US3881547A - Heat transfer device employing fins in a fluid stream - Google Patents

Heat transfer device employing fins in a fluid stream Download PDF

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Publication number
US3881547A
US3881547A US415068A US41506873A US3881547A US 3881547 A US3881547 A US 3881547A US 415068 A US415068 A US 415068A US 41506873 A US41506873 A US 41506873A US 3881547 A US3881547 A US 3881547A
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US
United States
Prior art keywords
fins
array
wave
revolution
axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US415068A
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English (en)
Inventor
Gordon R Lavering
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.)
Varian Medical Systems Inc
Original Assignee
Varian Associates 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 Varian Associates Inc filed Critical Varian Associates Inc
Priority to US415068A priority Critical patent/US3881547A/en
Priority to CA213,400A priority patent/CA1032528A/en
Priority to DE19742453016 priority patent/DE2453016A1/de
Priority to GB4878574A priority patent/GB1472551A/en
Priority to FR7437322A priority patent/FR2250972B1/fr
Priority to JP49130393A priority patent/JPS5844196B2/ja
Application granted granted Critical
Publication of US3881547A publication Critical patent/US3881547A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01J—ELECTRIC DISCHARGE TUBES OR DISCHARGE LAMPS
    • H01J23/00—Details of transit-time tubes of the types covered by group H01J25/00
    • H01J23/02—Electrodes; Magnetic control means; Screens
    • H01J23/027—Collectors
    • H01J23/033—Collector cooling devices
    • 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
    • F28F1/14—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 longitudinally
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01J—ELECTRIC DISCHARGE TUBES OR DISCHARGE LAMPS
    • H01J19/00—Details of vacuum tubes of the types covered by group H01J21/00
    • H01J19/28—Non-electron-emitting electrodes; Screens
    • H01J19/32—Anodes
    • H01J19/36—Cooling of anodes
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01J—ELECTRIC DISCHARGE TUBES OR DISCHARGE LAMPS
    • H01J2893/00—Discharge tubes and lamps
    • H01J2893/0001—Electrodes and electrode systems suitable for discharge tubes or lamps
    • H01J2893/0012—Constructional arrangements
    • H01J2893/0027—Mitigation of temperature effects

Definitions

  • the heat exchanger comprises a device coupled in heat exchanging relation with a fluid stream by means of an arcuate array of radially directed, circumferentially spaced, thermally conductive fins with the mean plane of each fin being generally parallel of the axis of revolution of the arcuate array.
  • the fins are corrugated into a wave-like geometry, with the waves increasing in amplitude with increase in radial distance from the axis of revolution, and with the wave fronts running generally laterally to the axis of revolution of the array.
  • the fluid stream flows between adjacent fins in a serpentine path through the array in the axial direction.
  • the present invention relates in general to heat exchanging apparatus, and more particularly to an im' proved heat exchanger particularly suited for cooling anode structures of electron beam tubes, wherein a stream of fluid coolant such as air is directed through a circular array of cooling fins for removing heat from the anode of the tube.
  • heat exchangers have been proposed for cooling the anodes of electron beam tubes.
  • a circular array of radially directed cooling fins was coupled to the anode with the fins projecting outwardly therefrom in circumferentially spaced relation from each other to accomodate an axial flow of fluid through the array for cooling of the fins and the anode.
  • the fins were corrugated into a wave-like geometry with the wave fronts being generally parallel to the axis of revolution of the circular array of fins.
  • Such an arrangement of cooling fins is disclosed and claimed in US Pat. No. 3,293,480, patented Dec. 20, 1966 and assigned to the same assignee as the present invention.
  • the louvered fins have certain definite problems.
  • One of the problems is that the flow of air, or other fluid, past the bridge-like tabs provides a source of noise which is particularly shrill in the audio-range of 600 Hz to L200 Hz.
  • the louvers collect lint which impedes the flow of fluid coolant through the array and which results in a loss of heat transfer effi' ciency.
  • the principal object of the present invention is to provide an improved heat transfer device employing fins in a fluid coolant stream.
  • the heat transfer device includes a circular array of heat exchanging fins which are corrugated to provide a wavelike geometry, with the wave fronts being disposed at a substantial angle to the direction of air flow through the array of fins, such air flow being parallel to the axis of revolution of the array, whereby improved heat transfer is achieved.
  • the corrugations in the circular array of fins define wave geometries wherein the wave fronts are at a substantial angle to the axis of revolution and to the fluid flow stream, and wherein the amplitude of the wave-like corrugations increases in a radially outward direction, thereby increasing the length of the fluid flow path as a function of radius and causing some of the stream to be directed toward the center or core, of the fin array for improved heat transfer.
  • the wave crests in the adjacent fins of the array are in registration to define therebetween a serpentine fluid flow path axially of the array, such flow path being of generally uni form thickness at a given radius from the center of the array.
  • FIG. 1 is a fragmentary side elevational view, partly broken away, of the anode of an electron beam tube employing an array of cooling fins of the present invention
  • FIG. 2 is an enlarged schematic line diagram of a ser pentine shaped flow path defined between adjacent fins of the array of FIG. 1,
  • FIG. 3 is a view similar to that of FIG. 2 depicting an alternative wave shape
  • FIG. 4 is a plan view of a prior art louvered cooling fin
  • FIG. 5 is a sectional view through the louvered fin structure of FIG. 4 depicting the flow path between two adjacent fins.
  • FIG. 1 there is shown an electron beam collector or anode assembly 11 of an electron beam tube such as a power grid tube, klystron, travelling wave tube, or the like, wherein an electron beam is collected on the interior surfaces of a cylindrical evacuated collector bucket 12, as of copper, having an outer cylindrical shape.
  • a circular array of cooling fins 13 is coupled or affixed to the outer cylindrical periphery of the collector 12, as by brazing or soldering.
  • the fins 13 in a typical example are fitted within longitudinal recesses 14 in the periphery of the collector bucket 12 and are brazed at their root portions to the interior walls of the recesses 14.
  • the cooling fins 13 are thin sheets of a thermally conductive material, such as copper or aluminum and preferably copper, which radiate outwardly from the collector bucket 12 in a circular array.
  • the fins 13 are made of a copper sheet 0.025 inches thick having a radial extent of approximately 3.25 inches.
  • the fins 13 are corrugated to form a wave-like geometry, with the wave fronts, as defined by the ridge lines 15, running along the crest of the wave and ex tending at an angle to and generally laterally of the axis of revolution of the circular array of fins.
  • the amplitude of the waves increases in the radial outward direction from the axis of revolution to define a serpentine-shaped fluid flow path 16 between adjacent wavy fins as more clearly shown in FIG. 2.
  • a fluid coolant stream as of air, is directed generally longitudinally of the axis of revolution of the array through the adjacent serpentine-shaped flow paths 16 between adjacent fins 13.
  • the circumferential spacing between adjacent fins is approximately equal to the amplitude of the wavelike distortion of the fins.
  • the mean plane of each fin 13, as indicated by the broken line 18, is parallel to the axis of revolution of the array.
  • the wave-like corrugations of each fin 13 need not be of the half-wave type as shown in FIGS. 1 and 2 but may be of a more sinusoidal shape with substantially equal corrugation of the fin on the opposite sides of the mean plane 18 of each fins. Equal wave amplitudes on opposite sides of the fin are shown in FIG. 3 where the corrugations are more of a triangular wave-shape than of the sinusoidal form shown in FIGS. 1 and 2.
  • the length of the serpentine flow path 16 increases with increase in radius from the axis of revolution of the array. Increasing the flow path length tends to increase the local impedance of the coolant passage to fluid flow and to counteract the reduction in impedance due to the increase in width of the flow path near the outer perimeter of the array.
  • the serpentine shape of the flow path 16 causes the molecules of the fluid in the stream to impinge and to scrub the surfaces of he fins 13 as shown by the arrows in FIG. 2. It is believed that this contributes substantially to increased heat transfer between the fluid stream and the fins for improved heat transfer efficiency.
  • the corrugations which have increased amplitude near the outer periphery tend to direct some of the flow toward the center core 12 and toward the root portions of the cooling fins 13 for improved heat transfer efficiency.
  • louvered fin 21 having the pushed out bridgeshaped tabs or louvers 22 located near the outer periphery of the fin 21.
  • the problem with this type of fin geometry is that heat transfer to the bridge-shaped louver portions 22 is restricted clue to the break in the continuity of the fin caused by the bridge 22 being severed along opposite edges from the fin at 23, such that the heat flow into the bridge portion 22 is only from opposite ends thereof.
  • the louvered fin geometry provides additional heat transfer area in the central region of the fluid flow stream, the apparent heat transfer advantage of the louvered portion is not fully obtained due to the relatively poor heat flow to the louver portion 22.
  • the fin is perforated in forming the louvers 22, the flow of air through the array of fins in the axial direction generates substantial noise. More particularly, in one of the typical prior art louvered geometries, there is a peak in the noise power spectrum in the audio frequency range between 600 Hz and 1,200 Hz. This turns out to be a rather shrill sound resulting in substantial discomfort to nearby workmen and operators.
  • the advantage of the corrugated fins of the present invention is that they provide a substantial increase in heat transfer efficiency. More particularly, the heat transfer horsepower parameter, i.e., a quantity proportional to the product of fluid flow rate in cubic feet per minute times pressure drop in the fluid flow stream required to maintain the core 12 at a given temperature, is directly related to the amount of horsepower required to move the fluid coolant through the cooling array. In one case, this parameter was reduced by percent utilizing the corrugated fins of the present invention as contrasted with a comparable louvered fin geometry as shown in FIGS. 4 and 5.
  • the corrugated fin geometry of the present invention provides a relatively clean aerodynamic flow passage 16 through the array, thereby eliminating the objectionable shrill noises previously produced by the louvered fin geometries.
  • the relatively clean aerodynamic surfaces of the present invention prevent the collection of lint in a fin array.
  • the amount of fin material, such as copper can be reduced by a factor of at least 20 percent resulting in substantial cost savings.
  • the fluid ducting or manifolds required for directing the fluid coolant through the fin array can be reduced in diameter, and the fans and blowers can be reduced in weight and size.
  • the wavy fins 13 of the present invention have, thus far, been described as being radially directed to provide a fluid flow path thickness that increases with increase in radial distance from the core 12, this is not a requirement.
  • the radial fins 13 may be curved into an involute of a circle arc such that the spacing between adjacent fins is constant over the radial extent of the fins.
  • the crest of the waves in the fins 13 need not be continuous but may be interrupted. However, the interruptions in adjacent waves in a given fin 13 should be staggered so as to minimize non-serpentine shaped portions of the fluid flow paths 16.
  • a heat transfer apparatus for transferring heat between a device and a stream of fluid wherein said device comprises an elongate member and a sleeve surrounding said elongate member and where said stream of fluid flows between said elongate member and said nearer to said axis of revolution of said array. surrounding sleeve member 2.
  • each of Said the amplitude of said wave-like configuration is subfins bemg corrugated F' configufa' stantially zero at the innermost radial extent of each of tion, the mean plane of the wave-like configuration Said fins of each of Said fins being generally parallel to the 3.
  • said fins are axis of revolution of said arcuate array;

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Common Detailed Techniques For Electron Tubes Or Discharge Tubes (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
US415068A 1973-11-12 1973-11-12 Heat transfer device employing fins in a fluid stream Expired - Lifetime US3881547A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US415068A US3881547A (en) 1973-11-12 1973-11-12 Heat transfer device employing fins in a fluid stream
CA213,400A CA1032528A (en) 1973-11-12 1974-11-08 Heat transfer device employing fins in a fluid stream
DE19742453016 DE2453016A1 (de) 1973-11-12 1974-11-08 Waermetauscher
GB4878574A GB1472551A (en) 1973-11-12 1974-11-11 Heat transfer device employing fins in a fluid stream
FR7437322A FR2250972B1 (enrdf_load_stackoverflow) 1973-11-12 1974-11-12
JP49130393A JPS5844196B2 (ja) 1973-11-12 1974-11-12 ネツデンタツソウチ

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US415068A US3881547A (en) 1973-11-12 1973-11-12 Heat transfer device employing fins in a fluid stream

Publications (1)

Publication Number Publication Date
US3881547A true US3881547A (en) 1975-05-06

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Family Applications (1)

Application Number Title Priority Date Filing Date
US415068A Expired - Lifetime US3881547A (en) 1973-11-12 1973-11-12 Heat transfer device employing fins in a fluid stream

Country Status (6)

Country Link
US (1) US3881547A (enrdf_load_stackoverflow)
JP (1) JPS5844196B2 (enrdf_load_stackoverflow)
CA (1) CA1032528A (enrdf_load_stackoverflow)
DE (1) DE2453016A1 (enrdf_load_stackoverflow)
FR (1) FR2250972B1 (enrdf_load_stackoverflow)
GB (1) GB1472551A (enrdf_load_stackoverflow)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4358706A (en) * 1979-05-31 1982-11-09 Thomson-Csf Insulated collector for an electronic power tube and a tube equipped with such a collector
US4729428A (en) * 1984-06-20 1988-03-08 Showa Aluminum Corporation Heat exchanger of plate fin type
US5019880A (en) * 1988-01-07 1991-05-28 Prime Computer, Inc. Heat sink apparatus
US5355843A (en) * 1993-07-12 1994-10-18 University Of Chicago Heat transfer mechanism with thin filaments including ceramic high temperature heat exchanger
US5913289A (en) * 1998-06-08 1999-06-22 Gas Research Institute Firetube heat exchanger with corrugated internal fins
US20110127022A1 (en) * 2009-12-01 2011-06-02 Lockheed Martin Corporation Heat Exchanger Comprising Wave-shaped Fins
US9541331B2 (en) 2009-07-16 2017-01-10 Lockheed Martin Corporation Helical tube bundle arrangements for heat exchangers
US9670911B2 (en) 2010-10-01 2017-06-06 Lockheed Martin Corporation Manifolding arrangement for a modular heat-exchange apparatus
US9777971B2 (en) 2009-10-06 2017-10-03 Lockheed Martin Corporation Modular heat exchanger
US10209015B2 (en) 2009-07-17 2019-02-19 Lockheed Martin Corporation Heat exchanger and method for making
US20220219966A1 (en) * 2021-01-08 2022-07-14 Grad Aps Apparatus for dispensing a beverage

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2289984A (en) * 1940-07-12 1942-07-14 Westinghouse Electric & Mfg Co Air cooler for power tubes
US2347957A (en) * 1939-06-17 1944-05-02 William E Mccullough Heat exchange unit
US2535721A (en) * 1946-06-14 1950-12-26 Chausson Usines Sa Cylindrical heat exchanger

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS441869Y1 (enrdf_load_stackoverflow) * 1965-12-28 1969-01-24

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2347957A (en) * 1939-06-17 1944-05-02 William E Mccullough Heat exchange unit
US2289984A (en) * 1940-07-12 1942-07-14 Westinghouse Electric & Mfg Co Air cooler for power tubes
US2535721A (en) * 1946-06-14 1950-12-26 Chausson Usines Sa Cylindrical heat exchanger

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4358706A (en) * 1979-05-31 1982-11-09 Thomson-Csf Insulated collector for an electronic power tube and a tube equipped with such a collector
US4729428A (en) * 1984-06-20 1988-03-08 Showa Aluminum Corporation Heat exchanger of plate fin type
US5019880A (en) * 1988-01-07 1991-05-28 Prime Computer, Inc. Heat sink apparatus
US5355843A (en) * 1993-07-12 1994-10-18 University Of Chicago Heat transfer mechanism with thin filaments including ceramic high temperature heat exchanger
US5913289A (en) * 1998-06-08 1999-06-22 Gas Research Institute Firetube heat exchanger with corrugated internal fins
US9541331B2 (en) 2009-07-16 2017-01-10 Lockheed Martin Corporation Helical tube bundle arrangements for heat exchangers
US10209015B2 (en) 2009-07-17 2019-02-19 Lockheed Martin Corporation Heat exchanger and method for making
US9777971B2 (en) 2009-10-06 2017-10-03 Lockheed Martin Corporation Modular heat exchanger
US20110127022A1 (en) * 2009-12-01 2011-06-02 Lockheed Martin Corporation Heat Exchanger Comprising Wave-shaped Fins
US9670911B2 (en) 2010-10-01 2017-06-06 Lockheed Martin Corporation Manifolding arrangement for a modular heat-exchange apparatus
US20220219966A1 (en) * 2021-01-08 2022-07-14 Grad Aps Apparatus for dispensing a beverage

Also Published As

Publication number Publication date
FR2250972B1 (enrdf_load_stackoverflow) 1978-08-18
GB1472551A (en) 1977-05-04
CA1032528A (en) 1978-06-06
JPS5844196B2 (ja) 1983-10-01
DE2453016A1 (de) 1975-05-15
JPS5079858A (enrdf_load_stackoverflow) 1975-06-28
FR2250972A1 (enrdf_load_stackoverflow) 1975-06-06

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