EP3517873B1 - Échangeur de chaleur et procédé de refroidissement d'un flux d'air chauffé - Google Patents

Échangeur de chaleur et procédé de refroidissement d'un flux d'air chauffé Download PDF

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Publication number
EP3517873B1
EP3517873B1 EP18211108.8A EP18211108A EP3517873B1 EP 3517873 B1 EP3517873 B1 EP 3517873B1 EP 18211108 A EP18211108 A EP 18211108A EP 3517873 B1 EP3517873 B1 EP 3517873B1
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EP
European Patent Office
Prior art keywords
cooling fluid
flow
plate pairs
heat exchanger
directing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Application number
EP18211108.8A
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German (de)
English (en)
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EP3517873A1 (fr
Inventor
Frank Lippke
Rainer Glück
Thomas Peskos
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Modine Manufacturing Co
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Modine Manufacturing Co
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Priority claimed from US15/880,624 external-priority patent/US10690421B2/en
Application filed by Modine Manufacturing Co filed Critical Modine Manufacturing Co
Publication of EP3517873A1 publication Critical patent/EP3517873A1/fr
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Publication of EP3517873B1 publication Critical patent/EP3517873B1/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
    • 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
    • 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
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0082—Charged air coolers

Definitions

  • the present invention relates to a heat exchanger.
  • the invention relates to a heat exchanger, for example an indirect air cooler, in which the air, for example compressed charge air for an internal combustion engine, is cooled, for example, by means of a fluid, wherein the heat exchanger is constructed from stacked pairs of plates with fins arranged therebetween, and the stack is arranged in a housing to which the air flows, flows through the fins and flows out, wherein said air is cooled by the fluid flowing in the plate pairs, which fluid is conducted into the plate pairs via at least one inlet and conducted away via at least one outlet, wherein the inlet and the outlet are located at a common edge of the plates and the air flows through the fins approximately in the direction of this edge.
  • the air for example compressed charge air for an internal combustion engine
  • Charge air coolers which are installed in motor vehicles and serve to cool the charge air by means of a cooling fluid are often referred to as indirect air coolers, in contrast to direct air coolers, a term used when the exemplary charge air is cooled with ambient air which is conveyed through the cooler by means of a fan.
  • the cooling fluid used is cooled directly by means of cooling air and is then used for cooling the engine as well as for other cooling purposes, and recently also to a greater extent for (indirect) charge air cooling.
  • the object of the invention is to construct the described heat exchanger with simple structural features, that is to say features which are also manufacture-friendly, in such a way that said heat exchanger provides a relatively high level of efficiency.
  • This object is met by a heat exchanger and a method of cooling a flow of heated air according to claims 1 and 9 respectively.
  • Advantageous embodiments of the invention are defined in claims 2-8 and 10-13.
  • the fluid can be conducted in an inlet region and/or outlet region of the plate pairs in at least one flow path approximately parallel to the air flow direction and/or of the common edge, flows further through at least a first duct approximately in cross current with respect to the air, and passes through the plate pairs over the largest heat exchange area of the plate pairs, substantially approximately in countercurrent with respect to the air, in order to flow through at least one second duct, approximately in cross current, back to the outlet.
  • the preferred fluid flows approximately in the direction of the air.
  • the lengths of the flow paths can be minimized by arrangement of the inlets and outlets at the corners of the plates. According to the present invention the entire mass flow of the fluid does not pass over the entire length of the ducts but instead a considerable portion thereof does. Shortly after the entry of the fluid into the at least one first duct, a partial flow already flows through the plate pairs in countercurrent with respect to the air via corrugated internal fins. The same applies to the at least one second duct which leads to the outlet-side flow path.
  • the ducts have a relatively low flow resistance so that the regions of the plates which are remote from the outlet are also sufficiently involved in the exchange of heat.
  • the cross-sectional geometry of the ducts can be of corresponding design so that sufficient involvement is achieved.
  • the corrugated internal fins can be embodied as lanced and offset fins, such as are used, for example, in the field of oil cooling and elsewhere.
  • parts of the corrugation edges are arranged offset alternately to the right and to the left. Breakthroughs or cutouts are present between the offset parts. They permit a throughflow in the longitudinal direction. If this direction is blocked, a throughflow in the lateral direction is also possible.
  • the longitudinal direction is parallel to the direction of the corrugation edges here.
  • the internal fins in the plate pairs have a significantly smaller pressure loss than in the lateral direction when throughflow occurs in the longitudinal direction.
  • the direction in which the corrugations of the corrugated internal fins run is preferably provided transversely with respect to the longitudinal direction of the plates so that the fluid can flow in the longitudinal direction with relatively little resistance along the offset corrugation edges.
  • a significantly larger flow resistance is present in the direction in which the corrugations run, a direction which, as mentioned above, is located transversely with respect to the direction of the corrugation edges because the fluid must flow through the numerous breakthroughs or cutouts in the corrugation edges and in the process also experiences numerous changes in the direction of flow.
  • Approximately the entire mass flow flows through one flow path which is formed near to the inlet and the outlet by means of a flow barrier. In the flow path, the fluid flows in countercurrent with exemplary air since the flow barrier is arranged approximately parallel to the lateral edges.
  • the flow barrier is also located relatively close to the one lateral edge of the plate pairs, which is referred to above as the common edge. At the ends of the flow barrier located opposite there is a hydraulic connection to the ducts. At the other lateral edge of the plate pairs there is preferably no such flow path or duct so that the fluid cannot escape or is forced to take the path through the internal fin which has greater pressure loss and is located in countercurrent with respect to the airflow.
  • the inlet 4 and the outlet 5 are located at the right-hand edges of metallic plates 1, which therefore represent the "common" edges E here.
  • the inlet 4 is arranged at the end remote from the air inflow side AAir of the heat exchanger.
  • the outlet 5 is, on the other hand, located closer to the inflow side of the charge air which is indicated by three block arrows.
  • the inlet and outlet connectors have the reference symbols 40 and 50.
  • the inlet and outlet cross sections have a circular shape in these embodiments.
  • a mixture of charge air and exhaust gas or pure exhaust of an internal combustion engine (not shown) can also be present.
  • edges E are the lateral edges of the plates 1.
  • Two parallel longitudinal edges of the plates 1 are located approximately perpendicularly on the lateral edges, wherein the terms are used merely to differentiate between the edges, but do not in any case mean that the longitudinal edges, as shown in the exemplary embodiment, are longer than the lateral edges.
  • the edges can all have the same length.
  • the lateral edges can also be longer than the longitudinal edges.
  • the fact that the edges in the exemplary embodiment shown are straight and therefore approximately rectangular plates 1 are present is also not an important precondition for solving the stated problem.
  • the edges can also be arcuate or embodied in some other way which deviates from a straight line.
  • the plates 1 have a cutout 8 at the common edge E which is the right-hand lateral edge in fig. 1 .
  • the depth of the cutout 8 is somewhat smaller than the depth of the inlet and outlet region 10.
  • the position of the inlets and outlets 4, 5 is situated approximately in the center between the central longitudinal axis 15 of the plates 1 and their longitudinal edges.
  • the inlet-side flow paths 11 extend from the inlets to the first ducts 12, which are arranged in the inner edge region of the one longitudinal edge in the plate pairs 1a, 1b. In the inner edge region of the other longitudinal edge there is the at least one second duct 13 which leads to the outlet-side flow path 11 and further to the outlet 5.
  • the ducts 12, 13 have the same cross section throughout.
  • the ducts 12, 13 have a low flow resistance, that is to say at least a partial cross section of the ducts 12, 13 does not have flow impediments or the like. Since, as mentioned, approximately rectangular plates are present in the exemplary embodiment shown, the flow paths 11 and the ducts 12, 13 are also located approximately perpendicularly with respect to one another.
  • the inlets and outlets 4, 5 are also arranged at a common edge E but in the vicinity of the corners of the plates 1 here, with the result that the lengths of the flow paths 11 becomes virtually zero.
  • fluid can enter virtually directly into the first ducts 12 and virtually directly enter the outlets 5 from the second ducts 13.
  • the inlets 4 in the corners and merely to position the outlets 5 approximately as shown, or vice versa.
  • outlet-side flow paths 11 would be present in such embodiments while the length of the inlet-side flow paths 11 would approach zero, that is to say would be virtually invisible.
  • the designer therefore has multiple options available for adapting the heat exchanger to restrictions forced on him by the installation location, without having to accept a loss of power.
  • the flow paths 11 can be implemented by construction of beads in the plates 1 forming the pairs, as is apparent from the illustrations according to figs. 4 and 5 .
  • beads which are inserted and soldered in the plate pairs can also be provided.
  • the beads or the rods form the flow barriers 6 mentioned above.
  • the plate 1b shown in figure 5 is rotated through 180° about its longitudinal axis 15 and is positioned on the plate 1a in fig. 4 .
  • the two beads come to bear one against the other in the plate pair 1a, 1b and are connected later. They accordingly have a height which is approximately half as large as the distance between the two plates 1 which form the plate pair 1a, 1b.
  • the height of the internal fin 14 must correspond to this distance.
  • the plates 1a and 1b come to bear one against the other with their edges and are connected to one another in a sealed fashion. In the exemplary embodiment they are bent-over edges.
  • the inlet and outlet openings 4, 5 of the plate pair 1a, 1b are provided with collars 41, 51 which protrude upward at the upper plate 1a and downward at the lower plate 1b.
  • the connection to the adjacent plate pairs 1a, 1b takes place at these collars.
  • Sealing rings which are located between the plate pairs and connect the latter are also an alternative to such collars 41, 51.
  • one of the plates 1 has a bead whose height has to be correspondingly larger, that is to say which should correspond to the height of the internal fin 14.
  • the entire stack that is to say the plate pairs and the fins 2 located therebetween, are connected to one another, preferably connected metallically, for example soldered in a soldering oven.
  • the soldered-in internal fin 14 through which the fluid flows is located within each plate pair 1a, 1b.
  • the aforementioned internal fin 14 can have a smaller dimension than the plate 1 in which it is inserted owing to construction of the ducts 12, 13, the position of the internal fin 14 is indeterminate, which is disadvantageous.
  • a correct position of the internal fin 14 within the plate 1 can be implemented by virtue of the fact that inwardly protruding knobs or similar shaped elements 16 are formed in the corners of the plates 1 and serve as a stop for the internal fin 14.
  • the preassembly of the heat exchanger improves. With this measure it is also possible to prevent an undesired bypass for the fluid, or at least largely suppress it. However, in some embodiments such a bypass may be desirable, as described in greater detail hereafter.
  • the inlet and outlet region which has already been mentioned is provided with the reference symbol 10. It makes up approximately 12% of the entire heat-exchanging area here. Since this region for exchanging heat cannot contribute very much, the aim is to make it as small as possible.
  • two arrows indicate that the corrugated internal fin 14 is preferably inserted into the plate pair 1a, 1b in such a way that when there is a flow through them in the longitudinal direction a significantly lower pressure loss dp occurs than when there is a throughflow in the lateral direction.
  • the fluid is forced by the special design to take the path in the lateral direction and accordingly to flow though the plate pairs 1a, 1b in countercurrent with respect to the direction of the flow of air.
  • the heat exchanger thereby provides multiple cooling fluid flow paths extending hydraulically in parallel with one another between the inlet 4 for the cooling fluid and the outlet 5 for the cooling fluid, with each one of the multiple cooling fluid flow paths extending through one of the plate pairs 1a, 1b.
  • Each such cooling fluid flow path includes a first portion 12 extending between one of the internal fins 14 and a longitudinal edge of the pair, and a second portion 13 extending between that one of the internal fins 14 and the opposing longitudinal edge of the plate pair.
  • a third portion of the cooling fluid flow path extends through the internal fin in the high pressure drop direction to provide fluid communication between the first portion 12 and the second portion 13.
  • the direction of the cooling fluid flow along that third portion of the cooling fluid flow path is counter to the direction of the heated air flow.
  • the cooling fluid flow path also includes a portion 11 located within the inlet and outlet region and extending from the inlet 4 for the cooling fluid to the first portion 12, as well as another portion 11 located within the inlet and outlet region and extending from the second portion 13 to the outlet 5 for the cooling fluid.
  • Fig. 6 shows, in a section, a perspective view of the corrugated internal fin 14 which is located in the plate 1. Some details of the corrugated internal fin 14 can be seen.
  • the direction in which the corrugation runs in the heat exchanger is the lateral direction thereof, that is to say the direction of the significantly higher pressure loss dp.
  • In the corrugation edges 17 there are breakthroughs or cutouts 18 offset alternately to the left and to the right when viewed in the direction of said corrugation edge 17.
  • the width of the ducts 12, 13 is determined by the distal end of the flow barrier 6 and the longitudinal edge of the plate. As is also shown by Fig. 6 , a narrow strip of the duct 12 is completely free.
  • the entire duct 12, 13 is of free design.
  • the longitudinal edge of the internal fin 14 extends directly to the longitudinal edge of the plates 1, with the result that the entire duct cross section is occupied by a section of the internal fin 14.
  • the function of the ducts 12, 13 is retained because the aforementioned section points in the direction of the low pressure loss dp which corresponds to the direction of the duct.
  • the compressed charge air AAir to be cooled flows through an opening into a housing 3 in which the aforementioned stack made of plate pairs 1a, 1b and fins 2 (not illustrated in more detail) are located ( Fig. 7 ).
  • the housing 3 can be the intake manifold of an internal combustion engine.
  • the charge air then flows through the corrugated fins 2 in countercurrent with respect to the fluid flowing in the plate pairs, and in the process it is cooled extremely efficiently.
  • the direction of flow of the charge air is, also according to the proposal, provided in the direction of the common edge E at which the inlet 4 and the outlet 5 for the fluid are located, or in the exemplary embodiment in the direction of the lateral edges of the plates 1.
  • the cooled charge air leaves the heat exchanger through another opening in the housing 3 in order to be available for charging the internal combustion engine (not shown).
  • the protruding edge 9.1, of the cover plate 9 which can be seen in Fig. 2 and which terminates the stack and is connected metallically thereto, for example, can be used in a known fashion to attach the plate stack in the housing 3 and therefore serves as a closure of an assembly opening in the housing 3.
  • Fig. 8 shows a plate 1 with elongate holes as inlets and outlets 4, 5.
  • the flow paths 11 have been virtually integrated into the elongate holes since there to a certain extent a flow guide is formed in the direction of the common edge E, as is also the case with the flow paths of the other exemplary embodiments.
  • the inlets and outlet 4, 5 have other different hole shapes. These may also include hole shapes which are configured asymmetrically.
  • Fig. 9 in turn shows round plate holes 4, 5 but modified flow barriers 6.
  • Figs. 10A-10D show several variations of a plate 1 of the invention, wherein a bypass channel 21 is incorporated into each one of the plate pairs 1a, 1b.
  • the bypass 21 allows a portion of the cooling fluid passing through the plate pair 1a, 1b between the cooling fluid inlet 4 and the cooling fluid outlet 5 to bypass the corrugated internal fin 14 along a lateral edge of the plates 1.
  • a flow barrier 18 is provided in order to provide a fluid separation between the heat transfer region, characterized for example by the corrugated internal fin 14, and the bypass channel 21.
  • the flow barrier 18 can be constructed in a similar fashion as the flow barrier 6, such as by beads formed into the plates 1.
  • the cooling fluid flow path through the plate pair 1a, 1b is thereby modified to add a fourth portion (characterized by the bypass channel 21) arranged between the internal fin 14 and a lateral edge of the plates 1.
  • the fourth portion 21 is fluidly connected to the first portion 12 of the cooling fluid flow path, so that the cooling fluid flowing along the cooling fluid flow path is directed through either the third portion or the fourth portion.
  • Heat transfer between the charge air and that portion of the cooling fluid which passes through the bypass channel 21 is intentionally inhibited, for example through the absence of any heat transfer enhancing features within the bypass channel 21, so that the portion of the cooling fluid passing through the bypass channel 21 is essentially unchanged in temperature.
  • the transfer of heat between the charge air and the portion of the cooling fluid passing through the bypass channel 21 can be inhibited by blocking or impeding the flow of charge air through those portion of the air flow passages directly adjacent the bypass channel 21, for example by way of formed features of the edges of the plates 1.
  • the bypass section 21 thereby allows a portion of the cooling fluid to bypass the heat exchange section of the plate pair 1a, 1b, characterized by that section of the plate pair that is occupied by the corrugated internal fin 14.
  • the bypass channel 21 can be fluidly connected to the channel 13 so that the portion of the cooling fluid passing through the bypass channel 21 can discharge directly into the channel 13.
  • the momentum of the cooling fluid passing through the bypass channel 21 will cause it to be directed towards the longitudinal plate edge of the channel 13.
  • This has the beneficial effect of allowing the relatively unheated cooling fluid to cool the leading edges of the plates 1 onto which the heated charge air directly impinges.
  • the inventors have found that such a cooling effect helps to reduce the metal temperature of these leading plate edges, thereby avoiding an undesirable boiling of the cooling fluid which might otherwise result.
  • the channel 13 is divided into a first portion 13a and a second portion 13b by another flow barrier 19.
  • the flow barrier 19 can be, but need not necessarily be, joined to the flow barrier 18.
  • the flow barrier 19 maintains the separation within the flow channel 13 of the portion of the cooling fluid that passed through the bypass channel 21 and the portion of the cooling fluid that passed through the heat exchange section 14. As a result, the cooling effect on the leading edges of the plates 1 can be enhanced, and the risk of cooling fluid boiling can be further reduced.
  • the flow channel portion 13b thereby defines a fifth portion of the cooling fluid flow channels that is connected in series to the fourth portion defined by the bypass channel 21.
  • Figs. 10C and 10D depict variations of the plates 1 of Figs. 10A and 10B , respectively.
  • the corrugated internal fin 14 defining the heat exchange section of the plate pair has been replaced by a successively arranged series of flow passages 22 through which that portion of the cooling fluid flow that is not directed through the bypass channel 21 is directed.
  • the series of flow passages 22 together constitute a heat exchange section 14' of the plate pair.
  • Each of the flow passages 22 extend in a direction that is parallel to the longitudinal edges of the plates 1 between the flow barrier 6 and the flow barrier 18.
  • the cooling fluid is directed through the series of flow passages 22 in a counter-cross-flow direction to the flow of heated air through the heat exchanger.
  • Additional flow barriers 23 are arranged between adjacent ones of the flow channels 22 in order to define the flow channels 22, with the flow barriers 23 alternatingly extending from the flow barrier 6 and from the flow barrier 18.
  • One of those flow barriers 23 also serves to separate the initial one of the flow passages 22 from the duct 12, while another one of those flow barriers 23 also serves to separate the terminal one of the flow passages 22 from the duct 13.
  • a heat exchanger built using the plates 1 as described in Figs. 10A-D can be particular desirable for cooling a flow of heated air (such as for example compressed charge air for an internal combustion engine) using a flow of liquid cooling fluid with high heat exchange efficiency without the increased risk of causing undesirable boiling of the cooling fluid.
  • a flow of heated air Aair for example, compressed charge air for an internal combustion engine
  • a flow of cooling fluid is directed into the heat exchanger and is distributed among the plate pairs 1a, 1b of the heat exchanger through coolant inlets 4 of the plate pairs.
  • the cooling fluid is first directed through a first duct 12 in a direction that is perpendicular to the air flow direction.
  • a first portion of the cooling fluid is then directed from the first duct 12 through a heat exchange section 14, 14'.
  • the cooling fluid is directed in a direction that is overall counter to the air flow direction, such as in a counter-flow or a cross-counter-flow direction. Heat is transferred from the flow of heated air to that first portion of the cooling fluid as it flows through the heat exchange section 14, 14'.
  • a second portion of the cooling fluid is directed from the first duct 12 through a bypass section 21 of the plate pair, also in a direction that is counter to the air flow direction.
  • the transfer of heat between the flow of heated air and the second portion of the cooling fluid is inhibited within the bypass section, so that the second portion of the cooling fluid exits the bypass section at a lower temperature than the first portion exits the heat exchange section.
  • the first and the second portions are subsequently directed through a second duct 13 in a direction that is again perpendicular to the air flow direction.
  • the second duct 13 is a single duct through which the first portion of the cooing fluid and the second portion of the cooling fluid both flow. In such an embodiment, some mixing of the first and second portions of the cooling fluid can occur within the second duct 13. In other embodiments, such as for example ones using plates 1 as are depicted in Fig. 10B and Fig. 10D , the first portion of the cooling fluid and the second portion of the cooling fluid are separated within the second duct 13 and mixing of the two portions within that duct 13 is prevented.
  • the first portion of the cooling fluid can be directed through a portion 13a of the second duct 13 while the second portion of the cooling fluid can be directed through a portion 13b of the second duct 13.
  • the portion 13b can advantageously be arranged to be upstream of the portion 13b with respect to the direction of the heated air flow through the heat exchanger, so that the portion of the flow of cooling fluid that passed through the bypass duct 21 (and which is, consequently, at a lower temperature) can sufficiently depress the temperature of the plates surfaces that are directly impacted by the hottest air in order to prevent any boiling of the cooling fluid.

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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)

Claims (13)

  1. Échangeur de chaleur, comprenant :
    une pluralité de paires de plaques empilées (1a, 1b) ayant des passages d'écoulement d'air agencés entre des paires adjacentes de la pluralité de paires de plaques empilées (1a, 1b), les passages d'écoulement d'air s'étendant entre un ensemble de premiers bords longitudinaux des paires de plaques empilées (1a, 1b) et un ensemble opposé de seconds bords longitudinaux des paires de plaques empilées (1a, 1b) pour définir une direction d'écoulement d'air à travers l'échangeur de chaleur perpendiculaire aux premiers et seconds bords longitudinaux ;
    une région d'entrée et de sortie (10) pour fluide de refroidissement, chacune de la pluralité de paires de plaques empilées (1a, 1b) ayant une entrée (4) pour fluide de refroidissement et une sortie (5) pour fluide de refroidissement agencées à l'intérieur de la région d'entrée et de sortie (10) et alignées avec la direction d'écoulement d'air ;
    une pluralité d'ailettes internes ondulées, chacune étant située à l'intérieur d'une de la pluralité de paires de plaques empilées (1a, 1b) et ayant une direction de chute de basse pression alignée avec la direction des bords longitudinaux et une direction de chute de haute pression alignée avec la direction d'écoulement d'air ;
    une pluralité de barrières d'écoulement comprenant une pluralité de premières barrières d'écoulement (6) construites par des nervures des paires de plaques (1a, 1b), ladite pluralité de premières barrières d'écoulement (6) étant agencées entre la région d'entrée et de sortie (10) pour le fluide de refroidissement et la pluralité d'ailettes internes ondulées ; et
    une pluralité de chemins d'écoulement de fluide de refroidissement (11), chacun des chemins d'écoulement de fluide de refroidissement (11) s'étendant à travers une de la pluralité de paires de plaques empilées (1a, 1b) entre l'entrée (4) pour fluide de refroidissement et la sortie (5) pour fluide de refroidissement et incluant une première partie s'étendant entre une de la pluralité d'ailettes internes ondulées (14) et un de l'ensemble de premiers bords longitudinaux, une deuxième partie s'étendant entre celle-ci de la pluralité d'ailettes internes ondulées (14) et un de l'ensemble de seconds bords longitudinaux, et une troisième partie s'étendant à travers celle-ci de la pluralité d'ailettes internes ondulées (14) dans la direction de chute de haute pression pour fournir une communication fluidique entre la première partie et la deuxième partie, dans lequel la direction d'écoulement de fluide de refroidissement le long de la troisième partie est contraire à la direction d'écoulement d'air,
    caractérisé en ce que
    chacun des chemins d'écoulement de fluide de refroidissement (11) inclut en outre une quatrième partie agencée entre celle-ci de la pluralité d'ailettes internes ondulées (14) et un bord latéral des paires de plaques (1a, 1b) perpendiculaire aux bords longitudinaux des paires de plaques (1a, 1b), la quatrième partie étant raccordée de façon fluidique à la première partie de telle sorte qu'un fluide de refroidissement orienté le long du chemin d'écoulement de fluide de refroidissement (11) s'écoule à travers la troisième partie ou la quatrième partie et que la pluralité de barrières d'écoulement comprenant en outre une deuxième pluralité de barrières d'écoulement (18) construites par des nervures des paires de plaques (1a, 1b), la deuxième pluralité de barrières d'écoulement (18) bornant au moins partiellement les quatrièmes parties de la pluralité de chemins d'écoulement de fluide de refroidissement (11).
  2. Échangeur de chaleur selon la revendication 1, dans lequel chacun des chemins d'écoulement de fluide de refroidissement (11) inclut en outre une quatrième partie située à l'intérieur de la région d'entrée et de sortie (10) et s'étendant depuis l'entrée (4) pour fluide de refroidissement et la première partie, et une cinquième partie située à l'intérieur de la région d'entrée et de sortie (10) et s'étendant depuis la deuxième partie jusqu'à la sortie (5).
  3. Échangeur de chaleur selon la revendication 1, dans lequel la région d'entrée et de sortie (10) pour fluide de refroidissement est au moins partiellement bornée par des bord latéraux des paires de plaques (1a, 1b) perpendiculaires aux bords longitudinaux des paires de plaques (1a, 1b).
  4. Échangeur de chaleur selon la revendication 1, dans lequel chacune de la pluralité d'ailettes internes ondulées (14) est agencée entre une de la première pluralité de barrières d'écoulement (6) et une de la deuxième pluralité de barrières d'écoulement (18).
  5. Échangeur de chaleur selon la revendication 1, dans lequel chacun des chemins d'écoulement de fluide de refroidissement (11) inclut en outre une cinquième partie raccordée de façon fluidique à la quatrième partie pour recevoir un écoulement à partir de celle-ci, la cinquième partie étant agencée entre la deuxième partie et un de l'ensemble de seconds bords longitudinaux.
  6. Échangeur de chaleur selon la revendication 5, comprenant en outre une troisième pluralité de barrières d'écoulement (23) construites par des nervures des paires de plaques (1a, 1b), les deuxièmes parties des chemins d'écoulement de fluide de refroidissement (11) étant séparées des quatrièmes parties des chemins d'écoulement de fluide de refroidissement (11) par la troisième pluralité de barrières d'écoulement (23).
  7. Échangeur de chaleur selon la revendication 6, dans lequel chacune de la deuxième pluralité de barrières d'écoulement (18) est jointe à une de la troisième pluralité de barrières d'écoulement (23).
  8. Échangeur de chaleur selon la revendication 1, dans lequel la quatrième partie est raccordée de façon fluidique à la deuxième partie.
  9. Procédé de refroidissement d'un écoulement d'air chauffé, comprenant :
    l'orientation d'un écoulement d'air chauffé à travers des passages d'écoulement d'air d'un échangeur de chaleur dans une direction d'écoulement d'air ;
    l'orientation d'un écoulement de fluide de refroidissement dans l'échangeur de chaleur et la distribution de l'écoulement de fluide de refroidissement parmi des paires de plaques (1a, 1b) de l'échangeur de chaleur à travers des entrées de fluide de refroidissement des paires de plaques (1a, 1b), les passages d'écoulement d'air étant agencés entre des paires adjacentes des paires de plaques (1a, 1b) ;
    à l'intérieur de chacune des paires de plaques (1a, 1b), l'orientation du fluide de refroidissement à travers une première conduite (12) dans une direction perpendiculaire à la direction d'écoulement d'air ;
    à l'intérieur de chacune des paires de plaques (1a, 1b), l'orientation d'une première partie du fluide de refroidissement à partir de la première conduite (12) à travers une section d'échange de chaleur de la paire de plaques (1a, 1b) (1a, 1b) dans une direction contraire à la direction d'écoulement d'air ;
    le transfert de chaleur à partir de l'écoulement d'air chauffé à la première partie du fluide de refroidissement lorsque la première partie du fluide de refroidissement s'écoule à travers la section d'échange de chaleur de la paire de plaques ;
    à l'intérieur de chacune des paires de plaques (1a, 1b), l'orientation d'une deuxième partie du fluide de refroidissement à partir de la première conduite (12) à travers une section de dérivation (21) de la paire de plaques (1a, 1b) (1a, 1b) dans une direction contraire à la direction d'écoulement d'air, le transfert de chaleur entre l'écoulement d'air chauffé et la deuxième partie du fluide de refroidissement étant empêché à l'intérieur de la section de dérivation (21) pour que la deuxième partie du fluide de refroidissement sorte de la section de dérivation (21) à une température inférieure à celle à laquelle la première partie du fluide de refroidissement sort de la section d'échange de chaleur ;
    à l'intérieur de chacune des paires de plaques (1a, 1b), l'orientation de la première partie du fluide de refroidissement à travers une seconde conduite (13) dans une direction perpendiculaire à la direction d'écoulement d'air après l'orientation de la première partie du fluide de refroidissement à travers la section d'échange de chaleur de la paire de plaques ;
    à l'intérieur de chacune des paires de plaques (1a, 1b), l'orientation de la deuxième partie du fluide de refroidissement à travers la seconde conduite (13) dans une direction perpendiculaire à la direction d'écoulement d'air après l'orientation de la deuxième partie du fluide de refroidissement à travers la section de dérivation (21) de la paire de plaques ; et
    l'élimination de l'écoulement de fluide de refroidissement à partir de l'échangeur de chaleur à travers des sorties de fluide de refroidissement des paires de plaques (1a, 1b).
  10. Procédé selon la revendication 9, dans lequel les étapes de l'orientation de la première partie du fluide de refroidissement à travers la seconde conduite (13) et l'orientation de la deuxième partie du fluide de refroidissement à travers la seconde conduite (13) inclut l'agencement de la deuxième partie en amont de la première partie par rapport à la direction d'écoulement d'air.
  11. Procédé selon la revendication 9, dans lequel le mélangeage de la première partie de l'écoulement de fluide de refroidissement avec la deuxième partie de l'écoulement de refroidissement à l'intérieur de la seconde conduite (13) est empêché.
  12. Procédé selon la revendication 9, dans lequel l'orientation de la première partie de l'écoulement de fluide de refroidissement à travers une section d'échange de chaleur de la paire de plaques (1a, 1b) (1a, 1b) inclut le passage de la première partie de l'écoulement de fluide de refroidissement à travers une ailette interne ondulée (14) agencée à l'intérieur de la paire de plaques.
  13. Procédé selon la revendication 9, dans lequel l'orientation de la première partie de l'écoulement de fluide de refroidissement à travers une section d'échange de chaleur de la paire de plaques (1a, 1b) inclut le passage de la première partie de l'écoulement de fluide de refroidissement à travers une série successivement agencée de passages d'écoulement (22), chacun de la série successivement agencée de passages d'écoulement (22) s'étendant dans une direction perpendiculaire à la direction d'écoulement d'air.
EP18211108.8A 2018-01-26 2018-12-07 Échangeur de chaleur et procédé de refroidissement d'un flux d'air chauffé Active EP3517873B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US15/880,624 US10690421B2 (en) 2012-03-28 2018-01-26 Heat exchanger and method of cooling a flow of heated air

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EP3517873A1 EP3517873A1 (fr) 2019-07-31
EP3517873B1 true EP3517873B1 (fr) 2021-07-21

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US6016864A (en) * 1996-04-19 2000-01-25 Heatcraft Inc. Heat exchanger with relatively flat fluid conduits
DE19646349B4 (de) * 1996-11-09 2011-08-11 Behr GmbH & Co. KG, 70469 Verdampfer und damit ausgerüstete Fahrzeugklimaanlage
AT404877B (de) 1997-05-30 1999-03-25 Wagner Wilfried Gegenstrom-plattenwärmetauscher
EP1626238B1 (fr) * 2004-08-14 2006-12-20 Modine Manufacturing Company Echangeur de chaleur avec tubes plats
DE102006005106A1 (de) * 2006-02-04 2007-08-09 Modine Manufacturing Co., Racine Wärmetauscher mit einer Anschlussplatte, insbesondere Ladeluftkühler
DE102006048667A1 (de) 2006-10-14 2008-04-17 Modine Manufacturing Co., Racine Wärmeübertrageranordnung und Verfahren zur Wärmeübertragung
US7610949B2 (en) * 2006-11-13 2009-11-03 Dana Canada Corporation Heat exchanger with bypass
FR2977309B1 (fr) * 2011-06-30 2017-12-29 Valeo Systemes Thermiques Lame d'echangeur de chaleur a zone de contournement
DE102012006346B4 (de) * 2012-03-28 2014-09-18 Modine Manufacturing Co. Wärmetauscher
DE102012008700A1 (de) * 2012-04-28 2013-10-31 Modine Manufacturing Co. Wärmetauscher mit einem Kühlerblock und Herstellungsverfahren
US9234707B2 (en) * 2012-09-21 2016-01-12 The Boeing Company Heat exchanger systems and methods for controlling airflow cooling
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CN110081743A (zh) 2019-08-02
EP3517873A1 (fr) 2019-07-31
CN110081743B (zh) 2021-05-18

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