EP1802933B1 - Plate-type heat exchanger - Google Patents

Plate-type heat exchanger Download PDF

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Publication number
EP1802933B1
EP1802933B1 EP05797019A EP05797019A EP1802933B1 EP 1802933 B1 EP1802933 B1 EP 1802933B1 EP 05797019 A EP05797019 A EP 05797019A EP 05797019 A EP05797019 A EP 05797019A EP 1802933 B1 EP1802933 B1 EP 1802933B1
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EP
European Patent Office
Prior art keywords
fluid
plate
barrier portion
heat exchanger
oil
Prior art date
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Active
Application number
EP05797019A
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German (de)
English (en)
French (fr)
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EP1802933A1 (en
EP1802933A4 (en
Inventor
Michel St. Pierre
Thomas F. Seiler
Pascal B. Bradu
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Dana Canada Corp
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Dana Canada Corp
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Publication of EP1802933A4 publication Critical patent/EP1802933A4/en
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Publication of EP1802933B1 publication Critical patent/EP1802933B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F3/042—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 in the form of local deformations of the element
    • F28F3/044—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 in the form of local deformations of the element the deformations being pontual, e.g. dimples
    • 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
    • F28D9/0031—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 conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—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 conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—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 conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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
    • F28D9/0031—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 conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—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 conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/0056—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 conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another with U-flow or serpentine-flow inside conduits; with centrally arranged openings on the plates

Definitions

  • This invention relates to plate-type heat exchangers for effecting heat transfer between two fluids, for example between a lubricating oil and a liquid coolant.
  • Plate-type heat exchangers comprising a stack of heat exchanger plates are well known. Such heat exchangers are commonly employed for effecting heat transfer between a first fluid, for example a lubricating oil to be cooled, and a second fluid, for example a liquid coolant.
  • a first fluid for example a lubricating oil to be cooled
  • a second fluid for example a liquid coolant
  • US 5954126 discloses a heat exchanger comprising a plurality of first fluid core plates and a plurality of second fluid core plates, each of the core plates comprising a periphery; a first end; a second end; a generally flat base having a top surface and a bottom surface; a first fluid inlet opening proximate the first end of the plate; a first fluid outlet opening spaced from the first fluid inlet opening toward the second end of the plate; a second fluid inlet opening; and a second fluid outlet opening; wherein the first fluid inlet and outlet openings are spaced from one another along a plate axis and wherein the second fluid inlet and outlet openings are located on opposite sides of the plate axis; each of the first fluid core plates further comprises a first raised barrier portion having an upper surface which is raised relative to the top surface of the base and relative to the first fluid inlet and outlet openings, the first raised barrier portion having a first end proximate the first fluid inlet opening and a second end spaced from the first fluid in
  • US 2004/0040697 discloses a heat exchanger comprised of a plurality of coolant core plates 10 and a plurality of oil core plates 25 stacked in alternating order.
  • the coolant core plates 10 are each provided with an oil inlet opening 19 and an oil outlet opening 22 which are formed in the upper surfaces of respective bosses 17 and 20, and has a coolant inlet opening 13 and a coolant outlet opening 14 which are co-planar with the base 11 of plate 10.
  • the oil core plate 25 has an oil inlet opening 34 which is partially surrounded by an upwardly extending flange 35 and an oil outlet opening which is partially surrounded by an upwardly extending flange 39.
  • the coolant inlet and outlet openings 29 and 31 of oil core plate 25 are formed in the upper surfaces of bosses 28 and 30.
  • the bosses 28 and 30 extend in the same direction as the flanges 35 and 39, i.e. upwardly in relation to the base 26 of oil core plate 25.
  • a heat exchanger comprising a plurality of first fluid core plates and a plurality of second fluid core plates, each of the core plates comprising a periphery; a first end; a second end; a generally flat base having a top surface and a bottom surface; a first fluid inlet opening proximate the first end of the plate; a first fluid outlet opening spaced from the first fluid inlet opening toward the second end of the plate; a second fluid inlet opening; and a second fluid outlet opening; wherein the first fluid inlet and outlet openings are spaced from one another along a plate axis and wherein the second fluid inlet and outlet openings are located on opposite sides of the plate axis; each of the first fluid core plates further comprises a first raised barrier portion having an upper surface which is raised relative to the top surface of the base and relative to the first fluid inlet and outlet openings, the first raised barrier portion having a first end proximate the first fluid inlet opening and a second end spaced from the first
  • first fluid may flow in the reverse direction through the first fluid flow passage in which case the first fluid outlet openings in the plates would function as first fluid inlet openings, and the first fluid inlet openings, in the plates would function as first fluid outlet openings.
  • the preferred embodiment of the invention relates to a plate-type heat exchanger for effecting heat transfer between a first fluid to be cooled and a second fluid.
  • the first fluid may preferably comprise a lubricating oil such as natural or synthetic engine oil, transmission oil or power steering oil or other fluid to be cooled, such as fuel.
  • the second fluid may preferably comprise a liquid coolant for cooling the oil in the heat exchanger, for example a glycol coolant.
  • at least one of the first and second fluids could be, for example, water, deionized water, or refrigerant, the fluid being in liquid, gaseous or two-phase form.
  • the first and second fluids are referred to as the oil and the coolant, respectively and are in liquid form.
  • Oil core plate 10 comprises a generally flat, planar base 12 having a top surface 14 and a bottom surface 16.
  • the periphery 18 of plate 10 is provided with an upstanding flange 20, this flange 20 being outwardly inclined in a direction away from the base 12, such that there is an obtuse angle between the flange 20 and the adjacent portion of base 12.
  • the base 12 has an oil inlet opening 22 proximate a first end 24 of plate 10 and an oil outlet opening 26 spaced from the oil inlet openings 22 toward a second end 28 of plate 10.
  • the oil inlet and outlet openings 22, 26 are spaced from one another along a plate axis P which, in the preferred embodiment shown in the drawings, longitudinally bisects the plate 10. It will, however, be appreciated that the axis P does not necessarily bisect the plate 10.
  • Plate 10 further comprises a coolant inlet opening 30 and a coolant outlet opening 32 together with, in the preferred embodiment shown in the drawings, a further opening 34 located between the oil inlet and outlet openings 22, 26.
  • the coolant inlet and outlet openings 30, 32 are preferably located on opposite sides of the plate axis P, and are preferably located proximate the second end 28 of the plate 10.
  • the further opening 34 is preferably located between the oil inlet and outlet openings 22, 26, preferably in close proximity to openings 22, 26 and preferably located along the plate axis P.
  • the base 12 of oil core plate 10 is provided with a plurality of protrusions and depressions in order to direct flow of the heat exchange fluids along its top and bottom surfaces 14, 16.
  • the core plate 10 is provided with features which protrude in opposite directions from its top and bottom surfaces 14, 16.
  • the features which protrude from the top surface 14 of the base 12 are described as "raised”, while those protruding from the bottom surface 16 are described as “depressed”. Again, it will be appreciated that these terms are used for convenience only.
  • the top surface 14 of base 12 is provided with a first raised barrier portion 36 having an upper surface 38 which is raised relative to the top surface 14 of base 12 and relative to the oil inlet and outlet openings 22, 26.
  • the function of the first raised barrier portion 36 is to direct the flow of oil along the top surface 14 of base 12 between the oil inlet and outlet openings 22, 26 in a manner which maximizes the use of the plate surface area and thereby provides optimal heat transfer with the coolant. This will be described in detail below.
  • the first raised barrier portion 36 has a first end 40 proximate the oil inlet opening 22 and a second end 42 spaced from the oil inlet opening 22 toward the second end 28 of plate 10.
  • An oil flow gap 44 is preferably provided between the second end 42 of first raised barrier portion 36 and the second end 28 of the plate 10, through which oil can flow between the oil inlet and outlet openings 22, 26, as explained in detail below.
  • the bottom surface 16 of base 12 is provided with a first recessed barrier portion 46 having a lower surface 48 which is recessed relative to the bottom surface 16.
  • the function of the first recessed barrier portion 46 is to direct the flow of coolant along the bottom surface 16 of base 12 between the coolant inlet and outlet openings 30, 32 in a manner which optimizes heat transfer with the oil. This is described in detail below.
  • the first recessed barrier portion 46 has a first end 50 proximate the first end 24 of plate 10 and a second end 52 proximate the second end 28 of plate 10. Both the oil inlet and outlet openings 22, 26 are formed in the lower surface 48 of the first recessed barrier portion 46, with the oil inlet opening 22 preferably being located proximate the first end 50 of barrier portion 46 and the oil outlet opening 26 preferably being located intermediate the first and second ends 50, 52 of barrier portion 46.
  • the first recessed barrier portion 46 extends along the plate axis P, with the coolant inlet and outlet openings 30, 32 being located on opposite sides of the barrier portion 46.
  • At least one coolant flow gap is provided, either through the first recessed barrier portion 46 or between the barrier portion 46 and the first end 24 of plate 10, through which the coolant can flow generally transversely as it flows between the coolant inlet and outlet openings 30, 32.
  • a first coolant flow gap 54 is provided between the first end 50 of the first recessed barrier portion 46 and the first end 24 of plate 10, through which the coolant can flow between the coolant openings 30, 32.
  • the coolant flow gap 54 is spaced toward the first end 24 of plate 10 relative to the coolant openings 30, 32, and preferably the coolant flow gap 54 and coolant openings 30, 32 are located at opposite ends of plate 10.
  • Coolant core plate 60 comprises a generally flat, planar base 62 having a top surface 64 and a bottom surface 66.
  • the periphery 68 of plate 60 is provided with an upstanding flange 70, this flange 70 being outwardly inclined in a direction away from the base 62, such that there is an obtuse angle between the flange 70 and the adjacent portion of base 62.
  • the base 62 has an oil inlet opening 72 proximate a first end 74 of plate 60 and an oil outlet opening 76 spaced from the oil inlet opening 72 toward a second end 78 of plate 60, preferably along plate axis P.
  • Plate 60 further comprises a coolant inlet opening 80 and a coolant outlet opening 82 together with, in the preferred embodiment shown in the drawings, a further opening 84 located between the oil inlet and outlet openings 72, 76.
  • the purpose of opening 84 will be explained in detail later.
  • the coolant inlet and outlet openings 80, 82 are preferably located on opposite sides of the plate axis P, and are preferably located proximate the second end 78 of the plate 60.
  • the further opening 84 is preferably located between the oil inlet and outlet openings 72, 76, preferably in close proximity to openings 72, 76 and preferably located along the plate axis P.
  • the base 62 of coolant core plate 60 is provided with a plurality of protrusions and depressions in order to direct flow of the heat exchange fluids along its top and bottom surfaces 64, 66.
  • the core plate 60 is provided with features which protrude in opposite directions from its top and bottom surfaces 64, 66.
  • the features which protrude from the top surface 64 of the coolant core plate 60 are described as "raised”, while those protruding from the bottom surface 66 are described as "depressed”. Again, it will be appreciated that these terms are used for convenience only.
  • the second raised barrier portion 86 has a first end 90 proximate the first end 74 of plate 60 and a second end 92 proximate the second end 78 of plate 60. Both the oil inlet and outlet openings 72, 76 are formed in the upper surface 88 of the second raised barrier portion 86, with the oil inlet opening 72 preferably being located proximate the first end 80 of barrier portion 86 and the oil outlet opening 76 preferably being located intermediate the first and second ends 90, 92 of barrier portion 86.
  • the second raised barrier portion 86 extends along the plate axis P, with the coolant inlet and outlet openings 80, 82 being located on opposite sides of the barrier portion 86.
  • At least one coolant flow gap is provided, either through the second raised barrier portion 86 or between the barrier portion 86 and the first end 74 of plate 60, through which the coolant can flow generally transversely as it flows between the coolant inlet and outlet openings 80, 82.
  • a first coolant flow gap 94 is provided between the first end 90 of the second raised barrier portion 86 and the first end 74 of plate 60, through which the coolant can flow between the coolant openings 80, 82.
  • the coolant flow gap 94 is spaced toward the first end 74 of plate 60 relative to the coolant openings 30, 32, and preferably the coolant flow gap 94 and coolant openings 80, 82 are located at opposite ends of plate 60.
  • the bottom surface 66 of base 62 is provided with a second recessed barrier portion 96 having a lower surface 98 which is recessed relative to the bottom surface 66 of base 62 and relative to the oil inlet and outlet openings 72, 76.
  • the function of the second recessed barrier portion 96 is to direct the flow of oil along the bottom surface 66 of base 62 between the oil inlet and outlet openings 72, 76 in a manner which optimizes heat transfer with the coolant. This will be described in detail below.
  • the second recessed barrier portion 96 has a first end 100 proximate the oil inlet opening 72 and a second end 102 spaced from the oil inlet opening 72 toward the second end 78 of plate 60.
  • An oil flow gap 104 is preferably provided between the second end 102 of second recessed barrier portion 96 and the second end 78 of the plate 60, through which oil can flow between the oil inlet and outlet openings 72, 76, as explained in detail below.
  • first raised barrier portion 36 of the oil core plate 10 and the second recessed barrier portion 96 of coolant core plate 60 correspond in size, shape and location so that their respective upper and lower surfaces 38 and 98 are in sealed contact with one another in the assembled heat exchanger.
  • Preferred features of first raised barrier portion 36 are now described below with reference to the drawings. Except where noted to the contrary, the following discussion also applies to the second recessed barrier portion 96 of plate 60, and corresponding features of the second recessed barrier portion 96 are identified in the drawings with corresponding, primed reference numerals.
  • the first raised barrier portion 36 comprises a first portion 106 and a pair of legs 108, 110.
  • the first portion 106 of barrier portion 36 is located between the oil inlet and outlet openings 22, 26 and includes the first end 40 of barrier portion 36.
  • the first portion 106 of barrier portion 36 comprises a raised, approximately circular rib surrounding the further opening 34 of oil core plate 10, the outer periphery of the rib being in close proximity to both the oil inlet and outlet openings 22, 26.
  • the legs 108, 110 of first raised barrier portion 36 extend from the first portion106 of barrier portion 36 toward the second end 28 of plate 10.
  • the terminal ends 112, 114 of legs 108, 110 are located at the second end 42 of barrier portion 36 and are proximate to the second end 28 of plate 10, with the oil flow gap 44 being defined by the distance (measured parallel to axis P) between the terminal ends 112, 114 of the legs 108, 110 and the second end 28 of plate 10.
  • the legs 108, 110 extend along opposite sides of the oil outlet opening 26 for at least a portion of their lengths and are spaced apart so as to define a channel 116.
  • the channel 116 provides a flow path extending from gap 44 toward the first end of plate 10, along which the oil must flow in order to reach the oil outlet opening 26. This has the effect of lengthening the flow path between the oil inlet and outlet openings 22, 26, thereby maximizing use of the plate surface area and optimizing heat transfer.
  • the channel 116 is coplanar with the first fluid outlet opening 26 and with the first recessed barrier portion 46, i.e. it is recessed relative to the base 12.
  • the channel 116 preferably extends continuously along axis P from the oil outlet opening 26 to the second end 28 of plate 10.
  • a pair of grooves 118 and 120 is formed in the top surface 14 of plate 10.
  • Each groove 118, 120 extends along a side of one of the legs 108, 110 opposite the channel 116.
  • the grooves 118, 120 are coplanar with the channel 116 and each have an end communicating with the channel 116 at the terminal end 112 or 114 of one of the legs 108 or 110.
  • the base 12 of oil core plate 10 is provided on its top surface 14 with a pair of upstanding bosses 122, 124 having respective upper surfaces 126, 128 in which the coolant inlet and outlet openings 30, 32 are formed.
  • the upper surfaces 126, 128 of bosses 122, 124 are raised relative to the base 12 and relative to the first raised barrier portion 36, with the corresponding coolant inlet and outlet openings 80, 82 of the coolant core plate 60 being coplanar with the base 62 thereof. It will, however, be appreciated that this is not necessarily the case.
  • the upper surfaces 126, 128 of raised bosses 122, 124 could be coplanar with the upper surface 38 of raised barrier portion 36, and the coolant core plate could be provided with corresponding recessed bosses (not shown) which come into sealed contact with the raised bosses 122, 124.
  • first recessed barrier portion 46 of the oil core plate 10 and the second raised barrier portion 86 of coolant core plate 60 correspond in size, shape and location so that their respective lower and upper surfaces 48 and 88 are in sealed contact with one another in the assembled heat exchanger.
  • Preferred features of first recessed barrier portion 46 are now described below with reference to the drawings. Except where noted to the contrary, the following discussion also applies to the second raised barrier portion 86 of plate 60, and corresponding features of the second raised barrier portion 86 are identified in the drawings with corresponding, primed reference numerals.
  • the first recessed barrier portion 46 is comprised of a plurality of bosses, including a first boss 130 in which the oil inlet opening 22 is formed and a second boss 132 in which the oil outlet opening 26 is formed.
  • the barrier portion 46 further comprises a third boss 134 located between and in close proximity to the first and second bosses 130, 132.
  • the third boss 134 surrounds the further opening 34 and is located radially inwardly of the approximately circular rib comprising the first portion 106 of the first raised barrier portion 36, discussed above.
  • the first coolant flow gap 54 is located between the first boss 130 and the first end 24 of plate 10.
  • a second coolant flow gap 136 is located between the first boss 130 and the third boss 134
  • a third coolant flow gap 138 is located between the second boss 132 and the third boss 134.
  • the first gap 54 is preferably wider than the second and third gaps 136, 138 so that most of the coolant flowing from the coolant inlet opening 30 to the coolant outlet opening 32 will be forced to flow around the first boss 130, thereby maximizing the distance travelled by the coolant and maximizing use of the plate surface area, thereby optimizing heat transfer.
  • the second boss 132 is elongate and extends axially from the oil outlet opening 26 to the second end 28 of plate 10, thereby preventing short circuit flow of coolant across the plate between inlet and outlet openings 30, 32. It will also be appreciated that the second boss is coextensive with the recessed channel 116, discussed above, which is formed in the top surface 14 of plate 10.
  • the first recessed barrier portion 46 further comprises a pair of legs 140, 142 to help direct flow of the coolant. These legs 140, 142 extend alongside and in close proximity to the second boss 132 and are coincident with the grooves 118,120 on the other side of the plate 10. Each of the legs 140, 142 has a free end which terminates proximate the third coolant flow gap 138 and an opposite end which is joined to a side of the second boss 132.
  • the legs .140, 142 are spaced from the second boss 132 by a pair of narrow grooves 144, 146, comprising the undersides of the legs 08, 110 formed in the top surface 14 of plate 10.
  • the grooves 144, 146 are preferably coplanar with a groove 148 surrounding the third boss 134, which forms the underside of the first portion 106 of the first raised barrier portion 36, described above.
  • each oil core plate 10 has its top surface 14 facing the bottom surface 66 of an upwardly adjacent coolant core plate 60 and each coolant core plate 60 has its top surface 64 facing the bottom surface 16 of an upwardly adjacent oil core plate 10. Only some of the plates comprising heat exchanger 150 are shown in the drawings.
  • the first raised barrier portions 36 of the oil core plates 10 are in sealed contact with the corresponding second recessed barrier portions 96 of an upwardly adjacent coolant core plate 60, the barrier portions 36, 96 being in sealed contact along their upper and lower surfaces 38, 98, respectively.
  • the barrier portions 36,96 are preferably identical in size and shape and are of sufficient height so that each raised element making up barrier portion 36 (i.e. first portion 106 and legs 108, 110) is in sealed contact with a corresponding recessed element of barrier portion 96 (i.e. first portion 106' and legs 108', 110').
  • the oil flow gaps 44 and 104 of the respective oil and coolant core plates 10, 60 are aligned, as are the channels 116, 116' and the grooves 118, 118', 120 and 120' of respective plates 10, 60.
  • the second raised barrier portions 86 of the coolant core plates 60 are in sealed contact with the corresponding first recessed barrier portions 46 of an upwardly adjacent oil core plate 10, the barrier portions 86, 46 being in sealed contact along their upper and lower surfaces 88, 48, respectively.
  • the barrier portions 46, 86 are preferably identical in size, shape and height so that each recessed element making up barrier portion 46 (i.e. first boss 130, second boss 132, third boss 134 and legs 140, 142) is in sealed contact with a corresponding raised element of barrier portion 86 (i.e. first boss 130', second boss 132', third boss 134' and legs 140', 142').
  • first coolant flow gaps 54 and 94 of the respective oil and coolant core plates 10, 60 are aligned, as are the second coolant flow gaps 136, 136', the third coolant flow gaps 138,138' and the narrow grooves 144, 144', 146 and 146' of the respective plates 10, 60.
  • each oil core plate 10 in which the coolant inlet and outlet openings 30, 32 are formed, are sealed along their upper surfaces 126, 128 to the bottom surface 66 of an upwardly adjacent coolant core plate 60.
  • the plates 10, 60 are sealed together with the openings of each oil core plate 10 (i.e. oil inlet opening 22, oil outlet opening 26, coolant inlet opening 30, coolant outlet opening 32, further opening 34) being in alignment with the corresponding openings of each coolant core plate 60 (i.e. oil inlet opening 72, oil outlet opening 76, coolant inlet opening 80, coolant outlet opening 82, further opening 84).
  • the plates are made of a metallic material, they may be provided with a brazing filler metal in the form of a cladding, a coating or shim plates so that, after assembly of the plurality of oil core plates 10 and the plurality of coolant core plates 60 as described above, the assembled plates 10, 60 may be disposed in a brazing furnace or other suitable heating means thereby to provide the above-described sealing contact between the plates 10, 60.
  • Metallic plates can also be joined by alternate suitable means such as welding, adhesive bonding, or mechanical assembly using sealing gaskets.
  • Non-metallic plates can be joined by other means, such as ultrasonic wending.
  • Ends plates 156 and 158 are schematically shown in the drawings for sealing the ends of the plate stack and connecting it to the oil and coolant systems.
  • FIG. 9 shows lower end plate 158 being provided with a coolant inlet opening 160 and a coolant inlet fitting 162, and also with a coolant outlet opening 164 and a coolant outlet fitting 166.
  • the coolant inlet opening 160 of plate 158 is in communication with the coolant flow passages 154 and is aligned with the coolant inlet openings 30, 80 of the stacked plates 10, 60.
  • the coolant outlet opening 164 of plate 158 is in communication with the coolant flow passages 154 and is aligned with the coolant outlet openings 32, 82 of the plates 10, 60.
  • the aligned inlet openings 30, 80 and aligned outlet openings 32, 82 are closed at the upper end of heat exchanger 150 by the upper end plate 158.
  • the lower end plate 158 may preferably be mounted to an engine block 168 and the upper end plate may preferably be mounted to an oil filter 170.
  • the lower end plate 158 is provided with an oil inlet opening 172 through which oil enters the heat exchanger 150 from an internal flow passage 174 in the engine block 168.
  • the oil inlet opening 172 of lower end plate 158 is in communication with oil flow passages 152 and is aligned with the oil inlet openings 22, 72 of the stacked plates 10, 60.
  • the upper end plate 156 is provided with an oil outlet opening 176 which is in communication with an inlet opening 178 of the oil filter 170.
  • the oil outlet opening 176 is also in communication with oil flow passages 152 and is aligned with the oil outlet openings 26, 76 of the plates 10, 60.
  • the upper end plate 156 is also provided with an oil return opening 180 through which filtered oil is returned to the engine block 168 via the aligned further openings 34, 84 of the stacked plates 10, 60 which together form an oil return passage 182 which is sealed from the oil flow passages 152.
  • the oil return passage 182 is in communication with an oil return opening 184 in the lower end plate 158 and with an oil return passage 186 of the engine block 168.
  • oil from engine block 168 enters the heat exchanger 150 through the oil inlet opening 172 in the lower end plate 158 and then flows into one end of the aligned oil inlet openings 22, 72. Since the other end of the aligned openings 22, 72 is blocked by upper end plate 156, the oil is forced to flow through the oil flow passages 152 as indicated in chain-dotted lines in Figure 5 .
  • the oil In order to flow from the oil inlet opening 22 to the oil outlet opening 26, the oil must flow alongside the first raised barrier portion 36 toward the second end 28 of plate 10, through oil flow gap 44 and along channel 116 to oil outlet opening 26. Therefore, the oil must flow-over a substantial portion of the base 12 of each plate 10 as it flows from the oil inlet opening 22 to the oil outlet opening 26.
  • the flow of oil through the engine block 168, heat exchanger 150 and oil filter 170 is indicated by arrows in Figure 10 . In this embodiment, it will be appreciated that the oil is cooled before it is filtered.
  • the oil flow may be reversed so that it is filtered before being cooled by heat exchanger 150.
  • the oil flows from passage 186 of engine block 168 into the passage 182 of heat exchanger 150.
  • the oil flows through passage 182 and enters the oil filter 170 to be filtered.
  • the filtered oil then enters the heat exchanger 150 through opening 176 in upper end plate 156 and exits the heat exchanger through the opening 172 in the lower end plate 158, returning to engine block 168 through passage 174.
  • the aligned inlet openings 22, 72 are sealed from direct flow communication with the oil filter 170 under all operating conditions, i.e. the oil must pass through the oil flow passages 152 before entering the oil filter 170. It may be preferred to provide a further opening (not shown) in the upper end plate 156 which is aligned with the inlet openings 22, 72 of plates 10, 60 and which is provided with a by-pass valve (not shown), for example an active pressure or thermal relief valve, to permit oil to by pass the heat exchanger under start-up conditions and directly enter the oil filter. Such by-pass valves are known in the art and do not form part of the present invention. Alternatively, it may be preferred to provide a passive by-pass orifice, in the form of a calibrated opening in the upper end plate 156, so as to permit controlled flow of fluid to the oil filter under various conditions.
  • coolant enters the heat exchanger 150 through a coolant inlet opening 160 in the lower end plate 158 and then flows into one end of the aligned coolant inlet openings 30, 80. Since the other end of the aligned openings 30, 80 is blocked by upper end plate 158, the coolant is forced to flow through the coolant flow passages 154 following the path indicated in chain-dotted lines in Figure 7 .
  • the coolant In order to flow from the coolant inlet opening 30 to the coolant outlet opening 32, the coolant must flow along one side of the second raised barrier portion 86 toward the first end 24 of plate 10, through the first coolant flow gap 54, then alongside the other side of barrier portion 86 toward the second end 28 of plate 10, to the coolant outlet opening 32.
  • the coolant must flow over a substantial portion of the base 62 of each coolant core plate 60 as it flows from the coolant inlet opening 30 to the coolant outlet opening 32. It will be appreciated that a relatively small amount of coolant will flow through the second and third coolant flow gaps 136, 138, but this has a minimal impact on the performance of heat exchanger 150.
  • the heat exchanger 150 thus achieves a high rate of heat transfer between the oil and the coolant.
  • the openings 32, 82 could be the coolant inlet openings with the openings 30, 80 being the coolant outlet openings.
  • the openings 26, 76 could function as the oil inlet openings, with the openings 22, 72 functioning as the oil outlet openings.
  • each oil flow passage 152 and the height of each coolant flow passage 154 is partly dependent on the extent of the nesting of the alternate plates 10, 60 and therefore is partly dependent on the angle of inclination of the flanges 20, 70. It will also be appreciated that the heights of the flow passages 152, 154 are also partly dependent on the heights of the barrier portions 36, 46, 86, 96 and the heights of bosses 122, 124.
  • Turbulisers which may be of conventional form, such as the turbulisers 60 of U.S. Patent No. 6,244,334 issued on June 12, 2001 to Wu, et al. , are preferably disposed in one or more of the oil flow passages 152 and may also be disposed in one or more of the coolant flow passages 154, these turbulisers serving to disrupt the oil or coolant flow in each of the oil or coolant flow passages 152, 154 in which they are installed and to disturb the boundary layers of the oil or coolant flow at the surfaces of the plates 10, 60, thereby improving the efficiency of heat transfer from the oil to the coolant in the heat exchanger 150.
  • the turbulisers 178, 180 have a high pressure drop (HPD) flow direction in which maximum turbulising of the oil flow occurs but with a high pressure drop in the oil flow, and a transverse low pressure drop (LPD) flow direction in which there is reduced turbulising of the oil flow but with low pressure drop in the oil flow.
  • HPD high pressure drop
  • LPD transverse low pressure drop
  • the turbulisers 178, 180 may each be disposed in either the HPD or LPD flow direction.
  • the base 62 of one or more of the coolant core plates 60 may be formed with spaced protrusions such as ribs and/or dimples, similar to those shown in Figures 1 and 2 of U.S. Publication No. 2004/0040697 A1 (St. Pierre et al.) published on March 4, 2004 and incorporated herein by reference in its entirety.
EP05797019A 2004-10-19 2005-10-19 Plate-type heat exchanger Active EP1802933B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CA2485036A CA2485036C (en) 2004-10-19 2004-10-19 Plate-type heat exchanger
PCT/CA2005/001607 WO2006042405A1 (en) 2004-10-19 2005-10-19 Plate-type heat exchanger

Publications (3)

Publication Number Publication Date
EP1802933A1 EP1802933A1 (en) 2007-07-04
EP1802933A4 EP1802933A4 (en) 2009-10-28
EP1802933B1 true EP1802933B1 (en) 2011-12-07

Family

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Application Number Title Priority Date Filing Date
EP05797019A Active EP1802933B1 (en) 2004-10-19 2005-10-19 Plate-type heat exchanger

Country Status (6)

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EP (1) EP1802933B1 (ja)
JP (1) JP4881867B2 (ja)
CN (1) CN100516752C (ja)
AT (1) ATE536524T1 (ja)
CA (1) CA2485036C (ja)
WO (1) WO2006042405A1 (ja)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE530011C2 (sv) * 2006-06-05 2008-02-05 Alfa Laval Corp Ab Värmeväxlarplatta och plattvärmeväxlare
RU2511779C2 (ru) * 2010-11-19 2014-04-10 Данфосс А/С Теплообменник
RU2502932C2 (ru) 2010-11-19 2013-12-27 Данфосс А/С Теплообменник
DE202011002197U1 (de) * 2011-02-01 2012-02-02 Dana Gmbh Wärmetauscher
CN102230698B (zh) * 2011-06-23 2013-12-25 柳州五菱宝马利汽车空调有限公司 汽车空调系统蒸发器
CN102252388B (zh) * 2011-06-23 2014-01-15 柳州五菱宝马利汽车空调有限公司 水、冷一体式汽车空调系统
EP2618093A3 (en) * 2012-01-23 2015-03-18 Danfoss A/S Heat exchanger, heat exchanger plate, and method for producing a heat exchanger
JP6126358B2 (ja) * 2012-11-08 2017-05-10 株式会社マーレ フィルターシステムズ 多板式オイルクーラ
FR3041422B1 (fr) * 2015-09-17 2017-12-01 Novares France Dispositif pour moteur comprenant un carter d’huile et un echangeur thermique
KR102173397B1 (ko) * 2017-09-22 2020-11-03 한온시스템 주식회사 오일쿨러
KR102562656B1 (ko) * 2018-06-19 2023-08-03 한온시스템 주식회사 오일쿨러
CN110657692B (zh) * 2018-06-29 2020-12-08 浙江三花汽车零部件有限公司 一种换热器
KR102598408B1 (ko) * 2018-12-06 2023-11-07 한온시스템 주식회사 열교환기
CN113465416A (zh) * 2020-03-30 2021-10-01 浙江三花汽车零部件有限公司 一种换热器
CN114688897A (zh) * 2020-12-31 2022-07-01 浙江三花汽车零部件有限公司 一种换热器

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61223492A (ja) * 1985-03-29 1986-10-04 Tsuchiya Mfg Co Ltd 熱交換器
DE19707647B4 (de) 1997-02-26 2007-03-01 Behr Gmbh & Co. Kg Scheibenkühler
CA2384712A1 (en) * 2002-05-03 2003-11-03 Michel St. Pierre Heat exchanger with nest flange-formed passageway

Also Published As

Publication number Publication date
CA2485036A1 (en) 2006-04-19
ATE536524T1 (de) 2011-12-15
CN100516752C (zh) 2009-07-22
EP1802933A1 (en) 2007-07-04
JP2008517240A (ja) 2008-05-22
CN101069059A (zh) 2007-11-07
CA2485036C (en) 2012-04-24
EP1802933A4 (en) 2009-10-28
JP4881867B2 (ja) 2012-02-22
WO2006042405A1 (en) 2006-04-27

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