US3779312A - Internally ridged heat transfer tube - Google Patents

Internally ridged heat transfer tube Download PDF

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Publication number
US3779312A
US3779312A US00232571A US3779312DA US3779312A US 3779312 A US3779312 A US 3779312A US 00232571 A US00232571 A US 00232571A US 3779312D A US3779312D A US 3779312DA US 3779312 A US3779312 A US 3779312A
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United States
Prior art keywords
tube
heat transfer
ridge
transfer tube
metal heat
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.)
Expired - Lifetime
Application number
US00232571A
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English (en)
Inventor
J Withers
E Habdas
M Jurmo
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
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Universal Oil Products Co
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Publication of US3779312A publication Critical patent/US3779312A/en
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.
Anticipated expiration legal-status Critical
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
    • F28F1/424—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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D15/00—Corrugating tubes
    • B21D15/04—Corrugating tubes transversely, e.g. helically
    • B21D15/06—Corrugating tubes transversely, e.g. helically annularly
    • 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

Definitions

  • ABSTRACT Metal heat transfer tube has a single start helical ridge on its inner surface which conforms to a range of values of a disclosed equation relating the height of the ridge to its pitch and to the inner diameter of the tube.
  • a method of designing a tube for maximum performance is also disclosed, The improved tube provides especially good results in systems, such as steam condensation systems, wherein a single phase fluid is carried by the tube.
  • 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 dimensionless inside heat transfer coefficient constant C, for the particular tube can be determined by means of a modified Wilson plot technique as described at pages 19-30 of Industrial Engineering Chemistry Process Design & Development, Vol. 10, No. 1, 1971, in an article entitled Steam Condensing On Vertical Rows Of Horizontal Corrugated And Plain Tubes by LG. Withers and EH. Young.
  • C dimensionless inside heat transfer coefficient constant
  • Another desirable design feature is to have the corrugated section of the tube have a diameter equal to the diameter of the tube ends since a tube will exhibit less friction loss and pressure drop if its corrugated portion has a diameter as large as the tube ends rather than a smaller one.
  • the metal heat transfer tube of the present invention which includes a single start helical ridge on its inner surface.
  • the function of the ridge is to perturb the liquid flowing in the tube so that the liquid can not build up boundary layers along the tube wall which would inhibit the transfer of heat from the fluid to the tube wall.
  • This parameter is a dimensionless severity parameter, which involves ridge height (e), pitch (p) and inside diameter ((1,), in such a way that:
  • FIG. 1 is a partially sectioned side plan view of a plain ended corrugated tube
  • FIG. 2 is an enlarged sectional view of a portion of the corrugated tube section in FIG. 1;
  • FIG. 3 is a fragmentary sectional view similar to FIG. 2 but showing a modified corrugation shape
  • FIG. 4 is a graph illustrating the heat transfer performance of a plurality of single-helix internal-ridged tubes which plots the Sieder-Tate-Equation Constant, C, as a function of the Severity Parameter 4);
  • FIG. 5 is a graph illustrating the heat transfer performance of a plurality of single-helix internal-ridged tubes which plots the Sieder-Tate-Equation Constant, C,, in relation to a function, which includes the ridge cap dimensions of the tube;
  • FIG. 6 is a graph illustrating the heat transfer performance of single-helix, internal-ridged tubes, expressed as an improvement ratio over a plain tube;
  • FIG. 7 is a graph illustrating the Pressure Drop characteristics of single-helix internal-ridged tubes taken at an arbitrary reference Reynolds Number equal to 35,000 as a function of Severity Parameter, (b;
  • FIG. 8 is a graph illustrating the effect of helix pitch on outside tube diameter when internal single-start helical ridges are formed by an external corrugating operation.
  • FIG. 9 is a graph illustrating a correlation of helix pitch reguired for a uniform diameter corrugated tube with the product of the outside diameter and the wall thickness.
  • FIG. 1 shows a corrugated tube indicated generally at 10 having a plain end 12 and a corrugated section 14.
  • the outer diameter A? of the plain end 12 is preferably equal to or very slightly greater than the outer diameter CT) of the corrugated section 14 while the plain end wall thickness E is equal to the corrugated section wall thickness (T.
  • the distance GE between identical points on adjacent internal ridges produced by the corrugations is defined as the pitch p.
  • the internal corrugations comprise ridge portions indicated generally at 20 and connecting portions indicated generally at 22.
  • the ridge portion 20 is generally convex toward the inside of the tube while the connecting portion 22 is generally concave.
  • the portions 20 and 22 join each other smoothly at points of inflection 26 where the ridge arc 20' and the connecting are 22' have a common tangent.
  • the convex curved portion 27 of the ridge 20 between the points 26 is termed the ridge cap.
  • the ridge cap has a width between points 26, 26 defined as t and a height y between its crest 28 and points 26.
  • the ridge height 2 is the radial distance between ridge crest 28 and the outermost point 30 on the inner surface of connecting portion 22.
  • the internal diameter d is the diametral distance between points 30 on opposite sides of the tube.
  • the pitch, p is the distance between any pair of identical points on adjacent ridges 20, such as the points 28.
  • FIG. 3 illustrates a modification of the tube shown in FIGS. 1 and 2 in that connecting portions 122 are altered in shape as compared to the concave connecting portions 22 of FIG. 2.
  • the connecting portion 122 is flat over a portion 34 of its length.
  • the outer surface of the tube is broken away in FIG. to illustrate the fact that the tube could have a number of different outer surface configurations other than the shape shown in FIG. 2. Since our invention is concerned with improving the tube side heat transfer properties, there is no need to discuss particular external shapes since these will depend on the external heat transfer conditions.
  • FIG. 4 is a plot of the data derived from testing a plain tube and many single-helix internally ridged tubes using the modified Wilson plot technique previously referenced to determine the value of the Sieder-Tate Equation constant C,.
  • the abcissa of the plot is the severity parameter d) which is equal to e/;; d, where e is the height of the corrugations (FIG. 2), p is the pitch and d, is the internal diameter.
  • the parameter d) is defined as a severity parameter since it is strongly dependent on the ridge height or severity of the corrugations. From the curve 36 it can be seen that C, reaches a peak value when d) 0.365 X 10 and then drops off as 4; increases.
  • the right hand portion of the curve 36 represents several prior art tubes.
  • Point 38 represents the l in. tube and point 40 represents the 5/8 in. tube discussed in the aforementioned Withers and Young article.
  • the single-helix ridged tubes tested represent variations in ridge height depth e from 0.0l40.046 in.
  • pitch p from 0.240-0.625 and internal diameter d, from 0.530-l .288 in. These values are not meant to be limiting, however, since it is felt that e could be at least as large as 0.09 in., the pitch p at least as great as 1.2 in. and the internal diameter d, any value up to about 3 inches.
  • FIG. 6 is a plot similar to FIG. 4 except that it relates, by curve 50, the improvement ratio over plain tube [C i/ (C 01?] to the d) parameter.
  • This alternative method of displaying the C vs 41 correlation is useful in comparing results from different laboratories since the base value, (C i)p, for plain tube may vary somewhat among different test setups.
  • FIG. 7 illustrates a correlation of pressure drop characteristics of single-helix, internal-ridge tubes as a function of the severity parameter 4; where the pressure drop is expressed as Friction Factor, f, at a reference Reynolds number of 35,000. It is commonly understood that the friction factor, f, is a direct index of pressure drop per unit length of tube, as long as one compares tubes of a given diameter at the same Reynolds number. Since it is evident from the curve 56 of FIG. 7 that pressure drop increases significantly with increases in the severity parameter qb, it is desirable that tubes be configured so that 4: not be permitted to increase beyond the optimum value of 0.365 X 10'. Such an increase in (1) would not only result in a lower value of C,, but would also cause a presumably undesirable increase in pressure drop.
  • FIG. 8 illustrates the effect of the helix pitch, p, on the outside diameter of a corrugated tube when internal single-start helical ridges are formed by an external corrugating operation of the type shown in Anderson U.S. Pat. No. 3,128,821.
  • the curve 58 shows that by varying the pitch, p, the outside diameter G (FIG. 2)
  • the curve 58 is obtained for any particular alloy, diameter and wall thickness by arbitrarily selecting a given corrugation depth, corrugating the tube at various helix angles, and measuring the resulting outer diameter and corresponding pitch for each of the helix angles. By connecting the test points with a curve as shown in FIG. 8, the pitch required to provide a uniform diameter can be readily determined.
  • FIG. 9 is a graph illustrating the helical pitch required to obtain a uniform diameter corrugated tube for any particular product of the tube outside diameter times its wall thickness.
  • the particular correlation curve 60 shown was determined from data derived from a given tube material (l0 cupronickel) and given groove depth (0.032 in.) where the tube was corrugated in a single helix style by apparatus such as shown in Anderson U.S. Pat. No. 3,128,821. A family of such curves could be determined for other tube materials and groove depths.
  • the correlation is possible since experiments have shown that there exists a certain helix pitch, (p),, which will yield a uniform diameter product in the sense that the maximum projected outer diameter of the corrugated section is essentially equal to the outside diameter of the plain starting tube.
  • teachings of the present invention relative to designing tubes for maximum internal heat transfer are applicable to any of the common tube materials such as cuprous alloys, titanium, stainless steel, carbon steel and aluminum and are independent of outside diameter and the outer configuration of the tube.
  • the metal heat transfer tube of claim 1 wherein the helical ridge has a convex ridge cap, the axial thickness t of said cap being equal to or greater than 0.085 inches.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Heat Treatment Of Articles (AREA)
  • Rigid Pipes And Flexible Pipes (AREA)
US00232571A 1972-03-07 1972-03-07 Internally ridged heat transfer tube Expired - Lifetime US3779312A (en)

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US23257172A 1972-03-07 1972-03-07

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JP (1) JPS5641915B2 (es)
AR (1) AR196754A1 (es)
AT (1) AT329608B (es)
AU (1) AU469249B2 (es)
BR (1) BR7301661D0 (es)
CA (1) CA968342A (es)
CH (1) CH564752A5 (es)
DE (1) DE2310315B2 (es)
EG (1) EG10775A (es)
ES (1) ES214248Y (es)
FR (1) FR2174872B1 (es)
GB (1) GB1418113A (es)
IL (1) IL41446A (es)
IT (1) IT977286B (es)
ZA (1) ZA73737B (es)

Cited By (43)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5169164U (es) * 1974-11-27 1976-06-01
US4007774A (en) * 1975-09-23 1977-02-15 Uop Inc. Heat exchange apparatus and method of controlling fouling therein
FR2374610A1 (fr) * 1976-12-15 1978-07-13 Gen Atomic Co Tube a cannelures helicoidales pour echanges de chaleur et son procede de fabrication
DE3007380A1 (de) * 1979-02-27 1980-09-04 Gen Atomic Co Waermeuebertragungsroehre
US4228852A (en) * 1979-02-28 1980-10-21 Akira Togashi Tubular body
US4245697A (en) * 1976-05-24 1981-01-20 Akira Togashi Tubular body
US4305460A (en) * 1979-02-27 1981-12-15 General Atomic Company Heat transfer tube
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
US4332294A (en) * 1978-04-06 1982-06-01 Metallgesellschaft Aktiengesellschaft Gas cooler with multiply deformed lead tubes
US4583389A (en) * 1978-08-28 1986-04-22 Ltv Steel Method for removing certain of the corrugations in a helically corrugated pipe
US4658892A (en) * 1983-12-28 1987-04-21 Hitachi Cable, Ltd. Heat-transfer tubes with grooved inner surface
US4679544A (en) * 1983-11-04 1987-07-14 Modern Home Products Corp. Threaded adjustable gas intake assembly
US4685292A (en) * 1985-09-09 1987-08-11 Zwick Energy Research Organization, Inc. Exhaust cooling system for internal combustion engine
US4690211A (en) * 1984-06-20 1987-09-01 Hitachi, Ltd. Heat transfer tube for single phase flow
US4773384A (en) * 1983-11-04 1988-09-27 Modern Home Products Corp. Adjustable gas intake assembly
US5271376A (en) * 1991-08-12 1993-12-21 Rheem Manufacturing Company Serpentined tubular heat exchanger apparatus for a fuel-fired forced air heating furnace
US5590711A (en) * 1993-12-14 1997-01-07 Kabushiki Kaisha Kobe Seiko Sho Heat transfer tube for absorber
US5655599A (en) * 1995-06-21 1997-08-12 Gas Research Institute Radiant tubes having internal fins
US5680772A (en) * 1995-11-29 1997-10-28 Sanyo Electric Co., Ltd. Absorption type refrigerating machine
US5697430A (en) * 1995-04-04 1997-12-16 Wolverine Tube, Inc. Heat transfer tubes and methods of fabrication thereof
US5979548A (en) * 1996-12-23 1999-11-09 Fafco, Inc. Heat exchanger having heat exchange tubes with angled heat-exchange performance-improving indentations
US7017651B1 (en) * 2000-09-13 2006-03-28 Raytheon Company Method and apparatus for temperature gradient control in an electronic system
US20060201568A1 (en) * 2002-11-18 2006-09-14 Henry Petersen Flexible, tubular device e.g. a bellows
US20070028984A1 (en) * 2003-03-18 2007-02-08 Imperial College Innovations Limited Helical piping
EP1793188A1 (en) * 2005-12-05 2007-06-06 GEA Ibérica S.A. Surface condenser
US20080017550A1 (en) * 2004-09-21 2008-01-24 Caro Colin G Piping
US20080257436A1 (en) * 2004-09-21 2008-10-23 Caro Colin G Piping
US20090013676A1 (en) * 2007-07-11 2009-01-15 Andreas Capelle Lightweight flow heat exchanger
US20090014151A1 (en) * 2007-07-11 2009-01-15 Andreas Capelle Exhaust gas heat exchanger with an oscillationattenuated bundle of exchanger tubes
US20090250198A1 (en) * 2006-09-08 2009-10-08 Tsinghua University Hot water corrugated heat transfer tube
US20100218912A1 (en) * 2008-04-07 2010-09-02 Lane Lawless Method, apparatus, header, and composition for ground heat exchange
US20110174469A1 (en) * 2010-01-15 2011-07-21 Kim Hongseong Double-pipe heat exchanger
US8029749B2 (en) 2004-09-21 2011-10-04 Technip France S.A.S. Cracking furnace
US20120060727A1 (en) * 2009-03-17 2012-03-15 ToTAL PETROCHECMICALS RESEARCH FELUY Process for quenching the effluent gas of a furnace
US8162040B2 (en) 2006-03-10 2012-04-24 Spinworks, LLC Heat exchanging insert and method for fabricating same
US8354084B2 (en) 2008-09-19 2013-01-15 Technip France S.A.S. Cracking furnace
US9121630B1 (en) 2008-04-07 2015-09-01 Rygan Corp. Method, apparatus, conduit, and composition for low thermal resistance ground heat exchange
US20150294764A1 (en) * 2012-12-25 2015-10-15 Yazaki Corporation Wire harness
US20150362174A1 (en) * 2014-06-17 2015-12-17 Doosan Heavy Industries Construction Co., Ltd. Transfer pipe for furnace
US9885523B2 (en) 2013-03-15 2018-02-06 Caloris Engineering, LLC Liquid to liquid multi-pass countercurrent heat exchanger
US20180104731A1 (en) * 2015-03-12 2018-04-19 Jfe Steel Corporation Steel pipe, steel pipe structure, method of manufacturing steel pipe, and method of designing steel pipe
US11493282B2 (en) * 2016-08-05 2022-11-08 Obshestvo S Ogranichennoi Otvetstvennost'u “Reinnolts Lab” Shell and tube condenser and the heat exchange tube of a shell and tube condenser (variants)
US11542440B2 (en) * 2019-05-31 2023-01-03 Centre National De La Recherche Scientifique Tube for a steam cracking furnace having a segment with an elliptical or lobed cross section

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5132456U (es) * 1974-08-31 1976-03-10
JPS5238663A (en) * 1975-09-22 1977-03-25 Hitachi Ltd Heat transmission tube
JPS5514956Y2 (es) * 1978-05-04 1980-04-05
JPS5526706Y2 (es) * 1978-12-13 1980-06-26
DE102006004704A1 (de) * 2006-01-31 2007-08-09 BRÜNDERMANN, Georg Verfahren zur Optimierung von Abhitzekesseln
DE102008030423B4 (de) 2007-12-05 2016-03-03 GIB - Gesellschaft für Innovation im Bauwesen mbH Rohr mit einer durch Noppen Oberflächenprofil-modifizierten Außenmantelfläche
JP6223298B2 (ja) * 2014-07-31 2017-11-01 株式会社コベルコ マテリアル銅管 管内単相流用伝熱管
DE102018204746A1 (de) * 2018-03-28 2019-10-02 Hanon Systems Abgaskühler

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US3612175A (en) * 1969-07-01 1971-10-12 Olin Corp Corrugated metal tubing

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US3088494A (en) * 1959-12-28 1963-05-07 Babcock & Wilcox Co Ribbed vapor generating tubes
US3213525A (en) * 1961-02-10 1965-10-26 Babcock & Wilcox Co Method of forming an internal rib in the bore of a tube
US3217799A (en) * 1962-03-26 1965-11-16 Calumet & Hecla Steam condenser of the water tube type

Patent Citations (1)

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US3612175A (en) * 1969-07-01 1971-10-12 Olin Corp Corrugated metal tubing

Cited By (52)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5169164U (es) * 1974-11-27 1976-06-01
US4007774A (en) * 1975-09-23 1977-02-15 Uop Inc. Heat exchange apparatus and method of controlling fouling therein
US4245697A (en) * 1976-05-24 1981-01-20 Akira Togashi Tubular body
FR2374610A1 (fr) * 1976-12-15 1978-07-13 Gen Atomic Co Tube a cannelures helicoidales pour echanges de chaleur et son procede de fabrication
US4332294A (en) * 1978-04-06 1982-06-01 Metallgesellschaft Aktiengesellschaft Gas cooler with multiply deformed lead tubes
US4583389A (en) * 1978-08-28 1986-04-22 Ltv Steel Method for removing certain of the corrugations in a helically corrugated pipe
DE3007380A1 (de) * 1979-02-27 1980-09-04 Gen Atomic Co Waermeuebertragungsroehre
US4305460A (en) * 1979-02-27 1981-12-15 General Atomic Company Heat transfer tube
US4228852A (en) * 1979-02-28 1980-10-21 Akira Togashi Tubular body
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
US4679544A (en) * 1983-11-04 1987-07-14 Modern Home Products Corp. Threaded adjustable gas intake assembly
US4773384A (en) * 1983-11-04 1988-09-27 Modern Home Products Corp. Adjustable gas intake assembly
US4658892A (en) * 1983-12-28 1987-04-21 Hitachi Cable, Ltd. Heat-transfer tubes with grooved inner surface
US4690211A (en) * 1984-06-20 1987-09-01 Hitachi, Ltd. Heat transfer tube for single phase flow
US4685292A (en) * 1985-09-09 1987-08-11 Zwick Energy Research Organization, Inc. Exhaust cooling system for internal combustion engine
US5271376A (en) * 1991-08-12 1993-12-21 Rheem Manufacturing Company Serpentined tubular heat exchanger apparatus for a fuel-fired forced air heating furnace
US5590711A (en) * 1993-12-14 1997-01-07 Kabushiki Kaisha Kobe Seiko Sho Heat transfer tube for absorber
US5697430A (en) * 1995-04-04 1997-12-16 Wolverine Tube, Inc. Heat transfer tubes and methods of fabrication thereof
US5655599A (en) * 1995-06-21 1997-08-12 Gas Research Institute Radiant tubes having internal fins
US5680772A (en) * 1995-11-29 1997-10-28 Sanyo Electric Co., Ltd. Absorption type refrigerating machine
US5979548A (en) * 1996-12-23 1999-11-09 Fafco, Inc. Heat exchanger having heat exchange tubes with angled heat-exchange performance-improving indentations
US7017651B1 (en) * 2000-09-13 2006-03-28 Raytheon Company Method and apparatus for temperature gradient control in an electronic system
US20060201568A1 (en) * 2002-11-18 2006-09-14 Henry Petersen Flexible, tubular device e.g. a bellows
US7334609B2 (en) * 2002-11-18 2008-02-26 Norsk Hydro Asa Flexible tubular device
US20070028984A1 (en) * 2003-03-18 2007-02-08 Imperial College Innovations Limited Helical piping
US20080017550A1 (en) * 2004-09-21 2008-01-24 Caro Colin G Piping
US20080257436A1 (en) * 2004-09-21 2008-10-23 Caro Colin G Piping
US7749462B2 (en) * 2004-09-21 2010-07-06 Technip France S.A.S. Piping
US8029749B2 (en) 2004-09-21 2011-10-04 Technip France S.A.S. Cracking furnace
US8088345B2 (en) 2004-09-21 2012-01-03 Technip France S.A.S. Olefin production furnace having a furnace coil
USRE43650E1 (en) 2004-09-21 2012-09-11 Technip France S.A.S. Piping
EP1793188A1 (en) * 2005-12-05 2007-06-06 GEA Ibérica S.A. Surface condenser
US8162040B2 (en) 2006-03-10 2012-04-24 Spinworks, LLC Heat exchanging insert and method for fabricating same
US20090250198A1 (en) * 2006-09-08 2009-10-08 Tsinghua University Hot water corrugated heat transfer tube
US20090013676A1 (en) * 2007-07-11 2009-01-15 Andreas Capelle Lightweight flow heat exchanger
US20090014151A1 (en) * 2007-07-11 2009-01-15 Andreas Capelle Exhaust gas heat exchanger with an oscillationattenuated bundle of exchanger tubes
US8387684B2 (en) * 2007-07-11 2013-03-05 Visteon Global Technologies, Inc. Exhaust gas heat exchanger with an oscillationattenuated bundle of exchanger tubes
US20100218912A1 (en) * 2008-04-07 2010-09-02 Lane Lawless Method, apparatus, header, and composition for ground heat exchange
US9121630B1 (en) 2008-04-07 2015-09-01 Rygan Corp. Method, apparatus, conduit, and composition for low thermal resistance ground heat exchange
US9816023B2 (en) * 2008-04-07 2017-11-14 Rygan Corp Method, apparatus, header, and composition for ground heat exchange
US8354084B2 (en) 2008-09-19 2013-01-15 Technip France S.A.S. Cracking furnace
US20120060727A1 (en) * 2009-03-17 2012-03-15 ToTAL PETROCHECMICALS RESEARCH FELUY Process for quenching the effluent gas of a furnace
US20110174469A1 (en) * 2010-01-15 2011-07-21 Kim Hongseong Double-pipe heat exchanger
US9627102B2 (en) * 2012-12-25 2017-04-18 Yazaki Corporation Wire harness
US20150294764A1 (en) * 2012-12-25 2015-10-15 Yazaki Corporation Wire harness
US9885523B2 (en) 2013-03-15 2018-02-06 Caloris Engineering, LLC Liquid to liquid multi-pass countercurrent 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
US20180104731A1 (en) * 2015-03-12 2018-04-19 Jfe Steel Corporation Steel pipe, steel pipe structure, method of manufacturing steel pipe, and method of designing steel pipe
US10189065B2 (en) * 2015-03-12 2019-01-29 Jfe Steel Corporation Steel pipe, steel pipe structure, method of manufacturing steel pipe, and method of designing steel pipe
US11493282B2 (en) * 2016-08-05 2022-11-08 Obshestvo S Ogranichennoi Otvetstvennost'u “Reinnolts Lab” Shell and tube condenser and the heat exchange tube of a shell and tube condenser (variants)
US11542440B2 (en) * 2019-05-31 2023-01-03 Centre National De La Recherche Scientifique Tube for a steam cracking furnace having a segment with an elliptical or lobed cross section

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AU5171573A (en) 1974-08-08
CA968342A (en) 1975-05-27
DE2310315C3 (es) 1979-07-26
FR2174872A1 (es) 1973-10-19
GB1418113A (en) 1975-12-17
ZA73737B (en) 1973-11-28
EG10775A (en) 1976-05-31
DE2310315A1 (de) 1973-09-13
ATA175473A (de) 1975-08-15
DE2310315B2 (de) 1978-11-16
IL41446A0 (en) 1973-04-30
CH564752A5 (es) 1975-07-31
ES214248U (es) 1976-07-01
AU469249B2 (en) 1976-02-05
BR7301661D0 (pt) 1974-05-16
JPS48101642A (es) 1973-12-21
ES214248Y (es) 1976-12-01
JPS5641915B2 (es) 1981-10-01
AT329608B (de) 1976-05-25
IT977286B (it) 1974-09-10
FR2174872B1 (es) 1976-04-30
AR196754A1 (es) 1974-02-19
IL41446A (en) 1975-06-25

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