US3326283A - Heat transfer surface - Google Patents

Heat transfer surface Download PDF

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Publication number
US3326283A
US3326283A US443264A US44326465A US3326283A US 3326283 A US3326283 A US 3326283A US 443264 A US443264 A US 443264A US 44326465 A US44326465 A US 44326465A US 3326283 A US3326283 A US 3326283A
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United States
Prior art keywords
fins
tube
cavities
heat transfer
knurling
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Expired - Lifetime
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US443264A
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English (en)
Inventor
Chester D Ware
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Trane US Inc
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Trane Co
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Filing date
Publication date
Application filed by Trane Co filed Critical Trane Co
Priority to US443264A priority Critical patent/US3326283A/en
Priority to GB25894/65A priority patent/GB1035460A/en
Priority to DE19661501656 priority patent/DE1501656A1/de
Priority to CH455466A priority patent/CH510473A/fr
Priority to FR55518A priority patent/FR1472815A/fr
Priority to US654287A priority patent/US3487670A/en
Application granted granted Critical
Publication of US3326283A publication Critical patent/US3326283A/en
Anticipated expiration legal-status Critical
Assigned to TRANE COMPANY THE reassignment TRANE COMPANY THE MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE 12/1/83 WISCONSIN Assignors: A-S CAPITAL INC., A CORP OF DE (CHANGED TO), TRANE COMPANY THE, A CORP OF WI (INTO)
Assigned to A-S CAPITAL INC., A CORP OF DE reassignment A-S CAPITAL INC., A CORP OF DE MERGER (SEE DOCUMENT FOR DETAILS). Assignors: TRANE COMPANY THE A WI CORP
Assigned to A-S CAPITAL INC. reassignment A-S CAPITAL INC. MERGER (SEE DOCUMENT FOR DETAILS). Assignors: TRANE COMPANY THE
Assigned to AMERICAN STANDARD INC., A CORP OF DELAWARE reassignment AMERICAN STANDARD INC., A CORP OF DELAWARE MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE DATE: 12/29/84 - STATE OF INCORP. DE. Assignors: A-S SALEM INC., TRANE COMPANY THE
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
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C37/00—Manufacture of metal sheets, bars, wire, tubes or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape
    • B21C37/06—Manufacture of metal sheets, bars, wire, tubes or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape of tubes or metal hoses; Combined procedures for making tubes, e.g. for making multi-wall tubes
    • B21C37/15—Making tubes of special shape; Making tube fittings
    • B21C37/20—Making helical or similar guides in or on tubes without removing material, e.g. by drawing same over mandrels, by pushing same through dies ; Making tubes with angled walls, ribbed tubes and tubes with decorated walls
    • B21C37/207—Making helical or similar guides in or on tubes without removing material, e.g. by drawing same over mandrels, by pushing same through dies ; Making tubes with angled walls, ribbed tubes and tubes with decorated walls with helical guides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/26—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being integral with the 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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • 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

Definitions

  • This invention relates to an improved heat transfer surface, and more particularly to a heat transfer surface provided with fins or projections for transferring heat from the relatively warm surface to a fluid.
  • nucleate boiling One method of transferring heat from such a surface to a liquid in contact with the surface is nucleate boiling. This is the well known phenomenon according to which vapor bubbles are formed (nucleation) and rise from active spots on the heat transfer surface known as nucleate boiling sites, as the surface temperature rises above the saturation temperature of the liquid.
  • nucleate boiling sites The precise nature of nucleate boiling sites is not known. However, it is generally recognized that nucleation takes place most often and most vigorously at surface irregularities or imperfections in which vapor forming the nucleus of a bubble may be trapped. The rapid emission of bubbles from these sites agitates the liquid adjacent he heat transfer surface, and this is, in part, the reason for the high rate of heat transfer associated with nucleate boiling.
  • the present invention is based on the premise that the rate of heat transfer will be increased as the number of nucleate boiling sites is increased.
  • the improvement lies in the provision of a large number of incipient nucleate boiling sites on a heat transfer surface by forming the surface into a unique shape in a simple and inexpensive manner.
  • the invention has as its object the formation of indentations in fins or projections extending from a solid heat transfer surface, said indentations having the ability to initiate and support nucleate boiling.
  • a further object is to provide indentations in the fin tip material extending from a heat transfer surface by mechanically rearranging the material without actually removing any material.
  • a third object of the invention is to provide indented fins as in the immediately preceding object wherein the indented tip material is flared out beyond the side walls of the fin so that the indentations take the form of cavities.
  • a fourth object is to form the indentations of the immediately preceding object by means of a knurling process.
  • FIGURE 1 is a frontelevation view of a tube embodying the improved heat transfer fins of the invention
  • FIGURE 2 is an end view of the tube of FIGURE 1;
  • FIGURE 3' is a longitudinal sectional view of a portion of the tube of FIGURE 1 taken along line 33 of FIGURE 2;
  • FIGURE 4 is a longitudinal sectional view of a portion of the tube of FIGURE 1 taken along line 4-4 of FIGURE 2;
  • FIGURE 5 is 'an enlarged, front elevation View of a section of the tube of FIGURE 1 more clearly showing the contour of the indentations in the fins;
  • FIGURE 6 is a front elevation view of the machine apparatus for forming indentations in the fins extending from a tube;
  • FIGURE 7 is a transverse sectional view of the ap- 3,326,283 Patented June 20, 1967 paratus of FIGURE 6 taken along the plane indicated by line 7-7;
  • FIGURE 8 is an end view of the apparatus of FIG- URE 6 showing only the roller support for the tubular work piece;
  • FIGURE 9 is a perspective view of a flat plate provided with the indented fins of the invention.
  • the improved heat transfer surface of this invention may be provided on a flat plate having spaced fins or projections on its surface, or on the well known integrally finned tubing commonly employed in evaporators and heat exchangers of the shell and tube type.
  • FIGURES 1 thru 5 illustrates the application of this invention to an integrally finned tube.
  • a plurality of spaced fins 2 extend in a helix along the surface of the tube 1, a number of the fins 2 on the left side of the tube being shown as they exist before being formed into my improved heat transfer surface.
  • superimposed upon the tip metal around the circumference of the fins 2 on the right side of the tube are a number of indentations generally indicated by reference numeral 3, which may preferably take the form of V-shaped cavities.
  • the cavities 3 are preferably formed by mechanically indenting the fin tip metal at spaced intervals in such a way that no metal is actually removed.
  • the metal is simply rearranged in a flared or flowered out cavity, the flared portions of the cavities 3 being indicated by reference numeral 4 in FIGURES 3 and 5. It is important with respect to the improved heat transfer effect to be obtained that the fin tip metal be flowered out transversely by the indenting tool beyond the side wall of the fin as shown at 4.
  • a number of nucleate boiling sites in the form of cavities 3 are provided.
  • the indenting operation is preferably performed by knurling the fins of the tube in a manner to be described below.
  • the impact of the knurling tool displaces the fin tip metal transversely beyond the opposite side walls of each fin to form cavities 3 of the configuration best shown in FIGURE 5. Since the knurling tool has a fiat rather than a sharp, V-shaped tip, the bottom 16 of cavities 3 is also flat as is best shown in FIGURE 2.
  • the indenting tool could be directed against the fins at such an angle as to displace the fin tip metal transversely outwards beyond only one side wall of the fins, as by a broaching operation.
  • Such a process would produce cavities similar to those shown at 3 in FIGURE 5 except that the cavity would be flared out on only one side of the fine by the action of the broaching tool moving transversely against the fin.
  • the impact of the tool striking the fin peripheral edge in a direction normal to the axis of the tube will also form a plurality of minute pockets 9 in the top surfaces of the side walls 12 of cavities 3, as is indicated in FIGURES 4 and 5.
  • the fin tip metal having been hardened initially by the fin forming operation, will be torn into seams 14 (FIGURE 5) of extremely small size along the edges 10 of flared out portions 4.
  • the edges 10 are very thin and very sharp, and thus are split or torn to a certain extent at the bottom 16 of cavities 3 by the indenting operation.
  • Nucleate boiling is actively induced by pockets 9 and seams 14, in which vapor forming the nucleus of a bubble may be trapped.
  • Sharp edges 10 serve the useful purpose of causing cavitation in the liquid flowing adjacent the external surface of tube 1. This results in the formation of small bubbles which initiate nucleate boiling.
  • the cavities 3 terminate short of the base of the fins 2, as is clearly indicated in FIGURES 3 and 4. This results in the formation of additional, relatively large recesses 5 in the space between the underside of flared out portions 4 and the side walls 7 of fins 2 (FIGURES 3 and Recesses 5 also serve as nucleate boiling sites.
  • Nucleate boiling also takes place from points 8 on the surface of tube 1 between adjacent fins 2 in cavities 6. Nucleate boiling at points 8 and the attendant high heat transfer will be rapid and continuous so long as the vapor bubbles produced at these points have an unimpeded discharge path. For this reason, gap a between adjacent edges of flared out portions 4 is controlled so as not to unduly restrict the flow of liquid to and vapor bubbles from points 8 on the surface of tube 1 (FIGURE 4). This is done by regulating the depth of cavities 3, and thus limiting the extent of flaring or flowering out of edges 10 during the indenting process.
  • gaps a within a range of 35% to 75% of the initial distance b (FIGURE 3) between the side walls 7 of adjacent fins 2 at the top thereof.
  • Optimum results were obtained with gaps a held within a range of 0.020 to 0.025 inch.
  • a range of 0.015 to 0.030 inch would also be workable, but not as satisfactory as the more limited range for gaps a.
  • the gaps a controlled in this manner the depth of cavities 3 will always be less than one-half of the height of fins 2.
  • the size of gaps a becomes a particular problem under conditions where there is a high temperature dilferential between the external surface of tube 1 and the boiling liquid.
  • the gap control problem discussed above could be substantially elminated by randomly spacing cavities 3 so that flared out portions 4 of adjacent fins are not in axial alignment. With such an arrangement, there would be no problem of forming relatively narrow gaps a between adjacent fins 2.
  • FIGURES 6 thru 8 The preferred machining arrangement for forming the indentations 3 in the fins 2 of the tube 1 of FIGURES 1 thru 5 is shown in FIGURES 6 thru 8.
  • the finned copper tube work piece 1 is supported at one end in the clamping teeth 22 of chuck 20.
  • Finned tube 1 is supported at its other end by means of a roller assembly comprised of a base portion 24 and a head portion 26.
  • Three roller wheels 28, 30, and 32 are mounted in the base 24 for rotation about their longitudinal axis.
  • a single roller wheel 34 is similarly mounted in head 26.
  • Head 26 is slidably mounted for transverse movement by means of pneumatic or hydraulic means not shown.
  • tube 1 may be placed in base portion 24 in contact with roller wheels 28, 30, and 32; and then head 26 may be moved transversely into the position shown, whereby roller wheel 34 will come into contact with the top of tube 1.
  • a knurling tool assembly generally indicated by reference numeral 50 is provided for forming the indentations 3 in the fins 2 of tube 1.
  • Knurling wheel 36 is mounted in base 40 of assembly 50 for free rotation about its longitudinal axis, and knurling wheel 38 is similarly mounted in transversely movable head 42.
  • Head 42 is fixedly mounted on base 40 for movement therewith, longitudinal movement being imparted to knurling assembly 50 by means of lead screw 44. Head 42 may also be moved transversely with respect to base 40 by hydraulic or pneumatic means not shown.
  • the axis of rotation of knurling wheel 38 is slightly laterally offset with respect to the longitudinal axis of tube 1.
  • the teeth 48 of knurling wheel 38 will advance into contact with the peripheral surface of fins 2 and force tube 1 downwardly against the teeth of knurling wheel 36 as head 42 is moved transversely into the position shown.
  • the depth of cavities 3, and thus the size of gap a between flared out portions 4 of adjacent fins 2 (FIGURES 3 and 4) i is determined by adjusting the ram force applied to head 42. It is noted that when a relatively long piece of finned tubing is to be knurled, a number of roller assemblies 2426 may be positioned at spaced intervals along the tube in order to properly support it. A plurality of knurling assemblies 50 may then be employed to knurl the portions of the finned tube between roller supports.
  • knurling tool assembly 50 could be mounted on a standard fin forming machine.
  • Apparatus as is conventionally employed for rolling fins in the wall of a tube is shown in United States Patent No. 1,865,- 575, issued on July 5, 1932 to Locke.
  • the fins are formed integrally with the tube wall by means of roller dies moving radially against the tube as the tube is propelled longitudinally past the roller.
  • Knurling wheels 36 and 38 could be positioned radially outwards from the path of longitudinal movement of the tubular work piece, and adjacent the roller dies beyond the final forming stage thereof so that as the rotating tube moves longitudinally forward, the fins will first be formed in the tube and then the fins will be indented by the knurling wheels.
  • the knurling wheels 36 and 38 would not move longitudinally as in the process illustrated in FIGURES 6-8, but rather the knurling wheels would be mounted at fixed stations positioned circumferentially about the longitudinally moving tube.
  • tube 1 is placed in position with one end in chuck 20 and the other end supported in roller base portion 24.
  • Roller head 26 is then moved transversely into the position shown in FIGURE 8.
  • a rotational force is applied to chuck 20, and to lead screw 44 by power transmission means within headstock 46, and motor means drivingly connected thereto (not shown).
  • Tube 1 will thus be caused to rotate with chuck 20.
  • knurling tool 38 is advanced into contact with fins 2 by transverse movement of head 42. Knurling tools 36 and 38 are rotated against fins 2 as a result of being in frictional contact with rotating tube 1.
  • teeth 48 of knurling tools 38 and 36 will deliver a series of impacts against the peripheral surface of fins 2 so as to displace the fin tip metal into the shape of cavities 3 shown in FIGURES l, 2 and 5.
  • Cavities 3 will be formed in fins 2 along the length of tube 1 as the knurling assembly 50 is moved parallel to the longitudinal axis of tube 1 by rotation of lead screw 44. This longitudinal movement of knurling assembly 50 causes more of the fin tip metal in cavities 3 to be displaced in the direction in which knurling assembly 50 is moving.
  • flared out portions 4 will extend farther beyond one side wall 7 of fins 2 than the other.
  • Knurling wheels 36 and 38 are so constructed and arranged that the teeth of lower wheel 36 strike fins 2 in generally, but not precisely, the same cavities3 formed by the teeth of upper Wheel 38. This causes cavities 3 to have roughened walls, the rough spots serving to induce nucleate boiling.
  • knurling wheels 36 and 38 have straight teeth parallel to the wheel axis. Tools of this type will form cavities 3 of the shape most clearly shown in FIGURE 5. Knurling tools having teeth in a herringbone or diamond pattern may also be employed. Such tools would of course produce cavities in fins 2 having a herringbone pattern.
  • the pitch (number of teeth per inch of circumference) of the knurling wheel is quite critical. Thus, if too coarse a knurling tool having less than 14 teeth per circumferential inch is used, the resulting low number of cavities formed will not produce a significant increase in heat transfer.
  • the number of streams of bubbles rising from active nucleation sites on the finned tube was seen to increase as much as ten times in comparison with an ordinary finned tube.
  • the operation of the shell and tube evaporator with my improved heat transfer surface resulted in a seven percent increase in overall heat transfer for a given temperature differential between the water and the refrigerant.
  • FIGURE 9 illustrates the application of my improved heat transfer surface to fins 62 extending from a flat plate 60.
  • a flat plate 60 Such a plate would normally be used in an application where boiling liquid is in contact with the fins 62 and the top of the plate 60, and a relatively warmer fluid is in contact with the bottom of the plate.
  • Cavities 64 of a configuration similar to that of cavities 3 shown in FIGURES 1 thru 5 are formed in fins 62 by placing plate 60 on the bed plate of a milling machine and moving a rotating knurling or milling tool over the finned surface in a horizontal direction parallel to the plane of plate 60. Edges 68 of side walls 66 of cavities 64 are flared out beyond side walls 70 of fins 62 for the purpose described above with respect to flared out portions 4 of cavities 3.
  • the imperfect surface of the indenting tool forming the cavities 64 will also form a plurality of minute pockets 72 similar to pockets 9 of cavities 3 in FIGURES 4 and 5.
  • the base 74 of cavities 64 will also be split into a number of extremely small seams 76 by the impact of the indenting tool on the fin surface.
  • the cavities 64 aided by pockets 72 and seams 76 in the surface thereof, serve to initiate and sustain nucleate boiling. As a result heat transfer to the liquid in contact with fins 62 is greatly increased.
  • the gap between adjacent flared-out edges 68 must be controlled in the manner described above with respect to gaps a by regulating the depth of cavities 64 so as not to unduly restrict the flow of bubbles rising from the top surface of plate 60 between fins 62.
  • a heat exchanger comprising a base wall, a plurality of spaced apart fins having opposed side walls extending from the surface of said base wall, a plurality of indentations disposed in the peripheral edge of each of said fins, each of said indentations extending entirely across the Width of one of said fins and including a flared out portion of fin tip material extending transversely beyond one of said side walls.
  • a heat exchanger comprising a base wall, a plurality of spaced apart fins having opposed side walls extending from the surface of said base wall, a plurality of indentations in the peripheral edge of each of said fins, each of said indentations extending entirely across the width of one of said fins and including flared out portions of fin tip material projecting transversely of each side of said fins beyond said opposed side walls.
  • indentations have side walls directed inwardly and downwardly toward said base wall in a generally V-shaped configuration; and further including a plurality of small nucleation pockets in the surface of said last mentioned side walls.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Turning (AREA)
  • Milling Processes (AREA)
US443264A 1965-03-29 1965-03-29 Heat transfer surface Expired - Lifetime US3326283A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US443264A US3326283A (en) 1965-03-29 1965-03-29 Heat transfer surface
GB25894/65A GB1035460A (en) 1965-03-29 1965-06-18 Improved heat transfer surface
DE19661501656 DE1501656A1 (de) 1965-03-29 1966-03-25 Waermeaustauscher
FR55518A FR1472815A (fr) 1965-03-29 1966-03-29 Surface de transmission de chaleur perfectionnée
CH455466A CH510473A (fr) 1965-03-29 1966-03-29 Elément d'échange de chaleur et procédé pour sa fabrication
US654287A US3487670A (en) 1965-03-29 1967-04-17 Method of forming indentations in fins extending from a heat transfer surface

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US443264A US3326283A (en) 1965-03-29 1965-03-29 Heat transfer surface

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US3326283A true US3326283A (en) 1967-06-20

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CH (1) CH510473A (de)
DE (1) DE1501656A1 (de)
GB (1) GB1035460A (de)

Cited By (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3457990A (en) * 1967-07-26 1969-07-29 Union Carbide Corp Multiple passage heat exchanger utilizing nucleate boiling
US3521708A (en) * 1968-10-30 1970-07-28 Trane Co Heat transfer surface which promotes nucleate ebullition
US3602027A (en) * 1969-04-01 1971-08-31 Trane Co Simultaneous finning and reforming of tubular heat transfer surface
US3696861A (en) * 1970-05-18 1972-10-10 Trane Co Heat transfer surface having a high boiling heat transfer coefficient
US3768290A (en) * 1971-06-18 1973-10-30 Uop Inc Method of modifying a finned tube for boiling enhancement
US3893322A (en) * 1974-08-21 1975-07-08 Universal Oil Prod Co Method for providing improved nucleate boiling surfaces
US4040479A (en) * 1975-09-03 1977-08-09 Uop Inc. Finned tubing having enhanced nucleate boiling surface
US4159739A (en) * 1977-07-13 1979-07-03 Carrier Corporation Heat transfer surface and method of manufacture
US4168618A (en) * 1978-01-26 1979-09-25 Wieland-Werke Aktiengesellschaft Y and T-finned tubes and methods and apparatus for their making
US4179911A (en) * 1977-08-09 1979-12-25 Wieland-Werke Aktiengesellschaft Y and T-finned tubes and methods and apparatus for their making
US4227572A (en) * 1978-03-27 1980-10-14 Seton-Scherr, Inc. Finned tubing
US4245695A (en) * 1978-05-15 1981-01-20 Furukawa Metals Co., Ltd. Heat transfer tube for condensation and method for manufacturing same
US4353234A (en) * 1977-07-13 1982-10-12 Carrier Corporation Heat transfer surface and method of manufacture
US4549606A (en) * 1982-09-08 1985-10-29 Kabushiki Kaisha Kobe Seiko Sho Heat transfer pipe
US5186252A (en) * 1991-01-14 1993-02-16 Furukawa Electric Co., Ltd. Heat transmission tube
US5203404A (en) * 1992-03-02 1993-04-20 Carrier Corporation Heat exchanger tube
US5332034A (en) * 1992-12-16 1994-07-26 Carrier Corporation Heat exchanger tube
US5458191A (en) * 1994-07-11 1995-10-17 Carrier Corporation Heat transfer tube
US5513699A (en) * 1993-01-22 1996-05-07 Wieland-Werke Ag Heat exchanger wall, in particular for spray vaporization
US6176302B1 (en) * 1998-03-04 2001-01-23 Kabushiki Kaisha Kobe Seiko Sho Boiling heat transfer tube
US6382311B1 (en) 1999-03-09 2002-05-07 American Standard International Inc. Nucleate boiling surface
US6427767B1 (en) 1997-02-26 2002-08-06 American Standard International Inc. Nucleate boiling surface
US20070131396A1 (en) * 2005-12-13 2007-06-14 Chuanfu Yu Condensing heat-exchange copper tube for an flooded type electrical refrigeration unit
US7276046B1 (en) * 2002-11-18 2007-10-02 Biosynergy, Inc. Liquid conductive cooling/heating device and method of use
DE102006054914A1 (de) * 2006-11-22 2008-05-29 Volkswagen Ag Verfahren und Vorrichtung zur Kühlung einer Brennstoffzelle
DE102009021334A1 (de) 2009-05-14 2010-11-18 Wieland-Werke Ag Metallisches Wärmeaustauscherrohr
US20110226457A1 (en) * 2010-03-18 2011-09-22 Golden Dragon Precise Copper Tube Group Inc. Condensation enhancement heat transfer pipe
US20120222447A1 (en) * 2009-04-30 2012-09-06 Uop Llc Tubular Condensers Having Tubes with External Enhancements
US20120285664A1 (en) * 2011-05-13 2012-11-15 Rochester Institute Of Technology Devices with an enhanced boiling surface with features directing bubble and liquid flow and methods thereof
US20130025834A1 (en) * 2011-07-26 2013-01-31 Choi Gun Shik Double tube type heat exchange pipe
DE102011121436A1 (de) 2011-12-16 2013-06-20 Wieland-Werke Ag Verflüssigerrohre mit zusätzlicher Flankenstruktur
US20130319645A1 (en) * 2011-01-06 2013-12-05 Tetra Laval Holdings & Finance S.A. Optimised surface for freezing cylinder
US20160025010A1 (en) * 2013-03-26 2016-01-28 United Technologies Corporation Turbine engine and turbine engine component with cooling pedestals
US10209014B2 (en) 2014-02-20 2019-02-19 Modine Manufacturing Company Brazed heat exchanger

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DE2758527C2 (de) * 1977-12-28 1985-04-25 Wieland-Werke Ag, 7900 Ulm Verfahren und Vorrichtung zur Herstellung eines Rippenrohres
DE2758526C2 (de) * 1977-12-28 1986-03-06 Wieland-Werke Ag, 7900 Ulm Verfahren und Vorrichtung zur Herstellung eines Rippenrohres
DE3048959C2 (de) * 1980-12-24 1985-08-29 Wieland-Werke Ag, 7900 Ulm Verfahren und Vorrichtung zur Herstellung eines Rippenrohres für Wärmeübertrager o.dgl.
GB2127327B (en) * 1982-08-20 1986-04-30 Alton Systems Limited An antiskid surface treatment for use on scaffolding components
EP0144460A1 (de) * 1983-12-10 1985-06-19 Wieland-Werke AG Verfahren zur Herstellung eines Wärmeübertragungsrohres
JPS63189793A (ja) * 1987-02-02 1988-08-05 Mitsubishi Electric Corp 蒸発・凝縮用伝熱管
DE4404357C2 (de) * 1994-02-11 1998-05-20 Wieland Werke Ag Wärmeaustauschrohr zum Kondensieren von Dampf
US5915470A (en) * 1997-10-15 1999-06-29 Dierbeck; Robert F. Modular heat exchanger
US6173493B1 (en) 1998-10-15 2001-01-16 Robert F. Dierbeck Modular heat exchanger and method of making

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DE1118235B (de) * 1959-10-13 1961-11-30 Thomson Houston Comp Francaise Siedekuehlvorrichtung fuer starker Hitze unterworfene Koerper, insbesondere Elektronenroehrenanoden
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US3457990A (en) * 1967-07-26 1969-07-29 Union Carbide Corp Multiple passage heat exchanger utilizing nucleate boiling
US3521708A (en) * 1968-10-30 1970-07-28 Trane Co Heat transfer surface which promotes nucleate ebullition
US3602027A (en) * 1969-04-01 1971-08-31 Trane Co Simultaneous finning and reforming of tubular heat transfer surface
US3696861A (en) * 1970-05-18 1972-10-10 Trane Co Heat transfer surface having a high boiling heat transfer coefficient
US3768290A (en) * 1971-06-18 1973-10-30 Uop Inc Method of modifying a finned tube for boiling enhancement
US3893322A (en) * 1974-08-21 1975-07-08 Universal Oil Prod Co Method for providing improved nucleate boiling surfaces
US4040479A (en) * 1975-09-03 1977-08-09 Uop Inc. Finned tubing having enhanced nucleate boiling surface
US4353234A (en) * 1977-07-13 1982-10-12 Carrier Corporation Heat transfer surface and method of manufacture
US4159739A (en) * 1977-07-13 1979-07-03 Carrier Corporation Heat transfer surface and method of manufacture
US4179911A (en) * 1977-08-09 1979-12-25 Wieland-Werke Aktiengesellschaft Y and T-finned tubes and methods and apparatus for their making
US4168618A (en) * 1978-01-26 1979-09-25 Wieland-Werke Aktiengesellschaft Y and T-finned tubes and methods and apparatus for their making
US4227572A (en) * 1978-03-27 1980-10-14 Seton-Scherr, Inc. Finned tubing
US4245695A (en) * 1978-05-15 1981-01-20 Furukawa Metals Co., Ltd. Heat transfer tube for condensation and method for manufacturing same
US4549606A (en) * 1982-09-08 1985-10-29 Kabushiki Kaisha Kobe Seiko Sho Heat transfer pipe
US5186252A (en) * 1991-01-14 1993-02-16 Furukawa Electric Co., Ltd. Heat transmission tube
US5203404A (en) * 1992-03-02 1993-04-20 Carrier Corporation Heat exchanger tube
US5332034A (en) * 1992-12-16 1994-07-26 Carrier Corporation Heat exchanger tube
US5513699A (en) * 1993-01-22 1996-05-07 Wieland-Werke Ag Heat exchanger wall, in particular for spray vaporization
US5458191A (en) * 1994-07-11 1995-10-17 Carrier Corporation Heat transfer tube
US6427767B1 (en) 1997-02-26 2002-08-06 American Standard International Inc. Nucleate boiling surface
US6176302B1 (en) * 1998-03-04 2001-01-23 Kabushiki Kaisha Kobe Seiko Sho Boiling heat transfer tube
US6382311B1 (en) 1999-03-09 2002-05-07 American Standard International Inc. Nucleate boiling surface
US7276046B1 (en) * 2002-11-18 2007-10-02 Biosynergy, Inc. Liquid conductive cooling/heating device and method of use
US20070131396A1 (en) * 2005-12-13 2007-06-14 Chuanfu Yu Condensing heat-exchange copper tube for an flooded type electrical refrigeration unit
US7762318B2 (en) * 2005-12-13 2010-07-27 Golden Dragon Precise Copper Tube Group, Inc. Condensing heat-exchange copper tube for an flooded type electrical refrigeration unit
DE102006054914A1 (de) * 2006-11-22 2008-05-29 Volkswagen Ag Verfahren und Vorrichtung zur Kühlung einer Brennstoffzelle
US9297580B2 (en) * 2009-04-30 2016-03-29 Uop Llc Tubular condensers having tubes with external enhancements
US20120222447A1 (en) * 2009-04-30 2012-09-06 Uop Llc Tubular Condensers Having Tubes with External Enhancements
US20140102134A1 (en) * 2009-04-30 2014-04-17 Uop Llc Tubular condensers having tubes with external enhancements
US8684337B2 (en) * 2009-04-30 2014-04-01 Uop Llc Tubular condensers having tubes with external enhancements
US20100288480A1 (en) * 2009-05-14 2010-11-18 Andreas Beutler Metallic heat exchanger tube
DE102009021334A1 (de) 2009-05-14 2010-11-18 Wieland-Werke Ag Metallisches Wärmeaustauscherrohr
US8550152B2 (en) 2009-05-14 2013-10-08 Wieland-Werke Ag Metallic heat exchanger tube
US20110226457A1 (en) * 2010-03-18 2011-09-22 Golden Dragon Precise Copper Tube Group Inc. Condensation enhancement heat transfer pipe
US9683791B2 (en) * 2010-03-18 2017-06-20 Golden Dragon Precise Copper Tube Group Inc. Condensation enhancement heat transfer pipe
US20130319645A1 (en) * 2011-01-06 2013-12-05 Tetra Laval Holdings & Finance S.A. Optimised surface for freezing cylinder
US20120285664A1 (en) * 2011-05-13 2012-11-15 Rochester Institute Of Technology Devices with an enhanced boiling surface with features directing bubble and liquid flow and methods thereof
US10697629B2 (en) * 2011-05-13 2020-06-30 Rochester Institute Of Technology Devices with an enhanced boiling surface with features directing bubble and liquid flow and methods thereof
US11598518B2 (en) 2011-05-13 2023-03-07 Rochester Institute Of Technology Devices with an enhanced boiling surface with features directing bubble and liquid flow and methods thereof
US20130025834A1 (en) * 2011-07-26 2013-01-31 Choi Gun Shik Double tube type heat exchange pipe
WO2013087140A1 (de) 2011-12-16 2013-06-20 Wieland-Werke Ag Verflüssigerrohre mit zusätzlicher flankenstruktur
DE102011121436A1 (de) 2011-12-16 2013-06-20 Wieland-Werke Ag Verflüssigerrohre mit zusätzlicher Flankenstruktur
US10094625B2 (en) 2011-12-16 2018-10-09 Wieland-Werke Ag Condenser tubes with additional flank structure
US10974309B2 (en) 2011-12-16 2021-04-13 Wieland-Werke Ag Condenser tubes with additional flank structure
US20160025010A1 (en) * 2013-03-26 2016-01-28 United Technologies Corporation Turbine engine and turbine engine component with cooling pedestals
US10209014B2 (en) 2014-02-20 2019-02-19 Modine Manufacturing Company Brazed heat exchanger

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GB1035460A (en) 1966-07-06
DE1501656A1 (de) 1969-10-30
CH510473A (fr) 1971-07-31

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