EP0865838A1 - Tube pour échangeur de chaleur et méthode pour fabriquer un tel tube - Google Patents

Tube pour échangeur de chaleur et méthode pour fabriquer un tel tube Download PDF

Info

Publication number
EP0865838A1
EP0865838A1 EP98630007A EP98630007A EP0865838A1 EP 0865838 A1 EP0865838 A1 EP 0865838A1 EP 98630007 A EP98630007 A EP 98630007A EP 98630007 A EP98630007 A EP 98630007A EP 0865838 A1 EP0865838 A1 EP 0865838A1
Authority
EP
European Patent Office
Prior art keywords
tube
fin
heat transfer
angle
convolution
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.)
Granted
Application number
EP98630007A
Other languages
German (de)
English (en)
Other versions
EP0865838B1 (fr
Inventor
Neelkanth S. Gupte
Steven J. Spencer
Daniel P. Gaffaney
Xin Liu
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.)
Carrier Corp
Original Assignee
Carrier Corp
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 US08/814,471 external-priority patent/US5933953A/en
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP0865838A1 publication Critical patent/EP0865838A1/fr
Application granted granted Critical
Publication of EP0865838B1 publication Critical patent/EP0865838B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C37/00—Manufacture of metal sheets, bars, wire, tubes or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape
    • B21C37/06—Manufacture of metal sheets, bars, wire, tubes or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape of tubes or metal hoses; Combined procedures for making tubes, e.g. for making multi-wall tubes
    • B21C37/15—Making tubes of special shape; Making tube fittings
    • B21C37/20—Making helical or similar guides in or on tubes without removing material, e.g. by drawing same over mandrels, by pushing same through dies ; Making tubes with angled walls, ribbed tubes and tubes with decorated walls
    • B21C37/207—Making helical or similar guides in or on tubes without removing material, e.g. by drawing same over mandrels, by pushing same through dies ; Making tubes with angled walls, ribbed tubes and tubes with decorated walls with helical guides
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with the tubular 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
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators

Definitions

  • the present invention relates generally to heat transfer tubes.
  • the invention relates to a heat transfer tube having a refrigerant surface configuration that is suitable for use in air conditioning and refrigeration system heat exchangers in both evaporating and condensing applications, as well as a method of manufacturing same.
  • a shell and tube type heat exchanger has a plurality of tubes contained within a shell.
  • the tubes are usually arranged to provide multiple parallel flow paths for one of two fluids between which it is desired to exchange heat.
  • the tubes are immersed in a second fluid that flows through the heat exchanger shell. Heat passes from the one fluid to the other fluid through the walls of the tube.
  • Many air conditioning systems contain shell and tube type heat exchangers.
  • a fluid commonly water
  • refrigerant flows through the heat exchanger shell.
  • the refrigerant cools the fluid by heat transfer from the fluid through the walls of the tubes. The transferred heat vaporizes the refrigerant in contact with the exterior surface of the tubes.
  • refrigerant is cooled and condenses through heat transfer to the fluid through the walls of the tubes.
  • the heat transfer capability of such a heat exchanger is largely determined by the heat transfer characteristics of the individual tubes.
  • the external configuration of an individual tube is important in establishing its overall heat transfer characteristics.
  • a finned tube offers improved condensing heat transfer performance over a tube having a smooth outer surface for another reason.
  • the condensing refrigerant forms a continuous film of liquid refrigerant on the outer surface of a smooth tube.
  • the presence of the film reduces the heat transfer rate across the tube wall. Resistance to heat transfer across the film increases with film thickness.
  • the film thickness on the fins is generally less than on the main portion of the tube surface due to surface tension effects, thus lowering the heat transfer resistance through the fins.
  • increasing the heat transfer area of the tube surface also improves the heat transfer performance of a heat transfer tube.
  • a surface configuration that promotes nucleate boiling on the surface of the tube that is in contact with the boiling fluid improves performance.
  • heat transferred from the heated surface vaporizes liquid in contact with the surface and the vapor forms into bubbles.
  • Heat from the surface superheats the vapor in a bubble and the bubble grows in size.
  • surface tension is overcome and the bubble breaks free of the surface.
  • liquid enters the volume vacated by the bubble and vapor remaining in the volume has a source of additional liquid to vaporize to form another bubble.
  • the continual forming of bubbles at the surface, the release of the bubbles from the surface and the rewetting of the surface together with the convective effect of the vapor bubbles rising through and mixing the liquid result in an improved heat transfer rate for the heat transfer surface.
  • the nucleate boiling process can be enhanced by configuring the heat transfer surface so that it has nucleation sites that provide locations for the entrapment of vapor and promote the formation of vapor bubbles. Simply roughening a heat transfer surface, for example, will provide nucleation sites that can improve the heat transfer characteristics of the surface over a similar smooth surface. Nucleation sites of the re-entrant type produce stable bubble columns and good surface heat transfer characteristics.
  • a re-entrant type nucleation site is a surface cavity in which the opening of the cavity is smaller than the subsurface volume of the cavity. An excessive influx of the surrounding liquid can flood a re-entrant type nucleation site and deactivate it.
  • the present invention is a heat transfer tube, and a method of manufacturing a heat transfer tube, having an external surface configured to provide improved heat transfer performance in both refrigerant condensing, flooded evaporation and film evaporation applications.
  • the tube has one or more fin convolutions formed on its external surface. Notches extend at an oblique angle across the fin convolutions at intervals about the circumference of the tube.
  • the portion of a fin convolution between adjacent notches in the fin convolution forms a spike.
  • the distal tip of the spike is split into two tip portions. Each tip portion extends outward from the proximal base of the fin toward the split fin tips in the adjacent fin convolution.
  • the notches and split spike tips further increase the outer surface area of the tube as compared to a conventional finned tube.
  • the grooves between adjacent fin convolutions, over which the split fin tips extend form reentrant cavities that promote refrigerant pool boiling in a flooded evaporator.
  • the relatively sharp spike tips promote drainage and spreading of refrigerant from the fin.
  • the tubes in a shell and tube type air conditioning heat exchanger run horizontally or nearly so.
  • the notched and split fin configuration promotes drainage of condensing refrigerant from the fins into the grooves between fins on the upper portion of the tube surface and also promotes drainage of condensed refrigerant off the tube on the lower portion of the tube surface.
  • the sharp tips and notches, and low surface tension of refrigerant aid in liquid spreading on the tube surface and along the tube axis. This promotes good wettability in a horizontal shell and tube falling film evaporator.
  • Manufacture of a notched split tip finned tube can be easily and economically accomplished by adding a notching disk or disks and a splitter disk or disks to the tool gang of a finning machine of the type that forms fins on the outer surface of a tube by rolling the tube wall between an internal mandrel and external finning disks.
  • the notching tool is configured to impart a twist to the sound spikes in order to facilitate splitting of the spike tips.
  • FIG. 1 is a pictorial view of the tube of the present invention.
  • FIG. 2 is a view illustrating how the tube of the present invention is manufactured.
  • FIG. 3 is a plan view of a portion of the external surface of the tube of the present invention.
  • FIG. 4 is a plan view of a portion a single fin convolution of the tube of the present invention.
  • FIG. 5 is a generic sectioned elevation view of two adjacent fin convolutions of the tube of the present invention.
  • FIG. 1 is a pictorial view of heat transfer tube 10 .
  • Tube 10 comprises tube wall 11 , tube inner surface 12 and tube outer surface 13 . Extending from the outer surface of tube wall 11 are external fin spikes 22 .
  • Tube 10 has outer diameter D o as measured from tube outer surface 13 excluding the height (H f ) of fin spikes 22 .
  • the tube of the present invention may be readily manufactured by a rolling process.
  • FIG. 2 illustrates such a process.
  • finning machine 60 is operating on tube 10 , which is made of a malleable metal such as copper, to produce both interior ribs and exterior fins on the tube.
  • Finning machine 60 has one or more tool arbors 61 , each containing a tool gang 62 , comprised of a number of finning disks 63 , notching disk 66 and splitting disk 67 . Extending into the tube is mandrel shaft 65 to which is attached mandrel 64 .
  • Wall 11 is pressed between mandrel 64 and finning disks 63 as tube 10 rotates. Under pressure, metal flows into the grooves between the finning disks and forms a ridge or fin on the exterior surface of the tube. As it rotates, tube 10 advances between mandrel 64 and tool gang 62 (from left to right in FIG. 2 ) resulting in a number of helical fin convolutions being formed on the tube.
  • the number of convolutions is a function of the number of finning disks 63 in tool gang 62 and the number of tool arbors 61 in use on finning machine 60 .
  • notching wheel 66 impresses oblique notches in to the metal of the fin convolutions.
  • splitting disk 67 splits the tip of each fin convolution into two portions.
  • Mandrel 64 may be configured in such a way, as shown in FIG. 2 , that it will impress some type of pattern into the internal surface 12 of the wall of the tube passing over it.
  • a typical pattern is of one or more helical rib convolutions. Such a pattern can improve the rate of heat transfer between the fluid flowing through the tube and the tube wall.
  • FIG. 3 shows, in plan view, a portion of the external surface of the tube. Extending from outer surface 13 of tube 10 are a number of fin convolutions 20 . Extending obliquely across each fin convolution at intervals are a pattern of notches 30 . Between each pair of adjacent notches in a given fin convolution is a fin spike 22 having two distal tips 23 .
  • FIG. 4 is a plan view of a portion of a single fin convolution of the tube of the present invention.
  • the angle of inclination of notch base 31 from tube longitudinal axis A T is angle ⁇ .
  • the angle of inclination of the distal tip 23 of fin 22 from longitudinal axis of the tube A T is angle ⁇ .
  • the interaction between rotating and advancing tube 10 and notching wheel 66 may result in the axis of fin spike 22 , indicated in FIG. 4 , is turned slightly from the angle between the teeth of the notching wheel and the fin convolution so that tip axis angle ⁇ is oblique with respect to angle ⁇ , i.e., ⁇ ⁇ ⁇ .
  • it is possible to have ⁇ ⁇ as a specific case. It is this turning of the spike that allows the splitting disk 67 to reliably split the spike because the notched spike presents a wider face for splitting than would the unnotched fin convolution.
  • the spikes will be caused to twist.
  • the twisting of the spikes enables the splitting of the spikes to be done more efficiently. Specifically, without the twisting, the fin tip thickness would be too small to reliably split the spikes.
  • the shape of the spikes after notching and just before splitting is essentially a parallelogram. After splitting the parallelogram is split along its diagonal to create two triangles.
  • FIG. 5 is a pseudo sectioned elevation view of two adjacent fin convolutions of the tube of the present invention.
  • the term pseudo is used because it is unlikely that a section taken through any part of the fin convolutions would look exactly as the section depicted in FIG. 5.
  • the figure, however, serves to illustrate many of the features of the tube.
  • Fin convolutions 20A and 20B extend outward from tube wall 11 .
  • Fin convolutions 20A and 20B have proximal portions 21 and spike portions 22 .
  • Extending through fin convolution 20A is a notch having notch base 32.
  • the overall height of fin convolutions 20A and 20B is H f .
  • the width of proximal portion 21 is W r and the width of spike portion 22 at its widest dimension is W t .
  • the outer extremity of spike 22 has two distal tips 23 .
  • the notch penetrates into the fin convolution to height H n above inner wall surface 13 .
  • notching wheel 66 does not cut notches out of the fin convolutions during the manufacturing process but rather impresses notches into the fin convolutions by displacing material from the notched area.
  • the excess material from the notched portion of the fin convolution moves both into the region between adjacent notches and outwardly from the sides of the fin convolution as well as toward tube wall 11 on the sides of the fin convolution .
  • W t is greater than W r .
  • the distance between similar points on adjacent fin convolutions, or fin pitch is P f .
  • the angle between the two distal tips 23 on a spike portion 22 is angle ⁇ .
  • a distal tip extending from one side of a fin convolution extends toward the adjacent fin convolution on that side leaving gap g between tips.
  • the relatively large number of sharp distal tips promote condensation on the surface of the tube when the tube is used in a condensing application. Because the distal tips overlie the volume between adjacent fin convolutions, a reentrant cavity is formed and thus forms a tube surface that promotes evaporation.
  • the performance of Prototype Family A is an average of about 2.5 times that of the smooth tube and the performance of Prototype Family B is about 3 times the smooth tube performance.
  • the performance of Prototype Family A is an average of about 19 times that of the smooth tube and the performance of Prototype Family B is about 23 times the smooth tube performance.
  • the tested prototypes have three convolutions or "starts."
  • the optimum number of fin convolutions or start depends more on considerations of ease of manufacture than upon the effect of the number on heat transfer performance. A higher number of starts increases the rate at which the fin convolutions can be formed on the tube surface.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Rigid Pipes And Flexible Pipes (AREA)
  • Metal Extraction Processes (AREA)
EP98630007A 1997-03-17 1998-02-27 Tube pour échangeur de chaleur et méthode pour fabriquer un tel tube Expired - Lifetime EP0865838B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US820472 1986-01-17
US82047297A 1997-03-17 1997-03-17
US08/814,471 US5933953A (en) 1997-03-17 1997-03-17 Method of manufacturing a heat transfer tube
US814471 2001-03-21

Publications (2)

Publication Number Publication Date
EP0865838A1 true EP0865838A1 (fr) 1998-09-23
EP0865838B1 EP0865838B1 (fr) 2002-05-08

Family

ID=27123850

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98630007A Expired - Lifetime EP0865838B1 (fr) 1997-03-17 1998-02-27 Tube pour échangeur de chaleur et méthode pour fabriquer un tel tube

Country Status (7)

Country Link
EP (1) EP0865838B1 (fr)
JP (1) JP2945649B2 (fr)
KR (1) KR100324065B1 (fr)
CN (1) CN100347512C (fr)
AU (1) AU722999B2 (fr)
CA (1) CA2230213C (fr)
ES (1) ES2174408T3 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003104736A1 (fr) * 2002-06-10 2003-12-18 Wolverine Tube, Inc. Tube de transfert de chaleur, procede et outil de production associes
US7284325B2 (en) 2003-06-10 2007-10-23 Petur Thors Retractable finning tool and method of using
US7311137B2 (en) 2002-06-10 2007-12-25 Wolverine Tube, Inc. Heat transfer tube including enhanced heat transfer surfaces
US7509828B2 (en) 2005-03-25 2009-03-31 Wolverine Tube, Inc. Tool for making enhanced heat transfer surfaces
CN103084813A (zh) * 2011-11-03 2013-05-08 秦彪 太阳花式散热器制造方法及其设备
US8573022B2 (en) 2002-06-10 2013-11-05 Wieland-Werke Ag Method for making enhanced heat transfer surfaces
US8720199B2 (en) 2007-02-28 2014-05-13 Behr Gmbh & Co. Kg Heat exchanger, exhaust gas recirculation system, charge air supply system, and use of the heat exchanger

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101151872B1 (ko) 2010-03-18 2012-05-31 (주)현대기공 터보냉동기의 증발기용 전열관
KR101151871B1 (ko) 2010-03-18 2012-05-31 (주)현대기공 터보냉동기의 응축기용 전열관
CN102147204A (zh) * 2011-03-24 2011-08-10 恩迅（上海）节能科技有限公司 一种节能防腐蚀的省煤器换热管及其制备方法
ITUB20159298A1 (it) * 2015-12-23 2017-06-23 Brembana & Rolle S P A Scambiatore di calore a fascio tubiero e mantello, tubi alettati per tale scambiatore e relativo metodo di produzione.
CN106391914B (zh) * 2016-11-10 2018-07-20 华南理工大学 一种轧制与犁切-挤压三维内外翅片管制造设备与方法
CN106391913B (zh) 2016-11-10 2018-07-20 华南理工大学 一种基于多刃犁切-挤压的三维内翅片管成型装置及方法
CN107774849B (zh) * 2017-10-27 2024-06-18 华南理工大学 一种蒸发冷凝两用阶梯宫格翅片管的成形刀具和成形方法
DE102017128163A1 (de) * 2017-11-28 2019-05-29 Liebherr-Components Biberach Gmbh Seiltrommel sowie Verfahren zu deren Herstellung
CN108168353B (zh) * 2017-12-28 2019-08-09 无锡市欣明换热新材料科技有限公司 一种冷凝器的冷凝管及其加工装置
CN110976724A (zh) * 2019-12-03 2020-04-10 鲁德祥 多头螺旋花刀

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4179911A (en) * 1977-08-09 1979-12-25 Wieland-Werke Aktiengesellschaft Y and T-finned tubes and methods and apparatus for their making
JPS5927739A (ja) * 1982-08-05 1984-02-14 Kobe Steel Ltd 沸騰伝熱管の製造方法
JPS59100396A (ja) * 1982-11-30 1984-06-09 Kobe Steel Ltd 凝縮伝熱管
EP0713073A2 (fr) * 1994-11-17 1996-05-22 Carrier Corporation Tube de transfert de chaleur

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4577381A (en) * 1983-04-01 1986-03-25 Kabushiki Kaisha Kobe Seiko Sho Boiling heat transfer pipes
US4660630A (en) * 1985-06-12 1987-04-28 Wolverine Tube, Inc. Heat transfer tube having internal ridges, and method of making same
US4765058A (en) * 1987-08-05 1988-08-23 Carrier Corporation Apparatus for manufacturing enhanced heat transfer surface
US5203404A (en) * 1992-03-02 1993-04-20 Carrier Corporation Heat exchanger tube
US5332034A (en) * 1992-12-16 1994-07-26 Carrier Corporation Heat exchanger tube
KR0134557B1 (ko) * 1993-07-07 1998-04-28 가메다카 소키치 유하액막식 증발기용 전열관

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4179911A (en) * 1977-08-09 1979-12-25 Wieland-Werke Aktiengesellschaft Y and T-finned tubes and methods and apparatus for their making
JPS5927739A (ja) * 1982-08-05 1984-02-14 Kobe Steel Ltd 沸騰伝熱管の製造方法
JPS59100396A (ja) * 1982-11-30 1984-06-09 Kobe Steel Ltd 凝縮伝熱管
EP0713073A2 (fr) * 1994-11-17 1996-05-22 Carrier Corporation Tube de transfert de chaleur

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003104736A1 (fr) * 2002-06-10 2003-12-18 Wolverine Tube, Inc. Tube de transfert de chaleur, procede et outil de production associes
US7311137B2 (en) 2002-06-10 2007-12-25 Wolverine Tube, Inc. Heat transfer tube including enhanced heat transfer surfaces
CN100449248C (zh) * 2002-06-10 2009-01-07 沃尔弗林管子公司 传热管以及用于制造该传热管的方法及工具
US7637012B2 (en) 2002-06-10 2009-12-29 Wolverine Tube, Inc. Method of forming protrusions on the inner surface of a tube
US8302307B2 (en) 2002-06-10 2012-11-06 Wolverine Tube, Inc. Method of forming protrusions on the inner surface of a tube
US8573022B2 (en) 2002-06-10 2013-11-05 Wieland-Werke Ag Method for making enhanced heat transfer surfaces
US7284325B2 (en) 2003-06-10 2007-10-23 Petur Thors Retractable finning tool and method of using
US7509828B2 (en) 2005-03-25 2009-03-31 Wolverine Tube, Inc. Tool for making enhanced heat transfer surfaces
US8720199B2 (en) 2007-02-28 2014-05-13 Behr Gmbh & Co. Kg Heat exchanger, exhaust gas recirculation system, charge air supply system, and use of the heat exchanger
CN103084813A (zh) * 2011-11-03 2013-05-08 秦彪 太阳花式散热器制造方法及其设备
CN103084813B (zh) * 2011-11-03 2016-11-23 秦彪 太阳花式散热器制造方法及其设备

Also Published As

Publication number Publication date
KR100324065B1 (ko) 2002-08-08
EP0865838B1 (fr) 2002-05-08
CA2230213C (fr) 2003-05-06
JPH10263734A (ja) 1998-10-06
CN1193722A (zh) 1998-09-23
AU722999B2 (en) 2000-08-17
CN100347512C (zh) 2007-11-07
JP2945649B2 (ja) 1999-09-06
AU5842698A (en) 1998-09-17
KR19980080288A (ko) 1998-11-25
CA2230213A1 (fr) 1998-09-17
ES2174408T3 (es) 2002-11-01

Similar Documents

Publication Publication Date Title
EP0713072B1 (fr) Tube de transfert de chaleur
EP0865838B1 (fr) Tube pour échangeur de chaleur et méthode pour fabriquer un tel tube
EP0713073B1 (fr) Tube de transfert de chaleur
JP2721309B2 (ja) 伝熱管
US7178361B2 (en) Heat transfer tubes, including methods of fabrication and use thereof
US5933953A (en) Method of manufacturing a heat transfer tube
US20060075772A1 (en) Heat transfer tubes, including methods of fabrication and use thereof
US4938282A (en) High performance heat transfer tube for heat exchanger
US6457516B2 (en) Heat transfer tube for evaporation with variable pore sizes
US5010643A (en) High performance heat transfer tube for heat exchanger
EP3995773A1 (fr) Tube de transfert thermique
US20230341193A1 (en) Metal heat exchanger tube

Legal Events

Date Code Title Description
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

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): ES FR GB IT

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 19990210

AKX Designation fees paid

Free format text: ES FR GB IT

RBV Designated contracting states (corrected)

Designated state(s): ES FR GB IT

REG Reference to a national code

Ref country code: DE

Ref legal event code: 8566

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

17Q First examination report despatched

Effective date: 20010419

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): ES FR GB IT

ET Fr: translation filed
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2174408

Country of ref document: ES

Kind code of ref document: T3

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20030211

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20060210

Year of fee payment: 9

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20070227

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070227

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20070228

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20080222

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070228

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20080212

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20060109

Year of fee payment: 9

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20091030

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090302

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090227