WO1991008433A1 - Ensemble d'echangeur thermique modulaire ameliore - Google Patents

Ensemble d'echangeur thermique modulaire ameliore Download PDF

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Publication number
WO1991008433A1
WO1991008433A1 PCT/US1990/006957 US9006957W WO9108433A1 WO 1991008433 A1 WO1991008433 A1 WO 1991008433A1 US 9006957 W US9006957 W US 9006957W WO 9108433 A1 WO9108433 A1 WO 9108433A1
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WO
WIPO (PCT)
Prior art keywords
header
outlet
inlet
fluid
flange
Prior art date
Application number
PCT/US1990/006957
Other languages
English (en)
Inventor
Robert F. Dierbeck
Original Assignee
Dierbeck Robert F
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
Priority claimed from US07/443,218 external-priority patent/US4981170A/en
Priority claimed from US07/508,962 external-priority patent/US4979560A/en
Priority claimed from US07/590,342 external-priority patent/US5042572A/en
Application filed by Dierbeck Robert F filed Critical Dierbeck Robert F
Priority to EP91901103A priority Critical patent/EP0502982B1/fr
Priority to DE69029813T priority patent/DE69029813T2/de
Publication of WO1991008433A1 publication Critical patent/WO1991008433A1/fr

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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
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation

Definitions

  • the present invention pertains to heat exchangers for flowing fluid materials and, more particularly, to a modular heat exchanger construction in which the individual modules are of a unique corrugated construction with interior turbulator plates or of a conventional construction, either of which utilize easily demountable connectors to facilitate separate module replacement.
  • each of the corrugations is provided with an interior baffle plate which blocks direct flow of the fluid through the conduit and causes the fluid to be diverted from a purely axial flow.
  • the diversion of fluid flow by the baffle plate slows the flow through the conduit somewhat and enhances the heat exchanging contact between the fluid and the walls of the conduit, the surface area of which is substantially enhanced by the corrugated construction.
  • Patent 3,099,315 shows a heat exchanger including a corrugated main tubular conduit in which each corrugation comprises a pair of concave disks attached at their outer peripheral edges to define a corrugation with an open interior and opposite axial openings for the flow of a fluid therethrough.
  • An interior baffle plate is enclosed in each corrugation and is provided with radially offset apertures to allow fluid to flow from one side of the baffle plate to the other after it is diverted from a purely axial direction.
  • Each baffle plate also includes a series of stationary vanes which serve to direct the axial flow of fluid into the corrugation radially outwardly to the holes in the baffle plate.
  • U.S. Patent 2,030,734 discloses a heat exchanger for a furnace which includes a series of axially connected heat exchanging chambers of annular construction, each of which encloses a baffle plate disposed to block direct axial flow and having an opening around its radial outer edge to direct the axial flow into the corrugation from the center radially outwardly around the outer edge, and then back to the center of corrugation on the opposite side of the baffle to exit axially therefrom.
  • a series of stationary vanes is used to attach each side of the baffle plate to the inside walls of the annular chamber and to impart a swirling movement to the air flowing through the chamber.
  • British Patent No. 2,354 shows a heat exchanger with annular chambers similar to those described in the foregoing patent. Each chamber includes a baffle plate which is attached between the outer walls of the annular chamber and has holes for the flow of fluid therethrough which are radially displaced from the axis of the heat exchanger. The interior heat exchanging surfaces of the annular chambers are generally smooth and uninterrupted.
  • U.S. Patent 4,561,494 shows an oil cooling heat exchanger comprising a series of axially aligned heat exchanging units also defining a generally corrugated construction.
  • Each unit comprises a pair of outer dish- shaped plates which enclose a double layer internal baffle plate, each of which baffle plates is provided with stamped strands displaced from the surface of the baffle plate to space the same from the interior walls of the unit in which it is disposed, to provide contact surfaces for brazing the baffle plates in position, and to create turbulence in the oil flowing therethrough.
  • the entire structure is intended to be enclosed in an outer housing through which a coolant, such as from an engine cooling system, is circulated to remove heat from the oil.
  • a core element including a series of generally parallel tubular conduits extends between and are attached at their opposite ends to inlet and outlet headers.
  • the tubular conduits are also generally provided with attached heat conducting and dissipating fins which may be of either a flat plate or serpentine construction.
  • the rigid joints between the fluid conduits and the headers are generally soldered or brazed and, as is well known in the art, are relatively weak. In fact, the soldered joints constitute the weakest points in a typical tube and header heat exchanger construction and are generally the first to fail under excessive loadings which may, for example, be caused by thermal expansion or shock loads.
  • U.S. Patent 1,816,159 shows a corrugated conduit heat exchanger which may be mounted between a pair of oppositely disposed headers via axially bolted end plates.
  • German Patent 577,743 and British Patent 114,821 disclose modular tube and header heat exchanger constructions in which the individual tubular modules are connected between the headers with threaded connectors. However, the threaded attachment of the connectors imposes an axial strain on the modules which might result in fracture of the soldered joints.
  • French Patent No. 673,524 discloses modular heat exchanger elements, but the same are demountably detached to the outer faces of the headers, rather than between the headers as in conventional construction. Summary of the Invention
  • a heat exchanger for a flowing fluid is provided with a stationary turbulator that provides enhanced heat exchanging surface area, imparts added turbulence to the flow of fluid and is of relatively simple construction.
  • the heat exchanger may be used for both liquid and gaseous fluids and is particularly adaptable for automotive use.
  • the heat exchanger may be utilized with any of the several fluids for which cooling in an automotive application may be necessary or desirable, including engine coolant, oil and air.
  • the heat exchanger includes a tubular conduit which has a corrugated wall extending between a fluid inlet and a fluid outlet.
  • the corrugated wall includes a series of generally parallel, axially spaced corrugations, each of which comprises a pair of opposed dish-shaped wall sections which are joined at their outer edges.
  • Each of the dish-shaped sections also includes a central opening defined by inner edge portions and lying on the axis of the tubular conduit.
  • Each of the inner edge portions is joined to the similar edge portion of the wall section of an adjacent corrugation to provide the continuous corrugated tubular conduit.
  • the surfaces of the wall sections of each corrugation diverge radially inwardly from their joined outer edges to the separate central openings therein.
  • a turbulator plate is mounted within each corrugation and is positioned between the central openings on opposite ends of the corrugation to block direct flow of fluid therethrough.
  • Each turbulator plate has an outer peripheral edge which is spaced radially inwardly from the outer edge of the corrugation to define a peripheral fluid flow passage through which the fluid is diverted in a circuitous path around the turbulator plate.
  • Each turbulator plate includes a rib means formed therein generally normal to the direction of fluid flow over the plate.
  • Each corrugation is also provided with positioning means to maintain spacing between each turbulator plate and the adjacent surfaces of the wall sections comprising the corrugation within which the plate is disposed. The positioning means also holds the plate in position within the corrugation.
  • the walls forming the corrugations may be provided with a plurality of outwardly extending protrusions to increase the heat exchanging surface area on both the inside and the outside of each corrugation, and to increase the turbulence in the flow of the primary fluid on the inside of the heat exchanger as well as the turbulence in the flow of any secondary fluid caused to flow across the exterior of the heat exchanger to enhance the heat exchanging capability.
  • the protrusions are preferably positioned generally parallel to one another and normal to the direction of the secondary fluid flow across the exterior of the heat exchanger unit.
  • the surfaces of the wall sections of each corrugation may also be provided with a plurality of inwardly extending protrusions which may be dimensioned to extend into contact with the interior turbulator plate to maintain the spacing thereof within the corrugation and to hold the plate in position.
  • the inwardly extending protrusions extend into direct contact with the ribs in the turbulator plate.
  • the contacting surfaces of the inwardly extending protrusions and the turbulator ribs may be directly attached, as by welding, brazing, adhesives, or the like.
  • the ribs in the turbulator plate extend axially in both directions from the plane of the plate. Portions of the turbulator ribs adjacent the oppose d surfaces of the wall sections of each corrugation may be upset and dimensioned to extend into contact with the wall sections to provide the positioning and securement of the turbulator plate within the corrugation.
  • Another construction of the present invention includes ribs in the turbulator plate which extend continuously along the surface thereof and comprise an array of ribs disposed in a concentric pattern extending radially from the outer peripheral edge of the plate to the region of the plate adjacent the central openings in the wall sections defining each corrugation.
  • the array of concentric ribs is generally wave-shaped in cross section to define a wave of increasing amplitude in a radial inward direction corresponding to the radially inward divergence of the wall sections of each corrugation.
  • the wall sections are preferably identical and each comprises a cylindrical outer flange adapted to be joined at its edge to the edge of the outer flange of the adjacent opposed wall section.
  • each wall section preferably comprises a cylindrical inner flange which is joined to the like inner flange of the wall section of an adjacent corrugation.
  • the joined inner flanges of each adjacent pairs of wall sections also define the common central opening of adjoining corrugations.
  • the corrugations and interior turbulator plates are generally rectangular in shape to optimize the amount of heat exchanging surface area for a given volume of space.
  • the outwardly extending protrusions on the walls of the corrugations are preferably positioned generally perpendicular to the longer edges of the rectangular corrugations and also perpendicular to the direction of flow of the secondary fluid (e.g. cooling air) caused to flow over the exterior of the heat exchanger.
  • the secondary fluid e.g. cooling air
  • the central openings between adjacent corrugations are also elongated in the direction of the longer edges of the rectangular corrugations.
  • a unique mounting assembly may be used to demountably attach either tube and header or corrugated heat exchanger modules in a true modular configuration.
  • the mounting assembly of the present invention provides the convenience of modular construction while simultaneously eliminating the detriments inherent in prior art unitary tube and header core constructions.
  • Each heat exchanger module in one embodiment of the present invention is mounted between an inlet header and an outlet header, and includes a series of generally parallel tubular conduits which extend between and are attached at their opposite ends, as by soldered joints, to a pair of header plates.
  • Each of the headers has a surface which defines a fluid opening to or from the heat exchanger module and the header surfaces are disposed in spaced, parallel face-to-face relation.
  • An end plate is attached by its outer edge to the outer edge of each header plate to form therewith an end chamber on each end of the heat exchanger module.
  • Each end plate has a centrally attached flange which defines a chamber opening.
  • a compressible seal is positioned between each flange and the adjacent header surface surrounding the fluid opening therein.
  • a mounting bracket is attached to each of the headers in alignment with the fluid opening, with each header bracket defining with the header surface a mounting slot for receipt of the flange and compressible seal on end of the module.
  • a pressure plate is slidably insertable into each slot between the mounting bracket and the flange and, by a wedging action, compresses the seal and secures the module to the header.
  • One of the end plates is constructed to be flexible in the direction of the longitudinal axis of the module to accommodate axial elongation of the module between the flanges in response to compression of the seals during mounting.
  • both end plates are flexible and are of thin sheet metal construction.
  • the headers are provided with a series of fluid openings in their opposed spaced parallel surfaces, which openings define opposed pairs of fluid openings between which a heat exchanger module may be demountably attached.
  • two or more tiers of parallel arrays of heat exchanger modules may be mounted utilizing an intermediate header or headers, each of which includes a series of fluid openings on parallel opposite header wall surfaces. Utilizing the demountable attachment assembly of the present invention, each intermediate header simultaneously accommodates connections from the outlet ends of the modules in one tier and the inlet ends of the modules in the other tier.
  • FIG. 1 is a partial axial cross section through the heat exchanger of one embodiment of the present invention and additionally showing its connection to a pump for circulating the flow of a fluid therethrough.
  • FIG. 2 is an enlarged partial axial section through the heat exchanger shown in FIG. 1.
  • FIG. 3 is a section through the heat exchanger taken on line 3-3 of FIG. 2.
  • FIG. 4 is a sec ⁇ n through the heat exchanger taken on line 4-4 of FIG. 2.
  • FIG. 5 is a bottom plan view of a common inlet tank showing details of the connection assembly of the present invention.
  • FIG. 6 is a sectional view of the heat exchanger taken on line 6-6 of FIG. 5.
  • FIG. 7 is a front elevation of a portion of a modular heat exchanger utilizing tube and header construction and the mounting assembly of the present invention.
  • FIG. 8 is a sectional view of the heat exchanger shown in FIG. 7 generally similar to FIG. 6.
  • FIG. 9 is a partial sectional view taken on line
  • FIG. 10 is a front elevation of a modular heat exchanger utilizing the modules and mounting assembly of the present invention. Detailed Description of the Preferred Embodiment
  • a heat exchanger 10 of the present invention is shown operatively attached to a pump 11 which causes a fluid to flow into the inlet 12 of the heat exchanger and to exit therefrom through an outlet 13 for return to the pump.
  • the pump for example, may comprise the water pump on an internal combustion engine.
  • the heat exchanger to be described in more detail hereinafter is also suited for cooling other fluids such as engine oil or engine combustion air, as well as for cooling or heating a variety of other fluids for entirely different applications.
  • the heat exchanger includes a tubular conduit 18 which has an inlet flange 14 on one end for attachment to an inlet header 15 and an outlet flange 16 on the opposite end for attachment to an outlet header 17.
  • the tubular conduit 18 comprises a series of generally parallel and axially spaced corrugations 20, each of which is identical.
  • each corrugation 20 is formed from a pair of identical dish-shaped wall sections 21, each wall section including an outer flange 22 and an inner flange 23.
  • the outer and inner flanges of each wall section extend in opposite axial directions and, to form a corrugation 20, a pair of opposed wall sections 21 are joined at the edges of their outer flanges 22 with a continuous outer seam 24.
  • adjacent corrugations 20 comprising the tubular conduit 18 are connected by joining the edges of adjacent inner flanges 23 with a continuous inner seam 25.
  • the seams 24 and 25 may be provided by welding, brazing, soldering, or even gluing in any manner which will provide a leak-tight seal of requisite strength.
  • the inner flanges 23 join adjacent corrugations
  • the corrugations 20 are of a generally rectangular shape, as viewed in a plane normal to the axis of the heat exchanger.
  • the surfaces of the wall sections 21 of each corrugation diverge radially inwardly such that each corrugation is narrowest at its peripheral outer edge, defined by the outer flanges 22, and widest at its inner edge, defined by the inner flanges 23.
  • a baffle or turbulator plate 27 Within each hollow corrugation 20 there is mounted within each hollow corrugation 20 there is mounted a baffle or turbulator plate 27.
  • Each turbulator plate comprises a solid sheet having a shape generally the same as the corrugation, namely, rectangular in the preferred embodiment shown in FIG. 3. Because of the solid construction of the turbulator plate 27, it poses a barrier to the direct flow of fluid through a corrugation from one central opening 26 to the other. However, the turbulator plate is somewhat smaller than the corrugation such that its outer peripheral edge 28 is spaced radially inwardly from the attached outer flanges 22 of the corrugation to define a peripheral fluid flow passage 30 therebetween.
  • the fluid flowing into a corrugation from an adjacent upstream corrugation (or from the inlet header 15) will be diverted radially outwardly by the solid turbulator plate 27, flow around the outer peripheral edge 28 and through the fluid flow passage 30 and radially inwardly to the downstream central opening 26.
  • This provides the general function of a typical baffle plate to slow somewhat the flow of fluid and to assure its enhanced contact with a larger heat exchanging surface area.
  • each of the turbulator plates 27 is provided with a series of turbulator ribs 31 which extend generally normal to the direction of radial fluid flow over the plate, as just described.
  • the ribs 31 thus provide at least a partial barrier to the fluid flow and surface irregularities which cause turbulence and mixing of the fluid to further enhance heat exchanging contact with the walls of the corrugations.
  • the turbulator ribs are formed in and extend from both sides of the turbulator plate 27 to present similar ribbed surfaces on both sides.
  • the ribs extend continuously along and around the entire surface of the plate and, in the preferred rectangular configuration, comprise a concentric array of rectangular ribs that extend radially from the outer peripheral edge 28 to the portion of the plate adjacent the central opening 26 in the corrugation, the center 32 of the turbulator plate is smooth and, as previously indicated, solid to present a direct barrier to fluid flow.
  • the size of the ribs 31 varies radially to conform to the divergent orientation of the wall sections 21 between which each turbulator plate is mounted.
  • the array of ribs in each plate is generally wave-shaped in cross section and defines a wave of increasing amplitude in a radial inward direction.
  • the outer surfaces of the wall sections 21 of each corrugation 20 are provided with a plurality of outwardly extending convex protrusions 33.
  • the protrusions are relatively narrow and long and, in the preferred rectangular shape shown in FIG. 3, are positioned generally parallel to one another and perpendicular to the longer edges of the rectangular corrugation.
  • the heat exchanger 10 of the present invention is utilized to remove heat from the engine coolant in an internal combustion engine, the cooling air flowing across the exterior of the heat exchanger will be caused to flow in the long direction of the rectangular shape and perpendicular to the convex protrusions 33. This assures an optimum flow of air over the greatest heat exchanging surface and the convex protrusions 33 are disposed to maximize air turbulent.
  • each corrugation 20 may also be provided with a plurality of concave protrusions 34 which extend into the interior of the corrugation.
  • the concave protrusions may be adapted to serve two separate and distinct purposes. First of all, the concave protrusions 34 enhance the heat exchanging surface area and provide interruptions which help create turbulence in the flow f fluid within the heat exchanger.
  • concave protrusions extending inwardly from opposite wall sections 21 may be utilized to capture and hold in place the turbulator plate 27. As shown in FIG. 2, the concave protrusions 34 may be positioned to bear upon the crests of the ribs 31 as a pair of wall sections 21 are brought together and sealed along the continuous outer seam 24.
  • the concave protrusions 34 thus also provide the requisite spacing. These inwardly extending protrusions may be dispersed between the outwardly extending convex protrusions 23 and of a substantially shorter length, as shown. Alternately, the concave protrusions 34 may be formed of generally the same length and alternately with the convex protrusions. If necessary, the contacting surfaces of the concave protrusions 34 and the crests of the ribs 31 may be utilized to spot weld, braze or otherwise secure the parts together.
  • the turbulator plates 27 are inherently captured and held in position between the wall sections as the latter are welded or otherwise secured together.
  • the crests of certain of the turbulator ribs 31 may be provided with spaced upset portions 35 (see FIG. 2) which extend into contact with the inside surfaces of the wall sections 21.
  • the small upset portions 35 may be formed in any convenient manner and, preferably, in the same stamping operation in which the ribs themselves are formed in the plates 27. If necessary or desirable, the upset portions 35 may also be utilized as brazing surfaces to positively attach the plates to the corrugation walls.
  • the heat exchanger 10 of the present invention may be made entirely of a stamped sheet metal construction.
  • Both the corrugations 20 and the baffle or turbulator plates 27 may be made of thin sheets of steel or brass, for example, with a typical material thickness of .018-.020 inches (.46-.51 mm). With the appropriate tooling, the dish-shaped wall sections 21 including the outer and inner flanges 22 n 23 and convex and/or concave protrusions 33 and 34 may be stamped in a single step.
  • the outer and inner seams 24 and 25 are preferably made by welding, but brazing and other methods may also be utilized.
  • the present invention is advantageously distinguished by its elimination of soldered seams and connections which are known to be troublesome.
  • FIGS. 5 and 6 there is shown an assembly for mounting a number of heat exchangers 10 of the present invention in a system for handling a flow of engine coolant.
  • a similar system may, however, also be utilized for cooling (or heating) other liquids and/or gases.
  • an inlet tank 36 is positioned above a parallel arrangement of heat exchangers 10.
  • the inlet tank 36 includes a conventional inlet opening 37 for the attachment of a coolant supply hose or the like, such as from the water pump 11 (FIG. l) .
  • the bottom surface 39 of the tank 36 includes a series of spaced outlet openings 38 which are elongated and of the same general shape as the central opening 26 through the heat exchanger conduit 18.
  • a mounting bracket 40 is attached to the lower surface of the tank 36 surrounding each of the outlet openings 38.
  • the mounting bracket 40 is of a U-shaped construction and of a shape corresponding to but slightly larger than the inner flange 23 of the first corrugation 20 attached to the inlet flange 14 of the heat exchanger conduit.
  • the mounting bracket is mounted spaced from the surface of the tank and the open end of the U defines a slot 41 between the bracket and the bottom surface 39 of the tank into which the inlet flange and an appropriate sealing ring 42 may be slid into place such that the central opening 26 in the inlet flange 14 is in alignment with the outlet opening 38 in the bottom tank surface 39.
  • a wedge-shaped pressure plate 43 is inserted into the open end of the slot 41 between the inside surface of the mounting bracket 40 and the opposing face of the inlet flange 14.
  • the pressure plate 43 has a bifurcated construction defined by a pair of spaced legs 44 which overlie the legs of the U-shaped slot 41 and, in a similar manner, surround the inner flange 23 defining the central opening 26 immediately adjacent the inlet flange 14. The wedging action of the pressure plate compresses the sealing ring 42 and secures the assembly together.
  • the opposite end of the pressure plate 43 includes a mounting flange 45 having a threaded hole therein for receipt of a tightening screw 46 adapted to bear against the side wall of the inlet tank 36.
  • the screw 46 may be rotated by hand with the integral wing nut 47 to establish the final position of the pressure plate 43 and the position maintained by tightening a lock nut 48 against the mounting flange 45.
  • each heat exchanger unit may be similarly attached to a common outlet header (not shown) for the several tubular conduits in a manner identical to the inlet end.
  • each of the tubular conduits 18 of a preferred rectangular shape is oriented in the direction of flow of the cooling air past the unit, as indicated by the large arrows in FIG. 5. This orientation provides optimized air turbulence and heat transfer.
  • each module 50 includes a series of tubular conduits 51 which extend in a generally parallel orientation between a pair of header plates 52.
  • Each header plate is provided with a pattern of holes 53, each of which holes is adapted to receive one end of a tubular conduit 51 which is rigidly secured therein with a soldered or brazed connection, all in a well known manner.
  • a multiplicity of fairly densely packed heat exchanging fins 54 are attached to the tubular conduits between the header plates 52, also in a known manner.
  • the tube and fin assembly may be supported on opposite faces by a pair of side plates 55, but the module 50 is open in a direction parallel to the side plates to allow cooling air to flow readily over the tubes and fins.
  • Each header plate 52 has its peripheral edge upturned in a direction away from the module to form a peripheral lip 56.
  • the header plates are relatively stiff and such stiffness is substantially enhanced by the rigid soldered connections of the multiple tubular conduits 51.
  • a thin flexible end plate 57 is attached by its outer peripheral edge to the peripheral lip 56 of the header plate 52.
  • Each end plate 57 may be of a construction substantially identical to the dish-shaped wall section 21 utilized in the embodiment previously described.
  • the end plate may include a peripheral outer flange 58 for direct attachment to the lip 56 of the header plate, as with a soldered, brazed or welded seam 60.
  • the connected header plate 52 and end plate 57 form chambers 61 on each end of the module 50.
  • the end plate 57 is provided with a central opening 62 (like the opening 26 of the previously described embodiment) , which opening 62 is defined by an axially extending sleeve 63.
  • the opposite end of the sleeve 63 has attached thereto a mounting flange 64, also of a construction similar to that previously described.
  • the mounting flange 64 is adapted to overlie the bottom surface 65 of the inlet header 66 such that the central opening 62 to the chamber 61 is aligned with the outlet opening 67 from the header.
  • a continuous compressible sealing member 68 overlies the outer face of the mounting flange 64.
  • the inlet header 66 is provided with a series of outlet openings 67 and a mounting bracket 70 is attached to the bottom surface 65 of the header at each fluid opening.
  • Each of the mounting brackets 70 has a generally channel shape when viewed in FIG. 7 and includes a pair of parallel side flanges 71 secured to the header surface and an integral center plate 72 extending between the side flanges 71.
  • the center plate 72 is provided with a U-shaped notch 73 large enough to allow the sleeve 63 on the end plate 57 to extend therein.
  • the interior of the mounting bracket 70 and the bottom surface 65 of the header define a mounting slot 74 into which the mounting flange 64 and sealing member 68 may be slid as the sleeve 63 is received in the U-shaped notch 73.
  • each module 50 (which is attached either to an intermediate header 77 or an outlet header 78 as will be described in greater detail) is provided with an identical mounting assembly such that the mounting flange/sealing member subassemblies on each end of the module are simultaneously inserted into the mounting slots 74 in the mounting brackets.
  • a pressure plate 75 is then slidably inserted into the mounting slot between the inside surface of the center plate 72 and the surface of the mounting flange 64 opposite the sealing member to compress the sealing member against the header surface and secure the module thereto.
  • the pressure plate is bifurcated to define a pair of legs 76 which straddle the sleeve 63 as the pressure plate is inserted into the mounting slot.
  • the remote edges of the legs 76 are provided with relatively sharp edges 80 to facilitate initial insertion of the legs between the mounting bracket 70 and the mounting flange 64.
  • the pressure plate may also be provided with a flanged handle 81 to facilitate manual insertion and removal of the pressure plate.
  • the mounting flanges 64 and sealing members 68 on opposite ends of the module are slid into their respective mounting brackets 70.
  • One of the pressure plates 75 is then inserted, as indicated, to secure that end of the module to the header, while simultaneously compressing the sealing member 68 to provide a fluid-tight seal.
  • the sealing member 68 will begin to be compressed, but the wedging action of the pressure plate will also cause an axial elongation of the module.
  • Such axial elongation will be readily accommodated by the flexible end plates 57 so that no undue tensile load is imposed upon the relatively low strength joints between the tubular conduits 51 and the header plates 52.
  • a modular heat exchanger 82 includes the upper inlet header 66, intermediate header 77 and lower outlet header 78 all tied together by a pair of side frame members 83 to form a generally rectangular supporting frame 84.
  • upper and lower parallel arrays 85 and 86 of modules 50 are disposed in two tiers separated by the intermediate header 77.
  • Each module 50 in the upper array 85 and the lower array 86 includes a flexible walled chamber 61 and mounting bracket assembly on each end.
  • Each of the headers 66, 77 and 78 has a substantially open interior for the fluid flowing into or out of the modules 50. If an individual module 50 is damaged so that fluid is escaping from the system, that module is simply replaced by reversing the mounting procedure described above and a replacement module attached in its place. However, should a replacement module not be available, the openings in the two headers to and from the damaged module may be temporarily plugged and operation of the heat exchanger continued without a significant loss of heat exchanging capacity.
  • the pressure plate 75 is removed, a thin solid shim in the approximate shape of a mounting flange 64 is inserted in the mounting slot 74 between the seal 68 and the header surface, and the pressure plate 75 is reinserted to compress the sealing member, force the shim against the surface of the header, and close off the header opening.
  • the open interiors of the various headers allow fluid flow through all remaining modules to be maintained. By leaving the damaged module in place, uniform flow of cooling air through the entire heat exchanger may be maintained.
  • the shim may be constructed of any material which is strong and rigid enough to provide a barrier to fluid flow and yet provide an adequate temporary seal. Various types of plastic materials are believed to be suitable and the shim may have a thickness in the range of, for example, .005- .010 inch.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Un ensemble d'échangeur thermique modulaire comprend des conduits (18) d'échange thermique tubulaires modulaires, comportant chacun des chambres terminales situées aux extrémités opposées du conduit, lesdites chambres comportant une paroi terminale (21) dilatable axialement. Le conduit (18) d'échange thermique peut comprendre une paroi extérieure ondulée d'échange thermique à chambres multiples, présentant des plaques de déviation fixes (27) montées à l'intérieur de la chambre définie par chaque ondulation (20) ou une construction classique d'échangeur thermique à tubes et à collecteurs. Chaque type de conduit d'échangeur thermique modulaire utilise une fixation unique à débranchement rapide, permettant de monter le module entre une admission (15) et des collecteurs de sortie (17) espacés. La compression axiale des joints d'étanchéité souple (42) entre les extrémités du conduit (18) d'échangeur thermique et les collecteurs (15, 17) pendant le montage, est reçue par la flexion des parois terminales souples (21) sur les chambres terminales du conduit (18).
PCT/US1990/006957 1989-11-29 1990-11-28 Ensemble d'echangeur thermique modulaire ameliore WO1991008433A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP91901103A EP0502982B1 (fr) 1989-11-29 1990-11-28 Echangeur de chaleur
DE69029813T DE69029813T2 (de) 1989-11-29 1990-11-28 Wärmetauscher

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
US443,218 1989-11-29
US07/443,218 US4981170A (en) 1989-11-29 1989-11-29 Heat exchanger with stationary turbulators
US07/508,962 US4979560A (en) 1989-11-29 1990-04-12 Heat exchanger with stationary turbulators
US508,962 1990-04-12
US590,342 1990-09-28
US07/590,342 US5042572A (en) 1989-11-29 1990-09-28 Mounting assembly for modular heat exchanger units

Publications (1)

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WO1991008433A1 true WO1991008433A1 (fr) 1991-06-13

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EP (1) EP0502982B1 (fr)
AU (1) AU6919391A (fr)
DE (1) DE69029813T2 (fr)
WO (1) WO1991008433A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3236191A1 (fr) * 2016-04-12 2017-10-25 Ecodrain Inc. Échangeur de chaleur présentant une meilleure aptitude à la fabrication

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GB114821A (fr) *
DE430345C (de) * 1925-01-01 1926-06-15 Hans Windhoff Dipl Ing Kraftwagenkuehler mit auswechselbaren Elementen
FR673524A (fr) * 1928-04-28 1930-01-16 Fiat Spa Dispositif pour le montage des éléments dans les radiateurs à éléments pour le refroidissement de l'eau dans les moteurs à combustion interne
US2030734A (en) * 1932-06-18 1936-02-11 Nichols Copper Co Furnace construction
US2243605A (en) * 1939-08-05 1941-05-27 Prime Mfg Co Grease fitting
US2870863A (en) * 1955-10-04 1959-01-27 Gen Electric Coupling
US3099315A (en) * 1959-05-27 1963-07-30 Joseph H Loehr Heat exchanger
US4216825A (en) * 1977-05-17 1980-08-12 Hisaka Works, Ltd. Plate type evaporator
US4494598A (en) * 1983-01-06 1985-01-22 Amana Refrigeration, Inc. Flue pipe connection assembly and method of connection thereof
DE3517488A1 (de) * 1985-05-15 1986-11-20 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart Rohranschluss, insbesondere fuer einen wasserkasten eines waermetauschers einer kraftfahrzeugheizung
JPS62221919A (ja) * 1986-03-25 1987-09-30 Hitachi Ltd ラジエ−タ

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB114821A (fr) *
DE430345C (de) * 1925-01-01 1926-06-15 Hans Windhoff Dipl Ing Kraftwagenkuehler mit auswechselbaren Elementen
FR673524A (fr) * 1928-04-28 1930-01-16 Fiat Spa Dispositif pour le montage des éléments dans les radiateurs à éléments pour le refroidissement de l'eau dans les moteurs à combustion interne
US2030734A (en) * 1932-06-18 1936-02-11 Nichols Copper Co Furnace construction
US2243605A (en) * 1939-08-05 1941-05-27 Prime Mfg Co Grease fitting
US2870863A (en) * 1955-10-04 1959-01-27 Gen Electric Coupling
US3099315A (en) * 1959-05-27 1963-07-30 Joseph H Loehr Heat exchanger
US4216825A (en) * 1977-05-17 1980-08-12 Hisaka Works, Ltd. Plate type evaporator
US4494598A (en) * 1983-01-06 1985-01-22 Amana Refrigeration, Inc. Flue pipe connection assembly and method of connection thereof
DE3517488A1 (de) * 1985-05-15 1986-11-20 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart Rohranschluss, insbesondere fuer einen wasserkasten eines waermetauschers einer kraftfahrzeugheizung
JPS62221919A (ja) * 1986-03-25 1987-09-30 Hitachi Ltd ラジエ−タ

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3236191A1 (fr) * 2016-04-12 2017-10-25 Ecodrain Inc. Échangeur de chaleur présentant une meilleure aptitude à la fabrication
US11009296B2 (en) 2016-04-12 2021-05-18 6353908 Canada Inc. Heat exchange conduit and heat exchanger

Also Published As

Publication number Publication date
EP0502982A4 (en) 1993-04-07
AU6919391A (en) 1991-06-26
DE69029813T2 (de) 1997-07-10
EP0502982A1 (fr) 1992-09-16
EP0502982B1 (fr) 1997-01-22
DE69029813D1 (de) 1997-03-06

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