EP3581871A1 - Tuyau d'échange thermique métallique - Google Patents

Tuyau d'échange thermique métallique Download PDF

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Publication number
EP3581871A1
EP3581871A1 EP19000245.1A EP19000245A EP3581871A1 EP 3581871 A1 EP3581871 A1 EP 3581871A1 EP 19000245 A EP19000245 A EP 19000245A EP 3581871 A1 EP3581871 A1 EP 3581871A1
Authority
EP
European Patent Office
Prior art keywords
rib
heat exchanger
fin
exchanger tube
metallic heat
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
EP19000245.1A
Other languages
German (de)
English (en)
Other versions
EP3581871B1 (fr
Inventor
Achim Gotterbarm
Jean El Hajal
Jochen Dietl
Andreas Schwitalla
Ronald Lutz
Martin Weixler
Manfred Knab
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
Original Assignee
Wieland Werke AG
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 filed Critical Wieland Werke AG
Priority to PL19000245T priority Critical patent/PL3581871T3/pl
Publication of EP3581871A1 publication Critical patent/EP3581871A1/fr
Application granted granted Critical
Publication of EP3581871B1 publication Critical patent/EP3581871B1/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
    • F28F1/26—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 integral with 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
    • 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
    • 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

Definitions

  • the invention relates to a metallic heat exchanger tube with ribs running around the outside of the tube according to the preamble of claim 1.
  • Metallic heat exchanger tubes of this type are used in particular for the evaporation of liquids from pure substances or mixtures on the outside of the tube.
  • Shell and tube heat exchangers are often used, in which liquids of pure substances or mixtures evaporate on the outside of the tube and thereby cool down brine or water on the inside of the tube. Such devices are referred to as flooded evaporators.
  • the size of the evaporators can be greatly reduced by intensifying the heat transfer on the inside or outside of the tube. As a result, the manufacturing costs of such apparatus decrease. In addition, the required amount of refrigerant drops, which can make up a not insignificant share of the total system costs with the chlorine-free safety refrigerants that are mainly used today. In the case of toxic or flammable refrigerants, the risk potential can also be reduced by reducing the filling quantity. Today's high-performance pipes are already four times more powerful than smooth pipes of the same diameter.
  • Integrally rolled finned tubes are understood to mean finned tubes in which the fins are made of the wall material a smooth tube were formed.
  • Various methods are known with which the channels located between adjacent ribs are closed in such a way that connections between the channel and the environment remain in the form of pores or slots.
  • such essentially closed channels are formed by bending or folding the ribs ( US 3,696,861 A ; US 5,054,548 A ; US 7 178 361 B2 ), by splitting and compressing the ribs ( DE 27 58 526 C2 ; US 4,577,381 A ) and by notching and compressing the ribs ( US 4,660,630 A ; EP 0 713 072 B1 ; US 4,216,826 A ) generated.
  • the most powerful, commercially available finned tubes for flooded evaporators have a finned structure on the outside of the tube with a fin density of 55 to 60 fins per inch ( US 5,669,441 A ; US 5 697 430 A ; DE 197 57 526 C1 ). This corresponds to a rib pitch of approximately 0.45 to 0.40 mm.
  • a smaller rib division inevitably requires equally fine tools.
  • finer tools are subject to a higher risk of breakage and faster wear.
  • the tools currently available enable the safe production of finned tubes with fin densities of up to 60 fins per inch. Furthermore, as the fin pitch decreases, the production speed of the pipes becomes slower, and consequently the manufacturing costs become higher.
  • These inventions have in common that the structural elements on the base of the groove do not have an undercut shape, which is why they do not intensify the formation of bubbles sufficiently.
  • EP 1 223 400 B1 and WO 2014/072 047 A1 It is proposed to produce undercut secondary grooves at the bottom of the groove, which extend continuously along the primary groove. The cross section of these secondary grooves can remain constant or can be varied at regular intervals.
  • WO 2014/072 046 A1 It is proposed to create pyramid-like undercut structural elements on the bottom of the groove between the ribs, which are arranged at regular intervals along the primary groove.
  • the invention has for its object to provide a performance-enhanced heat exchanger tube for the evaporation of liquids on the outside of the tube.
  • the invention includes a metallic heat exchanger tube comprising a tube wall and fins surrounding the tube outer side, which have a fin base, fin flanks and a fin tip, and a primary groove formed between the fins, the fin foot projecting essentially radially from the tube wall, and along the fin flanks the primary groove are provided with additional structural elements spaced apart from one another, which are formed as material projections formed from the material of the rib flank and arranged laterally on the rib flank.
  • the material projections are deformed in such a way that they touch the tube wall in the area of the primary groove, so that local cavities are formed.
  • the cavities have openings in the circumferential direction of the ribs.
  • the invention is based on the consideration that to increase the heat transfer during evaporation, the process of bubble boiling is intensified.
  • the formation of bubbles begins at the germ sites. These germ sites are mostly small gas or vapor inclusions. When the growing bubble has reached a certain size, it detaches from the surface. If the germ site were flooded with liquid in the course of the bubble detachment, the germ site is deactivated.
  • the surface must therefore be designed in such a way that a small bubble remains when the bubble is detached, which then serves as the nucleus for a new cycle of bubble formation. This is achieved by forming local cavities on the surface which have openings in the circumferential direction of the ribs. The liquid and vapor are exchanged through the opening.
  • a cavity is formed from material of the rib flank which, shaped like a chip, contacts the tube wall in the area of the primary groove as a material projection.
  • it is the front edge, i.e. the area of a material projection that is the most distant from the rib flank in the course of the curvature.
  • the deformed material projections have a point on the front, the front edges of which, or the surface portions immediately connected to these front edges by a conceivable rolling process in the manufacturing process, can come into contact with the tube wall in the region of the primary groove.
  • a cavity is consequently formed from the material projection and the rib foot remaining radially within the material projection and the region of the primary groove adjoining the rib foot until the material projection contacts.
  • the material projections are particularly preferably on both sides of the ribs arranged.
  • the length of the areas in the circumferential direction between two cavities can be between 0.2 mm and 0.5 mm. In this way, optimal coordination of the successive cavities and the areas in between is achieved.
  • the rib tips can be deformed in such a way that they cover and partially close off the primary grooves in the radial direction and thus form a helically surrounding, partially closed cavity.
  • the rib tips can, for example, have an essentially T-shaped cross section with pore-like recesses through which the vapor bubbles can escape.
  • the particular advantage of the invention is that the effect of a cavity on the formation of bubbles is particularly great if the exchange of liquid and vapor is controlled in a targeted manner and the flooding of the bladder germ site in the cavity is prevented.
  • the position of the cavities in the vicinity of the primary groove base is particularly favorable for the evaporation process, since the excess temperature is greatest at the groove base and therefore the highest driving temperature difference is available there for the formation of bubbles.
  • the cavities can form a cylindrical cavity.
  • the material projections can deform increasingly with increasing distance from the rib flank, so that they curl up to the point of contact with the tube wall and a cylindrical tube is thereby formed.
  • a cylinder-like cavity has two openings of essentially the same type in the circumferential direction of the ribs, via which a bubble germ supports the evaporation process of a fluid.
  • the maximum clear width of a cavity can advantageously be a maximum of half the longitudinal extent of the cavity.
  • elongated cavities are formed, which represent bladder germ sites particularly efficiently and contribute to an increase in the heat transfer during evaporation.
  • the bubble growing out of the elongated cavity has reached a certain size, it detaches from the surface. After detachment, the elongated tube as the germ site is only partially flooded with liquid, which means that the germ site remains constantly activated.
  • the dimension of the cavity is consequently designed such that when a bubble is detached, a small bubble remains, which then serves as the nucleus for a new cycle of bubble formation.
  • fluid guide structures can be arranged on the rib flanks between the cavities.
  • the bubbles formed in the evaporation process preferably originate in the cavities opened in the circumferential direction of the ribs, and the liquid flows through the fluid guide structures preferably radially along the rib flank near the closed regions of the cavity.
  • the escaping bladder is not hindered by the inflowing liquid working medium and can expand undisturbed in the primary groove.
  • the respective flow zones for the liquid and the vapor are ideally spatially separated from one another.
  • fluid guide structures can be arranged which extend from one cavity to the cavity adjacent in the circumferential direction of the ribs.
  • the liquid flows particularly radially along the rib flank.
  • the escaping bubble is not hindered by the inflowing liquid working medium and can expand in the primary groove until it detaches.
  • the respective flow zones for the liquid and for the vapor are spatially separated by the fluid guide structures.
  • the fluid guide structures on the rib flanks can extend in a raised arc segment rising towards the rib tip. Through such fluid guide structures, the fluid is led to the cavities as bubble nuclei for evaporation.
  • the fluid guide structures on the rib flanks can advantageously extend in the radial direction as raised fluid guide surfaces.
  • Raised fluid guiding surfaces can, due to comparatively sharp edges and the wetting behavior of the liquid fluid, be particularly effective for mass transport on the heat exchanger tube and thus for efficient heat exchange.
  • a fluid guide surface can end directed radially inwards at or in the immediate vicinity of a cavity. Structures of this type ensure targeted fluid guidance and thus efficient heat dissipation on the outside of the pipe.
  • a fluid guide surface can advantageously end radially outwards at or in the immediate vicinity of the rib tip.
  • the liquid fluid is already guided radially in the direction of the tube wall for heat exchange along the fin flanks.
  • the fluid-guiding structures on the rib flanks can extend outward in the radial direction up to a maximum of half the rib height.
  • the rib tip can be designed to be extremely narrow, as a result of which, in the radially inward direction, a rib only has a sufficient width and thus sufficient material in the central part and in the region of the rib foot in order to form a material projection from the flank.
  • Fig. 1 shows a perspective partial view of a rib section of a heat exchanger tube 1 with four material projections 4. From the tube outer side 21, only a part of the circumferential, integrally formed ribs 3 is shown.
  • the ribs 3 have a rib base 31 which attaches to the tube wall 2, rib flanks 32 and a rib tip 33.
  • the rib 3 projects essentially radially from the tube wall 2.
  • the rib flanks 32 are provided with additional structural elements which are designed as material projections 4 which attach laterally to the rib flank 32.
  • the material projections 4 have front ends 41 which touch the tube wall 2 in the region of the primary groove 34.
  • cavities 5 form, which are in the circumferential direction U of the ribs Have openings 51, 52.
  • Such cavities 5 preferably form bubble nuclei in the evaporation process of a fluid, which promote heat exchange.
  • the boundary surfaces of the material projections 4 are convexly curved on the side facing away from the tube wall 2. In principle, however, with each material projection 4, other boundary surfaces can also be provided with a convex curvature. The remaining, non-convex boundary surfaces can either be flat or concave.
  • the material of the integrally worked-out material projections 4 comes from the fin flank 32, with recesses 42 additionally being formed in the fin flank 32 due to a material shift during the manufacture of the heat exchanger tubes 1.
  • Fig. 2 shows a detailed view of a material projection 4 with a curved boundary surface and a tip 41 which touches the tube wall 2 in the region of the primary groove 34.
  • the cavity 5 formed from the rib base 31 and the inside of the material projections 4 has an approximately cylindrical cavity.
  • the maximum clear width x 1 of a cavity 5 is considerably smaller than the longitudinal extension x 2 of the cavity 5. This creates elongated cavities which form bubble nuclei particularly efficiently and contribute to an increase in the heat transfer during evaporation.
  • the dimension of the cavity is consequently designed such that when a bubble is detached in the evaporation process, a small bubble residue remains, which then serves as a nucleus for a new cycle of bubble formation.
  • liquid fluid is preferably accumulated in the area of the recess 42, as a result of which there is increasingly liquid in the area of the bladder germ, which is available for evaporation.
  • the structural size of the material projections 4 and thus also the cavities 5 are typically in the submillimeter range.
  • Fig. 3 shows a perspective partial view of a rib section of a heat exchanger tube 1 with material projections 4 and raised fluid guide structures 6. From the tube outer side 21, in turn, only part of one of the circumferential, integrally formed ribs 3 is shown.
  • the ribs 3 have a rib foot 31 which attaches to the tube wall 2, rib flanks 32 and a rib tip 33.
  • the ribs 3 protrude radially from the tube wall 2.
  • the rib flanks 32 are provided with additional structural elements which are designed as material projections 4.
  • the fluid guide structures 6 formed formed essentially extend in the axial and radial directions of the tube 1.
  • Fig. 3 two fluid guide surfaces 62 are assigned to each of the material projections 4.
  • the fluid guide surfaces 62 are brought radially from the outside to the material projections 4.
  • the surface of the tube 1 is enlarged by the fluid guide structures 6.
  • the edges of the fluid guide surfaces 62 facing away from the rib flank 32 represent convex edges, on which the liquid fluid is preferably collected and directed to the cavity 5.
  • Fluid guide surfaces 62 shown are flat surfaces. However, surfaces of this type can also be curved in themselves or also assume a wavy shape.
  • the axial extent of the fluid guiding surfaces 62 is smaller than the axial extent of the material projections 4. This results in pocket-like structures as recesses 42 on the rib flank 32. Consequently, in the case of a heat exchanger tube 1 designed in this way, liquid fluid can also collect in the pocket-like structures 42 are available for the evaporation process.
  • the surface of the tube 1 is thus specifically covered with liquid fluid. This favors the Evaporation process, which increases the performance of the pipe.
  • Fig. 4 shows a perspective partial view of a fin section of a heat exchanger tube 1 with a plurality of material projections 4. From the tube outer side 21, in turn, only a part of the circumferential, integrally formed fins 3 is shown.
  • the material of the integrally worked-out material projections 4 originates primarily from the rib flank 32, recesses 42 being produced by a material shift during the manufacture of the heat exchanger tubes 1.
  • fluid guide structures 6 run as arc segments 61, which rise on the rib flanks 32 0 toward the rib tip.
  • Such fluid guide structures 6 consequently extend from a cavity 5 to the cavity 5 adjacent in the circumferential direction of the ribs 3. As a result, the liquid flows particularly efficiently radially along the rib flank 32 to the cavity 5.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (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)
EP19000245.1A 2018-06-12 2019-05-17 Tuyau d'échange thermique métallique Active EP3581871B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL19000245T PL3581871T3 (pl) 2018-06-12 2019-05-17 Metalowa rura wymiennika ciepła

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102018004701.7A DE102018004701A1 (de) 2018-06-12 2018-06-12 Metallisches Wärmeaustauscherrohr

Publications (2)

Publication Number Publication Date
EP3581871A1 true EP3581871A1 (fr) 2019-12-18
EP3581871B1 EP3581871B1 (fr) 2020-06-24

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ID=66624947

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19000245.1A Active EP3581871B1 (fr) 2018-06-12 2019-05-17 Tuyau d'échange thermique métallique

Country Status (5)

Country Link
EP (1) EP3581871B1 (fr)
DE (1) DE102018004701A1 (fr)
HU (1) HUE051946T2 (fr)
PL (1) PL3581871T3 (fr)
PT (1) PT3581871T (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN118149627A (zh) * 2024-05-11 2024-06-07 浙江银轮机械股份有限公司 换热装置、逆变器冷却系统及变流器冷却系统

Citations (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3696861A (en) 1970-05-18 1972-10-10 Trane Co Heat transfer surface having a high boiling heat transfer coefficient
US4216826A (en) 1977-02-25 1980-08-12 Furukawa Metals Co., Ltd. Heat transfer tube for use in boiling type heat exchangers and method of producing the same
DE2758526C2 (de) 1977-12-28 1986-03-06 Wieland-Werke Ag, 7900 Ulm Verfahren und Vorrichtung zur Herstellung eines Rippenrohres
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
EP0222100A2 (fr) 1985-10-31 1987-05-20 Wieland-Werke Ag Tube à ailettes à fond de rainure muni d'encoches et son procédé de fabrication
US5054548A (en) 1990-10-24 1991-10-08 Carrier Corporation High performance heat transfer surface for high pressure refrigerants
US5186252A (en) 1991-01-14 1993-02-16 Furukawa Electric Co., Ltd. Heat transmission tube
EP0713072A2 (fr) 1994-11-17 1996-05-22 Carrier Corporation Tube de transfert de chaleur
US5697430A (en) 1995-04-04 1997-12-16 Wolverine Tube, Inc. Heat transfer tubes and methods of fabrication thereof
DE19757526C1 (de) 1997-12-23 1999-04-29 Wieland Werke Ag Verfahren zur Herstellung eines Wärmeaustauschrohres, insbesondere zur Verdampfung von Flüssigkeiten aus Reinstoffen oder Gemischen auf der Rohraußenseite
EP1223400A2 (fr) 2001-01-16 2002-07-17 Wieland-Werke AG Tube d'échangeur de chaleur et son procédé de fabrication
US20070034361A1 (en) * 2005-08-09 2007-02-15 Jiangsu Cuilong Copper Industry Co., Ltd. Heat transfer tubes for evaporators
US7178361B2 (en) 2002-04-19 2007-02-20 Wolverine Tube, Inc. Heat transfer tubes, including methods of fabrication and use thereof
US20070151715A1 (en) 2005-12-13 2007-07-05 Hao Yunyu A flooded type evaporating heat-exchange copper tube for an electrical refrigeration unit
JP4039596B2 (ja) 1998-10-06 2008-01-30 株式会社サンセイアールアンドディ パチンコ遊技機
EP2253922A2 (fr) * 2009-05-14 2010-11-24 Wieland-Werke AG Tuyau d'échange thermique métallique
WO2013087140A1 (fr) * 2011-12-16 2013-06-20 Wieland-Werke Ag Tubes de condenseur avec structure de flanc supplémentaire
WO2014072046A1 (fr) 2012-11-12 2014-05-15 Wieland-Werke Ag Tube de transfert de chaleur par évaporation doté d'une cavité creuse
WO2014072047A1 (fr) 2012-11-12 2014-05-15 Wieland-Werke Ag Tube de transfert de chaleur par évaporation

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE559831A (fr) * 1956-08-06
JP2854751B2 (ja) * 1992-03-12 1999-02-03 株式会社神戸製鋼所 熱交換器用伝熱管の製造方法

Patent Citations (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3696861A (en) 1970-05-18 1972-10-10 Trane Co Heat transfer surface having a high boiling heat transfer coefficient
US4216826A (en) 1977-02-25 1980-08-12 Furukawa Metals Co., Ltd. Heat transfer tube for use in boiling type heat exchangers and method of producing the same
DE2758526C2 (de) 1977-12-28 1986-03-06 Wieland-Werke Ag, 7900 Ulm Verfahren und Vorrichtung zur Herstellung eines Rippenrohres
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
EP0222100A2 (fr) 1985-10-31 1987-05-20 Wieland-Werke Ag Tube à ailettes à fond de rainure muni d'encoches et son procédé de fabrication
US5054548A (en) 1990-10-24 1991-10-08 Carrier Corporation High performance heat transfer surface for high pressure refrigerants
US5186252A (en) 1991-01-14 1993-02-16 Furukawa Electric Co., Ltd. Heat transmission tube
EP0713072A2 (fr) 1994-11-17 1996-05-22 Carrier Corporation Tube de transfert de chaleur
US5669441A (en) 1994-11-17 1997-09-23 Carrier Corporation Heat transfer tube and method of manufacture
US5697430A (en) 1995-04-04 1997-12-16 Wolverine Tube, Inc. Heat transfer tubes and methods of fabrication thereof
DE19757526C1 (de) 1997-12-23 1999-04-29 Wieland Werke Ag Verfahren zur Herstellung eines Wärmeaustauschrohres, insbesondere zur Verdampfung von Flüssigkeiten aus Reinstoffen oder Gemischen auf der Rohraußenseite
JP4039596B2 (ja) 1998-10-06 2008-01-30 株式会社サンセイアールアンドディ パチンコ遊技機
EP1223400A2 (fr) 2001-01-16 2002-07-17 Wieland-Werke AG Tube d'échangeur de chaleur et son procédé de fabrication
US7178361B2 (en) 2002-04-19 2007-02-20 Wolverine Tube, Inc. Heat transfer tubes, including methods of fabrication and use thereof
US20070034361A1 (en) * 2005-08-09 2007-02-15 Jiangsu Cuilong Copper Industry Co., Ltd. Heat transfer tubes for evaporators
US20070151715A1 (en) 2005-12-13 2007-07-05 Hao Yunyu A flooded type evaporating heat-exchange copper tube for an electrical refrigeration unit
EP2253922A2 (fr) * 2009-05-14 2010-11-24 Wieland-Werke AG Tuyau d'échange thermique métallique
WO2013087140A1 (fr) * 2011-12-16 2013-06-20 Wieland-Werke Ag Tubes de condenseur avec structure de flanc supplémentaire
WO2014072046A1 (fr) 2012-11-12 2014-05-15 Wieland-Werke Ag Tube de transfert de chaleur par évaporation doté d'une cavité creuse
WO2014072047A1 (fr) 2012-11-12 2014-05-15 Wieland-Werke Ag Tube de transfert de chaleur par évaporation

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN118149627A (zh) * 2024-05-11 2024-06-07 浙江银轮机械股份有限公司 换热装置、逆变器冷却系统及变流器冷却系统

Also Published As

Publication number Publication date
PT3581871T (pt) 2020-08-28
EP3581871B1 (fr) 2020-06-24
DE102018004701A1 (de) 2019-12-12
HUE051946T2 (hu) 2021-03-29
PL3581871T3 (pl) 2020-12-14

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