EP3465055A1 - Tube d'échangeur de chaleur - Google Patents

Tube d'échangeur de chaleur

Info

Publication number
EP3465055A1
EP3465055A1 EP17725858.9A EP17725858A EP3465055A1 EP 3465055 A1 EP3465055 A1 EP 3465055A1 EP 17725858 A EP17725858 A EP 17725858A EP 3465055 A1 EP3465055 A1 EP 3465055A1
Authority
EP
European Patent Office
Prior art keywords
tube
heat exchanger
projections
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
EP17725858.9A
Other languages
German (de)
English (en)
Other versions
EP3465055B1 (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
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 EP3465055A1 publication Critical patent/EP3465055A1/fr
Application granted granted Critical
Publication of EP3465055B1 publication Critical patent/EP3465055B1/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
    • F28F1/40—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
    • F28F1/12—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
    • F28F1/12—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
    • F28F1/42—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. For heat transfer tube bundle heat exchangers are often used in these areas. In many applications, a liquid flows on the inner side of the pipe, which is cooled or heated depending on the direction of the heat flow. The heat is released or withdrawn from the medium located on the tube outside.
  • One or both sides structured heat exchanger tubes for tube bundle heat exchangers usually have at least one structured area and smooth end pieces and possibly smooth spacers.
  • the smooth end or intermediate pieces limit the structured areas. So that the tube can be easily installed in the tube bundle heat exchanger, the outer diameter of the structured areas should not be greater than the outer Diameter of the smooth end and intermediate pieces.
  • Integrally rolled finned tubes are understood to mean finned tubes in which the fins have been formed from the material of the wall of a smooth tube.
  • finned tubes on the inside of the tube have a multiplicity of axially parallel or helically circumferential fins which increase the internal surface and improve the heat transfer coefficient on the inside of the tube.
  • the finned tubes On the outside, have annular or helical circumferential ribs.
  • substantially closed channels are formed by bending or flipping the rib (US 3,696,861, US 5,054,548), by splitting and upsetting the rib (DE 2 758 526 C2, US 4,577,381) and by notching and upsetting rib (US 4,660,630, EP 0 713 072 B1, US 4,216,826).
  • the axially parallel or helically encircling inner ribs can be provided with grooves, as described in the document DE 101 56 374 C1 and DE 10 2006 008 083 B4. It is important that the dimensions of the inner and outer structures of the finned tube can be adjusted independently of one another by the use of profiled mandrels disclosed therein to produce the inner fins and grooves. This allows the structures on the outside and inside to be adapted to the respective requirements and thus the tube can be designed.
  • the object of the present invention is to develop inner or outer structures of heat exchanger tubes of the aforementioned type so that a comparison with already known pipes, a further increase in performance is achieved.
  • the invention includes a heat exchanger tube with a tube longitudinal axis, wherein from the tube wall on the tube outside and / or inside tube continuously extending, axially parallel or helically encircling ribs are formed between each adjacent ribs continuously extending primary grooves are formed, the ribs at least one structured area the outside of the pipe and / or pipe inside have and the structured region has a plurality of protruding from the surface projections with a projection height, whereby the projections separated by notches are.
  • the projections are arranged in groups which repeat themselves periodically along the course of the ribs.
  • at least two indentations are formed between the protrusions within the group with a varying notch depth in a rib.
  • the structured region can, in principle, be formed on the outside of the pipe or on the inside of the pipe.
  • the structures described can be used for both evaporator and condenser tubes.
  • the protrusion height is expediently defined as the dimension of a protrusion in the radial direction.
  • the projection height is then in the radial direction, the distance from the pipe wall to the farthest from the pipe wall point of the projection.
  • the notch depth is the distance measured in the radial direction starting from the original rib tip to the lowest point of the notch. In other words, the notch depth is the difference between the original rib height and the residual rib height remaining at the lowest point of a notch.
  • An alternating notch depth is synonymous with the fact that the respective lowest point of the notches alternates and consequently changes the distance to the pipe wall. This is equivalent to the fact that the respective deepest point of the notches, which is referred to in this context as Kerbground, alternates at a distance from the tube longitudinal axis via successive notches in the rib direction.
  • the invention is based on the consideration that results from a different notch depth substantially different height, orientation and shape of the projections to each other. As a result, 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 a hindrance to a good heat transfer, is interrupted by additionally generated turbulence.
  • 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 adjusting suitable cutting blades or cutting geometries as well as by individually adapted rib shapes and geometries.
  • the projections cause an irregular immersion in the laminar flow core and thus an 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 shape are realized by the different cutting depths and alignment of the projections according to the inventive solution.
  • the notches adjacent to at least one projection in the notch depth can vary by at least 10%. More preferably, the variation of the notch depth can be at least 20% or even 50%. As a result, different levels of projections are achieved, which in turn lead to an interruption of the boundary layer and to increase turbulence and thus to an increase in the heat transfer coefficient.
  • the maximum notch depth can extend at most to the pipe wall. As a result, an interruption of the boundary layer and an increase in turbulence is achieved. This leads to a Increase of the heat transfer coefficient. Notches into the tube wall are rather disadvantageous and can lead to an undesirable weakening of the material in the tube wall, without, in turn, significantly further positively influencing the heat transfer coefficient.
  • the notches may be formed by cutting the inner ribs with a depth of cut transverse to the rib run to form fin layers and by raising the rib layers with a primary orientation along the rib run between primary grooves.
  • the process-side structuring of the heat exchanger tube according to the invention can be produced using a tool which has already been described in DE 603 17 506 T2.
  • the disclosure of this document DE 603 17 506 T2 is fully incorporated into the present 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 ribs on the inner surface of the tube to provide fin layers and a lifting edge for raising the rib layers to form the projections. In this way, the projections are formed without removal of 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 projection height and distance can be made variable and individually adapted to the requirements of the fluid in question, for example with regard to viscosity of the fluid, flow rate.
  • at least one projection can protrude out of the main alignment along the course of the ribs over the primary groove. This has the advantage that the formed boundary layer in the rib space is interrupted by this protrusion projecting into the primary groove, which causes an improved heat transfer.
  • a plurality of projections on the farthest from the pipe wall location have a parallel to the tube longitudinal axis surface.
  • the projections in the projection height, shape and orientation can vary with each other.
  • the individual projections can be selectively adapted to one another and vary from one another, in order to dive into the different boundary layers of the flow, particularly in the case of laminar flow through different rib heights, in order to divert the heat to the tube wall.
  • the projection height and the distance can be tailored to the requirements of e.g. Adjust the viscosity of the fluid, flow rate etc.
  • a projection on the side facing away from the pipe wall side have a pointed tip. This leads to optimized condensation at the tip for condenser tubes with the use of two-phase fluids.
  • a projection on the of The tube wall facing away from the side facing a curved tip whose local radius of curvature is reduced starting from the pipe wall with increasing distance.
  • the projections may have a different shape and / or height of a pipe beginning along the pipe longitudinal axis towards the opposite end of the pipe.
  • the tips of at least two protrusions may touch or cross each other along the course of the rib; which is especially advantageous in reversible operation during phase change, since the projections for the liquefaction project far out of the condensate and form a kind of cavity for the evaporation.
  • the tips of at least two projections over the primary groove can touch or cross one another. This in turn is advantageous in reversible operation during the phase change, since the projections for the liquefaction project far out of the condensate and form a type of cavity for the evaporation.
  • at least one of the projections be deformed such that its tip touches the tube inside or the tube outside. This is advantageous in particular in reversible operation during phase change, since the projections for liquefaction form a type of cavity and thus nucleation sites for the evaporation. This leads to increased heat transfer coefficients during the evaporation process.
  • FIG. 1 shows schematically an oblique view of a pipe section with the structure according to the invention on the inside of the pipe;
  • Fig. 3 shows schematically a rib portion with a collar over the primary groove
  • Fig. 4 shows schematically a rib portion with a rib direction at the
  • Fig. 5 shows schematically a rib portion with a projection with a parallel
  • Fig. 6 shows schematically a rib portion with two along the rib course mutually contacting projections
  • FIG. 7 schematically shows a rib section with two projections which cross each other along the rib course
  • FIG. 8 schematically shows a rib section with two projections mutually contacting over the primary groove
  • Fig. 9 shows schematically a rib portion with two mutually crossing over the primary groove over projections.
  • Fig. 1 shows schematically an oblique view of a pipe 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 outer side 21 and a tube inside 22.
  • On the tube inside 22 are from the tube wall 2 continuously extending, helical encircling ribs 3 shaped.
  • the tube longitudinal axis A runs opposite the ribs 3 at a certain angle. Between each adjacent ribs 3 continuously extending primary grooves 4 are formed.
  • the protrusions 6 are arranged in groups 10 which repeat periodically along the course of the ribs.
  • the protrusions 6 are formed by cutting the ribs 3 with a cross-sectional cutting depth to form rib layers and raising the rib layers with a primary orientation along the rib course between primary grooves 4 ,
  • the notches 7 are formed between the projections 6 within the group 10 with an alternating notch depth in a rib 3.
  • FIG. 2 shows schematically a rib section 31 with different cutting or notching depth ti, t 2 , t 3 .
  • the projections 6 have alternating notch depths ti, t 2 , t 3 through a rib 3. Dashed lines indicated in Fig. 2, the original shaped helical circumferential rib 3. From this, the projections 6 by cutting the rib 3 with a notch / cutting depth ti, t 2 , t 3 transverse to the rib course to form fin layers and by lifting formed the rib layers with a main orientation along the rib course.
  • the different notching / cutting depths ti, t 2l t 3 are thus dimensioned at the notch depth of the original rib in the radial direction.
  • the protrusion height h is shown in FIG. 2 as the dimension of a protrusion in the radial direction.
  • the projection height h is then in the radial direction Route starting from the pipe wall to the remote from the pipe wall point of the projection.
  • the notch depth ti, t 2 , t 3 is the distance measured in the radial direction, starting from the original rib tip to the lowest point of the notch.
  • the notch depth is the difference between the original rib height and the residual rib height remaining at the lowest point of a notch.
  • FIG. 3 schematically shows a rib section 31 with a structural element 6 projecting over the primary groove 4. This is a projection 6 which extends over the primary groove 4 from the main alignment with the tip 62 along the rib course. The further the protrusion is formed, the more intensively the formed boundary layer of the fluid in the rib space is disturbed, which causes an improved heat transfer.
  • Fig. 4 shows schematically a rib portion 31 with a rib-shaped at the tip 62 curved projection 6.
  • the projection 6 has at the curved tip 62 has a changing curvature.
  • the local radius of curvature decreases starting from the pipe wall with increasing distance.
  • the radius of curvature decreases along the line indicated by the points P1, P2, P3 towards the tip.
  • FIG. 5 schematically shows a rib section 31 with a projection 6 with a parallel surface 61 at the point furthest away from the tube wall in the region of the tip 62.
  • the rib portions 31 shown in Figs. 3 to 5 can be in the respective Groups may be involved individually or in larger numbers.
  • FIG. 6 schematically shows a rib section 31 with two projections 6 touching one another along the rib course. Furthermore, FIG. 7 schematically shows a rib section 31 with two projections 6 crossing one another along the rib path. FIG. 8 also shows schematically a rib section 31 with two mutually touching over the primary groove 4 away projections. 9 shows schematically a rib section 31 with two projections 6 which mutually cross over the primary groove 4.

Landscapes

  • 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)

Abstract

L'invention concerne un tube d'échangeur de chaleur (1) présentant un axe longitudunal (A), des nervures (3) périphériques s'étendant de manière continue, parallèles à l'axe ou en forme d'hélice étant formées à partir de la paroi de tube (2) sur le côté extérieur de tube (21) et/ou sur le côté intérieur de tube (22), des rainures primaires (4) s'étendant de manière continue étant formées entre des nervures (3) adjacentes respectives, les nervures (3) comprenant au moins une région structurée sur le côté extérieur de tube (21) et/ou sur le côté intérieur de tube (22), et la région structurée comprenant une pluralité de saillies (6) faisant saillie à partir de la surface et présentant une hauteur de saillie (h), de sorte que les saillies (6) soient séparées par des entailles (7). Selon l'invention, les saillies (6) sont disposées en groupes qui se répètent périodiquement le long de l'étendue des nervures. En outre, au moins deux entailles (7) sont formées dans une nervure (3) entre les saillies (6) dans le groupe (10) de manière à présenter une profondeur d'entaille variable.
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 true EP3465055A1 (fr) 2019-04-10
EP3465055B1 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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Also Published As

Publication number Publication date
WO2017207090A8 (fr) 2018-11-22
KR102449268B1 (ko) 2022-09-29
JP2019517652A (ja) 2019-06-24
EP3465055B1 (fr) 2022-06-22
US10976115B2 (en) 2021-04-13
MX2018014688A (es) 2019-02-28
US20190145717A1 (en) 2019-05-16
DE102016006967B4 (de) 2018-12-13
PT3465055T (pt) 2022-08-12
WO2017207090A1 (fr) 2017-12-07
JP6752294B2 (ja) 2020-09-09
KR20190011717A (ko) 2019-02-07
DE102016006967A1 (de) 2017-12-07
CN109196297A (zh) 2019-01-11
PL3465055T3 (pl) 2022-10-31

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