EP3394550B1 - Shell and tube heat exchanger, finned tubes for such heat exchanger and corresponding method - Google Patents

Shell and tube heat exchanger, finned tubes for such heat exchanger and corresponding method Download PDF

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Publication number
EP3394550B1
EP3394550B1 EP16810268.9A EP16810268A EP3394550B1 EP 3394550 B1 EP3394550 B1 EP 3394550B1 EP 16810268 A EP16810268 A EP 16810268A EP 3394550 B1 EP3394550 B1 EP 3394550B1
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EP
European Patent Office
Prior art keywords
tube
fin
heat exchanger
angle
shell
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Active
Application number
EP16810268.9A
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German (de)
English (en)
French (fr)
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EP3394550A1 (en
Inventor
Marco Rottoli
Marcello Garavaglia
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Brembana and Rolle SpA
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Brembana and Rolle SpA
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Publication of EP3394550A1 publication Critical patent/EP3394550A1/en
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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
    • F28F1/34—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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES, PROFILES OR LIKE SEMI-MANUFACTURED PRODUCTS OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C37/00—Manufacture of metal sheets, rods, wire, tubes, profiles or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape
    • B21C37/06—Manufacture of metal sheets, rods, wire, tubes, profiles 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 or 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 or tubes with decorated walls with helical guides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1607—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1615—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits being inside a casing and extending at an angle to the longitudinal axis of the casing; the conduits crossing the conduit for the other heat exchange medium
    • F28D7/1623—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits being inside a casing and extending at an angle to the longitudinal axis of the casing; the conduits crossing the conduit for the other heat exchange medium with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21H—MAKING PARTICULAR METAL OBJECTS BY ROLLING, e.g. SCREWS, WHEELS, RINGS, BARRELS, BALLS
    • B21H7/00—Making articles not provided for in the preceding groups, e.g. agricultural tools, dinner forks, knives, spoons
    • B21H7/18—Making articles not provided for in the preceding groups, e.g. agricultural tools, dinner forks, knives, spoons grooved pins; Rolling grooves, e.g. oil grooves, in articles
    • B21H7/187—Rolling helical or rectilinear grooves

Definitions

  • the present invention relates to a method for manufacturing finned tubes provided with a particular system of fins.
  • US 5 933953 A discloses such a finned tube.
  • Heat exchangers of shell and tube type are industrial heat exchangers of known type and consist essentially of a bundle of tubes positioned inside a containment casing (shell), usually cylindrical. In operating conditions two fluids flow through the heat exchanger: a first fluid, preferably the hotter, or more corrosive, or with higher fouling coefficient, flows inside the tubes ("tube side” flow), while a second fluid flows in the space delimited by the internal surface of the shell and by the outer surfaces of the tubes (“shell side” flow).
  • a first fluid preferably the hotter, or more corrosive, or with higher fouling coefficient
  • Transverse baffles are generally present inside the shell with the dual purpose of supporting the bundle of tubes and generating turbulence in the fluid on the shell side in order to increase the heat transfer coefficient.
  • the transverse baffles are made of sheet metal plates that occupy a part of the internal section of the heat exchanger 10, producing a tortuous path (as represented by the arrows in Fig. 3 ) of the fluid on the shell side, having longitudinal and above all transverse components with respect to the axis of the heat exchanger 10; this type of diaphragm configures the conventional solution classified according the TEMA standard commonly adopted at international level.
  • the flow of fluid on the shell side can also have a helical trend, for example as represented in Fig. 4 .
  • a certain number of diaphragms, made of stamped grids are positioned inside the heat exchanger 100 and inclined so as to set the fluid on the shell side in rotary motion during its advancement through the heat exchanger 100, thereby producing the overall helical motion of the fluid on the shell side, schematized by the arrows of Fig. 4 .
  • a typical problem that is encountered in heat exchangers of conventional TEMA type is given by the deposit of solid material transported by the fluid, or which forms by precipitation on the diaphragms or dead corners in the path of the fluid on the shell side.
  • the deposit of solid material can cause a decrease in the heat transfer coefficient resulting in a decrease in the performance of the heat exchanger.
  • the presence of solid material deposited inside the heat exchanger can cause uneven distribution of the flow of fluid on the shell side, and can therefore lead to worsening in the performance of the heat exchanger.
  • the tube In the field of heat exchangers, in particular heat exchangers of industrial type, there is known the use of tubes provided with surface fins to increase the heat exchange surface.
  • the tube In the case of shell and tube heat exchangers, depending on whether the performance is to be increased on the shell side or on the tube side, the tube can be provided with fins on its outer surface or on its internal surface. In particular cases, a finned tube is used on both surfaces.
  • tubes provided with helical fins or tubes in which the angle of advancement of the fin has a component in longitudinal direction with respect to the axis of the tube ( ⁇ ⁇ 90°).
  • the tube is normally subjected to annealing between two subsequent machining operations, with a noteworthy increase in the costs of the production process of the tube.
  • the main aim of the present invention is to provide a method for manufacturing finned tubes that allows the manufacture of tubes provided with helical fins ( ⁇ ⁇ 90°) even when said tubes are made of materials with high mechanical strength.
  • One more object of the subject matter of the present invention is to provide a shell and tube longitudinal flow heat exchanger, and a finned tube for heat exchangers, that is highly reliable and is easy to manufacture at competitive costs.
  • the final surface obtained is greater by a factor of 3.0-4.0, and can even reach a factor of 4.5, with respect to the initial smooth tube.
  • finned tubes made of materials with high mechanical strength, for example alloy steels, such as copper-nickel, stainless, duplex or titanium steels, which are critical for the reasons set forth above.
  • the term "low fins” is intended as fins with a height H of less than approximately 2mm and preferably between 0.5 and 1.5 mm.
  • the angle of advancement ⁇ of the fins is generally ⁇ 80°, and preferably 15° ⁇ ⁇ 60°, more preferably 20° ⁇ ⁇ 45°, this latter being the best range to obtain the optimum compromise between fin height and density, as can be experimentally verified.
  • the interruptions on the profile of the fin can be obtained by subjecting the tube to two finning operations in immediate sequence carried out with different angles of advancement.
  • the tube is subjected, with a first finning/grooving tool, to a first groove machining operation that produces a fin with an angle of advancement ⁇ , of low depth, preferably ⁇ 0.5 mm, to limit hardening of the material.
  • a second main finning operation is carried out on the tube thus grooved to produce the actual fins with an angle of advancement ⁇ .
  • the main fins are produced on a surface that already has ridges and grooves.
  • the method uses angles of advancement and pitches for the first finning/grooving tool and for the main finning tool such that the result of machining of the main tool is to increase the height of the finished fin with respect to what can be obtained starting from a normal circular smooth surface.
  • the main fin machining operation takes place according to a plane inclined by an angle ⁇ 2 with respect to the longitudinal axis of the tube
  • the fin/groove machining operation takes place according to plane inclined by an angle ⁇ 1 with respect to the longitudinal axis of the tube.
  • the relative angle between the two machining planes is chosen on the basis of a compromise between the largest obtainable increase in the height of the fin and the largest number of interruptions obtainable per unit of length measured according to the longitudinal axis of the tube.
  • the rake angle is therefore between 0° (maximum height increase and no interruption) and 90° (minimum height increase and maximum interruption effect).
  • the rake angle is between 30 and 60°, according to needs. In this way, both the increase in height of the final fins with respect to the single machining operation and, at the same time, the desired interruption are obtained.
  • the relative angle between said first angle of advancement ⁇ and said second angle of advancement ⁇ is preferably between 0° and 90°, and more preferably between 30° and 60°.
  • the interrupted fin thus obtainable can extend for the whole surface of the tube or for portions of any length, leaving the remaining portions smooth. This characteristic is useful when using tubes with U-shaped bends, so as not to weaken the curved section, retaining their mechanical strength in particular applications.
  • shell and tube longitudinal flow heat exchangers of EMbaffle ® type this characteristic is particularly useful as the smooth portion facilitates stable positioning of the baffle; for this reason, shell and tube longitudinal flow heat exchangers according to the present invention can advantageously be provided with tubes in which finned portions are alternated by smooth portions.
  • the shell and tube heat exchanger according to the present invention is advantageously provided with tubes that can be equipped with interior fins obtained by producing grooves on the internal surface.
  • the present invention also relates to a method for manufacturing a finned tube using a machine comprising a first working assembly and at least one support assembly.
  • the first working assembly comprises a first rotating finning/grooving tool and a second rotating finning tool mounted in sequence on the same driving axis.
  • the first rotating finning/grooving tool is provided with a first helical working profile having a first angle of advancement ⁇ 1
  • the second rotating finning tool is provided with a second helical working profile having a second angle of advancement ⁇ 2 , with ⁇ 2 ⁇ 1 .
  • the method according to the present invention comprises advancing said tube on a plane defined by said support assembly, forming a first (temporary) fin/groove on said tube by means of said first rotating tool, forming a second (main) fin on said tube by means of said second rotating tool, the formation of said second fin being immediately subsequent to the formation of said first fin; moreover, the height of said first fin is generally lower than the height of said second fin.
  • the first angle of advancement ⁇ 1 will have the same value as the second angle of advancement ⁇ of said first (temporary) fin/groove
  • the second angle of advancement ⁇ 2 will have the same value as the first angle of advancement ⁇ of said second (main) fin.
  • the relative angle (rake angle) between said first angle of advancement ⁇ 1 and said second angle of advancement ⁇ 2 is advantageously between 0° and 90°, and preferably between 30° and 60°, Moreover, the first rotating finning/grooving tool and the second rotating finning tool are advantageously shaped so that the height h of said first fin is preferably ⁇ 0.5 mm and the height H of said second fin is preferably ⁇ 2 mm.
  • a finned tube for heat exchangers, in particular for shell and tube heat exchangers, obtained using the method described herein also forms the subject matter of the present invention
  • the finned tubes of the present invention are provided on at least a part of their outer surface with a plurality of low fins, which are helically arranged on the outer surface of said tube with a first angle of advancement ⁇ and have a profile interrupted by helical grooves having a second angle of advancement ⁇ , with ⁇ , said angle of advancement ⁇ being preferably ⁇ 80°, and more preferably 15° ⁇ ⁇ 60°, the relative angle between said first angle of advancement ⁇ and said second angle of advancement ⁇ being preferably between 0° and 90°, and more preferably between 30° and 60°, said low fins having a height H preferably ⁇ 2mm and more preferably between 0.5 and 1.5 mm.
  • a second fluid flows inside the tubes 2, generally in counterflow (see arrows 210) to the direction of flow of the first fluid inside the shell 101 (see arrows 110).
  • one of the peculiar characteristics of the shell and tube longitudinal flow heat exchanger 1 according to the present invention is given by the fact that said tubes 2 are provided on at least a part of their outer surface with a plurality of low fins 21 that are helically arranged on the outer surface of said tube 2 according to a first angle of advancement ⁇ .
  • This angle of advancement ⁇ is generally less than 80°, and preferably between 15° and 60°, more preferably between 20° and 45°.
  • a further peculiar characteristic of the shell and tube longitudinal flow heat exchanger 1 according to the present invention is given by the fact that the low fins 21 have a profile interrupted by helical grooves 22 having a second angle of advancement ⁇ , with ⁇ .
  • a first machining phase of the tube 2 allows the base of the tube to be lowered (by an amount h ) and raised (by the same amount h ) so as to produce a corrugated profile having helical fins 22 and corresponding helical grooves with angle of advancement ⁇ , as shown in Fig. 6b .
  • the height h with respect to the base profile is preferably less than 0.5 mm.
  • a second machining phase of the tube 2 allows the final fin 21 to be obtained by lowering (by an amount H) and raising (by the same amount H ) the corrugated profile of the tube 2 of Fig. 11a according to a helical machining operation with angle of advancement ⁇ (see Fig. 6a ).
  • the final structure of the fin 21, in terms of height and of number of interruptions, will thus depend on the composition of the two deformations, in particular on the amounts h and H, and on the angles ⁇ and ⁇ .
  • the relative angle between ⁇ and ⁇ is close to 0° the maximum increase in the height of the fin 21 will be obtained, while when it is close to 90° the maximum number of interruptions on the profile of the fin 21 due to the grooves 22 will be obtained.
  • Figs. 7a-7c show some possible sections of the fin 21, without being in any way limited to these embodiments.
  • the tubes 2 are provided with finned portions 20 alternated by smooth portions 200. In this way, also with reference to Fig. 15 , stable positioning of the baffle 102 will be facilitated.
  • a finned tube 2 provided on at least one part of its outer surface with a plurality of low fins 21.
  • These fins 21 are helically arranged on said outer surface with a first angle of advancement ⁇ and have a profile interrupted by helical grooves 22 having a second angle of advancement ⁇ .
  • the method according to the invention is carried out using a machine 3 comprising a working assembly 30 and at least one support assembly 40.
  • the first working assembly 30 comprises a first rotating finning/grooving tool 32 and a second rotating finning tool 31 mounted in sequence on the same driving axis 33.
  • the support assembly 40 comprises two smooth surface cylindrical guides 34 and 36, the purpose of which is to maintain the tube 2 in position during machining, supporting the thrust load of the working assembly 30.
  • the first rotating finning/grooving tool 32 is provided with a first helical working profile symmetrical to the helical grooves 22 to be generated on the outer surface of the tube 2 and that has a first angle of advancement ⁇ 1 .
  • the second rotating finning tool 31 is provided with a second helical working profile symmetrical to the low fins 21 to be generated on the outer surface of the tube 2 and that has a second angle of advancement ⁇ 2 , with ⁇ 2 ⁇ 1 .
  • the method according to the invention comprises advancing the tube 2 on a plane defined by the support assembly 40 and forming a first fin/groove 22 on said tube 2 by means of the first rotating tool 32.
  • the fin/groove 22 has a depth preferably ⁇ 0.5 mm to limit hardening of the material.
  • a second fin 21 (main fin) is formed on said tube 2 by means of said second rotating finning tool 31.
  • the height of said second main fin 21 is greater than the height of said first fin 22, even if it is normally less than 2mm.
  • a plurality of low fins are formed both on its outer surface and on its internal surface.
  • the method according to the invention is carried out using a machine 5 comprising a first working assembly 50 and a support assembly 70, similar to the first working assembly 30 and to the support assembly 40 described previously.
  • the machine 5 also comprises a second working assembly that is adapted to produce the internal fins of the tube 2.
  • the internal fin is obtained by means of a finning tool 61 with profile symmetrical to what is to be obtained on the internal surface of the tube 2.
  • the tool 61 is inserted into the tube and is "actuated” by the pressure exerted by the first 32 and second 31 rotating tool on the tube 2 resting on the smooth surface cylindrical guides 71 and 72 of the support assembly 70. This causes a reduction in the internal diameter of the tube 2, which is thus finned by the internal tool 61.
  • the internal fin has a wrap angle contrary to that of the external fin 21 so as to prevent the external or internal tool from binding. Angle of advancement, height of fin and density of fins on the internal part are obtainable in the ranges known in the state of the art.
  • the method described uses two profiled tools for external (or external and internal) cold forming of a tube made of low or high alloy steel.
  • This configuration allows high productivity, preventing the otherwise frequent risks of damage/breakage of the tools and reducing to a minimum the complexity of the mechanical apparatus employed. It is also suitable for machining alloy steels, such as copper-nickel, stainless, duplex, titanium steels, which are critical for many alternative methods, as known from the state of the art.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Agronomy & Crop Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
EP16810268.9A 2015-12-23 2016-11-25 Shell and tube heat exchanger, finned tubes for such heat exchanger and corresponding method Active EP3394550B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITUB2015A009298A ITUB20159298A1 (it) 2015-12-23 2015-12-23 Scambiatore di calore a fascio tubiero e mantello, tubi alettati per tale scambiatore e relativo metodo di produzione.
PCT/EP2016/078809 WO2017108330A1 (en) 2015-12-23 2016-11-25 Shell and tube heat exchanger, finned tubes for such heat exchanger and corresponding method

Publications (2)

Publication Number Publication Date
EP3394550A1 EP3394550A1 (en) 2018-10-31
EP3394550B1 true EP3394550B1 (en) 2023-04-05

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP16810268.9A Active EP3394550B1 (en) 2015-12-23 2016-11-25 Shell and tube heat exchanger, finned tubes for such heat exchanger and corresponding method

Country Status (9)

Country Link
US (2) US20180372427A1 (ko)
EP (1) EP3394550B1 (ko)
JP (1) JP2019502084A (ko)
KR (1) KR20180098304A (ko)
CN (1) CN108431538A (ko)
DK (1) DK3394550T3 (ko)
ES (1) ES2944546T3 (ko)
IT (1) ITUB20159298A1 (ko)
WO (1) WO2017108330A1 (ko)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108759184B (zh) * 2018-08-13 2024-05-10 珠海格力电器股份有限公司 冷凝管及冷凝器
CN109489456A (zh) * 2018-11-28 2019-03-19 江阴市森博特种换热设备有限公司 一种高换热效率的碳化硅列管换热器
CN110763047B (zh) * 2019-11-18 2024-11-15 中国恩菲工程技术有限公司 管壳式蒸发器
SI4248160T1 (sl) 2020-11-17 2025-03-31 Wieland-Werke Ag Prenosnik toplote s cevnim snopom
CN115397184B (zh) * 2021-05-25 2025-09-02 英业达科技有限公司 电子装置及散热组件

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GB1359647A (en) * 1971-10-12 1974-07-10 Dewandre Co Ltd C Heat transfer tubes
US4660630A (en) * 1985-06-12 1987-04-28 Wolverine Tube, Inc. Heat transfer tube having internal ridges, and method of making same
US5141049A (en) * 1990-08-09 1992-08-25 The Badger Company, Inc. Treatment of heat exchangers to reduce corrosion and by-product reactions
CN1084876C (zh) * 1994-08-08 2002-05-15 运载器有限公司 传热管
DE69525594T2 (de) * 1994-11-17 2002-08-22 Carrier Corp., Syracuse Wärmeaustauschrohr
US5697430A (en) * 1995-04-04 1997-12-16 Wolverine Tube, Inc. Heat transfer tubes and methods of fabrication thereof
US5933953A (en) * 1997-03-17 1999-08-10 Carrier Corporation Method of manufacturing a heat transfer tube
CA2230213C (en) * 1997-03-17 2003-05-06 Xin Liu A heat transfer tube and method of manufacturing same
US6176302B1 (en) * 1998-03-04 2001-01-23 Kabushiki Kaisha Kobe Seiko Sho Boiling heat transfer tube
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US6176301B1 (en) * 1998-12-04 2001-01-23 Outokumpu Copper Franklin, Inc. Heat transfer tube with crack-like cavities to enhance performance thereof
CN100437011C (zh) * 2005-12-13 2008-11-26 金龙精密铜管集团股份有限公司 一种电制冷机组用满液式铜蒸发换热管
DE102006008083B4 (de) * 2006-02-22 2012-04-26 Wieland-Werke Ag Strukturiertes Wärmeaustauscherrohr und Verfahren zu dessen Herstellung

Also Published As

Publication number Publication date
KR20180098304A (ko) 2018-09-03
US20180372427A1 (en) 2018-12-27
CN108431538A (zh) 2018-08-21
DK3394550T3 (da) 2023-05-01
EP3394550A1 (en) 2018-10-31
ES2944546T3 (es) 2023-06-22
JP2019502084A (ja) 2019-01-24
ITUB20159298A1 (it) 2017-06-23
WO2017108330A1 (en) 2017-06-29
US20210033351A1 (en) 2021-02-04

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