-20 2019-11-05 KATA Systems LLC System and method for oil and condensate processing
US9763388B2 (en) 2015-09-15 2017-09-19 Cnh Industrial America Llc Agricultural harvester having a header based heat exchanger
EP3382314A1 (fr) * 2017-03-30 2018-10-03 Nederlandse Organisatie voor toegepast- natuurwetenschappelijk onderzoek TNO Production et utilisation améliorées de tcm
CN109443053A (zh) * 2018-10-30 2019-03-08 佛山科学技术学院 一种管壳式换热器
FR3136276B1 (fr) 2022-06-07 2024-06-14 Technip Energies France Echangeur thermique destiné à être refroidi par un flux gazeux, installation de liquéfaction de gaz naturel, et procédé associé

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2217469A (en) * 1940-03-09 1940-10-08 Vulcan Radiator Co Heat transfer unit
CH414705A (de) * 1964-10-15 1966-06-15 Bbc Brown Boveri & Cie Wärmeaustauschelement
EP0854344A2 (fr) 1997-01-20 1998-07-22 Kabushiki Kaisha Toshiba Echangeur de chaleur
US6349761B1 (en) * 2000-12-27 2002-02-26 Industrial Technology Research Institute Fin-tube heat exchanger with vortex generator
US20080023180A1 (en) * 2006-07-26 2008-01-31 General Electric Company Air cooled heat exchanger with enhanced heat transfer coefficient fins
US20100155041A1 (en) * 2008-12-19 2010-06-24 Gea Batignolles Technologies Thermiques Heat exchanger comprising tubes with grooved fins
KR20100102937A (ko) 2009-03-12 2010-09-27 주식회사 케이에이치이 열전달 성능이 향상된 핀튜브
US20100282456A1 (en) 2009-05-06 2010-11-11 General Electric Company Finned tube heat exchanger
WO2012102053A1 (fr) * 2011-01-27 2012-08-02 パナソニック株式会社 Échangeur de chaleur à tube à ailettes

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2400157A (en) * 1943-09-11 1946-05-14 United Aircraft Corp Brazed cylinder muff

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2217469A (en) * 1940-03-09 1940-10-08 Vulcan Radiator Co Heat transfer unit
CH414705A (de) * 1964-10-15 1966-06-15 Bbc Brown Boveri & Cie Wärmeaustauschelement
EP0854344A2 (fr) 1997-01-20 1998-07-22 Kabushiki Kaisha Toshiba Echangeur de chaleur
US6349761B1 (en) * 2000-12-27 2002-02-26 Industrial Technology Research Institute Fin-tube heat exchanger with vortex generator
US20080023180A1 (en) * 2006-07-26 2008-01-31 General Electric Company Air cooled heat exchanger with enhanced heat transfer coefficient fins
US7743821B2 (en) 2006-07-26 2010-06-29 General Electric Company Air cooled heat exchanger with enhanced heat transfer coefficient fins
US20100155041A1 (en) * 2008-12-19 2010-06-24 Gea Batignolles Technologies Thermiques Heat exchanger comprising tubes with grooved fins
FR2940422A1 (fr) 2008-12-19 2010-06-25 Gea Batignolles Technologies T Echangeur de chaleur comprenant des tubes a ailettes rainurees
KR20100102937A (ko) 2009-03-12 2010-09-27 주식회사 케이에이치이 열전달 성능이 향상된 핀튜브
US20100282456A1 (en) 2009-05-06 2010-11-11 General Electric Company Finned tube heat exchanger
WO2012102053A1 (fr) * 2011-01-27 2012-08-02 パナソニック株式会社 Échangeur de chaleur à tube à ailettes

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
DATABASE WPI Week 201253, Derwent World Patents Index; AN 2012-J95712, XP002700282 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110726323A (zh) * 2019-11-19 2020-01-24 广东美的暖通设备有限公司 用于换热器的散热翅片、换热器和制冷设备

Also Published As

Publication number Publication date
US20160273840A1 (en) 2016-09-22
WO2014154398A1 (fr) 2014-10-02

Similar Documents

Publication Publication Date Title
EP2784426A1 (fr) Échangeur de chaleur de tube à caractéristiques thermo-hydrauliques optimisées
US8376033B2 (en) Heat exchanger comprising tubes with grooved fins
US8276652B2 (en) High performance louvered fin for heat exchanger
EP2141435A1 (fr) Échangeur thermique de type tube à ailettes-plaques
US20100282456A1 (en) Finned tube heat exchanger
JP2009127937A (ja) 熱交換器
US20050150648A1 (en) Multi-spiral upset heat exchanger tube
EP3415827B1 (fr) Climatiseur
JP4073850B2 (ja) 熱交換器
US20060169019A1 (en) Tabbed transfer fins for air-cooled heat exchanger
EP1602417B1 (fr) Disque pour la formation de tubes à ailettes
JP4876660B2 (ja) フィン付き熱交換器及び空気調和機
WO2013054508A1 (fr) Échangeur de chaleur à tube à ailettes
EP0854344B1 (fr) Echangeur de chaleur
JP2013092306A (ja) フィンチューブ熱交換器
JP2006162183A (ja) フィン付き熱交換器
EP2147274B1 (fr) Dispositif d'échange thermique indirect et procédé d'échange thermique
JP2006097953A (ja) フィン付き熱交換器
JP2008209025A (ja) 伝熱部材およびそれを用いた熱交換器
WO2019087311A1 (fr) Dispositif de rayonnement de chaleur
JP5476080B2 (ja) アルミニウム製内面溝付伝熱管
JP2008101907A (ja) 熱交換器
EP3956623A1 (fr) Ailette de condenseur refroidie par de l'air turbulent
JP2019086264A (ja) フィンチューブ熱交換器
JP2006317117A (ja) 熱交換器

Legal Events

Date Code Title Description
17P Request for examination filed

Effective date: 20130327

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

R17P Request for examination filed (corrected)

Effective date: 20141217

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

17Q First examination report despatched

Effective date: 20150925

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20151127