US3109485A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US3109485A
US3109485A US794557A US79455759A US3109485A US 3109485 A US3109485 A US 3109485A US 794557 A US794557 A US 794557A US 79455759 A US79455759 A US 79455759A US 3109485 A US3109485 A US 3109485A
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fluid
jets
heat exchange
heat exchanger
heat
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US794557A
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Fortier Andre
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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
    • F28F13/02—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by influencing fluid boundary
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/908—Fluid jets

Definitions

  • FIG 4 FIG 5 United States Patent 3,] 99,485 HEAT EXCHANGER Andre Fortier, 12 Rue Leon Camhillard, Clamart, France Filed Feb. 20, N59, Ser. No. 794,557 Claims priority, application France Felt). 25, 1953 4 (Ilairns. (Cl. 165l)
  • This invention relates to a heat exchanger of the type in which a fluid is continuously flowing in heat-exchange relationship with a solid surface.
  • a heat-exchanger is characterized by a coefficient which will be called hereunder heat exchange coeflicient and which is equal to the ratio of the amount of heat exchanged per unit of area of the solid surface and per unit of time to the difierence between the maximum temperature of the surface and the fluid temperature as it enters the exchanger.
  • IP01 certain particular purposes such as quenching, wherein the only problem is to obtain quick cooling, it is usual to put the surface to be cooled in contact with a huge mass of water, either by suddenly immersing the part to be quenched into a water bath or by spraying said part with one or several jets of water without considering the pressure of projection nor the amount of water wasted.
  • the main object of the invention is to provide a multiple jet heat exchanger in which the heat exchange coefficient can be raised to very high values, for example of the same order as those which would be obtained with the above cited metals, but in which usual fluids, such as water, are used, the heat exchange nevertheless requiring but a negligible consumption of power.
  • An object of the invention is to provide a multiple jet heat exchanger in which:
  • a further object of the invention is to provide a multiple jet heat exchanger in which:
  • Still another object of the invention is to provide a multiple jet heat exchanger in which:
  • the function is plotted in FIG. 1 and the function may be considered as approximately equal to unity if complies with condition (2).
  • the five conditions hereabove recited define the characteristics of the heat exchanger i.e. the diameter D of the orifices, the distance e between the axes of the orifices, the distance d between the two surfaces and the velocity V of the fluid in the jets.
  • Conditions (1) and (5) define a maximum diameter and conditions (2), (3), (5) a minimum diameter for each value of the parameter D v/E that meets condition (4).
  • the power consumption is then of about kw. instead of 1,000 kw. with a conventional heat exchanger all other things being equal.
  • the invention makes it possible to obtain, with a same consumption of power, a heat exchange coefficient far higher than with any of the conventional methods by a suitable computation of the dimensions and spacing of the orifices, the length of the jets and the velocity of the fluid.
  • a same heat exchange coeflicient it is possible to reduce considerably the power consumption with respect to that required in the conventional heat exchangers.
  • the jets may be projected upon the heat exchange surface through a gas such as air as well as through the same liquid provided that the said jets have not to flow through a prohibitively thick mass of fluid.
  • the heat exchange surface lies horizontal and jets of liquid are projected upon the lower face of the surface from where the liquid easily drops down under the action of gravity.
  • the heat exchange surface is a cylindrical member upon which the jets are continuously projected through nozzles constituted by orifices drilled in the inner wall of an annular cylindrical member co-axial to the above-mentioned heat exchange surface and fed with pressure fluid, the exhaust of the fluid taking place through at least one end of the annular space comprised between the heat exchange surface and the apertured wall.
  • FIG. 1 is the already mentioned curve of the function brizi)
  • FIG. 2 shows the variations of the mechanical power actually consumed vs. its minimum as a function of
  • FIG. 3 is a much enlarged View showing the shape of a jet of liquid projected upon the heat exchange surface of a heat exchanger according to the invention.
  • FIG. 4 is a sectional view of an embodiment of the heat exchanger according to the invention.
  • FIG. 5 is a plan view corresponding to FIG. 4, and
  • FIG. 6 is an axial sectional view of an alternative embodiment.
  • jets of a usual fluid such as water, having a very small diameter D impinge from a very short distance d on a solid fiat heat exchange surface 4 on which they are flattened into extremely thin sheets such as 2, 2' merging into each other as shown at 65 to be then reflected normally to surface 4 as shown at 66, whereupon the fluid forms vortices 67 which flow out through the gaps such as 68 between the jets.
  • a jet of water about 5 mm. long projected through an orifice of 0.5 mm. diameter in a thin wall, the thickness of the liquid sheet is approximately 2/100 mm.
  • the abovednentioned solid surface constitutes the heat exchange surface of a heat-exchanger, according to the invention, the liquid projected on said surface being intended to derive calories from the said surface or, conversely to yield heat thereto, due to the extreme thinness of the liquid sheet and the high velocity of the fluid at the surface of said sheet, the heat exchanges between the solid surface and the fluid are very intense and the heat exchange coeificient h calculated from relation (5) (cf. preamble) the fluid being liquid water is:
  • h 73,000 kcal./tm. /h/C.
  • the jet spreads out in droplets and the heat exchange coeflicient decreases; the distance between the orifice and the heat exchange surface has been defined precisely in the preamble. For a jet of 0.3 diameter, the said distance should not overreach 45 mm. and may be as small as a few mm.
  • the surface 5 to be cooled is a flat surface of 10 cm? area, through which the thermal flux reaches 100 W/cmP.
  • a plurality of small tubes 6 extending vertically under the surface 5 are fixed by their basis on a chamber 7 from which they are fed with cooling water.
  • the upper end of each tube is provided with an orifice of 0.5 mm. diameter.
  • These tubes are disposed at the intersecting points of the lines of a pattern formed by a plurality of adjacent equilateral triangles, the density of the heat flux of the surface to be cooled being assumed to be substantially uniform.
  • the chamber 7 is provided with a pressure water inlet 9, and the space comprised between the surface 5 to be cooled and the chamber 7, i.e. the space in which the tubes 6 extend communicates with an outlet ii.
  • the heat exchange coeflicient has a well defined value.
  • the temperature of the liquid in contact with the hot surface increases and the diameter of the area covered by the liquid sheet also increases. This phenomenon results from the reduction of the surface tension of the liquid as the temperature increases.
  • the temperature of the liquid reaches the boiling point, the liquid in the liquid sheet is partly evaporated, but the vapour generated is carried away by the liquid flowing out at a high velocity which avoids any calefaction phenomena. It is 6 thus possible to vaporize a considerable proportion of the liquid without overreaching noticeably the boiling point which permits obtaining extremely high densities of thermal flux.
  • the number of the tubes per unit area is made proportional to the value of the said density.
  • the surface to be cooled is a cylindrical surface 13 extending for example vertically.
  • This surface is surrounded by a coaxial annular cylindrical member 14 in which extends a coaxial cylindrical wall 15 provided with a multitude of apertures 16.
  • the water feeding chamber 17 is constituted by the 'annular cylindrical space comprised within the walls 14 and 15; it is provided with an inlet 18.
  • the annular cylindrical space comprised between the surface to be cooled and the apertured wall is provided with an outlet '19 through which the water is exhausted.
  • the pressure water jets projected out of the chamber 17 through the apertures 16 impinge radially upon the surface 13 to be cooled on which they are flattened in thin cylindrical sheets as explained above.
  • the jets have to flow through the liquid layer comprised between the walls 13 and 15; the thickness of the said layer being of course reasonable, so that the linear velocity of the jets be not reduced too much.
US794557A 1958-02-25 1959-02-20 Heat exchanger Expired - Lifetime US3109485A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR759062 1958-02-25

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US3109485A true US3109485A (en) 1963-11-05

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ID=8705830

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US794557A Expired - Lifetime US3109485A (en) 1958-02-25 1959-02-20 Heat exchanger

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US (1) US3109485A (fr)
BE (1) BE575983A (fr)
CH (1) CH388357A (fr)
DE (1) DE1150696B (fr)
FR (1) FR1191927A (fr)
GB (1) GB876930A (fr)

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3205147A (en) * 1959-03-21 1965-09-07 Snecma Process and devices of heat exchange and nuclear reactor embodying same
US3323577A (en) * 1965-05-05 1967-06-06 Olin Mathieson Process for cooling metal
FR2062917A1 (en) * 1969-09-19 1971-07-02 Lage James R Indirect heat-exchanger
US3771589A (en) * 1970-11-10 1973-11-13 J Lage Method and apparatus for improved transfer of heat
US3788393A (en) * 1972-05-01 1974-01-29 Us Navy Heat exchange system
US4108242A (en) * 1971-07-23 1978-08-22 Thermo Electron Corporation Jet impingement heat exchanger
US4202408A (en) * 1978-03-06 1980-05-13 Temple Robert S Jet type heat exchanger
US4735775A (en) * 1984-02-27 1988-04-05 Baxter Travenol Laboratories, Inc. Mass transfer device having a heat-exchanger
USH1145H (en) 1990-09-25 1993-03-02 Sematech, Inc. Rapid temperature response wafer chuck
US5249358A (en) * 1992-04-28 1993-10-05 Minnesota Mining And Manufacturing Company Jet impingment plate and method of making
US5317805A (en) * 1992-04-28 1994-06-07 Minnesota Mining And Manufacturing Company Method of making microchanneled heat exchangers utilizing sacrificial cores
US20080037221A1 (en) * 2006-08-07 2008-02-14 International Business Machines Corporation Jet orifice plate with projecting jet orifice structures for direct impingement cooling apparatus
US20100101765A1 (en) * 2008-10-23 2010-04-29 International Business Machines Corporation Liquid cooling apparatus and method for cooling blades of an electronic system chassis
US20100103614A1 (en) * 2008-10-23 2010-04-29 International Business Machines Corporation Apparatus and method for immersion-cooling of an electronic system utilizing coolant jet impingement and coolant wash flow
US20100103618A1 (en) * 2008-10-23 2010-04-29 International Business Machines Corporation Apparatus and method for facilitating pumped immersion-cooling of an electronic subsystem
US20100103620A1 (en) * 2008-10-23 2010-04-29 International Business Machines Corporation Open Flow Cold Plate For Liquid Cooled Electronic Packages
US20100328891A1 (en) * 2009-06-25 2010-12-30 International Business Machines Corporation Condenser block structures with cavities facilitating vapor condensation cooling of coolant
US20100326628A1 (en) * 2009-06-25 2010-12-30 International Business Machines Corporation Condenser fin structures facilitating vapor condensation cooling of coolant
US20100328890A1 (en) * 2009-06-25 2010-12-30 International Business Machines Corporation Condenser structures with fin cavities facilitating vapor condensation cooling of coolant
US20100328889A1 (en) * 2009-06-25 2010-12-30 International Business Machines Corporation Cooled electronic module with pump-enhanced, dielectric fluid immersion-cooling
US20100328882A1 (en) * 2009-06-25 2010-12-30 International Business Machines Corporation Direct jet impingement-assisted thermosyphon cooling apparatus and method
US7961475B2 (en) 2008-10-23 2011-06-14 International Business Machines Corporation Apparatus and method for facilitating immersion-cooling of an electronic subsystem
US8179677B2 (en) 2010-06-29 2012-05-15 International Business Machines Corporation Immersion-cooling apparatus and method for an electronic subsystem of an electronics rack
US8184436B2 (en) 2010-06-29 2012-05-22 International Business Machines Corporation Liquid-cooled electronics rack with immersion-cooled electronic subsystems
US8345423B2 (en) 2010-06-29 2013-01-01 International Business Machines Corporation Interleaved, immersion-cooling apparatuses and methods for cooling electronic subsystems
US8351206B2 (en) 2010-06-29 2013-01-08 International Business Machines Corporation Liquid-cooled electronics rack with immersion-cooled electronic subsystems and vertically-mounted, vapor-condensing unit
US8369091B2 (en) 2010-06-29 2013-02-05 International Business Machines Corporation Interleaved, immersion-cooling apparatus and method for an electronic subsystem of an electronics rack

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1578208A (en) * 1977-01-19 1980-11-05 Hisaka Works Ltd Plate type indirect heat exchanger
SE456935B (sv) * 1984-05-24 1988-11-14 Armaturjonsson Ab Vaermevaexlare daer stroemningsplaatar med strilhaal aer placerade i varje slingaav ett serpentinformat roer samt saett foer framstaellning
FR2633379B1 (fr) * 1988-06-28 1990-09-28 Bertin & Cie Echangeur de chaleur a impact de jets
DE19827096A1 (de) * 1998-06-18 1999-12-23 Behr Gmbh & Co Wärmeübertragereinheit

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1043623A (fr) * 1950-10-12 1953-11-10 Dispositif servant à la transmission de chaleur de gaz chauds
US2772540A (en) * 1952-01-23 1956-12-04 Vierkotter Paul Cooling process and device for the performance of same
DE1014353B (de) * 1956-02-03 1957-08-22 Stoelzle Glasindustrie Ag Einhaengekuehler

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE459276C (de) * 1928-04-30 Gottfried Koerber Umlaufender Warmwassererzeuger
CH110357A (de) * 1924-08-25 1925-06-01 Stierle Karl Rauchgasvorwärmer.
GB255364A (en) * 1926-03-03 1926-07-22 Ewald Luetschen Improvements in heat interchangers
DE504257C (de) * 1929-05-04 1930-08-01 Schaffstaedt G M B H H Waermeaustauschvorrichtung, insbesondere fuer Warmwassererzeuger
DE702177C (de) * 1938-09-20 1941-01-31 Fritz Hecht Maschinen U Appbau Doppelseitig beheizter Trommelerhitzer

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1043623A (fr) * 1950-10-12 1953-11-10 Dispositif servant à la transmission de chaleur de gaz chauds
US2772540A (en) * 1952-01-23 1956-12-04 Vierkotter Paul Cooling process and device for the performance of same
DE1014353B (de) * 1956-02-03 1957-08-22 Stoelzle Glasindustrie Ag Einhaengekuehler

Cited By (42)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3205147A (en) * 1959-03-21 1965-09-07 Snecma Process and devices of heat exchange and nuclear reactor embodying same
US3323577A (en) * 1965-05-05 1967-06-06 Olin Mathieson Process for cooling metal
FR2062917A1 (en) * 1969-09-19 1971-07-02 Lage James R Indirect heat-exchanger
US3771589A (en) * 1970-11-10 1973-11-13 J Lage Method and apparatus for improved transfer of heat
US4108242A (en) * 1971-07-23 1978-08-22 Thermo Electron Corporation Jet impingement heat exchanger
US3788393A (en) * 1972-05-01 1974-01-29 Us Navy Heat exchange system
US4202408A (en) * 1978-03-06 1980-05-13 Temple Robert S Jet type heat exchanger
US4735775A (en) * 1984-02-27 1988-04-05 Baxter Travenol Laboratories, Inc. Mass transfer device having a heat-exchanger
USH1145H (en) 1990-09-25 1993-03-02 Sematech, Inc. Rapid temperature response wafer chuck
US5249358A (en) * 1992-04-28 1993-10-05 Minnesota Mining And Manufacturing Company Jet impingment plate and method of making
US5317805A (en) * 1992-04-28 1994-06-07 Minnesota Mining And Manufacturing Company Method of making microchanneled heat exchangers utilizing sacrificial cores
US20080037221A1 (en) * 2006-08-07 2008-02-14 International Business Machines Corporation Jet orifice plate with projecting jet orifice structures for direct impingement cooling apparatus
US20080062639A1 (en) * 2006-08-07 2008-03-13 International Business Machines Corporation Jet orifice plate with projecting jet orifice structures for direct impingement cooling apparatus
US7362574B2 (en) * 2006-08-07 2008-04-22 International Business Machines Corporation Jet orifice plate with projecting jet orifice structures for direct impingement cooling apparatus
US7375962B2 (en) 2006-08-07 2008-05-20 International Business Machines Corporation Jet orifice plate with projecting jet orifice structures for direct impingement cooling apparatus
US7983040B2 (en) 2008-10-23 2011-07-19 International Business Machines Corporation Apparatus and method for facilitating pumped immersion-cooling of an electronic subsystem
US7916483B2 (en) 2008-10-23 2011-03-29 International Business Machines Corporation Open flow cold plate for liquid cooled electronic packages
US20100103618A1 (en) * 2008-10-23 2010-04-29 International Business Machines Corporation Apparatus and method for facilitating pumped immersion-cooling of an electronic subsystem
US20100103620A1 (en) * 2008-10-23 2010-04-29 International Business Machines Corporation Open Flow Cold Plate For Liquid Cooled Electronic Packages
US8203842B2 (en) 2008-10-23 2012-06-19 International Business Machines Corporation Open flow cold plate for immersion-cooled electronic packages
US20100101765A1 (en) * 2008-10-23 2010-04-29 International Business Machines Corporation Liquid cooling apparatus and method for cooling blades of an electronic system chassis
US7961475B2 (en) 2008-10-23 2011-06-14 International Business Machines Corporation Apparatus and method for facilitating immersion-cooling of an electronic subsystem
US20100103614A1 (en) * 2008-10-23 2010-04-29 International Business Machines Corporation Apparatus and method for immersion-cooling of an electronic system utilizing coolant jet impingement and coolant wash flow
US7944694B2 (en) 2008-10-23 2011-05-17 International Business Machines Corporation Liquid cooling apparatus and method for cooling blades of an electronic system chassis
US20110103019A1 (en) * 2008-10-23 2011-05-05 International Business Machines Corporation Open flow cold plate for immersion-cooled electronic packages
US7885070B2 (en) 2008-10-23 2011-02-08 International Business Machines Corporation Apparatus and method for immersion-cooling of an electronic system utilizing coolant jet impingement and coolant wash flow
US20100328889A1 (en) * 2009-06-25 2010-12-30 International Business Machines Corporation Cooled electronic module with pump-enhanced, dielectric fluid immersion-cooling
US8059405B2 (en) 2009-06-25 2011-11-15 International Business Machines Corporation Condenser block structures with cavities facilitating vapor condensation cooling of coolant
US20100328882A1 (en) * 2009-06-25 2010-12-30 International Business Machines Corporation Direct jet impingement-assisted thermosyphon cooling apparatus and method
US20100328890A1 (en) * 2009-06-25 2010-12-30 International Business Machines Corporation Condenser structures with fin cavities facilitating vapor condensation cooling of coolant
US20100326628A1 (en) * 2009-06-25 2010-12-30 International Business Machines Corporation Condenser fin structures facilitating vapor condensation cooling of coolant
US8014150B2 (en) 2009-06-25 2011-09-06 International Business Machines Corporation Cooled electronic module with pump-enhanced, dielectric fluid immersion-cooling
US8018720B2 (en) 2009-06-25 2011-09-13 International Business Machines Corporation Condenser structures with fin cavities facilitating vapor condensation cooling of coolant
US7885074B2 (en) 2009-06-25 2011-02-08 International Business Machines Corporation Direct jet impingement-assisted thermosyphon cooling apparatus and method
US9303926B2 (en) 2009-06-25 2016-04-05 International Business Machines Corporation Condenser fin structures facilitating vapor condensation cooling of coolant
US8490679B2 (en) 2009-06-25 2013-07-23 International Business Machines Corporation Condenser fin structures facilitating vapor condensation cooling of coolant
US20100328891A1 (en) * 2009-06-25 2010-12-30 International Business Machines Corporation Condenser block structures with cavities facilitating vapor condensation cooling of coolant
US8345423B2 (en) 2010-06-29 2013-01-01 International Business Machines Corporation Interleaved, immersion-cooling apparatuses and methods for cooling electronic subsystems
US8351206B2 (en) 2010-06-29 2013-01-08 International Business Machines Corporation Liquid-cooled electronics rack with immersion-cooled electronic subsystems and vertically-mounted, vapor-condensing unit
US8369091B2 (en) 2010-06-29 2013-02-05 International Business Machines Corporation Interleaved, immersion-cooling apparatus and method for an electronic subsystem of an electronics rack
US8184436B2 (en) 2010-06-29 2012-05-22 International Business Machines Corporation Liquid-cooled electronics rack with immersion-cooled electronic subsystems
US8179677B2 (en) 2010-06-29 2012-05-15 International Business Machines Corporation Immersion-cooling apparatus and method for an electronic subsystem of an electronics rack

Also Published As

Publication number Publication date
CH388357A (fr) 1965-02-28
DE1150696B (de) 1963-06-27
FR1191927A (fr) 1959-10-22
GB876930A (en) 1961-09-06
BE575983A (fr) 1959-06-15

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