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WO2011013144A2 - Tube d'échangeur thermique - Google Patents

Tube d'échangeur thermique Download PDF

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Publication number
WO2011013144A2
WO2011013144A2 PCT/IN2010/000499 IN2010000499W WO2011013144A2 WO 2011013144 A2 WO2011013144 A2 WO 2011013144A2 IN 2010000499 W IN2010000499 W IN 2010000499W WO 2011013144 A2 WO2011013144 A2 WO 2011013144A2
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
tube
ovular
exchanger tube
indentations
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.)
Ceased
Application number
PCT/IN2010/000499
Other languages
English (en)
Other versions
WO2011013144A3 (fr
Inventor
Ghanshyam Singh
Arvind Pattamatta
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.)
Thermax Ltd
Original Assignee
Thermax Ltd
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
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Application filed by Thermax Ltd filed Critical Thermax Ltd
Priority to PL10804010T priority Critical patent/PL2459954T3/pl
Priority to DK10804010.6T priority patent/DK2459954T3/en
Priority to EP10804010.6A priority patent/EP2459954B1/fr
Publication of WO2011013144A2 publication Critical patent/WO2011013144A2/fr
Publication of WO2011013144A3 publication Critical patent/WO2011013144A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/06—Tubular elements of cross-section which is non-circular crimped or corrugated in cross-section
    • 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
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • 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
    • 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
    • F28F1/424—Means comprising outside portions integral with inside portions
    • F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F2001/027—Tubular elements of cross-section which is non-circular with dimples

Definitions

  • the present invention relates to the field of heat exchangers.
  • the present invention relates to the enhancement of heat transfer coefficient in heat exchangers.
  • oval used in the specification is to define a structure such as an oval, a tear-drop, egg-shaped, aerofoil-shaped, aerodynamic-shape, and the like.
  • Wl used in the specification defines the width of the wide end of the ovular structure.
  • W2 used in the specification defines the width of the narrow end of the ovular structure.
  • Nusselt number (Nu) used in the specification is the ratio of convective to conductive heat transfer across (normal to) the boundary.
  • Enhancement efficiency It is defined as:
  • Friction factor: f (0.7901n Re - 1.64)
  • ⁇ P Pressure gradient per unit tube length (L) (in Pascal/m)
  • L Tube length used in CFD analysis (i.e. one pitch length for coil inserts and five pitch lengths for dimple tubes).
  • Tw a ii Wall temperature (area weighted average)
  • T bu ik Fluid temperature (mass weighted average)
  • Heat exchanger is a device facilitating efficient heat transfer from one fluid to another; the heat exchanging fluids are generally separated by a solid wall to prevent their mixing, however in some cases can be kept in direct contact.
  • Heat exchangers are widely used in industries, prime applications including thermal power plants, chemical processing units, refrigeration, air conditioning, and radiators in automobiles. Heat exchangers typically comprise a plurality of metal tubes generally arranged in a tightly packed serpentine pattern to form multiple passes. In the past, several attempts have been made to reduce the size and increase the efficiency of the heat exchangers; to provide compact, cost-effective, and efficient heat exchangers having an improved heat transfer coefficient.
  • the heat transfer coefficient can be enhanced by increasing the heat transfer surface area and providing turbulence thereof.
  • These objectives can be achieved by providing one or more baffles within the heat exchanger tubes for breaking the laminar flow of the heat exchange fluid and increasing the heat transfer area.
  • the heat exchanger tubes can be flattened at certain locations to cause 1 turbulence; or projections and protrusions can be provided to increase the overall heat transfer efficiency.
  • the convective heat transfer inside a heat exchanger tube suffers largely due to the presence of a laminar sub-layer adjacent to the heat exchanger wall.
  • helical coil inserts and similar roughness elements have been used to enhance the heat transfer.
  • Figure 1 to Figure 6 disclose patterns of tube inserts and roughness causing elements that have been used in the past in heat exchangers to increase turbulence within the heat exchanger tubes by breaking the laminar sublayer.
  • FJgu re 1 shows a helical tube insert having a circular cross-section
  • Figure 2 shows a helical tube insert having a square cross-section.
  • the helical tube insert is typically a tube which is to be placed inside a heat exchanger tube to produce turbulence, wherein the helical tube insert has a helical pattern formed on the surface.
  • the helical tube insert referenced by numeral 100 in Figure 1, shows a helical pattern 102 having a circular cross-section of diameter 3 mm on the surface.
  • the helical tube insert shown by numeral 200 in Figure 2, shows a helical pattern 202 having a square cross-section of side 3 mm on the surface.
  • the helical tube inserts 100 and 200 provide a thick laminar sub-layer along the walls of the heat exchanger and further cause a high pressure drop in the fluid flowing through the heat exchanger tubes, which affect the overall efficiency of the heat exchanger and result in high operating costs for the heat exchanger.
  • Figure 3, 4, 5 and 6 show a heat exchanger tube provided with dimples on the outer surface such that the dimples form corresponding protrusions on the inner surface of the heat exchanger tube.
  • Figure 3 illustrates a heat exchanger tube, referred in Figure 3 by numeral 300, comprising hemispherical dimples 302 on the surface, wherein the hemispherical dimples 302 are arranged inline on the heat exchanger tube 300.
  • Figure 4 illustrates a heat exchanger tube, referred in Figure 4 by numeral 400, comprising hemispherical dimples 402 on the surface, wherein the hemispherical dimples are oriented in a staggered pattern.
  • Figure 5 illustrates a heat exchanger tube, referred in Figure 5 by numeral 500, comprising hemispherical dimples 502 on the surface, wherein the hemispherical dimples 502 are oriented at an angle of 10 degrees to the flow in a staggering pattern.
  • Figure 6 illustrates a heat exchanger tube, referred in Figure 6 by numeral 600, comprising ovular dimples 602 on the surface, wherein the ovular dimples 602 are oriented in a helical pattern.
  • US 2009/0229801 discloses a tube configuration for a heat exchanger, typically a radiator, the tube configuration comprising a plurality of protuberances formed on the inner surface of the tube such that the cross- sectional hydraulic area along the length of the tube is kept constant.
  • the tube as disclosed in US 2009/0229801 has a rectangular cross-section with circular, rectangular, oval, square, or oblong protuberances along the longitudinal axis.
  • the tube configuration as disclosed in US 2009/0229801 is suitable only for radiators used in automobiles.
  • US 2005/0161209 discloses a tubular heat exchanger provided with at least one pair of dimples which are extruded into at least one tube of the heat exchanger by deforming the tube wall inwardly; the dimples of each pair being provided in a facing relationship but being offset from each other in a direction parallel to a longitudinal axis of the tube.
  • the offset design allows each dimple to protrude beyond the centerline of the tube enhancing turbulence in the heat exchanger tube during operation.
  • the tube as claimed in US 2005/0161209 is generally U-shaped where only one of the leg portions is dimpled with elliptical concave indentations. The above disclosed invention is only applicable for serpentine tube heat exchangers.
  • EP 1179719 discloses a method for making a heat excanger tube comprising an elongated strip of aluminum based material with dimples formed in a row on the surface of the strip such that the dimples project from the other side of the strip, the strip is folded to obtain two rows of dimples one above the other aftd with their projections facing each other. A slit is placed between the apexes of the two rows of dimples to close the passage between dimples creating flow paths.
  • the dimples are employed for inducing turbulence and/or providing pressure resistance within the interiors of the heat exchanger tube.
  • US 4043388 discloses a heat exchanger for transmitting thermal energy from one fluid to another fluid.
  • the heat exchanger comprises a casing containing a folded sheet of heat conductive material, each folded section comprising a multiplicity of pairs of dimples formed therein, wherein each dimple pair including a raised dimple and an adjacent depressed dimple having height one-half the width of the fluid passage. The arrangement provides a low pressure drop for the fluid passing through the fluid passages.
  • US 4043388 discloses a particular structure for a heat exchanger comprising a casing and folded sheets with pairs of dimples forming a flow path therethrough.
  • US 3664928 discloses a heat transfer wall particularly for a distillation device having a plurality of dimples which protrude from the evaporating surface forming a tortuous flow path between the plurality of dimples.
  • the dimpled heat transfer walls enhance the overall effective heat transfer surface of the walls, however, the dimpled heat transfer walls as disclosed in US 3664928 are particularly applicable only for distillation apparatus.
  • An object of the present invention is to provide a heat exchanger tube for enhancement of the heat transfer coefficient higher than that offered by conventional heat transfer enhancements in tubes.
  • Another object of the present invention is to provide a heat exchanger tube which can operate efficiently over a wide range of Reynolds number.
  • Still another object of the present invention is to provide a heat exchanger tube which would lead to a compact heat exchanger.
  • Yet another object of the present invention is to provide a heat exchanger tube which is adapted to meet both the criteria of a low pressure drop and a low boundary layer thickness.
  • One more object of the present invention is to provide a heat exchanger tube which will lead to less frictional losses.
  • Still one more object of the present invention is to provide a heat exchanger tube which is suitable for various applications such as water, smoke, fire tube boilers or heat exchangers.
  • Yet one more object of the present invention is to provide a heat exchanger which is less in cost and economical to operate.
  • a heat exchanger tube comprising: • a tubular body defined by a wall having an exterior surface, an interior surface, and a conduit through said tubular body defining a longitudinal axis; and
  • said plurality of ovular indentations form humped protrusions on said interior surface of said tubular body.
  • the ratio of the width of said wide end (Wl) to the width of said narrow end (W2) is between 1.25_ to 3.75.
  • the cumulative volume of said plurality of ovular indentations is between 1.5% to 3.5% of the volume of said conduit.
  • said plurality of ovular indentations are oriented at an inclination.
  • said plurality of ovular indentations are oriented in a helical, inline, staggered, ring, or spiral pattern.
  • Figure 1 illustrates a helical tube insert having a circular cross-section
  • Figure 2 illustrates a helical tube insert having a square cross-section
  • Figure 3 illustrates a heat exchanger tube having hemispherical dimples arranged inline on the tube surface
  • Figure 4 illustrates a heat exchanger tube having hemispherical dimples oriented in a staggered pattern on the tube surface
  • Figure 5 illustrates a heat exchanger tube having hemispherical dimples oriented in a staggering pattern at an angle of 10 degrees to the flow
  • Figure 6 illustrates a heat exchanger tube having ovular dimples oriented in a helical pattern on the tube surface
  • Figure 7 illustrates a heat exchanger tube having a plurality of ovular indentations arranged inline along the tube surface, in accordance with the present invention
  • Figure 8 illustrates a heat exchanger tube having a plurality of ovular indentations arranged in a staggered pattern along the tube surface, in accordance with the present invention
  • Figure 9 illustrates a heat exchanger tube having a plurality of ovular indentations oriented in a staggering pattern at an angle of 10 degrees to the flow, in accordance with the present invention
  • Figure 10 illustrates a heat exchanger tube having a plurality of ovular indentations arranged helically on the tube surface, in accordance with the present invention
  • Figure 11 illustrates a graph plotted with friction factor on y-axis and Reynolds number on x-axis for a helical tube insert having a circular cross- section with 3 mm dia. and 15mm pitch;
  • Figure 12 illustrates a graph plotted with Nusselt number on y-axis and Reynolds number on x-axis for a helical tube insert having a circular cross- section ' with 3 mm dia. and 15mm pitch;
  • Figure 13 illustrates a graph plotted with friction factor on y-axis and Reynolds number on x-axis for a helical tube insert having a square cross- section with 3 mm side and 15mm pitch;
  • Figure 14 illustrates a graph plotted with Nusselt number on y-axis and Reynolds number on x-axis for a helical tube insert having a square cross- section with 3 mm side and 15mm pitch;
  • Figure 15 illustrates a graph plotted with heat transfer enhancement efficiency on y-axis and Reynolds number on x-axis for hemispherical dimple tube configuration and the ovular indentation heat exchanger tube configuration of the present invention (by using experimental data and computational fluid dynamics (CFD) simulation); and
  • Figure 16 illustrates a graph plotted with possible area reduction of heat exchanger on y-axis and Reynolds number on x-axis for hemispherical dimple tube configuration and the ovular indentation heat exchanger tube configuration of the present invention (by using experimental data and computational fluid dynamics (CFD) simulation).
  • CFD computational fluid dynamics
  • the present invention envisages a heat exchanger tube for enhancing the heat transfer efficiency of a heat exchanger.
  • the heat exchanger tube of the present invention comprises a plurality of ovular indentations formed directionally substantially parallel on the surface of the heat exchanger tube and streamlined to the fluid flow; such as to increase turbulence, reduce the boundary layer thickness, and minimize pressure drop in the fluid flowing through the heat exchanger tube.
  • the heat exchanger tube of the present invention can be used over a wide range of Reynolds number flow for a variety of boilers/heat exchangers including water, smoke, and fire tube boilers/heat exchangers.
  • the heat exchanger tube of the present invention further provides a compacted heat exchanger.
  • the heat exchanger tube of the present invention comprises a tubular body which is defined by a wall having an exterior surface, an interior surface, and a conduit through the tubular body which defines longitudinal axis.
  • a plurality of ovular indentations are provided directionally substantially parallel to the longitudinal axis in the wall, wherein the plurality of ovular indentations extend from the exterior surface and protrude through the interior surface of the wall such as to form humped protrusions on the interior surface of the tubular body.
  • the plurality of ovular indentations of the heat exchanger tube of the present invention are further characterized by a relatively wide end and a relatively narrow end, wherein the wide end is arranged in the upstream direction of the flow relative to the narrow end.
  • the ratio of Wl (width of the wide end of the ovular indentation) to W2 (width of the narrow end of the ovular indentation) is typically between 1.25 and 3.75. Further, the cumulative volume of the plurality of ovular indentations is between 1.5 and 3.5 % of the volume of the conduit through the tubular body.
  • the plurality of ovular indentations of the present invention can be oriented at an inclination in a helical, inline, staggered, ring, or spiral pattern and can be distributed continuously or discontinuously along the length of the wall of the tubular body.
  • the plurality of ovular indentations can be symmetrical or asymmetrical to each other with respect to the dimensions such as height, volume, surface area, depth etc.
  • the heat exchanger tube of the present invention is made by rolling, pressing, attaching, brazing, welding, etc., wherein the plurality of ovular indentations and the tubular body can be made from the same or different material.
  • FIG. 7 therein is disclosed a heat exchanger tube of the present invention, wherein the plurality of ovular indentations 710 are arranged inline along the wall of the tubular body 702.
  • the heat exchanger tube referenced in Figure 7 by numeral 700, illustrates the tubular body 702 showing the exterior surface 704 and the interior surface 706.
  • the conduit through the tubular body 702 defines the longitudinal axis which is referenced by numeral 708.
  • the plurality of ovular indentations 710 showing the wide end 716 and the narrow end 718, wherein Wl is referenced by 712 and W2 is referenced by numeral 714.
  • Figure 8 discloses a heat exchanger tube of the present invention, referenced by numeral 800, wherein the plurality of ovular indentations 804 are arranged in a staggering pattern along the wall of the tubular body 802.
  • the Wl is referenced by numeral 808
  • W2 is referenced by 806.
  • Figure 9 discloses a heat exchanger tube of the present invention, referenced by numeral 900, wherein the plurality of ovular indentations 908 are oriented in a staggering pattern at an angle of 10 degrees to the fluid flow, along the wall of the tubular body 902 showing the exterior surface 904 and the interior surface 906.
  • FIG. 10 illustrates a heat exchanger tube of the present invention, referenced by numeral 1000, wherein the plurality of ovular indentations 1020 are oriented helically along the walls of the tubular body 1010.
  • the wide end and the narrow end of the ovular indentations 1020 is represented by numerals 1040 and 1030 respectively.
  • the performance of the heat exchanger tubes with the ovular indentations is sensitive to the fluid flow direction, therefore, the indentations are typically provided directionally substantially parallel to the longitudinal axis with the wide end being upstream to the direction of flow relative to the narrow end.
  • the upstream and down stream profiles of the plurality of ovular indentations is so chosen, that flow separation is minimized.
  • the ovular indentations are filleted to avoid stress concentration.
  • an adverse pressure gradient zone is formed around them, which thereby decreases the thickness of the boundary layer and enhances the level of turbulence near the wall. This combined effect of reduced pressure drop and increased turbulence level helps in increasing the convective heat transfer inside the heat exchanger tube.
  • the present invention further aims at developing a heat exchanger tube in accordance with the present invention using the computational fluid dynamics (CFD) simulation.
  • CFD computational fluid dynamics
  • the data used for validation was chosen in such a way that it represented the typical baseline case for the tube inserts and the dimpled tube configurations (hemispherical and ovular). Furthermore, an ovular dimpled tube configuration was conceptualized to still enhance the heat transfer efficiency. This configuration was also studied and validated using the CFD approach for its improved performance.
  • Heat exchanger tubes with plurality of ovular indentations which can be streamlined to the fluid flow, as shown in Figures 7, 8, 9, & 10.
  • the critical parameters of the dimples/indentations considered during modeling were: Wl and W2, the ratio of Wl to W2, the height/distance between the wide end and the narrow end of the ovular indentations, the profile of the ovular section can be straight or curved to avoid excessive drag, the fillet radius with respect to the tube surface, the ends can be hemispherical or ovular to avoid excessive drag, the relative angle of the dimple/indentation with respect to the flow direction.
  • Wl and W2 of the dimple/ovular indentation pitch in circumferential and longitudinal directions, angle of the major axis or the minor axis of the dimple/ovular indentation with the flow direction, tube inside diameter (ID) and tube outside diameter (OD), tube length and fillet radius. Besides these parameters, the volume of the dimples/ovular indentations was kept the same for purpose of comparison.
  • a uniform heat flux of 100W/m 2 was applied on the wall.
  • tube wall thickness was taken as 1.5mm and constant shell conduction condition was applied.
  • Translational-periodic boundary condition was used to simulate fully developed flow regimes and the mass flow rate was varied to match the Reynolds number.
  • Figure 11 illustrates a graph plotted with friction factor on y-axis and Reynolds number on x-axis for the helical tube insert (as shown in Figure 1) having a circular cross-section with 3 mm dia. and 15mm pitch, the graph is generally indicated by reference numeral 1100; and
  • Figure 12 illustrates a graph plotted with Nusselt number on y-axis and Reynolds number on x-axis for a helical tube insert ( Figure 1) having a circular cross-section with 3 mm dia. and 15mm pitch, the graph is generally indicated by reference numeral 1200.
  • Figure 13 illustrates a graph plotted with friction factor on y-axis and Reynolds number on x-axis for a helical tube insert having a square cross- section with 3 mm side and 15mm pitch, the graph is generally indicated by reference numeral 1300;
  • Figure 14 illustrates a graph plotted with Nusselt number on y-axis and Reynolds number on x-axis for a helical tube insert having a square cross-section with 3 mm side and 15mm pitch, the graph is generally indicated by reference numeral 1400.
  • Experimental data for a helical tube insert having a square cross-section is also provided in "Thermal performance in circular tube fitted with coiled square wires," of Energy conversion and management by Pongjet Promvonge.
  • Results obtained from the experimental data and CFD simulation are plotted in 1300 and 1400, and again it is evident that data plotted using the CFD simulation matches with the experimental data and follows an identical path. Therefore, it can be assumed that the data obtained through the CFD simulation represents the real-time experimental data within the specified experimental uncertainty and can be used as actual.
  • Figure 15 illustrates a graph plotted with heat transfer enhancement efficiency on y-axis and Reynolds number on x-axis for hemispherical dimple tube configuration and the ovular indentation heat exchanger tube of the present invention (by using experimental data and computational fluid dynamics (CFD) simulation), the graph is indicated by reference numeral 1500.
  • Experimental data for the hemispherical dimple tube configuration is provided in "Heat Transfer and pressure drop for low Reynolds turbulent flow in helically dimpled tubes," International Journal of Heat and Mass Transfer by P.G. Vicente et al.
  • the hemispherical dimpled tube (experimental data and CFD simulation) is represented by numbers 1 & 2 respectively; and the ovular indentation tube (experimental data of the present invention and CFD simulation) is represented by numbers 4 & 3 respectively. It is observed in Figure 15 that the heat transfer enhancement efficiency of the ovular indentation tube of the present invention is higher than that of the hemispherical dimpled tube.
  • Figure 16 illustrates a graph plotted with possible area reduction of heat exchanger on y-axis and Reynolds number on x-axis for hemispherical dimple tube configuration and the ovular indentation heat exchanger tube configuration of the present invention (by using experimental data and computational fluid dynamics (CFD) simulation), the graph is indicated by reference numeral 1600.
  • Experimental data for the hemispherical dimple tube configuration is provided in "Heat Transfer and pressure drop for low Reynolds turbulent flow in helically dimpled tubes," International Journal of Heat and Mass Transfer by P.G. Vicente et al.
  • the hemispherical dimpled tube (experimental data and CFD simulation) is represented by numbers 1 & 2 respectively; and the ovular indentation tube (experimental data of the present invention and CFD simulation) is represented by numbers 4 & 3 respectively. It is observed in Figure 16 that the total area of heat exchanger using the ovular indentation tube of the present invention is substantially less than the total area of heat exchanger using the hemispherical dimpled tube.
  • a heat exchanger tube for enhancement of heat transfer efficiency in accordance with the present invention has several technical advantages including but not limited to the realization of:

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

Abstract

L'invention concerne un tube d'échangeur thermique (700) dont le corps tubulaire (702) est délimité par une paroi présentant une surface extérieure (704), une surface intérieure (706) et un conduit. Plusieurs dépressions ovales (718) sont formées sur la paroi, prolongeant la surface extérieure (704) et sortant en saillie à travers la surface intérieure (706) de la paroi. Le tube d'échangeur thermique (700) améliore l'efficience du transfert thermique et fonctionne efficacement sur une gamme étendue d'effets du nombre de Reynolds avec de faibles pertes de charge dues au frottement. Le tube d'échangeur thermique (700) est en outre efficient et économique en fonctionnement.
PCT/IN2010/000499 2009-07-29 2010-07-29 Tube d'échangeur thermique Ceased WO2011013144A2 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PL10804010T PL2459954T3 (pl) 2009-07-29 2010-07-29 Rurka wymiennika ciepła
DK10804010.6T DK2459954T3 (en) 2009-07-29 2010-07-29 Heat exchanger tube
EP10804010.6A EP2459954B1 (fr) 2009-07-29 2010-07-29 Tube d'échangeur thermique

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IN1735MU2009 2009-07-29
IN1735/MUM/2009 2009-07-29

Publications (2)

Publication Number Publication Date
WO2011013144A2 true WO2011013144A2 (fr) 2011-02-03
WO2011013144A3 WO2011013144A3 (fr) 2011-04-28

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PCT/IN2010/000499 Ceased WO2011013144A2 (fr) 2009-07-29 2010-07-29 Tube d'échangeur thermique

Country Status (4)

Country Link
EP (1) EP2459954B1 (fr)
DK (1) DK2459954T3 (fr)
PL (1) PL2459954T3 (fr)
WO (1) WO2011013144A2 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202012104478U1 (de) * 2012-11-20 2014-02-28 Makita Corporation Zylinder für eine luftgekühlte Brennkraftmaschine
DE102012216146A1 (de) * 2012-09-12 2014-03-13 Udo Hellwig Wärmeübertragungseinrichtung, Wärmeübertrager sowie Verfahren zur Übertragung von Wärme von einem ersten Fluid auf ein zweites Fluid
EP2816871A1 (fr) * 2013-06-19 2014-12-24 Behr GmbH & Co. KG Échangeur thermique et dispositif de chauffage
WO2017007649A1 (fr) 2015-07-09 2017-01-12 Sabic Global Technologies B.V. Minimisation de la formation de coke dans un système de craquage d'hydrocarbures
WO2021259763A1 (fr) * 2020-06-24 2021-12-30 Valeo Systemes Thermiques Conduit pour echangeur thermique
WO2023203500A1 (fr) * 2022-04-19 2023-10-26 Bosch Management Services (Pty) Ltd Tube d'échangeur de chaleur

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11709021B2 (en) 2020-07-13 2023-07-25 Transportation Ip Holdings, Llc Thermal management system and method

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1836063U (de) * 1961-04-14 1961-08-03 Christian Steeb Flachrohr mit eingepraegten nocken und dorn zu seiner herstellung.
US3664928A (en) * 1969-12-15 1972-05-23 Aerojet General Co Dimpled heat transfer walls for distillation apparatus
JPH06100432B2 (ja) * 1984-06-20 1994-12-12 株式会社日立製作所 伝熱管
RU2020304C1 (ru) * 1992-03-31 1994-09-30 Геннадий Ираклиевич Кикнадзе Поверхность обтекания для формирования динамических вихревых структур в пограничных и пристенных слоях потоков сплошных сред
JP3322292B2 (ja) * 1995-10-23 2002-09-09 日立電線株式会社 伝熱管
CN2293790Y (zh) * 1996-06-27 1998-10-07 湘潭大学 球面形凹凸换热管
DE20100116U1 (de) * 2001-01-05 2001-03-22 hde Metallwerk GmbH, 58706 Menden Wärmetauscherrohr für flüssige oder gasförmige Medien
US20060231241A1 (en) * 2005-04-18 2006-10-19 Papapanu Steven J Evaporator with aerodynamic first dimples to suppress whistling noise
JP4884140B2 (ja) * 2006-09-04 2012-02-29 パナソニック株式会社 フィンチューブ型熱交換器およびヒートポンプ装置
DE202008002466U1 (de) * 2008-02-21 2008-05-29 Pasemann, Lutz, Dr. Stirlingmotor-Erhitzer aus einem Bündel strukturierter Röhren

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of EP2459954A4 *

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012216146A1 (de) * 2012-09-12 2014-03-13 Udo Hellwig Wärmeübertragungseinrichtung, Wärmeübertrager sowie Verfahren zur Übertragung von Wärme von einem ersten Fluid auf ein zweites Fluid
DE202012104478U1 (de) * 2012-11-20 2014-02-28 Makita Corporation Zylinder für eine luftgekühlte Brennkraftmaschine
EP2816871A1 (fr) * 2013-06-19 2014-12-24 Behr GmbH & Co. KG Échangeur thermique et dispositif de chauffage
US9743464B2 (en) 2013-06-19 2017-08-22 Mahle International Gmbh Heat exchanger device and heater
WO2017007649A1 (fr) 2015-07-09 2017-01-12 Sabic Global Technologies B.V. Minimisation de la formation de coke dans un système de craquage d'hydrocarbures
US10611968B2 (en) 2015-07-09 2020-04-07 Sabic Global Technologies B.V. Minimizing coke formation in a hydrocarbon cracker system
WO2021259763A1 (fr) * 2020-06-24 2021-12-30 Valeo Systemes Thermiques Conduit pour echangeur thermique
FR3111972A1 (fr) * 2020-06-24 2021-12-31 Valeo Systemes Thermiques Conduit pour echangeur thermique
WO2023203500A1 (fr) * 2022-04-19 2023-10-26 Bosch Management Services (Pty) Ltd Tube d'échangeur de chaleur

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WO2011013144A3 (fr) 2011-04-28
EP2459954A4 (fr) 2014-05-21
PL2459954T3 (pl) 2018-08-31
EP2459954A2 (fr) 2012-06-06
DK2459954T3 (en) 2018-02-26
EP2459954B1 (fr) 2017-11-15

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