WO2000039516A1 - Echangeurs thermiques annulaires a ecoulement radial - Google Patents

Echangeurs thermiques annulaires a ecoulement radial Download PDF

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Publication number
WO2000039516A1
WO2000039516A1 PCT/CA1999/001246 CA9901246W WO0039516A1 WO 2000039516 A1 WO2000039516 A1 WO 2000039516A1 CA 9901246 W CA9901246 W CA 9901246W WO 0039516 A1 WO0039516 A1 WO 0039516A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
plate pairs
bosses
flow
plate
Prior art date
Application number
PCT/CA1999/001246
Other languages
English (en)
Inventor
Alan K. Wu
Bruce L. Evans
Henri P. T. Van Helden
Original Assignee
Long Manufacturing Ltd.
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 Long Manufacturing Ltd. filed Critical Long Manufacturing Ltd.
Priority to AT99964346T priority Critical patent/ATE225491T1/de
Priority to KR10-2001-7008124A priority patent/KR100412278B1/ko
Priority to JP2000591373A priority patent/JP3493519B2/ja
Priority to DE69903350T priority patent/DE69903350T2/de
Priority to AU30275/00A priority patent/AU755895B2/en
Priority to EP99964346A priority patent/EP1141645B1/fr
Publication of WO2000039516A1 publication Critical patent/WO2000039516A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • 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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0012—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form

Definitions

  • This invention relates to heat exchangers, and in particular, to oil coolers of the so called “doughnut” type that can be used separately or in conjunction with oil filters in automotive and other engine and transmission cooling applications.
  • Oil coolers have been made in the past out of a plurality of stacked plate pairs located in a housing or canister.
  • the canister usually has inlet and outlet fittings for the flow of engine coolant into and out of the canister circulating around the plate pairs.
  • the plate pairs themselves have inlet and outlet openings and these openings are usually aligned to form manifolds, so that the oil passes through all of the plate pairs simultaneously.
  • manifolds communicate with oil supply and return lines located externally of the canister.
  • An example of such an oil cooler is shown in Japanese Utility Model Laid Open Publication No. 63- 23579 published February 16, 1988.
  • the plate pairs are usually in the form of an annulus and a conduit passes through the centre of the annulus delivering oil to or from the filter located above or below the oil cooler and connected to the conduit.
  • the oil can pass through the filter and then the oil cooler, or vice- versa.
  • Examples of such oil coolers are shown in United States patents Nos. 4,967,835 issued to Thomas E. Lefeber and No. 5,406,910 issued to Charles M. Wallin.
  • a difficulty with these prior art oil coolers, however, is that they are not particularly efficient. They also often suffer from the disadvantage of high pressure drop on the oil side of the cooler.
  • the heat exchanger of the present invention is very efficient with relatively low pressure drop.
  • a first exchange fluid travels circumferentially through ringlike plate pairs, and all of a second heat exchange fluid flows between the plate pairs transversely relative to the first heat exchange fluid.
  • a heat exchanger which comprises a plurality of stacked plate pairs consisting of face- to-face, mating ringlike plates.
  • Each plate has an outer peripheral flange, an annular inner boss having a portion thereof located in a common plane with the peripheral flange, and an intermediate area located between the peripheral flange and the inner boss.
  • the peripheral flanges and inner bosses in the mating plates are joined together.
  • the intermediate areas have spaced-apart portions to form an inner flow passage between the plates.
  • the plate intermediate areas have spaced-apart intermediate bosses located between the outer peripheral flange and the inner boss that extend from the intermediate area in a direction opposite to the peripheral flange and inner boss.
  • the intermediate bosses define inlet and outlet openings and are arranged such that in back-to-back plate pairs, the intermediate bosses are joined and the respective inlet and outlet openings communicate to define inlet and outlet manifolds for the flow of a first exchange fluid circumferentially through the inner flow passages from the inlet manifold to the outlet manifold.
  • the adjacent intermediate areas in back-to-back plate pairs define outer flow passages therebetween.
  • a header encloses one of the inner bosses and outer peripheral flanges. The header includes a flow port for the flow of a second heat exchange fluid therethrough to force the second heat exchange fluid to flow transversely through the outer flow passages.
  • a method of transferring heat energy between lubricating fluids and engine coolant comprises the steps of providing a plurality of ringlike, closely spaced- apart, stacked plate pairs having inner flow passages therebetween and outer flow passages between the plate pairs. All of one of the fluid and the coolant is passed circumferentially through the plate pairs, and all of the other of the fluid and the coolant is passed transversely between the plate pairs.
  • Figure 1 is a diagrammatic vertical sectional view taken through a first preferred embodiment of a combination heat exchanger and oil filter employing a preferred embodiment of a heat exchanger according to the present invention
  • Figure 2 is an enlarged perspective view, partly broken away, of the heat exchanger employed in the embodiment shown in Figure 1 ;
  • Figure 3 is an enlarged perspective view similar to Figure 2, but showing the underside of the heat exchanger of Figure 2;
  • Figure 4 is an enlarged perspective view showing the inside surface of one of the plates used to form the plate pairs of the heat exchanger embodiment shown in Figures 2 and 3;
  • Figure 5 is a plan view of the plate shown in Figure 4.
  • Figure 6 is a further enlarged sectional view taken along lines 6-6 of Figure 5 and showing additional plates stacked above and below the plate of Figures 4 and 5;
  • Figure 7 is a vertical sectional view similar to Figure 6 but showing another embodiment where the plate header is formed on the outer periphery of the plate pairs;
  • Figure 8 is an enlarged sectional view of the lower left corner of Figure 1 showing yet another embodiment of a heat exchanger according to the present invention
  • Figure 9 is a perspective view similar to Figure 4, but showing another preferred embodiment of a plate used to make a heat exchanger according to the present invention.
  • Figure 10 is a plan view of the plate shown in Figure 9;
  • Figure 11 is a diagrammatic vertical sectional view similar to Figure 1, but showing another preferred embodiment of a combination heat exchanger and oil filter employing another embodiment of a heat exchanger according to the present invention therein;
  • Figure 12 is an enlarged perspective view, partly broken away, of the heat exchanger employed in the embodiment shown in Figure 11 ;
  • Figure 13 is a perspective view simlar to Figure 4 but showing the plate used to make the heat exchanger embodiment shown in Figure 12;
  • Figure 14 is a vertical sectional view taken along lines 14-14 of Figure 13 and showing additional plates stacked above and below the plate of Figure 13;
  • Figure 15 is a plan view of another preferred embodiment of a ringlike heat exchanger plate used to make a heat exchanger according to the present invention.
  • Figure 16 is a plan view of a top or bottom plate used to make a heat exchanger using the plates shown in Figure 15;
  • Figure 17 is a perspective view similar to Figures 4 and 9, but showing another embodiment of a plate in combination with a turbulizer as used to make a heat exchanger according to the present invention
  • Figure 18 is a diagrammatic vertical sectional view similar to Figures 1 and 11, but showing another preferred embodiment of a heat exchanger as used with a conventional oil filter to make a combination heat exchanger and filter;
  • FIG 19 is an enlarged perspective view, partly broken away, of the heat exchanger shown in Figure 18;
  • Figure 20 is a plan view of another embodiment of a plate used to make a heat exchanger according to the present invention.
  • Figure 21 is a plan view of an optional spacer that may be used with the plates of Figure 20;
  • Figure 22 is a perspective view looking at the inside of another embodiment of a plate used to make a heat exchanger according to the present invention.
  • Figure 23 is a plan view of the plate shown in Figure 14;
  • Figure 24 is a plan view of yet another embodiment of a plate used to make a heat exchanger according to the present invention.
  • Figure 25 is a plan view of yet another embodiment of a plate used to make a heat exchanger according to the present invention.
  • Combination unit 10 includes a housing 12 containing an oil filter 14 and a preferred embodiment of a heat exchanger according to the present invention indicated by reference numeral 16.
  • Oil filter 14 is conventional and is not per se considered to be part of the present invention.
  • Oil filter 14 is of the annular type and in Figure 1, oil flows from inside the housing inwardly through the filter walls to a central axial chamber 15 and passes downwardly through a pipe or conduit 18 to exit from combination unit 10.
  • housing 12 has a bottom plate 19 containing openings 20 therein for the passage of oil therethrough into heat exchanger 16 depending upon which way it is desired to have the oil flow through filter 14.
  • Conduits 22 and 24 are also attached to bottom plate 19 for the entry and exit of coolant into and out of heat exchanger 16.
  • heat exchanger 16 is formed of a plurality of stacked plate pairs 30 consisting of face-to-face mating, annular or ringlike plates 32.
  • each plate 32 has an outer peripheral flange 34, an annular inner boss 36 having a portion 37 located in a common plane with outer peripheral flange 34, and an intermediate area 39 located between peripheral flange 34 and inner boss 36.
  • a plurality of alternating ribs and grooves 38, 40 are formed in intermediate area 39 and extend between the inner boss 36 and the peripheral flange 34.
  • the ribs and grooves 38, 40 are flow augmentation means and are angularly disposed and in the form of spiral or involute curves, so that the ribs and grooves in the respective plates that make up plate pairs 30 cross forming an undulating inner flow passage 42 between the plates of each plate pair 30.
  • the ribs and grooves 38, 40 in adjacent back-to-back plate pairs cross forming undulating outer flow passages 44 between the plate pairs 30.
  • Outer flanges 34 contain optional alignment notches 45 to assist in the proper alignment of plates 32 during the assembly of heat exchanger 16. Such alignment notches could be used in all of the embodiments of the present invention, if desired.
  • Plates 32 have spaced-apart intermediate bosses 46 located between the outer peripheral flange 34 and the inner boss 36 and extending in a direction from the intermediate area 39 in a direction opposite to peripheral flange 34 and inner boss 36. . Intermediate bosses 46 define inlet and outlet openings 48, 50. The intermediate bosses 46 are arranged such that in back-to-back plate pairs, the respective inlet and outlet openings 48, 50 are joined around their peripheries to communicate and define inlet and outlet manifolds 52, 54 (see Figure 3) for the flow of a first heat exchange fluid, such as engine coolant, circumferentially inside or through the inner flow passages of the plate pairs from inlet manifold 52 to outlet manifold 54.
  • a first heat exchange fluid such as engine coolant
  • Heat exchanger 16 has top and bottom closure plates 56, 58.
  • Bottom closure plate 58 has openings 62, 64 which register with respective inlet and outlet manifolds 52, 54.
  • Conduits 22, 24 pass through housing bottom plate 19 to communicate with openings 62, 64.
  • Ribs 38 and grooves 40 have a predetermined height and intermediate bosses 46 have a height, or depth as seen in Figure 4, that is at least as high as ribs 38, and preferably the same height as ribs 38, so that when the plate pairs are placed back-to-back as seen best in Figure 6, the ribs 38 on adjacent plates touch as do the outer surfaces of intermediate bosses 46.
  • the height of inner annular bosses 36 and outer peripheral flanges 34 is greater than the height of the ribs and grooves, so that the adjacent ribs 38 on the inside of plate pairs 30 are slightly spaced apart. This reduces the water-side pressure drop for the coolant flowing through plate pairs 30.
  • a radial rib 66 extends between the intermediate bosses 46 from the inner boss 36 to the outer peripheral flange 34.
  • Radial rib 66 is in the same plane as or has the same height as inner boss 36 and outer peripheral flange 34, so that when two plates are put together to form a plate pair 30, the respective radial ribs 66 engage one another to prevent by-pass flow from inlet opening 48 to outlet opening 50.
  • Radial ribs 66 also form radial grooves on the outside or oil side of the plate pairs. These radial grooves improve the radial or transverse flow between the plate pairs near and around intermediate bosses 46.
  • Inner peripheral flanges 68 are formed on annular inner bosses 36 and have mating flange portions 69 located in a common plane with the intermediate bosses 46, so that the inner peripheral flanges 68 on back-to-back plate pairs are joined together to form, with the inner bosses 36, a header 70 (see Figure 6) to cause all of the coolant entering inlet openings 71 to flow transversely or radially through the outer flow passages 44 between the back-to-back plate pairs 30.
  • Inner boss 36 includes a plurality of apertures 72 spaced around inner boss 36. When plate pairs 30 are stacked together, apertures 72 are aligned or in registration to form flow ports for supplying fluid to header 70.
  • Figure 7 is a view similar to Figure 6, but which shows another embodiment of a heat exchanger 79 according to the present invention having stacked plate pairs that are similar to the embodiment of Figures 1 to 6, but where the inner header 70 of Figure 6 has been eliminated.
  • Primed reference numerals are used in Figures 7 to 25 to indicate modified components of the embodiment shown in Figures 1 to 6.
  • Inner bosses 36' have been truncated leaving annular slots 80 for the flow of fluid into or out of the outer flow passages 44 between the plate pairs.
  • outer distal flanges 74 form a header enclosing outer peripheral flanges 34' to cause all of the respective heat exchange fluid to pass transversely or radially between the plate pairs.
  • the inner annular boss 36' and outer peripheral flange 34' have a height that is equal to the height of the ribs and grooves, so that the adjacent ribs 38 in inner flow passages 42' are not spaced-apart as in the embodiment shown in Figures 1 and 6.
  • the adjacent ribs 38 in the inner flow passages 42' could be spaced-apart as in Figure 6, or the Figure 6 embodiment could be made like Figure 7 with ribs 38 not spaced-apart, if desired.
  • FIG 8 shows another embodiment of a heat exchanger 801 where a header 82 is formed by the annular space defined by top and bottom closure plates 56, 58 and conduit 18 sealingly engaged therein. Neither the inner bosses 36' nor the outer peripheral flanges 34 have additional flanges formed thereon to form headers.
  • Bottom closure plate 58 includes a flow port 84 for the flow of fluid into or out of header 82.
  • a ringlike plate 85 which is similar to plate 32 of Figures 4 and 5, but which has a plurality of spaced-apart dimples 87 and 89 formed in the intermediate area 39 as the flow augmentation means instead of ribs 38 and grooves 40.
  • Dimples 87 extend into the outer flow passages 44 and dimples 89 extend into the inner flow passages 42.
  • Dimples 87, 89 have a predetermined height which, in the case of dimples 87, is preferably equal to the height of intermediate bosses 46. However, some or all of the dimples 87 could have a height that is less than intermediate bosses 46.
  • plates 85 could be formed with outer distal flanges like flanges
  • headers 76 at the outer periphery of the plates, either in addition to or instead of the inner peripheral flanges 68 and headers 70 as shown in Figure 6.
  • Dimples 87 and 89 are shown arranged in respective circumferential rows and generally equi-spaced, but they could be mixed in orientation and spaced apart differently to achieve specific flow effects inside and between the plate pairs.
  • FIG 11 shows another preferred embodiment of a combination heat exchanger and filter 91 which is similar to combination unit 10 of Figure 1, but which employs a heat exchanger 28 as shown in detail in Figures 12 to 14.
  • Top plate 56' in heat exchanger 28 is the bottom wall of housing 12' that contains filter 14, and a removable lid 93 allows for the replacement of filter 14.
  • heat exchanger 28 could be considered to be a modification to heat exchanger 16 of Figures 2 to 6.
  • the plates 32' have outer peripheral flanges 34' that have been extended radially, and an outer distal flange 74 is formed on outer peripheral flange 34' having mating flange portions 75.
  • Mating flange portions 75 are located in a common plane with the intermediate bosses 46, so that the distal flanges 74 on back-to-back plate pairs 30' are joined to form, with the outer peripheral flanges 34', a header 76.
  • Apertures 77 are formed in outer peripheral flanges 34' and are aligned in the stacked plate pairs to form flow ports to receive fluid flowing between the back-to-back plate pairs. However, it will be appreciated that the flow direction could be reversed, so that header 76 supplies fluid to flow radially inwardly toward the centre of heat exchanger 28, if desired.
  • top closure plate 56' is formed with a plurality of openings 78 that communicate with apertures 77 and form part of headers 76 and also communicate with the inside of housing 12'. It will also be appreciated that heat exchanger 28 has two headers 70 and 76 with aligned apertures forming flow ports for these headers.
  • Figure 15 shows a plate 95 that is a modification of plate 32' such that plate 95 is rectangular in shape or plan view.
  • Outer peripheral flange 34" is rectangular as well, and although inner boss 36 is shown to be circular or annular, inner boss 36 could be rectangular as well, if desired.
  • plate 95 is still considered to come within the term annular or ringlike, the flow from inlet opening 48 to outlet opening 50 is still considered to be circumferential, and the flow from inner apertures 72 to outer apertures 77 is still considered to be radial or transverse with respect to the circumferential flow inside the plate pairs.
  • FIG 16 shows a modified top plate 56' for use with plates 95.
  • Top plate 56' has peripheral openings 97 that vary in size to obtain uniform flow distribution in the radial or transverse direction. It will be noted that the corner openings 97 are particularly large to increase the flow to the corners of a heat exchanger made with these plates. Alternatively, uniformly sized openings 97 spaced closer or further apart could be used to give a desired flow distribution instead of differently sized apertures 97. These aperture size or shape differences could also be employed in connection with apertures 77 in the core plates 95 of Figure 15, if desired.
  • Figure 17 shows yet another embodiment of a plate 99 used to form a heat exchanger according to the present invention which, like the plate 85 shown in Figures 9 and 10, has another type of flow augmentation instead of ribs and grooves as shown in Figures 1 to 6 or dimples as shown in Figures 9 and 10.
  • an expanded metal turbulizer 101 is used as the flow augmentation means.
  • turbulizer 101 could be formed of other materials than expanded metal, such as plastic mesh.
  • Figure 17 is a view of plate 99 looking at the oil side or outside of a plate pair. The intermediate areas 39 are located under turbulizer 101 and are still spaced-apart to form inner flow passages inside the plate pairs.
  • Turbulizer 101 could be any type of turbulizer, and if it has a flow resistance that varies in a particular direction, apertures 72 and 77 could be arranged differently or varied in size to suit the turbulizer and maintain uniform radial or transverse flow between the plate pairs. Turbulizers 101 could be employed inside the plate pairs in the inner flow passages as well as, or instead of, the turbulizers 101 used in the outer flow passages as shown in Figure 17.
  • FIGs 18 and 19 show a heat exchanger 28' that is a modification to the heat exchanger 28 shown in Figures 11 and 12.
  • an annular filter seat 103 is mounted on top of top closure plate 56 to accommodate a conventional spin-on oil filter 107 that screws onto conduit 18.
  • Filter seat 103 has inner openings 105 to allow fluid emerging from headers 76 or openings 78 to be delivered to filter inlet openings 109.
  • Figure 20 shows the inside or water side surface of a plate 32' where the inner annular boss 36' and the outer peripheral flange 34' are the same height with respect to both the intermediate bosses 46 and inner peripheral flange 68 as the height of the ribs and grooves 38, 40.
  • a spacer 86 as shown in Figure 21 can be used between the plates of the plate pairs.
  • Spacer 86 has an outer annular portion 88 which is located between outer peripheral flanges 34' and an inner annular portion 90 which is located between inner annular bosses 36'.
  • Inner annular portion 90 has a plurality of apertures 92 therein to correspond with apertures 72 in inner boss 36'. Rotation of spacer 86 relative to plates 32' causes apertures 92 to act as valves to obtain a predetermined setting or adjustment of the flow through apertures 72 during manufacture of heat exchangers using this type of plate.
  • Figures 22 and 23 show a plate 94 that is similar to plate 32' of Figure 20, but which has a peripheral by-pass groove 96 located inside the plate pairs adjacent to the outer peripheral flange 34'.
  • By-pass groove 96 has a first end portion 98 located adjacent to and communicating with one of the intermediate bosses 46 and extends just over half-way around the perimeter of plate 94 to a second end portion 100, so that when two plates 94 are arranged face-to-face, end portions 100 overlap and by-pass groove 96 forms a half-height groove extending all the way around the periphery of the plate pair from one intermediate boss 46 to the other.
  • By-pass groove 96 is used to reduce internal pressure drop inside the plate pairs, if desired.
  • Figure 24 shows a plate 102 similar to plate 94 of Figure 23, but having at least one by-pass groove 104 extending between intermediate bosses 46.
  • Figure 25 shows a plate 102' that is a modification of plate 102 of Figure 24.
  • the by-pass grooves 104 are formed with flow limiting indentations 106 to control or set a predetermined amount of by-pass flow between intermediate bosses 46.
  • the intermediate bosses containing the inlet and outlet openings could be made smaller, so that inner annular bosses 36 could be the same width all around their circumference allowing apertures 72 to extend around the full circumference of these bosses.
  • the various heat exchangers can be made using any number of plate pairs and the various plate pair embodiments could be mixed and matched to achieve a particular desired performance.
  • the top and bottom closure plates could be eliminated in certain applications where other means are used to close the various flow manifolds formed by openings in the plates.
  • end plates could be used that are similar to plates used to make the plate pairs, in which case, the various inlet and outlet openings and apertures in these end plates would not be punched out.
  • Other configurations for the ribs and grooves and dimples and turbulizers could also be employed in the plates, if desired.
  • the heat exchangers of the present invention can be used for cooling or heating other engine fluids, such as, fuel, transmission fluid, hydraulic steering fluid, refrigerant and even engine coolant itself. Either fluid can pass between the plate pairs or through the plate pairs, and the heat exchangers of the present invention can be used to heat fluids as well as cool them. Further, the heat exchangers of the present invention can be used in applications other than in the automotive industry.

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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)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un échangeur thermique, utilisant plusieurs paires de plaques (30) empilées, comprenant des plaques annulaires (32) d'accouplement opposées, chaque plaque présentant un rebord extérieur (34) périphérique, un bourrelet intérieur (36) annulaire situé dans le même plan que ledit rebord périphérique (34), et une zone intermédiaire (39) décalée située entre le rebord périphérique (34) et le bourrelet intérieur (36). Les rebords périphériques (34) et les bourrelets intérieurs (36) des plaques d'accouplement (32) sont reliés entre eux. Les zones intermédiaires (39) possèdent des bourrelets intermédiaires (46) reliés, orientés vers l'extérieur, présentant des ouvertures d'entrée et de sortie (48, 50) alignées, qui forment des collecteurs (52, 54) destinés à l'écoulement d'un premier fluide d'échange thermique, de manière circonférencielle à travers les paires de plaques (30), du collecteur d'entrée (52) vers le collecteur de sortie (54). L'échangeur thermique comprend également un conduit collecteur (70, 76, 82) renfermant les bourrelets intérieurs (36) ou les rebords périphériques (34) permettant à la totalité d'un second fluide d'échange thermique de passer entre les paires de plaques, transversalement par rapport au premier fluide d'échange thermique périphérique.
PCT/CA1999/001246 1998-12-23 1999-12-23 Echangeurs thermiques annulaires a ecoulement radial WO2000039516A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
AT99964346T ATE225491T1 (de) 1998-12-23 1999-12-23 Ringförmiger wärmetauscher mit radialströmung
KR10-2001-7008124A KR100412278B1 (ko) 1998-12-23 1999-12-23 방사류 환상 열 교환기
JP2000591373A JP3493519B2 (ja) 1998-12-23 1999-12-23 輻流環状熱交換器
DE69903350T DE69903350T2 (de) 1998-12-23 1999-12-23 Ringförmiger wärmetauscher mit radialströmung
AU30275/00A AU755895B2 (en) 1998-12-23 1999-12-23 Radial flow annular heat exchangers
EP99964346A EP1141645B1 (fr) 1998-12-23 1999-12-23 Echangeurs thermiques annulaires a ecoulement radial

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CA2,257,076 1998-12-23
CA002257076A CA2257076C (fr) 1998-12-23 1998-12-23 Echangeurs de chaleur annulaires a ecoulement radial

Publications (1)

Publication Number Publication Date
WO2000039516A1 true WO2000039516A1 (fr) 2000-07-06

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PCT/CA1999/001246 WO2000039516A1 (fr) 1998-12-23 1999-12-23 Echangeurs thermiques annulaires a ecoulement radial

Country Status (9)

Country Link
EP (1) EP1141645B1 (fr)
JP (1) JP3493519B2 (fr)
KR (1) KR100412278B1 (fr)
AT (1) ATE225491T1 (fr)
AU (1) AU755895B2 (fr)
CA (1) CA2257076C (fr)
DE (1) DE69903350T2 (fr)
ES (1) ES2186430T3 (fr)
WO (1) WO2000039516A1 (fr)

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WO2003056267A1 (fr) * 2001-12-27 2003-07-10 Vahterus Oy Ameliorations apportees a l'echange thermique d'un echangeur thermique a plaques rondes
KR100412278B1 (ko) * 1998-12-23 2003-12-31 롱 매뉴팩처링 리미티드 방사류 환상 열 교환기
WO2010087801A1 (fr) * 2009-02-02 2010-08-05 Eco-Power Turbines, Inc. Échangeur de chaleur
CN103175430A (zh) * 2012-06-28 2013-06-26 郑州大学 环形微通道换热板
CN105651084A (zh) * 2016-01-13 2016-06-08 宁波市哈雷换热设备有限公司 板式热交换器
CN112066600A (zh) * 2019-06-11 2020-12-11 广东美的制冷设备有限公司 换热器及空调设备

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JP4559251B2 (ja) * 2005-02-17 2010-10-06 本田技研工業株式会社 蓄熱装置
KR100704106B1 (ko) * 2006-12-01 2007-04-09 서동숭 유압기계 작동오일의 조립형 오일냉각기
DK3372941T3 (da) 2017-03-10 2021-01-11 Alfa Laval Corp Ab Pladepakke, plade og varmeveksleranordning
US20230349604A1 (en) * 2022-03-31 2023-11-02 Hanon Systems Receiver drier and economizer integration for vapor injection system

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CN112066600A (zh) * 2019-06-11 2020-12-11 广东美的制冷设备有限公司 换热器及空调设备

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EP1141645A1 (fr) 2001-10-10
KR20010083957A (ko) 2001-09-03
DE69903350T2 (de) 2003-07-10
DE69903350D1 (de) 2002-11-07
AU3027500A (en) 2000-07-31
ATE225491T1 (de) 2002-10-15
CA2257076C (fr) 2005-03-22
ES2186430T3 (es) 2003-05-01
AU755895B2 (en) 2003-01-02
KR100412278B1 (ko) 2003-12-31
EP1141645B1 (fr) 2002-10-02
CA2257076A1 (fr) 2000-06-23
JP2002533654A (ja) 2002-10-08
JP3493519B2 (ja) 2004-02-03

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