EP4237782A1 - Tube métallique d'échangeur de chaleur - Google Patents

Tube métallique d'échangeur de chaleur

Info

Publication number
EP4237782A1
EP4237782A1 EP21797938.4A EP21797938A EP4237782A1 EP 4237782 A1 EP4237782 A1 EP 4237782A1 EP 21797938 A EP21797938 A EP 21797938A EP 4237782 A1 EP4237782 A1 EP 4237782A1
Authority
EP
European Patent Office
Prior art keywords
projections
channel
heat exchanger
rib
exchanger tube
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
EP21797938.4A
Other languages
German (de)
English (en)
Other versions
EP4237782B1 (fr
Inventor
Achim Gotterbarm
Manfred Knab
Ronald Lutz
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
Publication of EP4237782A1 publication Critical patent/EP4237782A1/fr
Application granted granted Critical
Publication of EP4237782B1 publication Critical patent/EP4237782B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F28F1/42—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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins

Definitions

  • the invention relates to a metallic heat exchanger tube according to the preamble of claim 1.
  • Tube bundle heat exchangers are often used in which liquids of pure substances or mixtures evaporate on the outside of the tube and brine or water cools down on the inside of the tube.
  • the size of the evaporator can be greatly reduced by intensifying the heat transfer on the outside and inside of the tube. This reduces the manufacturing costs of such devices.
  • the amount of refrigerant required is reduced, which can make up a non-negligible proportion of the total system costs with the chlorine-free safety refrigerants that are now predominantly used.
  • the high-performance pipes commonly used today are around four times more powerful than smooth pipes of the same diameter.
  • EP 1 223400 B1 proposes producing undercut secondary grooves on the groove base between the ribs, which extend continuously along the primary groove.
  • the cross-section of these secondary grooves can remain constant or be varied at regular intervals.
  • the object of the invention is to further develop a performance-enhanced heat exchanger tube for evaporating liquids on the outside of the tube.
  • the invention includes a metallic heat exchanger tube with integral ribs formed on the outside of the tube with a rib foot, rib flanks and rib tip, the rib foot protruding radially from the tube wall and a channel with a channel base being formed between the ribs, in which additional structures spaced apart from one another are arranged.
  • the additional structures divide the channel between the ribs into segments.
  • the additional structures locally reduce the cross-sectional area through which flow can take place in the channel between two ribs and thereby at least limit a fluid flow in the channel during operation.
  • First additional structures are radially outwardly directed projections starting from the channel base, which are delimited in the radial direction by a closing surface located between the channel base and the rib tip, as a result of which a radial extent of the projections is defined.
  • material projections are arranged radially outwards as second additional structures, which are formed from material of the rib flanks.
  • the material projections are each arranged in the radial direction between an end surface and the tip of the rib, so that the material projections are formed lying laterally on the rib flank around the radial extent of the projections above the channel base of the channel.
  • the material projections extend further in the axial and radial directions than in the circumferential direction.
  • These metallic heat exchanger tubes are used in particular for evaporating liquids from pure substances or mixtures on the outside of the tube.
  • Such high-performance tubes can be manufactured on the basis of integrally rolled finned tubes using rolling discs.
  • integrally rolled Finned tubes are understood to mean finned tubes in which the fins were formed from the wall material of a plain tube.
  • Typical integral ribs formed on the outside of the tube are, for example, spirally circumferential and have a rib foot, rib flanks and rib tip, with the rib foot protruding essentially radially from the tube wall. The number of ribs is determined by counting consecutive bulges in the axial direction of a tube.
  • the structures according to the invention can be produced by a sharp-edged, toothed rolling disk, which deforms both the wall material on the channel base and the material on the rib flanks in the axial and radial directions.
  • the invention is based on the consideration that, in order to increase the heat transfer during evaporation, the space between the ribs is segmented by additional structures. This generates local overheating in the gaps and intensifies the nucleate boiling process. The formation of bubbles then takes place primarily within the segments and begins at nucleation sites. Small gas or vapor bubbles initially form at these nucleation sites. When the growing bubble reaches a certain size, it detaches from the surface. As the bubbles detach, the remaining cavity in the segment is flooded with liquid again and the cycle begins again.
  • the surface can be designed in such a way that when the bubble is detached, a small bubble remains, which then serves as the nucleus for a new cycle of bubble formation.
  • further material projections are located in the area of the first additional structures in the form of radially outwardly directed projections as second additional structures.
  • the material projections are arranged laterally on the rib flank and extend essentially in the axial and radial direction. From the manufacturing process by means of rolling, the material projections are formed from material of the rib flanks, which lie radially outwards and are preferably placed directly on the projections. In the structures formed by the material projections, the flow of liquid heat exchanger fluid into the adjacent segments is promoted, quasi from the side. Such a fluid guidance thus makes a contribution to the formation of bubbles in the segment.
  • the projections can extend between the respective rib foot of adjacent ribs in the axial direction over the entire channel base or only over part of the channel base. They represent a sort of barrier running between two ribs, starting from the bottom of the channel, which extends radially outwards and at least partially closes the channel in the circumferential direction.
  • material projections according to the invention placed on a preferably massive projection of the basic duct structure are formed as second additional structures from material of the rib flank and essentially form a flowing transition in the radial direction to the two side surfaces of the projection below.
  • These consequently represent a fluid guide structure, which guides liquid fluid into the segments from the side, as it were.
  • An end surface of the projections arranged radially on the outside can extend over the entire width of the channel.
  • liquid fluid can be exchanged between adjacent segments and can also get from one segment into an adjacent segment.
  • the cantilevers with The attached material protrusions therefore represent a threshold for the passage of fluid.
  • the material projections can also have a smaller extent in the axial direction than that of the projections arranged underneath. Due to the size, shape and alignment of the material projections, the wetting behavior of the heat exchanger fluid is primarily the cause of an increase in fluid flow.
  • the contour line of the material projections which extend essentially in the axial and radial directions, can also be designed to be curved or irregular.
  • this type of segmentation of the channel between two ribs repeatedly interrupts it in the circumferential direction and thus at least reduces or completely prevents the bubbles that form in the channel from migrating.
  • An exchange of liquid and vapor along the channel is increasingly supported less or not at all by the respective additional structure.
  • the particular advantage of the invention is that the exchange of liquid and vapor is controlled locally in a targeted manner and the flooding of the bubble nucleation point in the segment takes place locally and in particular through the material projections from the side.
  • the evaporator tube structures can be optimized in a targeted manner depending on the application parameters through a targeted selection of the channel segmentation, whereby an increase in the heat transfer is achieved. Since the temperature at the base of the rib is higher in the area of the bottom of the groove than at the tip of the rib, structural elements are also particularly effective for intensifying the formation of bubbles in the bottom of the groove.
  • the additional structures locally reduce the cross-sectional area through which flow can take place in the channel between two ribs. All in all the evaporator tube structures can be further optimized to increase the heat transfer by increasing the separation of individual channel sections during channel segmentation, depending on the application parameters.
  • the projections and the material projections can flow through the cross-sectional area in
  • the projections and the material projections can locally reduce the flow cross-sectional area in the channel between two ribs by 40 to 70%.
  • the channel section located between two segments forms a significant threshold on the fluid side in relation to adjacent channel sections.
  • the channel can be closed radially outwards except for individual local openings.
  • the ribs can have an essentially T-shaped or T-shaped cross section, as a result of which the channel between the ribs is closed except for pores as local openings. The vapor bubbles created during the evaporation process can escape through these openings.
  • the rib tips are deformed using methods that can be found in the prior art.
  • the rib tips can also be folded over in the axial direction or even shaped to a certain extent in the direction of the bottom of the channel.
  • the channel can therefore also consist of a combination of several complementing structural elements from below and the side and/or from above to the desired extent tapered until completely closed. In any case, in such a way that the channel between the ribs is divided into discrete segments.
  • the combination of the segments according to the invention with a channel which is closed except for pores or slits results in a structure which has a very high performance in the evaporation of liquids over a very wide range of operating conditions.
  • the heat transfer coefficient of the structure reaches a consistently high level.
  • This minimum requirement also ensures that gas bubbles that form in a channel segment during the evaporation process can escape to the outside.
  • the size and shape of the local openings are such that liquid medium can also pass through and flow into the channel section. Consequently, in order for the vaporization process to be sustained at a local opening, the same amounts of liquid and vapor must be transported through the opening in opposite directions to each other. Liquids that wet the pipe material well are usually used. Due to the capillary effect, such a liquid can enter the channels through any opening in the outer surface of the tube, even against an overpressure.
  • the quotient of the number of local openings to the number of segments can be 1:1 to 6:1. More preferably, this quotient can be 1:1 to 3:1.
  • the channels located between the ribs are essentially closed by the material of the upper rib areas, with the cavities thus created in the channel segments being connected to the surrounding space by openings.
  • These openings can also be called pores be designed, which can be designed in the same size or in two or more size classes. In the case of a ratio in which several local openings are formed on one segment, pores with two size classes can be particularly suitable. According to a regular, repeating scheme along the channels, for example, every small opening is followed by a large opening. This structure creates a directed flow in the channels.
  • Liquid is drawn preferentially through the small pores with the assistance of capillary pressure and wets the channel walls, creating thin films.
  • the vapor accumulates in the center of the channel and escapes at the points with the lowest capillary pressure.
  • the large pores must be dimensioned in such a way that the steam can escape quickly enough and the channels do not dry out.
  • the size and frequency of the vapor pores in relation to the smaller liquid pores must then be coordinated.
  • the projections can be formed as the first additional structures at least from material of the channel base between two integrally surrounding ribs.
  • a projection can also consist of material from the rib flank. The segmentation of the channel from a uniform material of the channel base is particularly favorable for the evaporation process.
  • the projections as the first additional structures, can have a height of between 0.15 and 1 mm.
  • This dimensioning of the additional structures is particularly well matched to the high-performance finned tubes and expresses the fact that the structure sizes of the outer structures are preferably in the sub-millimetre to millimeter range.
  • the projections can have asymmetrical shapes.
  • the asymmetry of the structures appears in a sectional plane running perpendicular to the longitudinal axis of the pipe. Asymmetric shapes can make an additional contribution to the evaporation process, especially if a larger surface area is formed.
  • the asymmetry can be pronounced both in the case of additional structures at the base of the canal and at the tip of the rib.
  • the projections can have a trapezoidal cross section in a sectional plane running perpendicular to the longitudinal axis of the pipe.
  • trapezoidal cross-sections are structural elements that are technologically easy to control. Slight production-related asymmetries of the otherwise parallel base sides of a trapezoid can occur here.
  • opposite material projections can be formed at the location of the projections in the direction of the longitudinal axis of the pipe.
  • the overhangs with the opposing material projections therefore represent the threshold for the passage of fluid.
  • FIG. 1 shows a schematic partial view of a cross section of a heat exchanger tube with segments subdivided by additional structures
  • FIG. 2 shows a schematic oblique view of part of the outer structure of a heat exchanger tube with fin tips folded over
  • 3 shows a schematic detailed view of material projections at the location of a projection
  • 4 shows a schematic detail view of a further embodiment of material projections at the location of a projection
  • FIG. 5 schematically shows an oblique view of a part of the outer structure of a heat exchanger tube with opposite material projections at the location of a projection.
  • Fig. 1 schematically shows a partial view of a cross section of a heat exchanger tube 1 according to the invention with segments 8 divided by additional structures 7.
  • the integrally rolled heat exchanger tube 1 has helically circumferential ribs 2 on the outside of the tube, between which a primary groove as channel 6 is formed.
  • the ribs 2 continuously extend along a helix line on the outside of the tube without interruption.
  • the rib base 3 protrudes essentially radially from the pipe wall 10 .
  • the fin height H is measured on the finished heat exchanger tube 1 from the deepest point of the channel base 61 starting from the fin base 3 across the fin flank 4 to the fin tip 5 of the fully formed finned tube.
  • a heat exchanger tube 1 is proposed, in which in the region of the channel base 61, an additional structure 7 in the form of radially outwardly directed projections 71 is arranged, which are each delimited in the radial direction by a terminal surface 713 located between the channel base 61 and the rib tip 5 .
  • These projections 71 are referred to as the first additional structure and are formed from the material of the pipe wall 10 from the bottom 61 of the duct.
  • the projections 71 are preferably arranged at regular intervals in the channel base 61 and extend transversely to the course of the channel from a rib foot 3 of a rib 2 at least partially in the direction or completely to the area above it, which is not shown in the plane of the figure lying nearest rib foot.
  • material projections 72 are arranged radially outwards as a second additional structure 7 , which are formed from material of the rib flanks 4 .
  • the material projections 72 are each arranged in the radial direction between an end surface 713 and the rib tip 5 so that the material projections 72 are formed lying laterally on the rib flank 4 around the radial extension of the projections 71 above the channel base 61 of the channel 6 .
  • the material projections 72 extend further in the axial and radial directions than in the circumferential direction. In this way, the primary groove as channel 6 is at least partially tapered at regular intervals.
  • the resulting segment 8 favors bubble nucleation in connection with the material projections 72 as guiding structures for the fluid flow in a special way.
  • the direct exchange of liquid and vapor between the individual segments 8 is at least reduced.
  • the rib tips 5 as the distal area of the ribs 2 are expediently deformed in such a way that they partially close the channel 6 in the radial direction with an axially folded rib tip 51.
  • the connection between the channel 6 and the environment is designed in the form of pores 9 as local openings so that vapor bubbles can escape from the channel 6.
  • the rib tips 5 are deformed using rolling methods which can be found in the prior art.
  • the primary grooves 6 represent undercut grooves in this way.
  • segment 8 in the form of a cavity, which is also characterized in that it has a very has high performance in evaporating liquids.
  • the liquid evaporates within segment 8, supported by material projections 72 as additional fluid conducting structures.
  • the resulting vapor escapes from the channel 6 at the local openings 9, through which liquid fluid also flows.
  • Well-wettable pipe surfaces can also be of help for the subsequent flow of the fluid.
  • the solution according to the invention relates to structured tubes in which the heat transfer coefficient on the outside of the tube is increased.
  • the heat transfer coefficient on the inside can also be intensified by suitable internal structuring 11 .
  • the heat exchanger tubes 1 for tube bundle heat exchangers usually have at least one structured area and smooth end pieces and possibly smooth intermediate pieces. The smooth end and intermediate pieces delimit the structured areas. So that the heat exchanger tube 1 can be installed in the tube bundle heat exchanger without any problems, the outer diameter of the structured areas must not be larger than the outer diameter of the smooth end and intermediate pieces.
  • FIG. 2 schematically shows an oblique view of part of the outer structure of a heat exchanger tube 1 with folded fin tips 51.
  • the rib tips 5 as the distal area of the ribs 2 are deformed in such a way that they partially close the channel 6 in the radial direction with an axially folded rib tip 51.
  • the connection between the channel 6 and the environment is designed as local openings 9 for vapor bubbles to escape from the channel 6 and for liquid fluid to flow into the channel 6 .
  • the primary grooves 6 in turn represent undercut grooves.
  • the axially folded rib tip 51 is formed from the rib 2 and thus extends in the axial direction over the channel 6 away.
  • the cross-sectional area through which flow can take place in the channel 6 between two ribs 2 is reduced locally in a particularly effective manner, in order thereby to limit the fluid flow in the channel 6 during operation.
  • Fig. 3 schematically shows a detailed view of material projections 72 at the location of a projection 71.
  • the material projections 72 placed radially on a preferably solid projection 71 of the duct base structure are produced from material of the rib flank 4 by a toothed rolling disk, which includes both wall material on the duct base 61 and material formed on the rib flank 4.
  • projections 71 and material projections 72 are thus formed from different areas of the pipe wall, material projections 72 can essentially have a transition flowing in the radial direction to the two side surfaces 711 of the ones underneath
  • Form projection 71 In this case, the projection 71 runs only in part of the channel base 61 and terminates in the axial direction of the tube with an end face 712 .
  • the material projections 72 are formed like a dividing wall and extend approximately radially and in the direction of the longitudinal axis A of the pipe and are pronounced, for example, in this axial direction up to approximately the middle of the channel.
  • the closing surface 713 of the projection 71 can also extend further in the direction of the longitudinal axis A of the pipe or even over the entire channel width between opposite ribs. Starting in this area, the fluid flow can be controlled more precisely and can contribute to the formation of bubbles in both segments 8 that are adjacent in the circumferential direction.
  • the projections 71 with the attached material projections 72 consequently also represent a threshold for the passage of fluid.
  • the axial extent of the material projections 72 is somewhat shorter than the axial extent of the projection 71 located underneath passed forth into the adjacent segments 8 to support the formation of bubbles.
  • Fig. 4 schematically shows a detailed view of a further embodiment of material projections 72 at the location of a projection 71.
  • the material projections 72 placed radially on a projection 71 of the duct base structure are made from material of the rib flank 4 by a toothed rolling disk, which uses both wall material on the duct base 61 and Material on the rib flank 4 reshaped.
  • the contour line of the material projections which extend essentially in the axial and radial direction, can also be designed to be curved or irregular.
  • the material projections 72 have a varying extent in the axial direction. In other words, viewed outwards in the radial direction, a smooth transition into the rib flank 4 is realized.
  • the surfaces of the material projections 72 are also slightly curved. These shapes are certain variations of otherwise flat surfaces, which are particularly favorable with regard to the surface properties and the wetting behavior of the liquid heat exchange fluid. Such structures lead the liquid heat exchange fluid in a particularly preferred manner from the side into the adjacent segments 8 to support the formation of bubbles.
  • FIG. 5 schematically shows an oblique view of part of the outer structure of a heat exchanger tube 1 with opposite material projections 72 at the location of a projection 71.
  • the rib tips 5 as the distal area of the ribs 2 are deformed in such a way that they partially close the channel 6 in the radial direction with an axially folded rib tip 51.
  • the connection between the channel 6 and the environment is as local openings 9 designed for the escape of vapor bubbles from the channel 6 and the inflow of liquid fluid into the channel 6.
  • the cross-sectional area through which flow can take place in the channel 6 between two ribs 2 is reduced locally in a particularly effective manner, in order thereby to limit the fluid flow in the channel 6 during operation.
  • the projections 71 extend over the entire channel width between adjacent ribs 2 in the direction of the longitudinal axis A of the pipe.
  • the projections 71 with the attached material projections 72 consequently represent a threshold for the passage of fluid.

Landscapes

  • 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)

Abstract

L'invention concerne un tube métallique d'échangeur de chaleur (1), qui comprend des nervures (2) monobloc formées sur l'extérieur du tube et présentant une base de nervure (3), des flancs de nervure (4) et un sommet de nervure (5), la base de nervure (3) faisant saillie radialement à partir de la paroi de tube (10), et un canal (6) présentant un fond de canal (61) étant formé entre les nervures (2), des structures supplémentaires (7, 71, 72) espacées les unes des autres étant disposées dans ledit canal. Les structures supplémentaires (7, 71, 72) divisent le canal (6) entre les nervures (2) en segments (8). Les structures supplémentaires (7, 71, 72) réduisent localement la section transversale à travers laquelle un écoulement peut passer dans le canal (6) entre deux nervures (2) et limitent ainsi au moins un écoulement de fluide dans le canal (6) pendant le fonctionnement. Des premières structures supplémentaires (7, 71) se présentent sous forme de parties saillantes (71) partant du fond de canal (61) et orientées radialement vers l'extérieur, chacune étant limitée dans la direction radiale par une surface terminale (713) située entre le fond de canal (61) et le sommet de nervure (5), définissant ainsi une extension radiale des parties saillantes (71). Au niveau de l'emplacement des parties saillantes (71), des parties saillantes de matériau (72) radialement extérieures sont disposées en tant que deuxièmes structures supplémentaires (7, 72), lesdites parties saillantes étant constituées du matériau des flancs de nervure (4). Les parties saillantes de matériau (72) sont chacune disposées entre une surface terminale (713) et le sommet de nervure (5) dans la direction radiale, de sorte que les parties saillantes de matériau (72) sont formées autour de l'extension radiale des parties saillantes (71) sur le fond de canal (61) du canal (6), reposant littéralement sur le flanc de nervure (4). Les parties saillantes de matériau (72) s'étendent dans la direction axiale et radiale plus loin qu'elles ne s'étendent dans la direction périphérique.
EP21797938.4A 2020-10-31 2021-10-07 Tube métallique d'échangeur de chaleur Active EP4237782B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020006684 2020-10-31
PCT/EP2021/000121 WO2022089773A1 (fr) 2020-10-31 2021-10-07 Tube métallique d'échangeur de chaleur

Publications (2)

Publication Number Publication Date
EP4237782A1 true EP4237782A1 (fr) 2023-09-06
EP4237782B1 EP4237782B1 (fr) 2024-10-23

Family

ID=78332748

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21797938.4A Active EP4237782B1 (fr) 2020-10-31 2021-10-07 Tube métallique d'échangeur de chaleur

Country Status (8)

Country Link
US (1) US20230341193A1 (fr)
EP (1) EP4237782B1 (fr)
JP (1) JP2023545916A (fr)
KR (1) KR20230098132A (fr)
CN (1) CN116507872A (fr)
CA (1) CA3192303A1 (fr)
MX (1) MX2023004840A (fr)
WO (1) WO2022089773A1 (fr)

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3664959D1 (en) 1985-10-31 1989-09-14 Wieland Werke Ag Finned tube with a notched groove bottom and method for making it
JP2788793B2 (ja) 1991-01-14 1998-08-20 古河電気工業株式会社 伝熱管
US5597039A (en) * 1994-03-23 1997-01-28 High Performance Tube, Inc. Evaporator tube
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
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
DE10101589C1 (de) 2001-01-16 2002-08-08 Wieland Werke Ag Wärmeaustauscherrohr und Verfahren zu dessen Herstellung
US7254964B2 (en) 2004-10-12 2007-08-14 Wolverine Tube, Inc. Heat transfer tubes, including methods of fabrication and use thereof
DE102009021334A1 (de) * 2009-05-14 2010-11-18 Wieland-Werke Ag Metallisches Wärmeaustauscherrohr
DE102014002829A1 (de) 2014-02-27 2015-08-27 Wieland-Werke Ag Metallisches Wärmeaustauscherrohr

Also Published As

Publication number Publication date
JP2023545916A (ja) 2023-11-01
CA3192303A1 (fr) 2022-05-05
US20230341193A1 (en) 2023-10-26
EP4237782B1 (fr) 2024-10-23
CN116507872A (zh) 2023-07-28
KR20230098132A (ko) 2023-07-03
WO2022089773A1 (fr) 2022-05-05
MX2023004840A (es) 2023-05-10

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