EP0207677A1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
EP0207677A1
EP0207677A1 EP86304626A EP86304626A EP0207677A1 EP 0207677 A1 EP0207677 A1 EP 0207677A1 EP 86304626 A EP86304626 A EP 86304626A EP 86304626 A EP86304626 A EP 86304626A EP 0207677 A1 EP0207677 A1 EP 0207677A1
Authority
EP
European Patent Office
Prior art keywords
heat transfer
fins
heat exchanger
heat
fluid
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Withdrawn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
EP86304626A
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German (de)
English (en)
French (fr)
Inventor
Arthur Richard Zingher
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.)
International Business Machines Corp
Original Assignee
International Business Machines Corp
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Filing date
Publication date
Application filed by International Business Machines Corp filed Critical International Business Machines Corp
Publication of EP0207677A1 publication Critical patent/EP0207677A1/en
Withdrawn legal-status Critical Current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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations 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
    • 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

Definitions

  • This invention relates to heat exchangers for transferring heat between the exchanger and a fluid.
  • heat transfer coefficient shall hereinafter refer to the amount of thermal power transferred from a hot solid substrate to a fluid divided by the temperature difference between the hot solid substrate and the fluid.
  • volumemetric heat transfer coefficient will refer to the heat transfer coefficient per unit volume of an array of heat transfer elements.
  • Areal heat transfer coefficient will refer to the heat transfer coefficient per unit area of heat transfer element.
  • Base heat transfer coefficient will refer to the thermal heat transfer coefficient per unit area of substrate on which the heat transfer elements lie.
  • the "hydraulic diameter" of a passage used for forced-convection heat transfer is two times the groove width between heat transfer elements.
  • the thermal conduction across the hydraulic diameter defines a scale, or measure, or the heat transfer coefficient per unit area.
  • Nusselt number will be used to refer to the normalised heat transfer characteristics of a system.
  • the Nusselt number measures the areal heat transfer coefficient along the scale defined by the hydraulic diameter.
  • heat exchanger will refer to a device that serves to transfer heat from solid substrate to fluids as well as between two or more fluids.
  • a "heat transfer element” will be used to describe a solid object, such as a tube, a fin or the like, which can be used to transfer heat between a substrate and a fluid or between an interior fluid and an exterior fluid. Heat transfer may take place between a cool element and a hot exterior fluid or between a hot element and a cool exterior fluid.
  • a “row” of heat transfer elements will be used to describe a plurality of elements spaced transversely across the direction of fluid flow.
  • a “column” of heat transfer elements will be used to describe a plurality of fins spaced along the direction of fluid flow.
  • the term “downstream” will be used to describe the direction along the fluid flow away from the origin of flow.
  • thermal boundary layer will hereinafter refer to the relatively warm fluid layer that develops adjacent to a heat transfer element as fluid flows past the element.
  • the thermal boundary layer is conventionally defined by an isotherm very close to the fluid temperature, usually the isotherm having a temperature approximately equal to that of the fluid, ie 99% of the temperature difference from the heat transfer element to the fluid.
  • the thermal boundary layer will refer to the layer bounded by the isotherm approximately one-half the temperature difference between the heat transfer element and the fluid. Defining the thermal boundary layer according to this 50% isotherm gives an average heat transfer coefficient.
  • the streamlines of that thermal boundary layer traced downstream will be referred to as a "wake-core" of a heat transfer element.
  • the volumetric heat transfer coefficient of prior designs is proportional to the Nusselt number associated with the designs divided by the groove width, and divided by the transverse pitch.
  • the minimum groove width is dictated by practical problems of fabrication and the possibility of fouling the heat exchanger.
  • Transverse pitch is limited by the size of the heat transfer elements used and the groove width.
  • Prior designs achieve a limited Nusselt number, and therefore a low volumetric heat transfer coefficient.
  • “Compact Heat Exchangers" Second Edition, W M Kays and A L London (McGraw-Hill, 1964) sets forth many conventional prior designs.
  • One conventional design employs a set of parallel long fins. At any fluid flow speed where fluid flow is laminar, a characteristic, relatively small Nusselt number can be calculated. A low Nusselt number is characteristic of a low volumetric heat transfer coefficient. Thus, this design is not an efficient method to transfer large amounts of thermal power.
  • Another conventional design uses a rectangular array of heat transfer elements in orthogonal rows in which each element is directly aligned with its downstream neighbour. This design also results in a relatively low Nusselt number.
  • Yet another conventional design employs an array of heat transfer elements in which alternate rows of elements are offset by one-half the transverse pitch between elements.
  • the Nusselt number of this array is also relatively small.
  • US-A-3,421,578 (Marton) describes a heat exchanger in which fins are arranged at substantially equal distance from each other along diagonal lines. US-A-3,421,578 proposes the use of a conventional offset pattern to improve heat transfer.
  • Laminar convection through closely spaced long fins leads to "fully developed laminar convection".
  • Upstream parts of each fin have adjacent streamlines, which flow along downstream parts of the fin. If the fin has constant power density, the downstream part of the fin becomes very hot.
  • Other streamlines flow near the centre of the gap between the fins, but do no impinge closely on the thermal boundary layer of the fins. These streamlines, therefore, cannot directly remove heat from the fins. They can only remove heat indirectly, from the streamlines nearer the fins.
  • a rectangular pattern of short fins causes "fully developed periodic laminar convection", and is similarly inefficient. All fins in a column share a wake-core. An upstream fin heats a wake-core, which immediately impinges on a downstream fin. By contrast, other streamlines, such as those flowing between the fins, never impinge on any fin. Therefore, they remove thermal power only indirectly, after it diffuses outside a wake-core.
  • thermal boundary layer determines the local heat transfer coefficient.
  • the thermal boundary layer grows in thickness along the downstream length of the element.
  • the prior art has not solved the problem of promoting efficient heat transfer with a convective heat transfer apparatus using laminar fluid flow for a given density of heat transfer elements in a small area, and for a given limited pressure gradient.
  • the present invention provides a heat exchanger for transferring heat between the exchanger and a fluid, the heat exchanger comprising at least one surface provided with a plurality of heat exchanging fins positioned on a grid defined by intersecting row and column lines such that each fin lies on a row line and in longitudinal alignment with a column line, characterised in that no fin is aligned, in either the row or column directions, with its nearest or next nearest neighbours.
  • the invention provides an apparatus for convective heat transfer to a fluid stream comprising a substrate and heat transfer elements, said heat transfer elements being arranged in a configuration on said substrate such that when said fluid stream having streamlines flows across the substrate, substantially every streamline flows close to some heat transfer element before many streamlines flow close to more than one heat transfer element.
  • heat transfer elements are arranged in a plurality of rows transverse to the fluid flow direction, the heat transfer elements in said rows being separated along a direction transverse to the fluid flow by irregular distances.
  • heat transfer elements located further away from the fluid source are downstream of said heat transfer elements located closer to said fluid source, said heat transfer elements being offset from each other in a direction transverse to the fluid flow such that a streamline flowing close to the thermal wake-core of a first heat transfer element does not flow close to the thermal wake-core of a downstream heat transfer element until the heat received from the first heat transfer element has been substantially diffused away from said wake-core.
  • Said transverse separation may be random.
  • said heat transfer elements are fins and have a base, a tip, a leading edge and a trailing edge wherein said fins have a wedged thickness decreasing from base to tip, a tapered chord decreasing from base to tip, a curved leading edge and a straight trailing edge.
  • each heat transfer element is preferably surrounded by a thermal boundary layer having a thickness N Z times thinner than the transverse gap between elements, each row successively downstream being transversely offset such that each streamline of the fluid passes through the thermal boundary layer of only one heat transfer element per N Z rows downstream of each other.
  • each successive row of heat transfer elements is displaced transversely by a factor (W times S) wherein W is the width of the transverse gap between heat transfer elements, and S is a number such that positive integers A and B having magnitudes less than N Z satisfy the inequality:
  • the numbers P and M are alternate Fibonacci numbers.
  • said heat transfer elements are further arranged such that most streamlines flow through the thermal boundary layer of at least one heat transfer element.
  • the invention comprises an apparatus for convective heat transfer comprising a substrate having a plurality of heat transfer elements, said heat transfer elements being arranged on said substrate such that any two elements located a small distance apart along the flow direction are misaligned transverse to the flow direction by a distance greater than the thickness of the thermal boundary layer formed by fluid flowing past said elements.
  • fluid flow it is not necessary for fluid flow to be parallel. It may instead be radial.
  • the heat exchange apparatus of this invention has rows of heat exchange elements organised in a pattern on a plate or substrate in such a way that the thermal boundary layers of the fluid are thin in comparison with the groove width, resulting in the efficient transfer of thermal power. Accordingly, the rows of heat transfer elements are transversely offset from each other such that the fluid streamlines impinging on any heat transfer element will not impinge on any other element until they have given up a substantial amount of transferred heat.
  • each streamline contacts one heat transfer element and is directly heated exactly once before any streamline contacts more than one element and is directly heated twice.
  • every streamline of the fluid is directly used for heat transfer.
  • an upstream heat transfer element heats its wake-core, enough time elapses to allow heat to diffuse sideways before these streamlines flow close to a downstream element.
  • no downstream heat transfer element is in the immediate thermal wake-core of any upstream heat transfer element. Because there is a heat transfer element close to every streamline, such an array is referred to as "omnipresent staggering".
  • the fluid does not contact elements in rapid succession the temperature difference between the fluid and the heat transfer element it contacts is sufficiently great to provide good heat transfer.
  • This invention therefore, uses aperiodic laminar convection or long period developed convection to avoid the inefficiency of conventionally staggered heat transfer elements.
  • each element functions as efficiently as an isolated heat transfer element, thus giving the best heat transfer for a given pressure gradient.
  • a heat exchange apparatus may be made having heat transfer elements in many configurations as long as the following requirements are met: (a) substantially every streamline of the fluid flows close to some heat transfer element in the array and (b) substantially every streamline flows close to one heat transfer element before many streamlines flow close to more than one heat transfer element.
  • heat transfer elements can be used for heat transfer according to this invention as long as they are not locally regular rectangular nor conventionally staggered patterns.
  • the heat transfer elements can be randomly placed in an irregular manner.
  • fluid streamlines would randomly impinge on the elements.
  • very few streamlines would avoid impinging the thermal boundary layer of a heat transfer element.
  • very few wake-cores flow immediately from one element to another nearby element.
  • heat transfer elements can be transversely offset such that each stream passes through the thermal boundary layer of only one heat transfer element per a certain number of successive rows, represented by the term N Z .
  • N Z is the ratio between the width, W, of the transverse gap between the heat transfer elements in each row and the thickness of the wake-core immediately beyond the downstream end of each element.
  • N Z is larger than 3. This will allow the streamline to flow past at least three rows of heat transfer elements before impinging directly on another element. Further, this configuration creates areas in which other streamlines can impinge on other heat transfer elements. This configuration affords considerable time for thermal power to diffuse sideways before the wake-core impinges on another heat transfer element.
  • each successive row is offset by a distance of S times W, where S is a suitable constant to be described below.
  • S is a suitable constant to be described below.
  • the wake-core of the zeroth element should pass outside of the thermal boundary layer of element (A, B).
  • the thickness of the thermal boudary layer is W/N Z . Therefore, the desired situation can be represented mathematically in the following way:
  • the value S must satisfy these inequalities for every (A, B) element in N Z rows downstream of the zeroth element. Algebraically, this can be represented by the following inequality:
  • M is an integer between N Z -l and N Z +1.
  • P is another integer, relatively prime to M. S can then be determined by the following equation:
  • N Z an S value which solves inequality (I) for one N Z value may not be suitable for faster flow and larger N Z .
  • N Z exceeds 13
  • 5/13 is not the best value for S, although it can enhance the normalised heat transfer to an intermediate degree independent of flow speed.
  • the mathematical art of "Diophantine approximations” leads to another class of solutions. There, a classical problem is to find numbers which are especially hard to approximate by rational fractions, such as, Phi, the "Golden Ratio" of classical mathematics. (See, for example, "Elementary Number Theory", J Roberts, 1977, Chapter XIII, MIT Press, pgs 116-119).
  • a Fibonaci number sequence is 1, 1, 2, 3, 5, 8, 13, 21 ... which is widely known in the field of mathematics.
  • Inequality (II) implies that Inequality (I) is solved for most positive integers B less than N Z .
  • the wake-core from an upstream element will miss elements in almost all of N Z downstream rows.
  • the wake-core will slightly impinge on a downstream fin. If N Z is 34, the wake-core of an original fin will miss every fin in the next 34 rows by more than 100% of (W/N Z ) except in rows 21 and 34, where the miss distances are 72% and 44% of W/N Z .
  • One skilled in solving Diophantine approximations can find many other satisfactory values of S involving irrational numbers. These values satisfy Inequality (I) for most values of B. They can be translated into arrays of heat transfer elements according to this invention. Of course, these patterns will not repeat and no two fins will be in the same column line.
  • Figure 1 is an example, however, of a repetitive pattern of heat transfer elements 101 arranged on a substrate in accordance with the invention. It can be seen that the pattern repeats every 8 rows so that fins which are longitudinally aligned are spaced by 8 rows. In some column lines, only one fin 101 is found.
  • Figure 2 shows a local section of another repetitive pattern of fins which has been distorted by transverse exaggeration.
  • Elements 201 are surrounded by representative isotherms 203. Fluid flows in the "x" direction.
  • Element 211 can be considered the “zeroth” element and has X and Y coordinates of (0,0).
  • W is the distance along the "y" axis, transverse to the flow, between Element 211 and Element 212, the next element having an x-coordinate of 0.
  • the tranverse width of the thermal boundary layer following each of the elements is 1/13 of the width W.
  • M the number of rows of elements in the offset pattern is thus 13.
  • the integer P which has been selected to be relatively prime to M, is 5.
  • the offset factor is P/M or 5/13.
  • Each successive row is therefore displaced transversely across the flow in the y-direction by 5/13 of W.
  • Element 207 is displaced from Element 209.
  • Elements having the same y-coordinate occur only every 13 x-units.
  • a streamline impinging on the zeroth Element 211 will not again impinge an element until the 13th row farther downstream.
  • much of the heat will diffuse away sideways. Therefore, heat transfer from a downstream element will be more efficient than if the subsequent element were located only one or two rows away.
  • Figure 3 shows further isotherms 203 around the fin positions 201 in the heat exchanger of Figure 2 and demonstrates more clearly the fact that streamlines do not impinge on more than one heat transfer element.
  • a heat exchanger made according to this invention can be used in a variety of applications, including cross-flow and tube fluid-fluid heat exchangers, in fin-and-fluid heat exchangers and the like. Fin-and-fluid heat exchangers can be used to dissipate heat from integrated circuits on a small scale.
  • the heat transfer element can be fins, tubes, wires or many other structures useful for convective heat transfer.
  • the fins should be streamlined. Where the fin is heated only at the bottom, it should have a cross-section like a symmetric airfoil, have a wedged thickness decreasing from base to tip, and tapered chord decreasing from base to tip, a curved leading edge and a straight trailing edge.
  • any type of fin known to those of skill in the art which is appropriate to the application may be used.
  • the novel offset pattern of this invention can be used in three-dimensional heat exchangers.
  • metal wire emerging from the substrate can be randomly crushed and used as convective fins.
  • fins in a conventional fin-and-fluid transfer device can be bent along random planes which thereby offset the fins at random.
  • the heat exchangers of this invention can be made according to methods known to those of ordinary skill in the art.
  • a fin-and-fluid type heat exchange apparatus can be made by the "lance and offset" process. In this process, a large metal sheet is lanced to produce slots. The resulting sheet is then pressed parallel and perpendicular to its base plane. The result is a dense array of fins.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP86304626A 1985-06-20 1986-06-16 Heat exchanger Withdrawn EP0207677A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US74714485A 1985-06-20 1985-06-20
US747144 1985-06-20

Publications (1)

Publication Number Publication Date
EP0207677A1 true EP0207677A1 (en) 1987-01-07

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ID=25003829

Family Applications (1)

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EP86304626A Withdrawn EP0207677A1 (en) 1985-06-20 1986-06-16 Heat exchanger

Country Status (3)

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EP (1) EP0207677A1 (pt)
JP (1) JPS629198A (pt)
BR (1) BR8602741A (pt)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0322185A1 (en) * 1987-12-23 1989-06-28 Minnesota Mining And Manufacturing Company Heat exchanger
EP0519886A1 (en) * 1991-06-18 1992-12-23 Ente per le nuove tecnologie, l'energia e l'ambiente ( ENEA) Fluid-dynamic device, particularly for heat exchange
EP1067350A3 (en) * 1999-07-09 2002-07-31 Ford Motor Company Beaded plate for a heat exchanger and method of making same
US11168924B2 (en) 2017-05-10 2021-11-09 Dyson Technology Limited Heater
CN115430390A (zh) * 2022-11-09 2022-12-06 山东法拉第氘源科技有限公司 一种氘代溴苯的加工制备装置及加工制备方法
US11589661B2 (en) 2017-01-12 2023-02-28 Dyson Technology Limited Hand held appliance
US20230069522A1 (en) * 2021-09-01 2023-03-02 Eagle Technology, Llc Heat exchanger

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006125767A (ja) * 2004-10-29 2006-05-18 Tokyo Institute Of Technology 熱交換器

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE325832C (de) * 1918-07-25 1920-09-21 Norddeutsche Kuehlerfabrik G M Fahrzeug- oder Flugzeugkuehler
FR536145A (fr) * 1921-01-08 1922-04-26 Muller Soc Perfectionnements apportés dans l'établissement des radiateurs
US2133502A (en) * 1936-05-22 1938-10-18 Gen Motors Corp Radiator fin structure
CH234859A (de) * 1941-02-15 1944-10-31 Sulzer Ag Kühl- bezw. Gefriervorrichtung zur Übertragung der Wärme vom Kühlgut zum Kälteträger.
GB627859A (en) * 1946-09-17 1949-08-17 Meyer Schlioma Frenkel Improvements in or relating to heat exchangers
US2647731A (en) * 1951-08-17 1953-08-04 Arvin Ind Inc Radiator core construction
US2789797A (en) * 1953-08-20 1957-04-23 Modine Mfg Co Heat exchanger fin structure
GB883547A (en) * 1958-04-12 1961-11-29 John Montague Laughton Improvements in and relating to the use of extended surfaces in heat transfer apparatus
DE2508727A1 (de) * 1975-02-28 1976-09-09 John Edward Randell Waermetauscher
US4019494A (en) * 1975-07-09 1977-04-26 Safdari Yahya B Solar air heater assembly

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE325832C (de) * 1918-07-25 1920-09-21 Norddeutsche Kuehlerfabrik G M Fahrzeug- oder Flugzeugkuehler
FR536145A (fr) * 1921-01-08 1922-04-26 Muller Soc Perfectionnements apportés dans l'établissement des radiateurs
US2133502A (en) * 1936-05-22 1938-10-18 Gen Motors Corp Radiator fin structure
CH234859A (de) * 1941-02-15 1944-10-31 Sulzer Ag Kühl- bezw. Gefriervorrichtung zur Übertragung der Wärme vom Kühlgut zum Kälteträger.
GB627859A (en) * 1946-09-17 1949-08-17 Meyer Schlioma Frenkel Improvements in or relating to heat exchangers
US2647731A (en) * 1951-08-17 1953-08-04 Arvin Ind Inc Radiator core construction
US2789797A (en) * 1953-08-20 1957-04-23 Modine Mfg Co Heat exchanger fin structure
GB883547A (en) * 1958-04-12 1961-11-29 John Montague Laughton Improvements in and relating to the use of extended surfaces in heat transfer apparatus
DE2508727A1 (de) * 1975-02-28 1976-09-09 John Edward Randell Waermetauscher
US4019494A (en) * 1975-07-09 1977-04-26 Safdari Yahya B Solar air heater assembly

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0322185A1 (en) * 1987-12-23 1989-06-28 Minnesota Mining And Manufacturing Company Heat exchanger
US4997034A (en) * 1987-12-23 1991-03-05 Minnesota Mining And Manufacturing Company Heat exchanger
EP0519886A1 (en) * 1991-06-18 1992-12-23 Ente per le nuove tecnologie, l'energia e l'ambiente ( ENEA) Fluid-dynamic device, particularly for heat exchange
EP1067350A3 (en) * 1999-07-09 2002-07-31 Ford Motor Company Beaded plate for a heat exchanger and method of making same
US11589661B2 (en) 2017-01-12 2023-02-28 Dyson Technology Limited Hand held appliance
US11712098B2 (en) 2017-01-12 2023-08-01 Dyson Technology Limited Hand held appliance
US11168924B2 (en) 2017-05-10 2021-11-09 Dyson Technology Limited Heater
US20230069522A1 (en) * 2021-09-01 2023-03-02 Eagle Technology, Llc Heat exchanger
US12000664B2 (en) * 2021-09-01 2024-06-04 Eagle Technology, Llc Heat exchanger
CN115430390A (zh) * 2022-11-09 2022-12-06 山东法拉第氘源科技有限公司 一种氘代溴苯的加工制备装置及加工制备方法

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Publication number Publication date
BR8602741A (pt) 1987-02-10
JPS629198A (ja) 1987-01-17

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