EP3465055B1 - Tube d'échangeur de chaleur - Google Patents

Tube d'échangeur de chaleur Download PDF

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Publication number
EP3465055B1
EP3465055B1 EP17725858.9A EP17725858A EP3465055B1 EP 3465055 B1 EP3465055 B1 EP 3465055B1 EP 17725858 A EP17725858 A EP 17725858A EP 3465055 B1 EP3465055 B1 EP 3465055B1
Authority
EP
European Patent Office
Prior art keywords
pipe
heat transfer
projections
rib
transfer pipe
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.)
Active
Application number
EP17725858.9A
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German (de)
English (en)
Other versions
EP3465055A1 (fr
Inventor
Achim Gotterbarm
Ronald Lutz
Jean El Hajal
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
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Wieland Werke AG
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Publication date
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Publication of EP3465055A1 publication Critical patent/EP3465055A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals
    • 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
    • F28F1/14—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 longitudinally
    • F28F1/16—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 longitudinally the means being integral with the element, e.g. formed by extrusion
    • F28F1/18—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 longitudinally the means being integral with the element, e.g. formed by extrusion the element being built-up from finned sections
    • 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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with the tubular element

Definitions

  • the present invention relates to a heat exchanger tube according to the preamble of claim 1.
  • Heat transfer occurs in many areas of refrigeration and air conditioning technology as well as in process and energy technology. Shell and tube heat exchangers are often used for heat transfer in these areas.
  • a liquid flows on the inside of the pipe, which is cooled or heated depending on the direction of the heat flow. The heat is given off to the medium on the outside of the pipe or withdrawn from it.
  • Heat exchanger tubes structured on one or both sides for tube bundle heat exchangers usually have at least one structured area as well as smooth end pieces and possibly smooth intermediate pieces.
  • the smooth end or intermediate pieces delimit the structured areas.
  • the outside diameter of the structured areas should not be larger than the outside so that the tube can be easily installed in the tube bundle heat exchanger Diameter of smooth end and intermediate pieces.
  • Integrally rolled finned tubes are often used as structured heat exchanger tubes. Integrally rolled finned tubes are understood to mean finned tubes in which the fins were formed from the material of the wall of a plain tube. In many cases, finned tubes have a large number of axially parallel or helically circumferential ribs on the inside of the tube, which increase the inner surface and improve the heat transfer coefficient on the inside of the tube. On the outside, the finned tubes have annular or helical fins running all the way around.
  • the axially parallel or helically circumferential inner ribs can be provided with grooves, as described in the publication DE 101 56 374 C1 and DE 10 2006 008 083 B4 is described. It is important here that the dimensions of the inner and outer structure of the finned tube can be adjusted independently of one another by the use of profiled rolling mandrels disclosed there for producing the inner ribs and grooves. As a result, the structures on the outside and inside can be adapted to the respective requirements and the tube can be designed in this way.
  • the pamphlets U.S. 2005/0145377 A1 and U.S. 03/104736 A1 disclose improved heat transfer surfaces that facilitate heat transfer from one side of the surface to the other. Described herein is another method of improving heat transfer surfaces by using a tool to cut the inner surface of a tube.
  • the tool has at least one tip with a cutting edge and a lifting edge.
  • Protrusions are formed by cutting the inner surface of a heat exchanger tube and raising the cut surface.
  • Boiling surfaces produced in this way have a multiplicity of primary grooves, projections and secondary grooves, for example to form boiling cavities.
  • the object of the present invention is to further develop the internal and external structures of heat exchanger tubes of the aforementioned type in such a way that a further increase in performance is achieved compared to tubes that are already known.
  • the structured area can in principle be formed on the outside of the tube and the inside of the tube.
  • the rib sections according to the invention are to be arranged inside the pipe.
  • the structures described can be used for both evaporator and condenser tubes.
  • Protrusion height is conveniently defined as the dimension of a protrusion in the radial direction. The height of the projection is then, in the radial direction, the distance starting from the pipe wall to the point of the projection which is furthest away from the pipe wall.
  • the notch depth is the distance measured in the radial direction from the original rib tip to the deepest point of the notch. In other words: the notch depth is the difference between the original rib height and the remaining rib height at the deepest point of a notch.
  • a changing notch depth is also synonymous with the fact that the deepest point of the notch alternates and consequently changes the distance to the pipe wall. Equally important here is that the respective deepest point of the notches, which in this context is referred to as the notch base, alternates at a distance from the longitudinal axis of the pipe over successive notches in the direction of the ribs.
  • the invention is based on the consideration that a different notch depth essentially results in a different height, orientation and shape of the projections relative to one another. It follows that the Projections deviate from a regulated order. This requires an optimized heat transfer with the lowest possible pressure loss in the single-phase flow, since the fluid boundary layer, which is an obstacle to good heat transfer, is interrupted by additionally generated turbulence. Compared to a uniform, homogeneous arrangement of the projections, this targeted interruption of the boundary layer has a particularly positive effect on the heat transfer coefficient.
  • the shapes, heights and arrangement of the projections can be adjusted by setting suitable cutting knives or cutting geometries and by individually adapted rib shapes and geometries.
  • the projections cause irregular immersion in the laminar flow core and thus optimized heat conduction from the tube wall into the laminar flow core or from the laminar flow core to the tube wall.
  • These optimizations for the turbulent and laminar flow form are realized by the different cutting depths and orientation of the projections according to the solution according to the invention.
  • the indentations that are adjacent at least by one projection vary in the indentation depth by at least 10%.
  • the variation in notch depth can be at least 20% or even 50%. This results in projections of different heights, which in turn lead to an interruption in the boundary layer and to an increase in turbulence and thus to an increase in the heat transfer coefficient.
  • the maximum notch depth can extend as far as the pipe wall. This breaks the boundary layer and increases turbulence. This leads to a Increase in the heat transfer coefficient. Indentations that extend into the tube wall tend to be disadvantageous and can lead to an undesirable weakening of the material in the tube wall without, in return, having a significantly further positive effect on the heat transfer coefficient.
  • the indentations may be formed by cutting the inner ribs with a cutting depth transverse to the rib path to form layers of ribs and raising the layers of ribs with a main orientation along the rib path between primary grooves.
  • the process-side structuring of the heat exchanger tube according to the invention can be produced using a tool which in the DE 603 17 506 T2 is already described.
  • the disclosure of this reference DE 603 17 506 T2 is fully included in the available documents.
  • the projection height and the distance can be made variable and individually adapted to the requirements, for example the viscosity of the liquid or the flow rate.
  • the tool used has a cutting edge for cutting through the fins on the inner surface of the tube to create layers of fins and a lifting edge for lifting the layers of fins to form the projections.
  • the protrusions are formed without removing metal from the inner surface of the tube.
  • the protrusions on the inner surface of the tube may be formed in the same or different processing as the formation of the ribs.
  • the protrusion height and distance can be made variable and individually adapted to the requirements of the fluid in question, for example with regard to the viscosity of the liquid and the flow rate.
  • At least one projection can protrude from the main alignment along the course of the ribs over the primary groove. This has the advantage that the boundary layer formed in the space between the ribs is interrupted by this projection protruding into the primary groove, which results in improved heat transfer.
  • the sections of the rib are unchanged between the groups. Further positive influences on the heat transfer through the interruption of the boundary layer can be derived from this, since different divisions / groupings and alternating rib shapes increase the effect described above.
  • a plurality of projections can have a surface parallel to the longitudinal axis of the tube at the point furthest away from the tube wall.
  • the projections can vary in projection height, shape and orientation.
  • the individual projections can be specifically adapted to one another and varied in relation to one another in order to dip into the different boundary layers of the flow, especially in the case of laminar flow, through different rib heights, in order to dissipate the heat to the tube wall.
  • the height of the protrusion and the distance can be individually adapted to the requirements, e.g. viscosity of the fluid, flow rate, etc.
  • a projection can have a pointed tip on the side facing away from the tube wall. This results in optimized tip condensation for condenser tubes using two-phase fluids.
  • a projection on the of have a curved tip on the side facing away from the pipe wall, the local radius of curvature of which is reduced starting from the pipe wall with increasing distance.
  • the projections can have a different shape and/or height from the beginning of the pipe along the longitudinal axis of the pipe to the opposite end of the pipe.
  • the advantage of this is a targeted adjustment of the heat transfer from the beginning of the pipe to the end of the pipe.
  • the tips of at least two projections can touch or cross one another along the course of the ribs; which is particularly advantageous in reversible operation during phase change, since the projections for the liquefaction protrude far out of the condensate and form a kind of cavity for the evaporation.
  • the tips of at least two projections can touch or cross one another across the primary groove. This, in turn, is advantageous in reversible operation during the phase change, since the projections for the liquefaction protrude far out of the condensate and form a type of cavity for the evaporation.
  • At least one of the projections be deformed in such a way that its tip touches the inside or outside of the pipe. This is advantageous in particular in reversible operation during the phase change, since the projections form a kind of cavity for the liquefaction for the evaporation and thus bubble nucleation sites. This leads to increased heat transfer coefficients during the evaporation process.
  • the heat exchanger tube 1 shows schematically an oblique view of a tube section of the heat exchanger tube 1 with the structure according to the invention on the tube inside 22.
  • the heat exchanger tube 1 has a tube wall 2, a tube outside 21 and a tube inside 22 shaped.
  • the longitudinal axis A of the tube runs at a certain angle relative to the ribs 3 .
  • Continuously extending primary grooves 4 are formed between each adjacent ribs 3 .
  • the projections 6 are arranged in groups 10 which are periodically repeated along the rib path.
  • the projections 6 are formed by cutting the ribs 3 with a cutting depth transverse to the rib path to form layers of ribs and by raising the layers of ribs with a main orientation along the rib path between primary grooves 4 .
  • the indentations 7 are formed in a rib 3 between the projections 6 within the group 10 with an alternating indentation depth.
  • FIG. 2 shows schematically a rib section 31 with different cutting or notching depths t 1 , t 2 , t 3 .
  • the terms cutting depth and notch depth represent the same terminology. Dashed is indicated in the 2 the original formed helical circumferential rib 3. From this the projections 6 are cut by cutting the rib 3 with a notch/cutting depth t 1 , t 2 , t 3 transverse to the rib path to form rib layers and by raising the rib layers with a main orientation along the rib path shaped. The different notch/cutting depths t 1 , t 2 , t 3 are consequently dimensioned based on the notch depth of the original rib in the radial direction.
  • the projection height h is in 2 is plotted as the dimension of a protrusion in the radial direction.
  • the projection height h is then in the radial direction Distance starting from the tube wall to the point of the projection that is furthest away from the tube wall.
  • the notch depth t 1 , t 2 , t 3 is the distance measured in the radial direction, starting from the original rib tip to the deepest point of the notch.
  • the notch depth is the difference between the original rib height and the remaining rib height at the deepest point of a notch.
  • FIG. 3 shows schematically a rib section 31 with a structural element 6 protruding over the primary groove 4.
  • This is a projection 6, which extends from the main alignment with the tip 62 along the course of the rib over the primary groove 4. The further the projection is formed, the more the boundary layer of the fluid formed in the space between the ribs is disturbed, which results in improved heat transfer.
  • FIG. 4 shows schematically a rib section 31 with a projection 6 curved in the direction of the ribs at the tip 62.
  • the projection 6 has a changing course of curvature at the curved tip 62.
  • the local radius of curvature decreases with increasing distance from the pipe wall. In other words, the radius of curvature decreases towards the tip along the line indicated by the points P1, P2, P3.
  • This has the advantage that the condensate that forms at the tip 62 in the case of two-phase fluids is transported more quickly to the base of the ribs due to the increasing convex curvature. This optimizes the heat transfer during liquefaction.
  • figure 5 shows schematically a fin section 31 with a projection 6 with a parallel surface 61 at the point furthest from the tube wall in the area of the tip 62.
  • Rib portions 31 shown can in the respective Groups can be involved individually or in larger numbers.
  • FIG. 6 shows schematically a rib section 31 with two mutually touching projections 6 along the course of the ribs.
  • FIG 7 schematically a rib section 31 with two along the course of the ribs mutually crossing projections 6.
  • FIG. 12 shows schematically a rib section 31 with two projections touching each other across the primary groove 4.
  • FIG. 9 shows schematically a rib section 31 with two mutually crossing projections 6 over the primary groove 4.
  • the structural elements shown are advantageous, especially in reversible operation with two-phase fluids, that they form a kind of cavity for evaporation.
  • the cavities of this special type form the exit points for bubble nuclei of an evaporating fluid.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Liquid Developers In Electrophotography (AREA)

Claims (12)

  1. Tube de transfert de chaleur (1) avec un axe longitudinal du tube (A), où
    - des nervures (3) s'étendant en continu, parallèles à l'axe ou circonférentielles hélicoïdales sont formées sur le côté interne du tube (22) depuis la paroi du tube (2),
    - des rainures primaires (4) s'étendant en continu sont formées entre les nervures (3) voisines respectives,
    - les nervures (3) présentent au moins une zone structurée sur le côté interne du tube (22),
    - la zone structurée présente une pluralité de saillies (6) dépassant de la surface avec une hauteur de saillie (h), où les saillies (6) voisines sont séparées par des entailles (7), où les saillies (6) sont disposées en groupes (10) qui se répètent périodiquement le long du tracé des nervures,
    - les entailles (7) sont formées entre les rainures primaires (4) par coupe des nervures internes (3) avec une profondeur de coupe (t1, t2, t3) transversalement au tracé des nervures pour former des couches de nervures et par élévation des couches de nervures avec une orientation principale le long du tracé des nervures, caractérisé
    - en ce qu'au moins deux entailles (7) sont formées entre les saillies (6) à l'intérieur du groupe (10) avec une profondeur d'entaille (t1, t2, t3) variable dans une nervure (3), et
    - en ce que les entailles (7) voisines d'au moins une saillie (6) varient dans la profondeur d'entaille (t1, t2, t3) d'au moins 10 %.
  2. Tube de transfert de chaleur (1) selon la revendication 1, caractérisé en ce que la plus grande profondeur d'entaille (t1, t2, t3) s'étend au maximum jusqu'à la paroi du tube (2).
  3. Tube de transfert de chaleur (1) selon la revendication 1 ou 2, caractérisé en ce qu'au moins une saillie (6) dépasse au-dessus de la rainure primaire (4) depuis l'orientation principale le long du tracé des nervures.
  4. Tube de transfert de chaleur (1) selon l'une des revendications 1 à 3, caractérisé en ce qu'une section partielle (31) de la rainure (3) est inchangée entre les groupes (10).
  5. Tube de transfert de chaleur (1) selon l'une des revendications 1 à 4, caractérisé en ce que plusieurs saillies (6) présentent une surface (61) parallèle à l'axe longitudinal du tube (A) à l'emplacement le plus éloigné de la paroi du tube (2).
  6. Tube de transfert de chaleur (1) selon l'une des revendications 1 à 5, caractérisé en ce que les saillies (6) varient entre elles dans la hauteur de saillie (h), la forme et l'orientation.
  7. Tube de transfert de chaleur (1) selon l'une des revendications 1 à 6, caractérisé en ce qu'une saillie (6) du côté opposé à la paroi du tube (2) présente une pointe (62) qui se termine en pointe.
  8. Tube de transfert de chaleur (1) selon l'une des revendications 1 à 7, caractérisé en ce que une saillie (6) présente, sur le côté opposé à la paroi du tube (2), une pointe (62) courbée dont le rayon de courbure local diminue, depuis la paroi du tube (2), à mesure que la distance augmente.
  9. Tube de transfert de chaleur (1) selon l'une des revendications 1 à 8, caractérisé en ce que les saillies (6) présentent une forme et/ou hauteur différente depuis un début du tube le long de l'axe longitudinal du tube (A) jusqu'à l'extrémité du tube opposée.
  10. Tube de transfert de chaleur (1) selon l'une des revendications 7 ou 8, caractérisé en ce que les pointes (62) d'au moins deux saillies (6) se touchent ou se croisent mutuellement le long du tracé des nervures.
  11. Tube de transfert de chaleur (1) selon l'une des revendications 7 ou 8, caractérisé en ce que les pointes (62) d'au moins deux saillies (6) se touchent ou se croisent mutuellement au-dessus de la rainure primaire (4).
  12. Tube de transfert de chaleur (1) selon l'une des revendications 7 ou 8, caractérisé en ce qu'au moins l'une des saillies (6) est déformée de telle manière que sa pointe (62) touche le côté interne du tube (22) ou le côté externe du tube.
EP17725858.9A 2016-06-01 2017-05-17 Tube d'échangeur de chaleur Active EP3465055B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016006967.8A DE102016006967B4 (de) 2016-06-01 2016-06-01 Wärmeübertragerrohr
PCT/EP2017/000596 WO2017207090A1 (fr) 2016-06-01 2017-05-17 Tube d'échangeur de chaleur

Publications (2)

Publication Number Publication Date
EP3465055A1 EP3465055A1 (fr) 2019-04-10
EP3465055B1 true EP3465055B1 (fr) 2022-06-22

Family

ID=58772828

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17725858.9A Active EP3465055B1 (fr) 2016-06-01 2017-05-17 Tube d'échangeur de chaleur

Country Status (10)

Country Link
US (1) US10976115B2 (fr)
EP (1) EP3465055B1 (fr)
JP (1) JP6752294B2 (fr)
KR (1) KR102449268B1 (fr)
CN (1) CN109196297A (fr)
DE (1) DE102016006967B4 (fr)
MX (1) MX2018014688A (fr)
PL (1) PL3465055T3 (fr)
PT (1) PT3465055T (fr)
WO (1) WO2017207090A1 (fr)

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GB201806020D0 (en) 2018-02-23 2018-05-30 Rolls Royce Conduit
US20190293364A1 (en) * 2018-03-22 2019-09-26 Johnson Controls Technology Company Varied geometry heat exchanger systems and methods

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JP2019517652A (ja) 2019-06-24
DE102016006967A1 (de) 2017-12-07
KR102449268B1 (ko) 2022-09-29
JP6752294B2 (ja) 2020-09-09
DE102016006967B4 (de) 2018-12-13
EP3465055A1 (fr) 2019-04-10
US10976115B2 (en) 2021-04-13
PT3465055T (pt) 2022-08-12
US20190145717A1 (en) 2019-05-16
MX2018014688A (es) 2019-02-28
CN109196297A (zh) 2019-01-11
WO2017207090A8 (fr) 2018-11-22
PL3465055T3 (pl) 2022-10-31
KR20190011717A (ko) 2019-02-07
WO2017207090A1 (fr) 2017-12-07

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