EP4237781A1 - Tube métallique d'échangeur de chaleur - Google Patents

Tube métallique d'échangeur de chaleur

Info

Publication number
EP4237781A1
EP4237781A1 EP21793853.9A EP21793853A EP4237781A1 EP 4237781 A1 EP4237781 A1 EP 4237781A1 EP 21793853 A EP21793853 A EP 21793853A EP 4237781 A1 EP4237781 A1 EP 4237781A1
Authority
EP
European Patent Office
Prior art keywords
channel
projections
rib
ribs
cavities
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
EP21793853.9A
Other languages
German (de)
English (en)
Other versions
EP4237781B1 (fr
Inventor
Achim Gotterbarm
Manfred Knab
Ronald Lutz
Zhong Luo
Jianying Cao
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 EP4237781A1 publication Critical patent/EP4237781A1/fr
Application granted granted Critical
Publication of EP4237781B1 publication Critical patent/EP4237781B1/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
    • 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
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main 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.
  • 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 Pat. No. 5,669,441 A; US Pat. No. 5,697,430 A; DE 197 57 526 C1). This corresponds to a rib spacing of approx. 0.45 to 0.40 mm. It is also known that performance-enhanced evaporation structures can be produced on the outside of the tube with the same rib pitch by using additional structural elements in the area of the groove base between brings in the ribs.
  • EP 1 223 400 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.
  • DE 10 2008 013 929 B3 discloses structures at the bottom of the groove which are designed as local cavities, whereby the process of nucleate boiling is intensified in order to increase the heat transfer during evaporation.
  • the location of the cavities near the primary bottom of the groove is favorable for the evaporation process, since the excess temperature is greatest at the bottom of the groove and therefore the highest driving temperature difference for the formation of bubbles is available there.
  • 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 extension of the projections is defined.
  • cavities are arranged radially outwards as second additional structures, which are formed from the material of the rib flanks and the terminal surface of the projections arranged radially on the outside.
  • the cavities are each arranged in the radial direction between an end surface and the rib tip, so that the cavities around the radial extent of the projections above the channel base of the channel are formed lying laterally on the rib flank.
  • the cavities are open in the axial direction.
  • These metallic heat exchanger tubes are used in particular for evaporating liquids from pure substances or mixtures on the outside of the tube.
  • 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 are produced by a sharp-edged rolling disk, which preforms material from the rib flank into the overhang, and a toothed rolling disk that follows the process, which forms both the wall material on the channel base and the preformed material on the rib flank into the cavity.
  • the structures according to the invention can be produced solely by means of a toothed rolling disk, which forms both wall material at the base of the channel and material from the rib flank into the cavity.
  • 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.
  • Bubble nuclei which contribute to the formation of bubbles in the segment, are preferably formed in the cavities formed by a cavity.
  • 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.
  • the projections, which are spaced apart from one another and follow one another in the channel, and the cavities, which are formed as additional structures and lie radially outwards, can each vary in terms of height and shape.
  • the cavity attached to the basic channel structure is formed from the material of the rib flank and essentially forms a smooth transition in the radial direction to the two side surfaces of the projection below.
  • the cavity is designed like a cave from side surfaces and a cover surface, which represents the closure in the direction of the rib tip, as well as from the closure surface of the projections arranged radially on the outside and from the surface portion of the rib flank that delimits the rear.
  • these side surfaces and cover surface form the boundary surfaces, which extend approximately in the direction of the longitudinal axis of the tube and, for example, extend in this axial direction to approximately the center of the channel.
  • An end surface of the projections arranged radially on the outside can extend over the entire width of the channel.
  • the cavity has an opening for the bubble nuclei to exit in the axial direction.
  • a bubble nucleus can contribute to bubble formation in both circumferentially adjacent segments.
  • liquid fluid can also be exchanged between adjacent segments as long as no bubble nucleus formed from gaseous fluid dominates there and virtually prevents the passage. In other words: as long as no bubble nucleus fills the junction of adjacent segments, liquid fluid can also get from one segment into an adjacent segment.
  • the projections with the attached cavities therefore represent a threshold for the passage of fluid.
  • the side surfaces of a cavity can also be made longer than the cover surface in the axial direction towards the neighboring rib. This results in an opening in the cavity that is inclined relative to the longitudinal axis of the tube, which releases bubble nuclei more easily into the adjacent segments for the bubbles to grow.
  • the front contour line of the side and top surface, which forms an opening in the cavity can also be designed to be curved or irregular. In these preferred embodiments, too, a cavity remains in one certain inclination essentially open in the axial direction.
  • 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 bubble nucleation point in the segment is flooded locally.
  • 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.
  • the evaporator tube structures can be further optimized to increase the heat transfer, depending on the application parameters, by increasing the separation of individual channel sections during the channel segmentation.
  • the projections and the cavities can locally reduce the flow cross-sectional area in the channel between two ribs by at least 30%.
  • the segments are sufficiently delimited locally for fluid passage.
  • the channel section lying between two segments is thus adjacent to one another lying channel sections on the fluid side sufficiently to largely separated.
  • the projections and the cavities 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. Consequently, the channel can also be tapered to the desired extent or completely closed from a combination of several structural elements that complement one another from below and the side and/or from above. In any case, in such a way that the channel between the ribs is divided into discrete segments.
  • 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.
  • the size and shape of the local openings are such that liquid medium can also pass through and flow into the channel section.
  • 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 designed as pores, which can be of the same size or else 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 vapor can be drawn out quickly enough can escape and the canals 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 technologically easy to control structural elements. Slight production-related asymmetries of the otherwise parallel base sides of a trapezoid can occur here.
  • two opposing cavities can be formed at the location of the projections in the direction of the longitudinal axis of the pipe.
  • the openings for the exit of the bubble nuclei are therefore directly opposite each other in the axial direction in the two cavities.
  • a bubble nucleus can contribute to bubble formation in both circumferentially adjacent segments.
  • the projections with the two attached cavities consequently represent the threshold for the passage of fluid. Openings in the cavities that are inclined relative to the longitudinal axis of the pipe can prove to be particularly advantageous here, as they release bubble nuclei more easily into the adjacent segments for the bubbles to grow.
  • 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
  • FIG. 3 shows a schematic detail view of a cavity at the location of a projection
  • FIG. 4 shows a schematic oblique view of part of the outer structure of a
  • Heat exchanger tube with two opposing cavities at the site of a projection Heat exchanger tube with two opposing cavities at the site 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 to the fin tip 5 of the fully formed finned tube.
  • a heat exchanger tube 1 is proposed, in which in the area 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 next rib foot lying above it (not shown in the plane of the figure).
  • cavities 72 are arranged radially outwards as a second additional structure 7, which are made of material from the rib flanks 4 and those arranged radially outwards
  • End surface 713 of the projections 71 are formed.
  • the cavities are in the radial direction between an end face 713 and the
  • Rib tip 5 arranged so that the cavities 72 are formed lying laterally on the rib flank 4 around the radial extension of the projections 71 over the channel base 61 of the channel 6 .
  • the cavities 72 are in the axial direction opened.
  • the primary groove as channel 6 is at least partially tapered at regular intervals.
  • the resulting segment 8 promotes bubble nucleation in connection with the cavities 72 in a special way. The 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.
  • a segment 8 in the form of a cavity which is also characterized in that it has a very high over a very wide range of operating conditions has high performance in evaporating liquids.
  • the liquid evaporates within the segment 8 aided by cavities 72 as additional nucleation sites.
  • the resulting vapor exits 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-over rib tip 51 is formed from the rib 2 and thus extends in the axial direction over the channel 6 .
  • the transition area from the rib flank 4 to the folded rib tip 51 can be seen in the figure by a small plateau-like structure along the course of the rib.
  • 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 a cavity 72 at the location of a projection 71.
  • the cavity 72 placed radially on a preferably solid projection 71 is made from material of the rib flank 4 by a toothed roller disk produced, which reshapes both the wall material on the channel base 61 and the material on the rib flank 4 .
  • projections 71 and cavities 72 are thus formed from different areas of the pipe wall, a cavity 72 can essentially form a transition that flows in the radial direction to the two side surfaces 711 of the projection 71 lying underneath.
  • 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 cavity 72 is cave-like from side surfaces 721 and a cover surface 722 as well as from the radially outwardly arranged closing surface 713 of the projection 71 and from the rear-limiting surface area (covered in FIG. 3 by a side surface 721) of the rib flank.
  • the side surfaces 721, cover surface 722 and end surface 713 of the projection 71 are the boundary surfaces of the cavity 72, which extend approximately in the direction of the pipe longitudinal axis A and are pronounced, for example, in this axial direction up to approximately the center of the channel.
  • the closing surface 713 of the projection 71 can extend further in the direction of the longitudinal axis A of the pipe or even over the entire channel width between opposite ribs.
  • the cavity 72 has an opening 723 for the bubble nuclei to exit essentially in the axial direction of the tube. Starting from there, a bubble nucleus can contribute to the formation of bubbles in the two segments 8 that are adjacent in the circumferential direction.
  • the projections 71 with the attached cavities 72 consequently represent a threshold for the passage of fluid.
  • the side surfaces 721 of the cavity 72 are longer than the cover surface 722 in the axial direction towards the neighboring rib. This results in an opening 723 of the cavity 72 which is inclined relative to the longitudinal axis A of the pipe and which releases bubble nuclei more easily into the adjacent segments 8 for the growth of the bubbles. Nevertheless, this means that a cavity 72 is essentially open in the axial direction A, even if the opening 723 is slightly inclined.
  • 4 schematically shows an oblique view of part of the outer structure of a heat exchanger tube 1 with two opposing cavities 72 at the location of a projection 71 and with folded rib tips 51. For better illustration, only the structural elements of the outer structure that are most important for understanding are shown.
  • 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 projections 71 and cavities 72 as additional structures 7 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 tube.
  • Two opposing cavities 72 are formed at the location of the projections 71 lying radially outwards.
  • the openings for exiting the bubble nuclei are consequently directly opposite one another in the axial direction A in the two cavities 72 .
  • a bubble nucleus can contribute to bubble formation in both circumferentially adjacent segments.
  • the projections 71 with the two attached cavities 72 consequently represent a threshold for the passage of fluid. Slightly inclined openings of the cavities 72 to the longitudinal axis A of the pipe can also prove to be particularly advantageous, which release bubble nuclei more easily into the adjacent segments for the bubbles to grow.

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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)

Abstract

L'invention concerne un tube métallique (1) d'échangeur de chaleur qui comprend des nervures intégrées (2) formées sur l'extérieur du tube ; lesdites nervures ont un pied (3) de nervure, des flancs (4) de nervure et une pointe (5) de nervure ; le pied (3) de nervure fait saillie radialement sur la paroi (10) du tube et un canal (6) est formé entre les nervures (2) ; ledit canal possède une partie inférieure (61) de canal ; des structures supplémentaires (7, 71, 72), espacées les unes des autres, sont agencées dans ledit canal. Les structures supplémentaires (7, 71, 72) divisent en segments (8) le canal (6) entre les nervures (2). Les structures supplémentaires (7, 71, 72) réduisent localement l'aire en section transversale à travers laquelle le fluide peut couler dans le canal (6) entre deux nervures (2), et délimitent ainsi au moins un écoulement de fluide dans le canal (6) pendant le fonctionnement. Des premières structures supplémentaires (7, 71) sont délimitées par des saillies (71) dirigées radialement vers l'extérieur, partant de la partie inférieure (61) du canal et délimitées chacune dans la direction radiale par une face de terminaison (713) située entre la partie inférieure (61) du canal et le pied (5) de nervure, délimitant ainsi une extension radiale des saillies (71). Des cavités (72), situées radialement vers l'extérieur, sont agencées en tant que secondes structures supplémentaires (7, 72) au niveau de l'emplacement des saillies (71), et sont formées à partir d'un matériau des flancs (4) de nervure et de la face de terminaison (713) des saillies (71), agencée radialement vers l'extérieur. Les cavités sont disposées chacune dans la direction radiale entre une face de terminaison (713) et la pointe (5) de nervure, de sorte que les cavités (72), autour de l'étendue radiale des saillies (71), sont formées au-dessus de la partie inférieure (61) du canal (6), latéralement contre le flanc (4) de nervure. Les cavités (72) sont ouvertes dans la direction axiale.
EP21793853.9A 2020-10-31 2021-10-07 Tube métallique d'échangeur de chaleur Active EP4237781B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020006683 2020-10-31
PCT/EP2021/000120 WO2022089772A1 (fr) 2020-10-31 2021-10-07 Tube métallique d'échangeur de chaleur

Publications (2)

Publication Number Publication Date
EP4237781A1 true EP4237781A1 (fr) 2023-09-06
EP4237781B1 EP4237781B1 (fr) 2024-10-23

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP21793853.9A Active EP4237781B1 (fr) 2020-10-31 2021-10-07 Tube métallique d'échangeur de chaleur

Country Status (8)

Country Link
US (1) US20230400264A1 (fr)
EP (1) EP4237781B1 (fr)
JP (1) JP2023545915A (fr)
KR (1) KR20230098133A (fr)
CN (1) CN116507864A (fr)
CA (1) CA3192309A1 (fr)
MX (1) MX2023004837A (fr)
WO (1) WO2022089772A1 (fr)

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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
CN100365369C (zh) * 2005-08-09 2008-01-30 江苏萃隆铜业有限公司 蒸发器热交换管
DE102008013929B3 (de) 2008-03-12 2009-04-09 Wieland-Werke Ag Verdampferrohr mit optimierten Hinterschneidungen am Nutengrund
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

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US20230400264A1 (en) 2023-12-14
CN116507864A (zh) 2023-07-28
WO2022089772A1 (fr) 2022-05-05
KR20230098133A (ko) 2023-07-03
EP4237781B1 (fr) 2024-10-23

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