EP0145867A2 - Wärmetauscher mit ultrakurzen Rippen - Google Patents

Wärmetauscher mit ultrakurzen Rippen Download PDF

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Publication number
EP0145867A2
EP0145867A2 EP84111657A EP84111657A EP0145867A2 EP 0145867 A2 EP0145867 A2 EP 0145867A2 EP 84111657 A EP84111657 A EP 84111657A EP 84111657 A EP84111657 A EP 84111657A EP 0145867 A2 EP0145867 A2 EP 0145867A2
Authority
EP
European Patent Office
Prior art keywords
fin
refrigerant
conduit
heat
conduits
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.)
Withdrawn
Application number
EP84111657A
Other languages
English (en)
French (fr)
Other versions
EP0145867A3 (de
Inventor
Charles Edward Kalb
Charles Leo Newton
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.)
Air Products and Chemicals Inc
Original Assignee
Air Products and Chemicals Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Air Products and Chemicals Inc filed Critical Air Products and Chemicals Inc
Publication of EP0145867A2 publication Critical patent/EP0145867A2/de
Publication of EP0145867A3 publication Critical patent/EP0145867A3/de
Withdrawn legal-status Critical Current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
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J5/00—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants
    • F25J5/002—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
    • F25J2290/44—Particular materials used, e.g. copper, steel or alloys thereof or surface treatments used, e.g. enhanced surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0033—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cryogenic applications

Definitions

  • the present invention is directed to an apparatus and process for the enhancement of heat transfer in a heat exchanger. More specifically, the present invention is directed to the use of ultra-low fins on conduits inside the shell of the heat exchanger which fins enhance heat transfer when utilized in the presence of a two-phase refrigerant.
  • the present invention has application for various heat exchange uses, but is particularly amenable to use in the coil-wound heat exchangers of base load natural gas liquefaction plants.
  • Enhanced heat exchange has been a goal sought for many industrial processes. Heat transfer enhancement is particularly attractive in the field of liquefaction of natural gas.
  • Natural gas is a low value fuel resource produced as a by-product from most oil field production operations. The liquefaction of natural gas is necessary for transport from distant production sites to regions having demand for such fuel. Liquefaction is an expensive energy-intensive process. In order to keep the costs of liquefaction for a unit of natural gas low, natural gas recovery and liquefaction are performed only where relatively high production rates of natural gas are available. As a result, base load liquefaction plants tend to be very large and the attendant coil-wound heat exchangers in such plants have become larger, only constrained to the size limitations for transport from the manufacture site to the site of use.
  • a refrigerant in the liquid phase which comprises either a pure compound or a mixture of compounds is vaporized inside a heat exchanger containment or shell and outside a series of conduits through which the material (natural gas) to be reduced in temperature is passed.
  • the temperature differential between the conduit wall and the refrigerant is usually too small to support nucleate boiling, but refrigerant vapor is produced at the liquid/vapor interface of the liquid film forming and flowing over the conduits inside the shell of the heat exchanger. This heat transfer process is called convective vaporization.
  • U.S. Patent 3,587,730 discloses a heat exchanger having porous layers bonded to the walls of the heat exchanger at the surfaces wherein the porous layer comprises conductive particles bonded together to form pores of capillary size on the heat exchange surface.
  • the claims are directed to a plate-fin type heat exchanger structure having a corrugated surface geometry.
  • U.S. Patent 4,118,944 discloses the use of integral internal fins in the heat exchange tube wherein a refrigerant is vaporized inside the tube against the finned surface thereof. No dimension configuration is set forth for this particular structure.
  • U.S. Patent 4,216,819 discloses the use of a single layer of randomly distributed metal bodies bonded to a substrate to provide an increased heat exchange surface for condensation. Surface tension characteristics are set forth as an active phenomenon effecting the enhancement of condensation using the recited surfaces.
  • a heat transfer surface for enhancing nucleate boiling is set forth wherein the surface is grooved at a microscopic density and the grooves are subsequently deformed to form restricted openings therein.
  • the restricted openings are the key to the effectiveness of the heat transfer surface.
  • the teaching of this geometry for use in nucleate boiling is dissimilar from the present invention's interest in convective vaporization.
  • the present invention overcomes the limitation of the prior-art heat exchange technology by providing for an ultra-low fin geometry which is controlled by various geometric dimensions, as well as physical properties of the refrigerant being utilized in the heat exchange.
  • the utilization of these dimensions and properties in a unique relationship provide for a fin geometry having unexpectedly high heat transfer enhancement.
  • the use of such heat transfer enhancement allows for the reduction in size of heat exchangers or the maintenance of heat exchanger size with increased heat exchange capacity.
  • Such a result is beneficial to heat exchange in general, but is particularly beneficial to the specific application of base load natural gas liquefaction wherein heat exchangers are presently at a near maximum in size and yet economics would dictate that even larger heat exchangers may be )desirable.
  • the present invention would provide the increased heat exchange capacity for a relatively smaller heat exchanger size.
  • the present invention is directed to a heat exchanger having at least one tubular conduit for conducting a fluid from which heat is to be removed through such a heat exchanger wherein a shell surrounding such conduit defines a refrigerant space between said shell and said conduit.
  • the conduit is aligned such that a two-phase refrigerant can pass over the conduit.
  • the conduit includes ultra-low fins affixed outward from the outer surface of said conduit wherein the fin height (H), the fin crest width (w) and the fin gap width (W) are selected in relationship to the density and surface tension of the refriqerant such that:
  • the present invention is particularly directed to a heat exchanger having a plurality of coil-wound tubular conduits such that a two-phase refrigerant can pass substantially perpendicular to the axis of said conduits wherein the ultra-low fins are affixed radially transverse or helically outward from the outer surface of the conduits.
  • a heat exchanger is particularly appropriate for the refrigeration and liquefaction of natural gas as the gas passes through the interior of the finned conduits.
  • the invention is also concerned with a process for heat exchanging a fluid in a heat exchanger which has at least one tubular conduit for such a fluid and a shell surrounding said conduit which defines a space for a two-phase refrigerant.
  • the refrigerant passes over the outside surface of the conduit to remove heat from the fluid passing through the conduit.
  • An enhanced level of heat transfer is achieved during the process of heat exchanging by passing the refrigerant over ultra-low fins affixed to the conduit outer surface wherein the fin height (H), the fin crest width (w) and the fin gap width (W) are selected in relationship to the density and surface tension of the refrigerant such that;
  • the process is more specifically directed to a method wherein the refrigerant passes over the outside surface of said conduits in a direction generally perpendicular to the axis of said conduits and in which the refrigerant passes over ultra-low fins which are radially transverse or helically affixed to the outer surface of said conduits.
  • the invention is more specifically directed to a process for the liquefaction of natural gas in a method as described above.
  • the invention is an improved means to chill or condense fluids flowing inside the tubes of a heat exchanger, the improvement comprising ultra-low fins affixed more-or-less radially outwards from the outer surface of the tubes.
  • the heat removed from said fluids is transferred to a liquid refrigerant flowing across and vaporizing on the ultra-low-finned tubes.
  • the extent of enhancement to the shellside heat transfer is remarkable and unexpected, exceeding even the maximum enhancement expected based on the increase in shellside heat transfer area. Because the fins are very small, the improved heat transfer is attained with little or no increase in the shellside pressure drop per unit length along the axis of the shell.
  • the ultra-low-fin tubing is distinguished from tubing which has been suggested in the prior art as being effective for vaporizing liquids by its very low fin height and relatively high fin density (number of fins per unit length).
  • the relatively small dimensions of the fins cause surface tension forces to become very large in relation to viscous and gravitational forces within the liquid films on the wetted finned tubing.
  • the surface tension forces ensure that extremely thin liquid films are maintained on the sides of the fins, especially near the fin crests, resulting in very high local heat transfer coefficients in this region.
  • the most effective fins are disposed approximately radially transverse on the tubing and can be integrally formed from the tubing base metal or be attached by other methods such as soldering, welding or tension winding. Fins tested and found effective to various extents had trapezoidal, rectangular, or essentially triangular cross sections. Other related fin shapes are expected to be similarly effective.
  • the fins may have flats at either the fin crests or between the fins at the fin root diameter, said flats being more or less parallel with the axis of the tubing.
  • the fin crests and valley bottoms between fins might also be rounded rather than flat.
  • the fins can be made using any of a number of techniques which have been developed and which are available in the art for making conventional finned tubing.
  • Equation (14) can be made as large as desired by decreasing the fin dimensions (H, w and W), an upper limit must be placed on the left-hand side of Equation (14) to avoid completely flooding the valleys between the fins with the liquid refrigerant.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Power Steering Mechanism (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
EP84111657A 1983-12-21 1984-09-28 Wärmetauscher mit ultrakurzen Rippen Withdrawn EP0145867A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US56390683A 1983-12-21 1983-12-21
US563906 1983-12-21

Publications (2)

Publication Number Publication Date
EP0145867A2 true EP0145867A2 (de) 1985-06-26
EP0145867A3 EP0145867A3 (de) 1985-12-11

Family

ID=24252369

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84111657A Withdrawn EP0145867A3 (de) 1983-12-21 1984-09-28 Wärmetauscher mit ultrakurzen Rippen

Country Status (7)

Country Link
EP (1) EP0145867A3 (de)
JP (1) JPS60228897A (de)
AU (1) AU548348B2 (de)
DK (1) DK453384A (de)
ES (1) ES8608671A1 (de)
NO (1) NO843793L (de)
OA (1) OA07826A (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0245057A2 (de) * 1986-05-06 1987-11-11 Kabushiki Kaisha Toshiba Heliumkühlapparat
EP0701100A1 (de) * 1994-09-12 1996-03-13 Carrier Corporation Wärmetauscherrohr
WO2002062568A2 (en) * 2001-02-07 2002-08-15 3M Innovative Properties Company Microstructured surface film for liquid acquisition and transport
CN108302965A (zh) * 2018-01-17 2018-07-20 江苏新方圆电气设备制造有限公司 一种用于物料余热回收的旋转筒体

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3158010A (en) * 1963-10-07 1964-11-24 Phillips Petroleum Co Two phase fluid heat exchanger
US3217799A (en) * 1962-03-26 1965-11-16 Calumet & Hecla Steam condenser of the water tube type
FR1444696A (fr) * 1964-12-17 1966-07-08 Thomson Houston Comp Francaise Perfectionnements apportés aux parois dissipatrices de chaleur et aux dispositifs comportant de telles parois
US3384154A (en) * 1956-08-30 1968-05-21 Union Carbide Corp Heat exchange system
DE2552679A1 (de) * 1974-11-25 1976-06-16 Hitachi Ltd Waermeuebertragungsrohr
US4216819A (en) * 1976-09-09 1980-08-12 Union Carbide Corporation Enhanced condensation heat transfer device and method

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3384154A (en) * 1956-08-30 1968-05-21 Union Carbide Corp Heat exchange system
US3217799A (en) * 1962-03-26 1965-11-16 Calumet & Hecla Steam condenser of the water tube type
US3158010A (en) * 1963-10-07 1964-11-24 Phillips Petroleum Co Two phase fluid heat exchanger
FR1444696A (fr) * 1964-12-17 1966-07-08 Thomson Houston Comp Francaise Perfectionnements apportés aux parois dissipatrices de chaleur et aux dispositifs comportant de telles parois
DE2552679A1 (de) * 1974-11-25 1976-06-16 Hitachi Ltd Waermeuebertragungsrohr
US4216819A (en) * 1976-09-09 1980-08-12 Union Carbide Corporation Enhanced condensation heat transfer device and method

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0245057A2 (de) * 1986-05-06 1987-11-11 Kabushiki Kaisha Toshiba Heliumkühlapparat
EP0245057A3 (en) * 1986-05-06 1988-09-14 Kabushiki Kaisha Toshiba Helium cooling apparatus
EP0701100A1 (de) * 1994-09-12 1996-03-13 Carrier Corporation Wärmetauscherrohr
WO2002062568A2 (en) * 2001-02-07 2002-08-15 3M Innovative Properties Company Microstructured surface film for liquid acquisition and transport
US6531206B2 (en) 2001-02-07 2003-03-11 3M Innovative Properties Company Microstructured surface film assembly for liquid acquisition and transport
WO2002062568A3 (en) * 2001-02-07 2003-09-04 3M Innovative Properties Co Microstructured surface film for liquid acquisition and transport
US6746567B2 (en) 2001-02-07 2004-06-08 3M Innovative Properties Company Microstructured surface film assembly for liquid acquisition and transport
CN108302965A (zh) * 2018-01-17 2018-07-20 江苏新方圆电气设备制造有限公司 一种用于物料余热回收的旋转筒体
CN108302965B (zh) * 2018-01-17 2023-08-04 江苏新方圆电气设备制造有限公司 一种用于物料余热回收的旋转筒体

Also Published As

Publication number Publication date
AU3328384A (en) 1985-08-15
OA07826A (en) 1986-11-20
NO843793L (no) 1985-06-24
AU548348B2 (en) 1985-12-05
DK453384A (da) 1985-06-22
ES8608671A1 (es) 1986-06-16
ES536195A0 (es) 1986-06-16
DK453384D0 (da) 1984-09-21
EP0145867A3 (de) 1985-12-11
JPS60228897A (ja) 1985-11-14

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Inventor name: NEWTON, CHARLES LEO

Inventor name: KALB, CHARLES EDWARD