US3847212A - Heat transfer tube having multiple internal ridges - Google Patents

Heat transfer tube having multiple internal ridges Download PDF

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Publication number
US3847212A
US3847212A US00376507A US37650773A US3847212A US 3847212 A US3847212 A US 3847212A US 00376507 A US00376507 A US 00376507A US 37650773 A US37650773 A US 37650773A US 3847212 A US3847212 A US 3847212A
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United States
Prior art keywords
tube
ridges
ridge
internal
heat transfer
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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.)
Expired - Lifetime
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US00376507A
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English (en)
Inventor
J Withers
K Rieger
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.)
Bank of Nova Scotia
Wolverine Tube Inc
Universal Oil Products Co
Original Assignee
Universal Oil Products Co
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 Universal Oil Products Co filed Critical Universal Oil Products Co
Priority to US00376507A priority Critical patent/US3847212A/en
Priority to ZA00743899A priority patent/ZA743899B/xx
Priority to PH15963A priority patent/PH10640A/en
Priority to ZM102/74A priority patent/ZM10274A1/xx
Priority to AU70597/74A priority patent/AU482063B2/en
Priority to DE2431162A priority patent/DE2431162C3/de
Priority to IT51855/74A priority patent/IT1016263B/it
Priority to SE7408823A priority patent/SE415060B/xx
Priority to GB2960374A priority patent/GB1473708A/en
Priority to BR5533/74A priority patent/BR7405533D0/pt
Priority to ES427964A priority patent/ES427964A1/es
Priority to FR7423527A priority patent/FR2236157B1/fr
Priority to JP49077236A priority patent/JPS5924311B2/ja
Application granted granted Critical
Publication of US3847212A publication Critical patent/US3847212A/en
Priority to IL46080A priority patent/IL46080A/xx
Assigned to WOLVERINE TUBE, INC., A DE. CORP. reassignment WOLVERINE TUBE, INC., A DE. CORP. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: UOP INC.,
Assigned to BANK OF NOVA SCOTIA, THE reassignment BANK OF NOVA SCOTIA, THE ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: WOLVERINE ACQUISITION CORP. A CORP. OF DE
Assigned to WOLVERINE ACQUISITION CORP., A DE CORP reassignment WOLVERINE ACQUISITION CORP., A DE CORP ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: WOLVERINE TUBE, INC.,
Assigned to WOLVERINE TUBE, INC., A CORP. OF AL reassignment WOLVERINE TUBE, INC., A CORP. OF AL CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: WOLVERINE ACQUISITION CORP.
Assigned to WOLVERINE TUBE, INC., AN AL CORP. reassignment WOLVERINE TUBE, INC., AN AL CORP. RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: BANK OF NOVA SCOTIA, THE
Assigned to SECURITY PACIFIC NATIONAL BANK reassignment SECURITY PACIFIC NATIONAL BANK SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WOLVERINE TUBE, INC.
Anticipated expiration legal-status Critical
Assigned to WOLVERINE TUBE, INC. reassignment WOLVERINE TUBE, INC. RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: BANK OF AMERICA TRUST AND SAVINGS ASSOCIATION, SUCCESSOR BY MERGER TO SECURITY PACIFIC NATIONAL BANK
Expired - Lifetime legal-status Critical Current

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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
    • F28F1/42—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
    • F28F1/42—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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/51—Heat exchange having heat exchange surface treatment, adjunct or enhancement
    • Y10S165/515—Patterned surface, e.g. knurled, grooved
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y10T29/49377—Tube with heat transfer means
    • Y10T29/49378—Finned tube
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y10T29/49377—Tube with heat transfer means
    • Y10T29/49378—Finned tube
    • Y10T29/49382—Helically finned
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y10T29/49377—Tube with heat transfer means
    • Y10T29/49378—Finned tube
    • Y10T29/49384—Internally finned

Definitions

  • ABSTRACT Improved externally finned metal heat transfer tube has multiple-start helical ridging on its inner surface which conforms to a range of values of a disclosed equation relating the size and shape of thc ridging to its pitch and to the inner diameter of the tube.
  • the inside tube wall profile, in axial section, is defined by a straight line interrupted by the internal ridges.
  • the ridge tips are connected to the straight line segments of the profile by convex and concave portions which meet at a point of common tangency.
  • the improved tube provides especially good results in systems. such as submerged-tube, refrigerated coolers, wherein the film resistance of the intube fluid would represent a substantial portion of the total thermal resistance if the improved internal surface were not provided.
  • a method of designing a tube for a particular coefficient of internal heat transfer is also disclosed 5 Claims, 12 Drawing Figures PAIENTED NOV 2 I974 Figure l/ saw a or 2 Figure /0 Figure l2 30! Prior An) Friction Fae/or, f, ((D NR5 35, 000
  • This invention relates to metal tubing for heat transfer purposes and particularly to such tubing wherein a special configuration is given to the inner surface to improve its performance.
  • the state of the finning art is such that external finned tubes can be produced having greatly extended surface and other beneficial properties which enable major improvements-in the outside film coefficient of heat transfer.
  • an additional improvement is logically to be sought by modification of the internal surface of external finned tube.
  • One approach is to provide helical or annular ridging of the inner surface to promote'fluid turbulence, as
  • This equation is applicable to singlephase fluid flowing turbulently inside of plain or internal ridged tubes, providedthe correct value of C is utilized.
  • the dimensionless insideheat transfer coefficient constant, 'C,-" for a particular tube can be determined experimentally by means of a modified Wilson-plot technique as described at pages 19-30 of Industrial Engineering Chemistry Process Design and Development, Vol. 10, No. 1, 1971, in an article entitled Steam Condensing On Vertical Rows of Horizontal Corrugated and Plain Tubes by .l. G. Withers and E.”-H.Young.
  • the metal heat transfer tube of the present invention which includes multiple start helical ridging integrally formed on its inner cylindrical surface.
  • the function of the ridges is to perturb the fluid flowing in the tube so that the fluid cannot build up boundary layers along the tube wall which would inhibit the transfer of heatbetween the'fluid and the tube'wall.
  • a co-pending patent application Ser. No. 232,571, filed Mar. 7, 1972 and assigned to a common assignee, discloses a correlation between C, and a geometrial-parameter called the severity factor.
  • This parameter,- is a dimensionless grouping which involves ridge height (e), pitch (p) and inside diameter (d,-), in such a way that:
  • the present invention incorporates the severity factor, 4), as a framework element. It also advances the art by clarifying the role of ridge shape, and ridge and tube dimensions, in the improvement of intube heat transfer performance in a multiple start internally ridged tube.
  • the instant invention relates specifically to internal tube walls which are so shaped as to define. in a longitudinal-section profile, intermediateflat portions between the internal ridges and convex and concave connecting portions between the ridge tips and the intermediate-flat portions.
  • Pat. No. 3,481,394 discloses several tube embodiments wherein the tube has a plurality of external fins and a single internal rib or ridge.
  • the pitch of the single internal rib of Pat. No. 3,481,394 is of course greater than the pitch of the plural external fins, the rib has the same lead as the fins since it is formed incident to the deepening of the groove defining two adjacent external fins.
  • the reduction in the outside root diameter of the tube adjacent the internal ridge results in the prior art tube being less stiff (and therefore more sensitive to vibration) than the tubing of the present invention wherein the lead of the plurality of helical ridges is greater than the lead of the fins.
  • the improved tube also provides additional latitude in design since the size, shape, number of starts and lead angle of the internal ridges can be chosen for their effect on heat transfer and pressure drop characteristics of the tube rather than be fixed relative to the external fins.
  • the tubing of the current application presents a uniform wall thickness under the fins except for thickened portions at the ridges; whereas the tube of Pat. No. 3,481,394, when manufactured by at least one method (U.S. Pat. No. 3,559,437), can result in thinning of the tube wall in the vicinity of the internal ridges.
  • the improved tube should require less metal.
  • ridges of greater width are easier to form to a greater depth than narrow ridges and also provide greater resistance to wear if contacted with an erosive fluid; however these benefits may obtain at the cost of excess tube material or the loss of some external heat transfer surface.
  • d the severity factor (Equation 2)
  • Equation 2 the severity factor (Equation 2)
  • b ridge base width (measured in an axial direction) p pitch measured between corresponding points on adjacent ridges in an axial direction
  • the equation is applicable to internally helically ridged tubes having cylindrical internal wall portions between adjacent internal ridges. Constraints on application of the equation to provide superior tubes are as follows: b/p should be between 0.l0 and 0.20, 4) should be less than 0.25 X 10*; and e/y should be between 1.50 and 500.
  • FIG. 1 is a fragmentary axial sectional view of a tube made in accordance with the invention.
  • FIG. 2 is a graph showing the inside heat transfer factor C,- as a function of the severity parameter q5 for certain multiple-helix internally ridged tubes having an intermediate fiat inner-wall profile;
  • FIG. 3 is a graph showing the correlation of experimental versus predicted values of the inside heat transfer factor C for several multiple-helix internally ridged tubes having an intermediate flat inner wall profile;
  • FIGS. 4-7 show several alternative ridge profiles, which may be used in a tube of a given severity, with the profiles shown in cross-section in a plan normal to the ridge;
  • FIG. 8 is a view identical to FIG. 5 except that the ridge is widened and the cross-section is taken in an axial plane;
  • FIGS. 9-11 are graphs illustrating the effect on the inside heat transfer factor, C caused by changes in the severity factor, (I), and in the ridge dimension ratios blp and e/y, as calculated from the equation 0, 0.0264 22.1 a Hi/in [e/yl;
  • FIG. 1 is an axial section through a tube indicated generally at 10 made in accordance with the invention.
  • the tube 10 includes a plurality of external fins I2, 14 and plurality of multiple start internal ridges 16, 18.
  • the external fins 12, 14 and the internal ridges 16, 18 are preferably integrally and simultaneously formed from the wall portion 20 of the tube on a grooved mandrel (not shown).
  • the inner wall 22 of the tube is of cylindrical cross-section except where it is interrupted by the internal ridges l6, 18.
  • the width of the ridges is b, the ridge pitch is p, and the ridge helix angle is 0, with 6 being measured from a perpendicular to the axis.
  • FIG. 2 is a graph plotting the severity factor (1) against the inside heat transfer factor C, for a number of tubes.
  • the lower curve 26 represents the performance line for single-helix corrugated tubes having a curvilinear inner wall profile as disclosed in copending application Ser. No. 232.571 filed Mar. 7, 1972.
  • the upper curve 28 represents a performance line for multiple-helix internal-ridged tubes having an intermediate flat inner-wall profile in accordance with the present invention.
  • the curves intersect at a value of C, 0.0264, the value for plain tube, when 0.
  • the lines 26, 28 generally illustrate the heat transfer characteristics of the tubes and their degree of improvement as compared to plain tube.
  • the relationship between heat transfer and pressure drop is given in FIG. 12 in terms of C,- and friction factor, f.
  • FIG. 3 is a graph plotting the experimental inside heat transfer factor C obtained experimentally for a number of multiple start internal ridgedtubes having an intermediate-flat inner wall profile and varying ridge shapes, against the predicted heat transfer factor C,- predicted by the aforementioned Equation 3.
  • the graph shows a good correlation between the predicted and experimental values as evidenced by the closeness of the various test points on the graph to the 45 line 32 which represents a perfect correlation.
  • FIGS. 47 illustrate four different ridge profiles, as viewed perpendicular to the ridge path, which have a common ridge width, b(cos 0), and a common ridge height, e, which in this illustration is taken equal to b(cos 0)]2.
  • Each of the ridge profiles shown in FIGS. 4-7 has its side boundary determined by a concave curved line 36 and a convex curved line 38. The lines 36, 38 meet at a point of inflection 40.
  • the ridges 44 defined in sectional edge profile by the combination of lines 36, 38 include a ridge cap portion 46 which has a height y equal to the radial distance between ridge peak 48 and the point of inflection 40.
  • the ridges 44 also include a ridge base portion 50 which has a width of b(cos 0) and a height of (e-y).
  • the various ridge profiles shown in FIGS. 4-7 differ in that the y dimension varies in each figure so that the four figures have values of e/y equal to 1.50, 2.00, 3.00, and 4.00, respectively.
  • the FIG. 8 ridge profile is identical to the FIG.
  • FIG. 8 is a view of the ridge cross section in an axial plane, the circular arcs of FIG. 5 become elliptical arcs, being elongated along withf(c0s 6) by the factor, llcos 0.
  • the wider base of the FIG. 8 ridge profile provides a lower coefficient of heat transfer than theprofile of FIG. 5, for example, but has advantages in fabrication.
  • FIG. 9 is a graph which illustrates the relationship between the severity factor (I) and theaforementioned heat transfer coefficient constant, C,, when Equation 3 is plotted for a value of b/p of 0.15 with e/y as parameter.
  • the graph shows that for a given value-of the severity factor (b, the value of C, increases as the value of e/y is increased from 1.5, to 5.0.
  • Lines 51, 52, 53, and 55 illustrate the increase for values of e/y of 1.5, 2, 3, and 5 respectively.
  • FIG. 10 is a graph similar to FIG. 9 but different in that various values of b/p are plotted against C, for Equation 3.
  • the graph which is plotted with a constant value of severity factor, 4), of 0.1 X 10 indicates that the value of C, decreases for any given value of e/y, such as values of e/y 2 and 5 represented by lines 62 and 65, as the value of b/p increases.
  • the graph thus indicates that heat transfer efficiency is improved by decreasing the width b of the ridge relative to the pitch,
  • FIG. 11 is a graph similar to FIGS. 9 and 10 but differing in that various values of e/y are plotted against C,- for Equation 3.
  • the graph which is plotted for a fixed value of the severity factor, d), of 0.1 X 10 illustrates that for a given value of b/p, the value of the heat transfer coefficient C, increases as e/y increases.
  • Lines 71 and 72 represent values of b/p of 0.1 and 0.2 respectively.
  • a metal tube having an improved heat transfer rate to or from an internally flowing fluid characterized in that said tube has at least one integral external helical tin of a predetermined pitch distance and lead angle and a plurality of integral multiple start internal helical ridges extending radially inwardly from the inner wall of the tube, said plurality of internal helical ridges having a lead angle of less than 60 (as measured from a perpendicular to the tube axis ⁇ and a pitch distance which is greater than the pitch distance of said at least one external fin but wherein the respective lead angles of said at least one external fin and said plurality of internal ridges are different from each other in magnitude and/or sense, said inner wall of said tube being so shaped as to define, in a longitudinal sectioned profile, an intermediate flat portion between adjacent internal ridges, with said ridges having a ridge cross-sectional profile which includes a pair of side boundaries connecting the flat inner wall portions of the tube intermediate adjacent pairs of ridges and the tips of the ridges, said side boundaries
  • a metal tube in accordance with claim 2 characterized in that the inside heat transfer coefficient con- 8 stant, C is approximately equal to 0.0264 (22.1)()(lb/p)(e/y)" and wherein: (ii is within the range 0.00057 0.0025; 2 is within the range 0.0125 0.075; p is within the range 0.25 0.70; d. is within the range 0.20 3.00; b is within the range 0.02 0. l 5; and, y is within the range 0.0065 0.05.
  • a metal tube having an improved heat transfer rate to or from an internally flowing fluid characterized in that said tube has annular integral external fins of a predetermined pitch distance and a plurality of integral multiple start internal helical ridges extending radially inwardly from the inner wall of the tube, said plurality of internal helical ridges having a pitch distance which is greater than the pitch distance of said external fins but wherein the lead angle of said plurality of internal ridges is less than 60 (as measured from a perpendicular to the tube axis), said inner wall of said tube being so shaped as to define, in a longitudinal sectioned profile, an intermediate flat portion between adjacent internal ridges, with said ridges having a ridge crosssectional profile which includes a pair of side boundaries connecting the flat inner wall portions of the tube intermediate adjacent pairs of ridges and the tips of the ridges, said side boundaries being comprised of concave and convex portions which connect at a point of inflection radially outward from the tip and at a distance from
  • a metal tube having an improved heat transfer rate to or from an internally flowing fluid characterized in that said tube has a plurality of integral radial external fins and a plurality of integral multiple start internal helical ridges extending radially inwardly from the inner wall of the tube, and wherein the lead angle of said plurality of internal ridges is less than 60, as measured from a perpendicular to the tube axis, but wherein the respective lead angle of said plurality of radial external fins and said plurality of internal ridges are different from each other in magnitude and/or sense, said inner wall of said tube being so shaped as to define, in a longitudinal sectioned profile, an intermediate flat portion between adjacent internal ridges, with said ridges having a ridge cross-sectional profile which includes a pair of said boundaries connecting the flat inner wall portions of the tube intermediate adjacent pairs of ridges and the tips of the ridges, said side boundaries being comprised of concave and convex portions which con nect at a point of inflection radi

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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)
  • Rigid Pipes And Flexible Pipes (AREA)
US00376507A 1973-07-05 1973-07-05 Heat transfer tube having multiple internal ridges Expired - Lifetime US3847212A (en)

Priority Applications (14)

Application Number Priority Date Filing Date Title
US00376507A US3847212A (en) 1973-07-05 1973-07-05 Heat transfer tube having multiple internal ridges
ZA00743899A ZA743899B (en) 1973-07-05 1974-06-18 Heat transfer tube having multiple internal ridges
PH15963A PH10640A (en) 1973-07-05 1974-06-21 Heat transfer tube having multiple internal ridges
ZM102/74A ZM10274A1 (en) 1973-07-05 1974-06-25 Heat transfer tube having multiple interal ridges
AU70597/74A AU482063B2 (en) 1974-06-28 Heat transfer tube having multiple internal ridges
DE2431162A DE2431162C3 (de) 1973-07-05 1974-06-28 Rippenrohr
IT51855/74A IT1016263B (it) 1973-07-05 1974-07-01 Perfezionamento nei tubi di trasfe rimento di calore
GB2960374A GB1473708A (en) 1973-07-05 1974-07-04 Heat transfer tube having multiple internal ridges
BR5533/74A BR7405533D0 (pt) 1973-07-05 1974-07-04 Tubo de metal tendo uma taxa de transferencia de calor aperfeicoada
ES427964A ES427964A1 (es) 1973-07-05 1974-07-04 Un tubo metalico que tiene un regimen mejorado de transmi- sion del calor ano desde un fluido que circula en su inte- rior.
SE7408823A SE415060B (sv) 1973-07-05 1974-07-04 Flensror for vermeoverforing
FR7423527A FR2236157B1 (de) 1973-07-05 1974-07-05
JP49077236A JPS5924311B2 (ja) 1973-07-05 1974-07-05 多数の内部的隆起部を有する熱転移管
IL46080A IL46080A (en) 1973-07-05 1974-11-13 Heat transfer tubes having multiple internal ridges

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US00376507A US3847212A (en) 1973-07-05 1973-07-05 Heat transfer tube having multiple internal ridges

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US3847212A true US3847212A (en) 1974-11-12

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US (1) US3847212A (de)
JP (1) JPS5924311B2 (de)
BR (1) BR7405533D0 (de)
DE (1) DE2431162C3 (de)
ES (1) ES427964A1 (de)
FR (1) FR2236157B1 (de)
GB (1) GB1473708A (de)
IL (1) IL46080A (de)
IT (1) IT1016263B (de)
PH (1) PH10640A (de)
SE (1) SE415060B (de)
ZA (1) ZA743899B (de)
ZM (1) ZM10274A1 (de)

Cited By (36)

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FR2396260A1 (fr) * 1977-06-29 1979-01-26 Carrier Corp Echangeur de chaleur a performances elevees
US4330036A (en) * 1980-08-21 1982-05-18 Kobe Steel, Ltd. Construction of a heat transfer wall and heat transfer pipe and method of producing heat transfer pipe
EP0114640A2 (de) * 1983-01-25 1984-08-01 Wickes Products, Inc. Rippenrohr für Wärmetauscher mit optimierten Wärmeübertragungseigenschaften
EP0206640A1 (de) * 1985-06-12 1986-12-30 Wolverine Tube, Inc. (Alabama) Wärmeübertragungsrohr mit Innenrippen
US4678548A (en) * 1986-07-21 1987-07-07 Aluminum Company Of America Corrosion-resistant support apparatus and method of use for inert electrodes
US4685514A (en) * 1985-12-23 1987-08-11 Aluminum Company Of America Planar heat exchange insert and method
US4702312A (en) * 1986-06-19 1987-10-27 Aluminum Company Of America Thin rod packing for heat exchangers
US4705106A (en) * 1986-06-27 1987-11-10 Aluminum Company Of America Wire brush heat exchange insert and method
US4715436A (en) * 1984-10-05 1987-12-29 Hitachi, Ltd. Construction of a heat transfer wall of a heat transfer pipe
US4858682A (en) * 1986-11-17 1989-08-22 Sandvik Ab Cylinder for heat exchangers
US4866830A (en) * 1987-10-21 1989-09-19 Carrier Corporation Method of making a high performance, uniform fin heat transfer tube
US4872689A (en) * 1986-12-12 1989-10-10 Nuraseal Co. Ltd. Mechanical seal with heat exchanger
US4921042A (en) * 1987-10-21 1990-05-01 Carrier Corporation High performance heat transfer tube and method of making same
EP0547363A1 (de) * 1991-12-14 1993-06-23 Wieland-Werke Ag Metallisches Wärmeaustauscherrohr zur Kühlung von zähen Medien
US5275234A (en) * 1991-05-20 1994-01-04 Heatcraft Inc. Split resistant tubular heat transfer member
EP0654647A1 (de) * 1993-11-18 1995-05-24 Dejatech B.V. Rippenrohr für Wärmetauscher
US5690167A (en) * 1994-12-05 1997-11-25 High Performance Tube, Inc. Inner ribbed tube of hard metal and method
US5697430A (en) * 1995-04-04 1997-12-16 Wolverine Tube, Inc. Heat transfer tubes and methods of fabrication thereof
US5996686A (en) * 1996-04-16 1999-12-07 Wolverine Tube, Inc. Heat transfer tubes and methods of fabrication thereof
US6098420A (en) * 1998-03-31 2000-08-08 Sanyo Electric Co., Ltd. Absorption chiller and heat exchanger tube used the same
WO2002084197A1 (en) 2001-04-17 2002-10-24 Wolverine Tube, Inc. Improved heat transfer tube with grooved inner surface
US6488078B2 (en) * 1999-12-28 2002-12-03 Wieland-Werke Ag Heat-exchanger tube structured on both sides and a method for its manufacture
WO2003089865A1 (en) 2002-04-19 2003-10-30 Wolverine Tube, Inc. Heat transfer tubes, including methods of fabrication and use thereof
WO2003104736A1 (en) 2002-06-10 2003-12-18 Wolverine Tube, Inc. Heat transfer tube and method of and tool for manufacturing the same
US6760972B2 (en) * 2000-09-21 2004-07-13 Packless Metal Hose, Inc. Apparatus and methods for forming internally and externally textured tubing
US6810800B1 (en) * 1999-10-08 2004-11-02 Koenig & Bauer Aktiengesellschaft Cylinder for a rotary press
US20050145377A1 (en) * 2002-06-10 2005-07-07 Petur Thors Method and tool for making enhanced heat transfer surfaces
US20060075772A1 (en) * 2004-10-12 2006-04-13 Petur Thors Heat transfer tubes, including methods of fabrication and use thereof
US20060112535A1 (en) * 2004-05-13 2006-06-01 Petur Thors Retractable finning tool and method of using
US20060213346A1 (en) * 2005-03-25 2006-09-28 Petur Thors Tool for making enhanced heat transfer surfaces
US20070234871A1 (en) * 2002-06-10 2007-10-11 Petur Thors Method for Making Enhanced Heat Transfer Surfaces
WO2011043779A1 (en) * 2009-10-08 2011-04-14 Hamon Research-Cottrell, Inc. Dual enhanced tube for vapor generator
US20110302928A1 (en) * 2009-02-27 2011-12-15 Purdue Research Foundation Liquid-gas heat exchanger
US8162040B2 (en) 2006-03-10 2012-04-24 Spinworks, LLC Heat exchanging insert and method for fabricating same
WO2012078564A2 (en) * 2010-12-10 2012-06-14 Uop Llc Process for transferring heat or modifying a tube in a heat exchanger
US20150362174A1 (en) * 2014-06-17 2015-12-17 Doosan Heavy Industries Construction Co., Ltd. Transfer pipe for furnace

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DE2939597A1 (de) * 1979-09-29 1981-04-02 Ritter Heiztechnik GmbH, 4200 Oberhausen Anlage zur waermegewinnung unter ausnutzung von luft- und sonnenenergie
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ZA831483B (en) * 1982-03-11 1983-11-30 British Steel Corp Cooling of materials
JPS5913805U (ja) * 1982-07-20 1984-01-27 株式会社東芝 パルス燃焼機
JPS60139418A (ja) * 1983-12-28 1985-07-24 Fanuc Ltd 射出成形機における製品突出し装置
DE3414230A1 (de) * 1984-04-14 1985-10-24 Ernst Behm Waermetauscherrohr
JPS6110825U (ja) * 1984-06-26 1986-01-22 フアナツク株式会社 射出成形機におけるエジエクタ−機構
JPS6128511U (ja) * 1984-07-25 1986-02-20 フアナツク株式会社 射出成形機におけるエジェクター装置
JPH0235470Y2 (de) * 1984-09-28 1990-09-26
DE3643782A1 (de) * 1986-12-20 1988-07-07 Wieland Werke Ag Kraftstoffkuehler
DE4229177C1 (de) * 1992-09-02 1994-04-21 Testoterm Mestechnik Gmbh & Co Gaskühler
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EP0114640A2 (de) * 1983-01-25 1984-08-01 Wickes Products, Inc. Rippenrohr für Wärmetauscher mit optimierten Wärmeübertragungseigenschaften
EP0114640A3 (en) * 1983-01-25 1984-08-15 Gulf And Western Industries, Inc. Finned heat exchanger tube having optimized heat transfer characteristics
US4715436A (en) * 1984-10-05 1987-12-29 Hitachi, Ltd. Construction of a heat transfer wall of a heat transfer pipe
EP0206640A1 (de) * 1985-06-12 1986-12-30 Wolverine Tube, Inc. (Alabama) Wärmeübertragungsrohr mit Innenrippen
US4660630A (en) * 1985-06-12 1987-04-28 Wolverine Tube, Inc. Heat transfer tube having internal ridges, and method of making same
EP0305632A1 (de) * 1985-06-12 1989-03-08 Wolverine Tube, Inc. (Alabama) Verfahren zur Herstellung eines Wärmeübertragungsrohres
US4685514A (en) * 1985-12-23 1987-08-11 Aluminum Company Of America Planar heat exchange insert and method
US4702312A (en) * 1986-06-19 1987-10-27 Aluminum Company Of America Thin rod packing for heat exchangers
US4705106A (en) * 1986-06-27 1987-11-10 Aluminum Company Of America Wire brush heat exchange insert and method
US4678548A (en) * 1986-07-21 1987-07-07 Aluminum Company Of America Corrosion-resistant support apparatus and method of use for inert electrodes
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US5275234A (en) * 1991-05-20 1994-01-04 Heatcraft Inc. Split resistant tubular heat transfer member
EP0547363A1 (de) * 1991-12-14 1993-06-23 Wieland-Werke Ag Metallisches Wärmeaustauscherrohr zur Kühlung von zähen Medien
NL9301995A (nl) * 1993-11-18 1995-06-16 Dejatech Bv Vinbuis voor een warmteuitwisselinrichting.
EP0654647A1 (de) * 1993-11-18 1995-05-24 Dejatech B.V. Rippenrohr für Wärmetauscher
US5690167A (en) * 1994-12-05 1997-11-25 High Performance Tube, Inc. Inner ribbed tube of hard metal and method
US5697430A (en) * 1995-04-04 1997-12-16 Wolverine Tube, Inc. Heat transfer tubes and methods of fabrication thereof
US5996686A (en) * 1996-04-16 1999-12-07 Wolverine Tube, Inc. Heat transfer tubes and methods of fabrication thereof
US6098420A (en) * 1998-03-31 2000-08-08 Sanyo Electric Co., Ltd. Absorption chiller and heat exchanger tube used the same
US6810800B1 (en) * 1999-10-08 2004-11-02 Koenig & Bauer Aktiengesellschaft Cylinder for a rotary press
US6488078B2 (en) * 1999-12-28 2002-12-03 Wieland-Werke Ag Heat-exchanger tube structured on both sides and a method for its manufacture
US6760972B2 (en) * 2000-09-21 2004-07-13 Packless Metal Hose, Inc. Apparatus and methods for forming internally and externally textured tubing
WO2002084197A1 (en) 2001-04-17 2002-10-24 Wolverine Tube, Inc. Improved heat transfer tube with grooved inner surface
US6883597B2 (en) 2001-04-17 2005-04-26 Wolverine Tube, Inc. Heat transfer tube with grooved inner surface
US20060075773A1 (en) * 2002-04-19 2006-04-13 Petur Thors Heat transfer tubes, including methods of fabrication and use thereof
US20040010913A1 (en) * 2002-04-19 2004-01-22 Petur Thors Heat transfer tubes, including methods of fabrication and use thereof
US7178361B2 (en) 2002-04-19 2007-02-20 Wolverine Tube, Inc. Heat transfer tubes, including methods of fabrication and use thereof
WO2003089865A1 (en) 2002-04-19 2003-10-30 Wolverine Tube, Inc. Heat transfer tubes, including methods of fabrication and use thereof
WO2003104736A1 (en) 2002-06-10 2003-12-18 Wolverine Tube, Inc. Heat transfer tube and method of and tool for manufacturing the same
US20050145377A1 (en) * 2002-06-10 2005-07-07 Petur Thors Method and tool for making enhanced heat transfer surfaces
US7637012B2 (en) 2002-06-10 2009-12-29 Wolverine Tube, Inc. Method of forming protrusions on the inner surface of a tube
US8573022B2 (en) 2002-06-10 2013-11-05 Wieland-Werke Ag Method for making enhanced heat transfer surfaces
US20040069467A1 (en) * 2002-06-10 2004-04-15 Petur Thors Heat transfer tube and method of and tool for manufacturing heat transfer tube having protrusions on inner surface
US20070124909A1 (en) * 2002-06-10 2007-06-07 Wolverine Tube, Inc. Heat Transfer Tube and Method of and Tool For Manufacturing Heat Transfer Tube Having Protrusions on Inner Surface
US8302307B2 (en) 2002-06-10 2012-11-06 Wolverine Tube, Inc. Method of forming protrusions on the inner surface of a tube
US20070234871A1 (en) * 2002-06-10 2007-10-11 Petur Thors Method for Making Enhanced Heat Transfer Surfaces
US7311137B2 (en) 2002-06-10 2007-12-25 Wolverine Tube, Inc. Heat transfer tube including enhanced heat transfer surfaces
US20100088893A1 (en) * 2002-06-10 2010-04-15 Wolverine Tube, Inc. Method of forming protrusions on the inner surface of a tube
US7284325B2 (en) 2003-06-10 2007-10-23 Petur Thors Retractable finning tool and method of using
US20060112535A1 (en) * 2004-05-13 2006-06-01 Petur Thors Retractable finning tool and method of using
US20060075772A1 (en) * 2004-10-12 2006-04-13 Petur Thors Heat transfer tubes, including methods of fabrication and use thereof
US7254964B2 (en) 2004-10-12 2007-08-14 Wolverine Tube, Inc. Heat transfer tubes, including methods of fabrication and use thereof
US7509828B2 (en) 2005-03-25 2009-03-31 Wolverine Tube, Inc. Tool for making enhanced heat transfer surfaces
US20060213346A1 (en) * 2005-03-25 2006-09-28 Petur Thors Tool for making enhanced heat transfer surfaces
US8162040B2 (en) 2006-03-10 2012-04-24 Spinworks, LLC Heat exchanging insert and method for fabricating same
US20110302928A1 (en) * 2009-02-27 2011-12-15 Purdue Research Foundation Liquid-gas heat exchanger
WO2011043779A1 (en) * 2009-10-08 2011-04-14 Hamon Research-Cottrell, Inc. Dual enhanced tube for vapor generator
WO2012078564A3 (en) * 2010-12-10 2012-09-13 Uop Llc Process for transferring heat or modifying a tube in a heat exchanger
US20120145368A1 (en) * 2010-12-10 2012-06-14 Uop, Llc Process for transferring heat or modifying a tube in a heat exchanger
WO2012078564A2 (en) * 2010-12-10 2012-06-14 Uop Llc Process for transferring heat or modifying a tube in a heat exchanger
US8613308B2 (en) * 2010-12-10 2013-12-24 Uop Llc Process for transferring heat or modifying a tube in a heat exchanger
US20140020875A1 (en) * 2010-12-10 2014-01-23 Uop Llc Process for transferring heat or modifying a tube in a heat exchanger
US9631873B2 (en) * 2010-12-10 2017-04-25 Uop Llc Process for transferring heat or modifying a tube in a heat exchanger
US20150362174A1 (en) * 2014-06-17 2015-12-17 Doosan Heavy Industries Construction Co., Ltd. Transfer pipe for furnace
US10274193B2 (en) * 2014-06-17 2019-04-30 DOOSAN Heavy Industries Construction Co., LTD Transfer pipe for furnace

Also Published As

Publication number Publication date
GB1473708A (en) 1977-05-18
DE2431162C3 (de) 1980-06-19
IT1016263B (it) 1977-05-30
AU7059774A (en) 1976-01-08
ES427964A1 (es) 1976-12-01
IL46080A0 (en) 1975-04-25
PH10640A (en) 1977-07-22
BR7405533D0 (pt) 1975-05-06
ZM10274A1 (en) 1975-05-21
DE2431162B2 (de) 1979-10-04
ZA743899B (en) 1975-06-25
JPS5924311B2 (ja) 1984-06-08
SE415060B (sv) 1980-09-01
FR2236157A1 (de) 1975-01-31
DE2431162A1 (de) 1975-01-30
SE7408823L (de) 1975-01-07
IL46080A (en) 1978-03-10
JPS5038123A (de) 1975-04-09
FR2236157B1 (de) 1976-12-24

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