US3696861A - Heat transfer surface having a high boiling heat transfer coefficient - Google Patents
Heat transfer surface having a high boiling heat transfer coefficient Download PDFInfo
- Publication number
- US3696861A US3696861A US37476A US3696861DA US3696861A US 3696861 A US3696861 A US 3696861A US 37476 A US37476 A US 37476A US 3696861D A US3696861D A US 3696861DA US 3696861 A US3696861 A US 3696861A
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- Prior art keywords
- fins
- boiling
- heat transfer
- next adjacent
- portions
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Classifications
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- 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
- F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
- F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B37/00—Component parts or details of steam boilers
- F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
- F22B37/10—Water tubes; Accessories therefor
- F22B37/101—Tubes having fins or ribs
-
- 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
- Y10T29/49353—Heat pipe device making
-
- 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
- Y10T29/49385—Made from unitary workpiece, i.e., no assembly
Definitions
- HEAT TRANSFER SURFACE HAVING A HIGH BOILING HEAT TRANSFER COEFFICIENT [72] Inventor: Ralph L. Webb, La Crosse, Wis.
- ABSTRACT A heat transfer surface comprising a heat conductive base member and a plurality of spaced apart fins extending therefrom, each of said fins being bent over towards the next adjacent fin so as to form therebetween elongated, re-entrant cavities.
- the gap between the tip of one of said fins and the next adjacent fin is sufficiently small to promote and sustain nucleate boiling of a fluid in contact with said fins and said base member.
- nucleation sites be covered by a certain thickness of superheated liquid.
- the bubbles rise in continuous columns from nucleation sites, they interrupt the boundary layer of superheated liquid and carry superheated liquid away from the hot wall surface. It is believed that the greater part of vapor formation in nucleate boiling occurs as superheated liquid evaporates into the liquid-vapor interface of rising bubbles. Moreover, the agitation of the liquid by rapid bubble departures increases the rate of heat transfer to the liquid by forced convection.
- the boiling heat transfer coefficient will vary with the area density of nucleation sites. It would therefore be highly desirable from a performance standpoint to treat or condition a heat transfer surface in such a way as to cause a greater density of bubble columns for a particular value of AT.
- the fins are bent in such a manner and to such extent that the tip of each fin is spaced from the next adjoining fin by a gap which is narrower than the space between the bases of said fins.
- the aforesaid gap is controlled so as to be small enough to initiate nucleate boiling, and is preferably between 0.0015 and 0.0035 inches wide where the boiling fluid is Refrigerant 11.
- the aforesaid elongated, nucleation promoting grooves are produced by bending the fins over on a finned tube of the well known type commonly employed in shell-and-tube heat exchangers.
- FIG. 1 is a front elevation view of a finned tube showing a number of the fins shaped to provide the nucleate boiling surface of my invention.
- FIG. 2 is a vertical section view taken along line 2-2 of FIG. 1.
- FIG. 3 is a vertical section view on an enlarged scale taken along line 3-3 of FIG. 2.
- F IG. 4 is a diagrammatic view of a refrigeration system including an evaporator in which my improved nucleate boiling surface could be employed.
- FIG. 5 is a graph showing the improved heat transfer performance obtained with a surface conditioned in accordance with this invention.
- FIG. 6 is a schematic illustration of a machining arrangement for forming the heat transfer surface geometry of this invention.
- FIG. 1 illustrates the manner in which my nucleate boiling groove concept can be applied to a finned tube.
- a plurality of spaced apart fins 2 extend from the base member or tube 1, and may be connected in a continuous helical pattern as in the configuration shown. Fins 2 could be made from a separate material and attached to the outer surface of tube 1 or they could be machined from tube 1 so as to be integral therewith. The latter arrangement has been shown for illustrative purposes.
- the substantially vertically extending fins 2 on the left side of tube 1 represent a conventional finned tube surface prior to forming according to my invention.
- the saturated nucleate boiling obtained from fins formed as shown in the right portion of FIG. 1 and having a gap in the range of 0.001 0.005 will provide a substantially higher heat flux at a given AT than would be provided by fins formed as shown in the left portion of FIG. 1.
- a second requisite characteristic of the final fin geometry is that the distance of gap a between the tip edge 6 of one fin andthe next adjacent fin be less than the distance between base portions 8 of adjacent fins 2. This insures that a re-entrant shaped cavity or groove 10 having a restricted opening defined by gap a is formed between adjacent fins 2. Additionally, fins'2 are bent from their bases 8 so that bases 8 intersect tube 1 at an angle to the vertical. This permits tip portions 4 to be bent over sufficiently far that their outer edges 6 overlap the base 8 of the next adjacent fin by a distance b shown in FIG. 3. I prefer that the dimension b shall be in the range of one-half to one and one-half times the thickness of the fin.
- fins 2 When the basic surface to be modified in accordance with my invention is a tube, fins 2 may be'rollformed from the tube outer surface in a continuous helix in a manner well known in the art. Fins 2 may then be bent over to provide the above described elongated re-entrant grooves 10 in a simple operation as illustrated in FIG. 6. I have accomplished this by rotating a finned tube 1 in a chuck and feeding a bending or rolling tool 14 parallel to the tube axis by means of a lead screw. The folling or bending tool must have an angled tip 16 capable of producing the desired degree of bending of the fins. The direction of rotation of tube land the direction of movement of tool 14 are indicated by arrows in FIG. 6.
- the performance curves of FIG. 5 illustrate the improved heat transfer achieved with my novel surface. These results were obtained in a pool boiling environment using Refrigerant 11 at a saturated pool boiling temperature of F.
- Curve I shows the boiling performance of an ordinary finned surface as illustrated on the left side of the tube of FIG. 1.
- Curve II shows the boiling performance achieved with fins 2 bent over to form re-entrant grooves 10 as illustrated on the right side of the tube in FIG. 1 and in FIGS. 2 and 3.
- the dramatic improvement in boiling performance obtained with my bent fin arrangement is readily apparent. For example, with a AT of 4, the total boiling heat flux in Btu per hour per square foot of base surface for my improved boiling surface was 1 1,000 compared to a value of only 1,750 for the ordinary finned surface.
- FIG. 4 illustrates diagrammatically a standard compression refrigeration system with a shell-and-tube evaporator 20 in which my bent fin tube surface could be used.
- Evaporator 20 is connected in a refrigeration circuit including compressor 22, condenser '24, and flow regulating valve 26. Either a reciprocating or centrifugal type of compressor could be employed, centrifugal compressor 22 having been shown for illustrative purposes.
- Evaporator 20 is comprised of a shell 21, headers 23 and 25, and closely spaced tubes 30 for conducting fluid to be cooled from inlet header 23 to outlet header 25. Water or other fluid to be cooled flows from inlet 28 through tubing 30 and is discharged through outlet 32.
- Refrigerant liquid from condenser 24 is expanded into shell 21 as it flows from control valve 26.
- the refrigerant which enters evaporator 20 is a mixture of liquid and vapor.
- the liquid is evaporated as the refrigerant flows through shell 21 in contact with the outside of tubing 30.
- Heat transfer to the refrigerant thus takes place by the combined modes of forced convection and nucleate boiling, thus making it more difficult to predict the total increase in heat flux to be realized by improving the nucleate boiling performance of finned tubing 30.
- My experimental results have demonstrated that a significant increase in total heat flux is achieved by utilizing my bent fin surface unser such conditions. The net increase in heat flux closely approximates the direct addition of the pool boiling and forced convection heat fluxes for a particular surface.
- the high boiling performance may be due at least in part to modifications of the hydrodynamic conditions in the vicinity of preexisting nucleation sites in the form of pits and scratches on tube 1 and the walls of fins 2.
- Nucleate boiling theory assumes that when a bubble departs from a surface, liquid surrounding the nucleation site rushes in to fill the void left by the departed bubble. The site will not again activate until this liquid is warmed up to the necessary superheat level.
- ordinary finned tubes, or with prior art boiling surfaces having a plurality of surface pits cold, saturated liquid from above the fins or base surface rushes directly onto the fully exposed nucleation sites.
- My bent fin surface achievesthe desirable goal of substantially improving the nucleate boiling performance of the widely utilized finned tube. This has been accomplished ina very simple way requiring only the rolling over of the fins in the manner described above. Although I have shown and described the rolled over fin configuration as applied to a tubular base membenit could readily be formed on a flat plate as well. Whether the base member is a tube or a plate, there are obviously a great variety of heat transfer ap plications on which the unique boiling surface geometry of this invention could be applied.
- a heat exchange comprising: a heat conductive base member for transferring heat from a heat source on one side thereof to a boiling fluid on the other side thereof; a plurality of spaced apart fins having substantially smooth and uninterrupted side surfaces extending from said other side of said base member, each of said fins having a base portion joined to said base member and a tip portion, said tip portions being bent over toward the next adjacent one of said fins to form a a continuous gap having a width of from 0.001 to 0.005 inches, the gaps between said tip portions and said next adjacent one of said fins being less than the spaces between said base portions, whereby a continuous reentrant shaped cevity sufficient to promote nucleate boiling of a given liquid is formed between adjacent ones of said fins; said boiling fluid selected from the group of refrigerant fluids consisting of trichloromonofluoromethane, monochlorodifluoromethane, dichlorodifluoromethane, trichlorotrifluoroethane, dich
- bent fins are of curvilinear cross-section over substantially their entire height.
- said tip portions overlap said base portion of saidnext adjacent one of said finssby a distance of from one-half to one and one-half times the thickness of one of said fins.
- said boiling fluid comprises trichloromonofluoromethane and said gaps between said tip portions and said next adjacent one of said fins are within a range of from 0.0015 to 0.0035 inches.
- said fins are formed integrally with said base member.
- said tip portions overlap said base portion of said next adjacent fins.
- an improved heat transfer surface for said evaporator comprising: a plurality of tubular members through which a relatively warm fluid to be cooled passes; a plurality of spaced apart fins having substantially-smooth and uninterrupted side'surfaces extending from each of said tubular members, the outside of said tubular members and said fins being in contact with refrigerant fluid flowing through said evaporator; and each of said fins having a base portion joined to one.
- each of said tip portions being bent over toward .the next adjacent one of said fins to overlap said base portion of said next adjacent one of said fins and being separated therefrom by a gap sufficiently narrow to promote and sustain nucleate boiling of said refrigerant fluid; said boiling fluid selected from the group consisting of trichloromonofluoromethane, monochlorodifuloromethane, dichlorotetrafluoroethane and a 48.8/51.2 weight percent azeotropic mixture of monochlorodifuloromethane and monochloropentafluoroethane, respectively; said gaps between said tip portions and said next adjacent one of said fins being in the range of from 0.001 to 0.005 inches.
- each of said fins is curved over its entire height towards said next adjacent one of said fins.
- said refrigerant fluid comprises trichloromonofluoromethane and said gap is between 0.0015 and 0.0035 inches wide.
- a heat exchanger comprising a plurality of tubes for conducting a relatively warm fluid to be cooled by transferring heat to a boiling fluid surrounding said tubes, helical heat transfer fins on said tubes and ex-v tending outwardly from said tube, said helical heat transfer fins having base portions integral with the outer surface of said tube and having substantially smooth and uninterrupted side surfaces and tip portions, said tip portions being bent over toward the next adjacent one of said heat transfer fins, the spaces between said heat transfer fins at their outer ends being less than the spaces between said. heat transfer fins at their bases whereby continuous re-entrant shaped cavities are provided to enhance boiling.
- a heat exchanger comprising a plurality of tubes for conducting a relatively warm fluid to be cooled by transferring heat to a boiling fluid surrounding said tubes, helical heat transfer fins on the outer surface of said tubes, said helical fins having base portions integral with the outer surface of said tubes, said fins having substantially smooth and uninterrupted side surfaces and extending outwardly from their base portions to distal portions, the distal portions being curved toward the next adjacent fins, the spaces between the distal portions and the next adjacent fins being less than the spaces between the base portions of the fins whereby substantially continuous re-entrant shaped cavities are provided to enhance boiling.
- a heat exchanger comprising a tube for conducting a relatively warm fluid to be cooled by transferring heat to a boiling fluid surrounding said tube, helical heat transfer fins at the outer surface of and substantially co-axially disposed with respect to said tube, said helical fins having base portions integral with the outer surface of said tube, said fins having substantially smooth and uninterrupted side surfaces and extending outwardly from their base portions to distal portions, the distal portions being curved toward one end of the tube and terminating in closely spaced relation with the next adjacent fin to define substantially uniform helical gaps between the distal portions and the next adjacent fins which are substantially less in width than the spaces between the base portions of the fins whereby substantially continuous helically shaped re-entrant cavities are provided to enhance boiling.
Abstract
Description
Claims (14)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US3747670A | 1970-05-18 | 1970-05-18 |
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US3696861A true US3696861A (en) | 1972-10-10 |
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US37476A Expired - Lifetime US3696861A (en) | 1970-05-18 | 1970-05-18 | Heat transfer surface having a high boiling heat transfer coefficient |
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Cited By (56)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3768290A (en) * | 1971-06-18 | 1973-10-30 | Uop Inc | Method of modifying a finned tube for boiling enhancement |
US3850236A (en) * | 1973-03-26 | 1974-11-26 | Peerless Of America | Heat exchangers |
US3881342A (en) * | 1972-07-14 | 1975-05-06 | Universal Oil Prod Co | Method of making integral finned tube for submerged boiling applications having special o.d. and/or i.d. enhancement |
US4018264A (en) * | 1975-04-28 | 1977-04-19 | Borg-Warner Corporation | Boiling heat transfer surface and method |
US4059147A (en) * | 1972-07-14 | 1977-11-22 | Universal Oil Products Company | Integral finned tube for submerged boiling applications having special O.D. and/or I.D. enhancement |
US4060125A (en) * | 1974-10-21 | 1977-11-29 | Hitachi Cable, Ltd. | Heat transfer wall for boiling liquids |
DE2829070A1 (en) * | 1977-07-13 | 1979-02-01 | Carrier Corp | AREA USED FOR HEAT TRANSFER AND METHOD FOR PRODUCING THE SAME |
USRE30077E (en) * | 1968-05-14 | 1979-08-21 | Union Carbide Corporation | Surface for boiling liquids |
US4186063A (en) * | 1977-11-01 | 1980-01-29 | Borg-Warner Corporation | Boiling heat transfer surface, method of preparing same and method of boiling |
US4216826A (en) * | 1977-02-25 | 1980-08-12 | Furukawa Metals Co., Ltd. | Heat transfer tube for use in boiling type heat exchangers and method of producing the same |
US4258783A (en) * | 1977-11-01 | 1981-03-31 | Borg-Warner Corporation | Boiling heat transfer surface, method of preparing same and method of boiling |
US4359086A (en) * | 1981-05-18 | 1982-11-16 | The Trane Company | Heat exchange surface with porous coating and subsurface cavities |
US4366859A (en) * | 1975-04-02 | 1983-01-04 | Keyes John M | Refractory heat exchange tube |
US4438807A (en) * | 1981-07-02 | 1984-03-27 | Carrier Corporation | High performance heat transfer tube |
US4471833A (en) * | 1981-08-31 | 1984-09-18 | Agency Of Industrial Science & Technology | Augmentation method of boiling heat transfer by applying electric fields |
US4495988A (en) * | 1982-04-09 | 1985-01-29 | The Charles Stark Draper Laboratory, Inc. | Controlled heat exchanger system |
US4660630A (en) * | 1985-06-12 | 1987-04-28 | Wolverine Tube, Inc. | Heat transfer tube having internal ridges, and method of making same |
US4767497A (en) * | 1987-04-01 | 1988-08-30 | The Boc Group, Inc. | Process of forming enhanced heat transfer surfaces |
US4846267A (en) * | 1987-04-01 | 1989-07-11 | The Boc Group, Inc. | Enhanced heat transfer surfaces |
US4951742A (en) * | 1975-04-02 | 1990-08-28 | High Performance Tube, Inc. | Refractory heat exchange tube |
US5018573A (en) * | 1989-12-18 | 1991-05-28 | Carrier Corporation | Method for manufacturing a high efficiency heat transfer surface and the surface so manufactured |
US5054548A (en) * | 1990-10-24 | 1991-10-08 | Carrier Corporation | High performance heat transfer surface for high pressure refrigerants |
US5333682A (en) * | 1993-09-13 | 1994-08-02 | Carrier Corporation | Heat exchanger tube |
US5351397A (en) * | 1988-12-12 | 1994-10-04 | Olin Corporation | Method of forming a nucleate boiling surface by a roll forming |
US5388329A (en) * | 1993-07-16 | 1995-02-14 | Olin Corporation | Method of manufacturing a heating exchange tube |
US5415225A (en) * | 1993-12-15 | 1995-05-16 | Olin Corporation | Heat exchange tube with embossed enhancement |
US5669441A (en) * | 1994-11-17 | 1997-09-23 | Carrier Corporation | Heat transfer tube and method of manufacture |
DE19757526C1 (en) * | 1997-12-23 | 1999-04-29 | Wieland Werke Ag | Heat exchanger tube manufacturing method |
US6067712A (en) * | 1993-12-15 | 2000-05-30 | Olin Corporation | Heat exchange tube with embossed enhancement |
EP1156294A2 (en) | 2000-05-18 | 2001-11-21 | Wieland-Werke AG | Tube for evaporative heat exchanger with pores having different size |
US6382311B1 (en) | 1999-03-09 | 2002-05-07 | American Standard International Inc. | Nucleate boiling surface |
EP1223400A2 (en) | 2001-01-16 | 2002-07-17 | Wieland-Werke AG | Tube for heat exchanger and process for making same |
US6427767B1 (en) | 1997-02-26 | 2002-08-06 | American Standard International Inc. | Nucleate boiling surface |
DE10156374C1 (en) * | 2001-11-16 | 2003-02-27 | Wieland Werke Ag | Heat exchange tube structured on both sides has inner fins crossed by secondary grooves at specified rise angle |
US20040010913A1 (en) * | 2002-04-19 | 2004-01-22 | Petur Thors | Heat transfer tubes, including methods of fabrication and use thereof |
US20040256088A1 (en) * | 2003-06-18 | 2004-12-23 | Ayub Zahid Hussain | Flooded evaporator with various kinds of tubes |
US20060075772A1 (en) * | 2004-10-12 | 2006-04-13 | Petur Thors | Heat transfer tubes, including methods of fabrication and use thereof |
US20060175044A1 (en) * | 2005-02-10 | 2006-08-10 | Chin-Wei Lee | Heat dissipating tube sintered with copper powders |
US20070028649A1 (en) * | 2005-08-04 | 2007-02-08 | Chakravarthy Vijayaraghavan S | Cryogenic air separation main condenser system with enhanced boiling and condensing surfaces |
US20070193728A1 (en) * | 2006-02-22 | 2007-08-23 | Andreas Beutler | Structured heat exchanger tube and method for the production thereof |
US7276046B1 (en) * | 2002-11-18 | 2007-10-02 | Biosynergy, Inc. | Liquid conductive cooling/heating device and method of use |
US20090121367A1 (en) * | 2007-11-13 | 2009-05-14 | Lundgreen James M | Heat exchanger for removal of condensate from a steam dispersion system |
US20090166018A1 (en) * | 2007-11-13 | 2009-07-02 | Lundgreen James M | Heat transfer system including tubing with nucleation boiling sites |
EP2101136A2 (en) | 2008-03-12 | 2009-09-16 | Wieland-Werke Ag | Vaporiser pipe with optimised undercut on groove base |
WO2013091759A1 (en) | 2011-12-21 | 2013-06-27 | Wieland-Werke Ag | Evaporator tube having an optimised external structure |
US20130206368A1 (en) * | 2010-10-19 | 2013-08-15 | Nec Corporation | Cooling device and method for producing the same |
US20130219954A1 (en) * | 2010-11-02 | 2013-08-29 | Nec Corporation | Cooling device and method for producing the same |
US8875780B2 (en) | 2010-01-15 | 2014-11-04 | Rigidized Metals Corporation | Methods of forming enhanced-surface walls for use in apparatae for performing a process, enhanced-surface walls, and apparatae incorporating same |
US9109844B2 (en) | 2012-03-01 | 2015-08-18 | Rheem Manufacturing Company | Nested helical fin tube coil and associated manufacturing methods |
WO2017207090A1 (en) | 2016-06-01 | 2017-12-07 | Wieland-Werke Ag | Heat exchanger tube |
DE102016006913A1 (en) | 2016-06-01 | 2017-12-07 | Wieland-Werke Ag | heat exchanger tube |
WO2017207089A1 (en) | 2016-06-01 | 2017-12-07 | Wieland-Werke Ag | Heat exchanger tube |
US9945618B1 (en) * | 2017-01-04 | 2018-04-17 | Wieland Copper Products, Llc | Heat transfer surface |
US10088180B2 (en) | 2013-11-26 | 2018-10-02 | Dri-Steem Corporation | Steam dispersion system |
US10174960B2 (en) | 2015-09-23 | 2019-01-08 | Dri-Steem Corporation | Steam dispersion system |
DE102018004701A1 (en) | 2018-06-12 | 2019-12-12 | Wieland-Werke Ag | Metallic heat exchanger tube |
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Cited By (92)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
USRE30077E (en) * | 1968-05-14 | 1979-08-21 | Union Carbide Corporation | Surface for boiling liquids |
US3768290A (en) * | 1971-06-18 | 1973-10-30 | Uop Inc | Method of modifying a finned tube for boiling enhancement |
US3881342A (en) * | 1972-07-14 | 1975-05-06 | Universal Oil Prod Co | Method of making integral finned tube for submerged boiling applications having special o.d. and/or i.d. enhancement |
US4059147A (en) * | 1972-07-14 | 1977-11-22 | Universal Oil Products Company | Integral finned tube for submerged boiling applications having special O.D. and/or I.D. enhancement |
US3850236A (en) * | 1973-03-26 | 1974-11-26 | Peerless Of America | Heat exchangers |
US4060125A (en) * | 1974-10-21 | 1977-11-29 | Hitachi Cable, Ltd. | Heat transfer wall for boiling liquids |
US4366859A (en) * | 1975-04-02 | 1983-01-04 | Keyes John M | Refractory heat exchange tube |
US4951742A (en) * | 1975-04-02 | 1990-08-28 | High Performance Tube, Inc. | Refractory heat exchange tube |
US4018264A (en) * | 1975-04-28 | 1977-04-19 | Borg-Warner Corporation | Boiling heat transfer surface and method |
US4216826A (en) * | 1977-02-25 | 1980-08-12 | Furukawa Metals Co., Ltd. | Heat transfer tube for use in boiling type heat exchangers and method of producing the same |
US4159739A (en) * | 1977-07-13 | 1979-07-03 | Carrier Corporation | Heat transfer surface and method of manufacture |
FR2397615A1 (en) * | 1977-07-13 | 1979-02-09 | Carrier Corp | HEAT TRANSFER SURFACE AND METHOD FOR MANUFACTURING THIS SURFACE |
DE2829070A1 (en) * | 1977-07-13 | 1979-02-01 | Carrier Corp | AREA USED FOR HEAT TRANSFER AND METHOD FOR PRODUCING THE SAME |
US4186063A (en) * | 1977-11-01 | 1980-01-29 | Borg-Warner Corporation | Boiling heat transfer surface, method of preparing same and method of boiling |
US4258783A (en) * | 1977-11-01 | 1981-03-31 | Borg-Warner Corporation | Boiling heat transfer surface, method of preparing same and method of boiling |
US4359086A (en) * | 1981-05-18 | 1982-11-16 | The Trane Company | Heat exchange surface with porous coating and subsurface cavities |
US4438807A (en) * | 1981-07-02 | 1984-03-27 | Carrier Corporation | High performance heat transfer tube |
US4471833A (en) * | 1981-08-31 | 1984-09-18 | Agency Of Industrial Science & Technology | Augmentation method of boiling heat transfer by applying electric fields |
US4495988A (en) * | 1982-04-09 | 1985-01-29 | The Charles Stark Draper Laboratory, Inc. | Controlled heat exchanger system |
US4660630A (en) * | 1985-06-12 | 1987-04-28 | Wolverine Tube, Inc. | Heat transfer tube having internal ridges, and method of making same |
US4767497A (en) * | 1987-04-01 | 1988-08-30 | The Boc Group, Inc. | Process of forming enhanced heat transfer surfaces |
US4846267A (en) * | 1987-04-01 | 1989-07-11 | The Boc Group, Inc. | Enhanced heat transfer surfaces |
US5351397A (en) * | 1988-12-12 | 1994-10-04 | Olin Corporation | Method of forming a nucleate boiling surface by a roll forming |
US5018573A (en) * | 1989-12-18 | 1991-05-28 | Carrier Corporation | Method for manufacturing a high efficiency heat transfer surface and the surface so manufactured |
US5054548A (en) * | 1990-10-24 | 1991-10-08 | Carrier Corporation | High performance heat transfer surface for high pressure refrigerants |
EP0483047A1 (en) * | 1990-10-24 | 1992-04-29 | Carrier Corporation | High performance heat transfer surface for high pressure refrigerants |
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