US3841136A - Method of designing internally ridged heat transfer tube for optimum performance - Google Patents
Method of designing internally ridged heat transfer tube for optimum performance Download PDFInfo
- Publication number
- US3841136A US3841136A US00375242A US37524273A US3841136A US 3841136 A US3841136 A US 3841136A US 00375242 A US00375242 A US 00375242A US 37524273 A US37524273 A US 37524273A US 3841136 A US3841136 A US 3841136A
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- US
- United States
- Prior art keywords
- tube
- heat transfer
- diameter
- internal
- plain
- 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
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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
-
- 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
- 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
-
- 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 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 trans- I fer purposes and particularly to such tubing wherein a, special configuration is given to the inner surface to improve its performance.
- Another desirable design feature is to have the corrugated section of the tube have a diameter equal to the diameter ofthe 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 layersjalong the tube wall which would inhibit the transfer of heat from the fluid to the tube wall.
- This parameter is a dimensionless severity parameter, (b, which involves ridgeheight (e pitch (p) and inside diameter (d,),.in sucha way that: v
- 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
- 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; a
- FIG. 6 is a graph illustrating theheattransfer performance of single-helix, internal-ridged tubes, expressed as an improvement ratio over-a plain tube; 1
- FIG. 7 is a graph illustrating the Pressure Drop characteristics of single-helix internal-ridged tubes taken at an arbitrary. reference Reynolds Number equal ot 35,000 as a function of Severity Parameter, 4:;
- FIG. 8 is a graph illustrating the effect of helix pitch on outside tube diameter when internal single-start he lical ridges are formed by an external corrugating oper-
- FIG. 9 is a graph illustrating a correlation of helix pitch required 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 outerdiameter A of the plain end 12 is preferably equal to or very slightly greater than the outer diameter (T) of the corrugated section 14 while the plain end wall thickness E is equal to the corrugated section wall thickness CF.
- the distance on 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 arc 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 e" 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 conecting 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 which is equal to e p d, where e is the depth 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 0.365 X 10f and then drops offas 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 n in. tube disas 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 .6 eter and wall thickness by arbitrarily selecting a given corrugation depth, corrugating the tube at various helix 1 angles, and measuring the resulting outer diameter and corresponding pitch for each of the helix angles.' By connecting the test points witha curve as shown in FIG.
- 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 (90-10 cupronickel) and given groove depth (.032 in.) where the tube was corrugated in a single helix sytle by apparatus such as shown in Anderson US. Pat. No. 3,128,821. A family of such curves could be determined for other tubematerials and groove depths.
- FIG. 7 illustrates a correlation of pressure drop characteristics of single-helix, internal-ridge tubes as a function of the severity parameter (1) where the pressure drop is expressed as Friction Factor, f, at a reference Reynolds number of 35,000.
- Friction Factor f
- 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 Reyonlds number. Since it is evident from the curve 56 of FIG. 7 that pressure drop increases significantly with increases in the severity parameter (1:, it is desirable that tubes be configured so that not be permitted to increase beyond the optimum vvalue of 0.365 X 10' Such an increase in 4) would not only result in a lower value of C, but would also cause a presumably undesirable increase in pressure drop. In certain instances, design limitations on length, pressure drop, diameter, etc.
- 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,l28',82l.'
- the curve 58 slflvs that by varying the pitch p, the outside diameter CD (FIG. 2) of the corrugated section 14 can be varied so as to either decrease or increase relative to the outside diameter A B of the uncorrugated section 12 of the tube 10.
- the curve 58 is obtained for any particular alloy, diamside diameter of the plain starting tube.
- teachings of the present invention relative to designing tubesfor maximum internal heat transfer are 1 applicable to any of the commom tube materials such as cuprous alloys, titanium, stainlesssteel, carbon steel and aluminum and are independent of outside diameter and the outer configuration of the tube.
- a method of making a heat transfer tube having a single start helical ridge on its internal surface so that a single phase fluid flowing in the tube will have maximum heat transfer with the tube wall, comprising the ter, 11;, the depth, e of such corrugations on the interior surface being selected so that e /Pd, will be euqal to about 0.365 X 10*2.
- corrugating at least a portion of the interior of said tube at a helix angle and depth so as to define an internal helical groove having a pitch p, and an internal diameter d,-" such that e /Pd; will have a value in the range 00.365 X 10 generally proportional to the amount of heat transfer desired between that for a plain tube and the maximum possible for such a ridged tube.
Abstract
Description
Claims (2)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US00375242A US3841136A (en) | 1972-03-07 | 1973-06-29 | Method of designing internally ridged heat transfer tube for optimum performance |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US23257172A | 1972-03-07 | 1972-03-07 | |
US00375242A US3841136A (en) | 1972-03-07 | 1973-06-29 | Method of designing internally ridged heat transfer tube for optimum performance |
Publications (1)
Publication Number | Publication Date |
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US3841136A true US3841136A (en) | 1974-10-15 |
Family
ID=26926134
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US00375242A Expired - Lifetime US3841136A (en) | 1972-03-07 | 1973-06-29 | Method of designing internally ridged heat transfer tube for optimum performance |
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Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1998050693A1 (en) * | 1997-05-08 | 1998-11-12 | Brilev, Viktor Leonidovich | Engine with external heat exchanging and method of operating |
US6568076B2 (en) * | 1998-06-05 | 2003-05-27 | Halliburton Energy Services, Inc. | Method of making an internally profiled stator tube |
US9446245B2 (en) | 2001-03-30 | 2016-09-20 | Case Western Reserve University | Systems and methods for selectively stimulating components in, on, or near the pudendal nerve or its branches to achieve selectively physiological responses |
US20160341491A1 (en) * | 2014-01-20 | 2016-11-24 | Neotiss Sas | Improved tube for a heat exchanger |
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) |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB860510A (en) * | 1959-03-26 | 1961-02-08 | Titeflex Inc | Art of forming flexible corrugated tubing |
FR2009762A1 (en) * | 1968-05-31 | 1970-02-06 | Yorkshire Imperial Metals Ltd | |
US3612175A (en) * | 1969-07-01 | 1971-10-12 | Olin Corp | Corrugated metal tubing |
-
1973
- 1973-06-29 US US00375242A patent/US3841136A/en not_active Expired - Lifetime
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB860510A (en) * | 1959-03-26 | 1961-02-08 | Titeflex Inc | Art of forming flexible corrugated tubing |
FR2009762A1 (en) * | 1968-05-31 | 1970-02-06 | Yorkshire Imperial Metals Ltd | |
US3612175A (en) * | 1969-07-01 | 1971-10-12 | Olin Corp | Corrugated metal tubing |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1998050693A1 (en) * | 1997-05-08 | 1998-11-12 | Brilev, Viktor Leonidovich | Engine with external heat exchanging and method of operating |
US6568076B2 (en) * | 1998-06-05 | 2003-05-27 | Halliburton Energy Services, Inc. | Method of making an internally profiled stator tube |
US9446245B2 (en) | 2001-03-30 | 2016-09-20 | Case Western Reserve University | Systems and methods for selectively stimulating components in, on, or near the pudendal nerve or its branches to achieve selectively physiological responses |
US20160341491A1 (en) * | 2014-01-20 | 2016-11-24 | Neotiss Sas | Improved tube for a heat exchanger |
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) |
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AS | Assignment |
Owner name: WOLVERINE TUBE, INC., 2100 MARKET STREET, N.E., DE Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:UOP INC.,;REEL/FRAME:004657/0711 Effective date: 19861027 Owner name: WOLVERINE TUBE, INC., A DE. CORP.,ALABAMA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:UOP INC.,;REEL/FRAME:004657/0711 Effective date: 19861027 |
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Owner name: BANK OF NOVA SCOTIA, THE, 44 KING STREET, WEST, TO Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:WOLVERINE ACQUISITION CORP. A CORP. OF DE;REEL/FRAME:004696/0897 Effective date: 19870313 |
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Owner name: WOLVERINE ACQUISITION CORP., CORPORATION TRUST CEN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:WOLVERINE TUBE, INC.,;REEL/FRAME:004728/0083 Effective date: 19870318 Owner name: WOLVERINE ACQUISITION CORP., A DE CORP,DELAWARE Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:WOLVERINE TUBE, INC.,;REEL/FRAME:004728/0083 Effective date: 19870318 |
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Owner name: WOLVERINE TUBE, INC., A CORP. OF AL Free format text: CHANGE OF NAME;ASSIGNOR:WOLVERINE ACQUISITION CORP.;REEL/FRAME:004827/0237 Effective date: 19870626 Owner name: WOLVERINE TUBE, INC., A CORP. OF AL,ALABAMA Free format text: CHANGE OF NAME;ASSIGNOR:WOLVERINE ACQUISITION CORP.;REEL/FRAME:004827/0237 Effective date: 19870626 |
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Owner name: WOLVERINE TUBE, INC., 2100 MARKET STREET, N.E., P. Free format text: RELEASED BY SECURED PARTY;ASSIGNOR:BANK OF NOVA SCOTIA, THE;REEL/FRAME:005639/0755 Effective date: 19910123 |
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Owner name: SECURITY PACIFIC NATIONAL BANK Free format text: SECURITY INTEREST;ASSIGNOR:WOLVERINE TUBE, INC.;REEL/FRAME:005648/0195 Effective date: 19910124 |
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Owner name: WOLVERINE TUBE, INC., ALABAMA Free format text: RELEASED BY SECURED PARTY;ASSIGNOR:BANK OF AMERICA TRUST AND SAVINGS ASSOCIATION, SUCCESSOR BY MERGER TO SECURITY PACIFIC NATIONAL BANK;REEL/FRAME:006401/0575 Effective date: 19930108 |