EP3824240A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur

Info

Publication number
EP3824240A1
EP3824240A1 EP19734679.4A EP19734679A EP3824240A1 EP 3824240 A1 EP3824240 A1 EP 3824240A1 EP 19734679 A EP19734679 A EP 19734679A EP 3824240 A1 EP3824240 A1 EP 3824240A1
Authority
EP
European Patent Office
Prior art keywords
slots
heat exchanger
exchanger according
ribs
cooling tubes
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.)
Granted
Application number
EP19734679.4A
Other languages
German (de)
English (en)
Other versions
EP3824240B1 (fr
Inventor
Andreas SCHLIEPER
Frank KORNETZKY
Sentuerk ORUC
Matthias Klein-Lassek
Dietmar Krauss
Martin Lohbreyer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kelvion Machine Cooling Systems GmbH
Original Assignee
Kelvion Machine Cooling Systems GmbH
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 Kelvion Machine Cooling Systems GmbH filed Critical Kelvion Machine Cooling Systems GmbH
Publication of EP3824240A1 publication Critical patent/EP3824240A1/fr
Application granted granted Critical
Publication of EP3824240B1 publication Critical patent/EP3824240B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements

Definitions

  • the invention relates to a heat exchanger with the features of patent claim 1.
  • Hot gas coolers for cooling gases come as hot gas coolers e.g. in the form of exhaust gas recoolers or charge air coolers.
  • Hot gas coolers allow a mixture of recirculating exhaust gases with combustion gases at the lowest possible temperature for engines with medium or low speed. Hot gas coolers are therefore a crucial element of exhaust gas recirculation systems in order to meet the applicable emission guidelines.
  • exhaust gases can be cooled down from over 700 ° C to 50 ° C. The thermal load on such hot gas coolers is very high. High thermal stresses arise in the components of the exhaust gas flow.
  • Rib arrangements where the stiffness is too high can cause fatigue fractures on the cooling tubes, especially in the transition to the tube sheet. It was therefore proposed in DE 10 2012 217 323 A1 that a rib has an expansion bead for tension compensation and that the material thickness is additionally reduced in the area of the expansion bead or a slot is introduced for tension compensation.
  • the production of expansion beads in combination with the reduction in material thickness or the additional introduction of slots in the area of the expansion bead is technically comparatively complex.
  • the object of the invention is to demonstrate a heat exchanger which, even with very high temperature gradients, has lower stress loads in the cooling tubes and in which the fatigue strength is consequently improved.
  • the heat exchanger according to the invention for cooling hot gases is, in particular, an exhaust gas recooler or a charge air cooler. It has a gas inlet and a gas outlet at a distance from the gas inlet. Several cooling tubes are arranged between the gas inlet and the gas outlet. They extend transversely to the direction of flow of the gas.
  • the cooling medium is especially water.
  • the cooling tubes are surrounded by fins.
  • the ribs can also be called lamellae.
  • a fin has a plurality of openings, so that a plurality of cooling tubes are guided through a fin or lamella at the same time. It is therefore not a question of individual ribbing on the individual cooling tubes, but rather a package. Such a package preferably extends over almost the entire flow cross-section of the heat exchanger.
  • the ribs have slots in the invention. These slots are used to compensate for thermal stresses and to homogenize the gas flow.
  • the gas flow flows through the slots.
  • the slots are located at a distance from the openings in which the cooling tubes are located.
  • a special arrangement of the slots is used: the slots are arranged in a honeycomb shape. This means that several slots in hexagonal arrangement each surround an opening or a cooling tube. A hexagon surrounds an opening. The slots follow the edge of the hexagon, so that the slots are preferably straight.
  • the invention does not rule out an odd slot course, provided that the arrangement remains hexagonal overall and not e.g. is circular.
  • the ends of slots at one corner of the hexagon are therefore at an angle to each other.
  • the hexagon is in particular equilateral and equiangular as in a regular hexagon.
  • Each slot ends at a deformation point on the rib.
  • This deformation point is located on the corner of the hexagon.
  • This deformation point is special compared to designs in which there are openings in the ribs.
  • the deformation area has the positive effect that the rigidity of the rib is reduced and which allows plastic deformation at high (thermal) loads.
  • the creation A deformation point within the rib enables the flexible point to be plastically deformed in an emergency, ie when there is a high point load. However, this does not lead to continuous deformations within the entire fin and does not lead to functional impairments of other parts of the heat exchanger. This reduction in stiffness results in lower thermally induced stresses in the cooling pipes.
  • the width of the slots is greater than the minimum width of the deformation point.
  • the deformation points should therefore be relatively narrow.
  • the width of the slots depends on the desired mixing of the gas flow above and below the slots. It is not provided that the slots are arranged in the area of a bead of the ribs.
  • the fin itself is essentially flat, apart from collars or passages for the cooling tubes to rest on the fin. The slits already influence the flow and minimize stresses induced by thermal expansion on the openings or pipes. In this context, "even” means that the rib is not corrugated or corrugated.
  • a rib can have individual embossings.
  • the slots are preferably outside of the embossments. Individual embossments can improve flow guidance. Slots outside of the embossing are easier to manufacture.
  • the slots are not covered by exposures of the rib as they occur when the punched-out part for making the slot is attached to one side of the slot or to at least one end of the slot. The aim is for the ribs to have a very high elongation at break. In particular, it should be above 25%.
  • a single slot is arranged between two adjacent openings. This slot is at the same distance from the neighboring openings.
  • the invention also encompasses that the single slot between two adjacent openings has constrictions, constrictions or interruptions, so that a plurality of shorter slots, which follow one another in their longitudinal directions, functionally form the single, longer slot which extends between two adjacent openings. It is not the number of slots that is important, but the honeycomb arrangement along the edge of a hexagon.
  • the cooling tubes of two successive rows of tubes are arranged offset to the direction of flow of the gas. If all the slots are the same length, the result is a constant, repeating, hexagonal or honeycomb pattern within a rib.
  • the opening for the cooling tube is the center of such a hexagon or honeycomb.
  • the deformation point is the center of a star-shaped arrangement of three slots. In this sense, the deformation point is also star-shaped.
  • the slots are preferably rounded at the ends, in particular completely rounded.
  • the diameter of the curve preferably corresponds to the width of the slots.
  • each slot in the preferred honeycomb shape extends over an angle of somewhat less than 60 ° with respect to the adjacent opening.
  • hexagon or honeycomb shape in the context of the patent application should not be understood to mean that all sides of the hexagon must be of the same length or at the same angle to one another. It is possible within the scope of the invention that the opposing slots are of equal length, wherein a pair of the opposing slots has a different length than the other two pairs of opposing slots. Such an arrangement of hexagons, which are somewhat elongated, can result if the distance between the rows of pipes is not equal to the distance between the pipes within a row. In this case, the slots pointing from row of tubes to row of tubes are longer than the other pairs of slots. If the rows of pipes are smaller than the distance between the pipes within a row, the slots that point from row of pipes to rows of pipes are somewhat shorter than the other two pairs of slots.
  • several groups of cooling tubes are arranged between the gas inlet and the gas outlet of the heat exchanger. At least one first group of cooling tubes adjacent to the gas inlet is penetrated by said ribs. A second and third group are preferably also penetrated by said cooling tubes.
  • the formation of groups enables the individual groups to be structurally adapted to the local thermal conditions.
  • the Groups are arranged close together. In three consecutive groups or stages, for example, three ribs follow one another and are spaced apart from one another. In particular, all groups of cooling tubes are provided with said fins.
  • a single group of cooling tubes comprises at least two rows of tubes which follow one another in the direction of flow of the gas.
  • the rows of pipes are staggered, so that the largest possible inflow area of the pipes.
  • the ribs have edge sides lying in the flow direction of the gas, at least one edge side being profiled like a sawtooth (approx. ⁇ 30 ° to the inflow surface in the preferred honeycomb shape).
  • the profiled course can correspond to the course of the slots.
  • the said ribs can be made from larger sheet metal plates. They are separated on the edges of the ribs. The separation process can take place in the area of the deformation points, so that very little material has to be processed for the separation. The effort to separate the ribs into smaller units is very low.
  • a recess can be provided on the edge sides to form a deformation point.
  • This deformation point is intended to cooperate with the respective slot which is adjacent to the at least one edge side. These are the slots that point in the direction of flow.
  • the recess reduces the areal expansion of the deformation point.
  • the highest point loads occur in the inflow area of the heat exchanger. Particularly low bending stiffness is an advantage here.
  • the cutouts should therefore remain intact and at the same time simplify assembly. Nevertheless, they have the function of being plastically deformed in an emergency without adversely affecting other areas of the fin or the cooling tube.
  • the slots it is possible, as it were, to round or smooth the sawtooth-like edge sides, so that there are no particularly sharp or pointed corners on the edge sides.
  • the slots it is possible for the slots to extend to the edge side, in particular on the inflow edge side, so that there are no deformation points at all on the edge side.
  • the slits leading to the edge are open.
  • the slits can even be a little wider at their mouth.
  • These widenings can be produced by removing the originally existing deformation points, for example by punching them out.
  • the punched-out area can be chosen somewhat larger than the area of the deformation point, so that there are no constrictions in the transition from the edge side to the width of the slot.
  • the punchings are therefore preferably larger in width or in diameter than the width of the slot.
  • the fins are preferably stacked and completely surround the cooling tube.
  • a collar arranged on the ribs serves as a spacer. The height of the collar determines the distance between adjacent ribs. The collar surrounds the openings.
  • the ribs are essentially flat.
  • the large number of slots, openings and the small deformation points mean that such ribs are relatively light, but at least lighter than ribs in which turbulators are exposed in the same direction or alternately.
  • the weight saving has a positive effect on the total weight of the heat exchanger.
  • Said ribs have a thickness of a few tenths of a millimeter.
  • the ribs are preferably thick less than 0.16 mm.
  • the thickness is preferably 0.10 mm to 0.15 mm. Due to the relatively small thickness, ribs of this type are also spoken of.
  • the diameters of the openings and thus of the cooling tubes are preferably in a range from 6 mm to 10 mm.
  • the openings preferably have a diameter of 7 to 8 mm.
  • the distance between adjacent tubes is approximately twice the diameter of the cooling tubes or the diameter of the opening.
  • the width of the slots is approximately 15% to 25% of the diameter of the openings.
  • the high proportion of openings and openings does not have a negative impact on the effectiveness of the heat transfer.
  • the configuration of the fins provides a heat exchanger with high fatigue strength.
  • Figure 1 shows a fin of a heat exchanger in plan view
  • Figure 2 shows the rib of Figure 1 in perspective
  • Figure 3 In an enlarged view a predetermined breaking area between three
  • Figure 4 is a perspective view of a heat exchanger insert for cooling hot gases
  • FIG. 1 The heat exchanger insert of Figure 4 partially in section
  • FIG. 6 The heat exchanger insert of FIG. 4, partly in section, in a further perspective view looking towards the hot gas inlet;
  • Figure 7 shows another embodiment of a fin of a heat exchanger in plan view
  • Figure 8 shows another embodiment of a fin of a heat exchanger in plan view
  • Figure 9 shows another embodiment of a fin of a heat exchanger in plan view.
  • FIG. 1 shows a fin 1 of a heat exchanger (not shown) for cooling gases.
  • FIG. 2 shows said rib 1 in a perspective view.
  • the fins 1 are assembled in a stacked arrangement (FIG. 6).
  • Circular openings 2 in the fins 1 accommodate the cooling tubes 13 (FIG. 5).
  • the openings 2 each have a collar 3 pointing downward in the image plane of FIG. 2.
  • the collar 3 simultaneously determines the distance between two successive, stacked ribs 1.
  • Several ribs 1 or fins arranged one above the other form one with the cooling tubes 13 arranged therein Group 14-17 ( Figure 4).
  • a single group 14-17 can also be referred to as a heat exchanger package.
  • the individual packages or groups 14-17 can be arranged at a distance from one another. According to the invention it is provided that at least one of these groups 14-17 of cooling tubes 13 in combination with the said fins 1 is arranged within the heat exchanger 10 according to the invention. In particular, it is the group 14 that is closest to the gas inlet 11 (FIG. 4).
  • the perspective view in FIG. 2 shows that the said rib 1 is flat apart from the collar 3. It is a rib 1 which is made from a sheet metal plate. Due to the use in heat exchangers 10 with an aggressive environment, the fins 1 are made of stainless steel.
  • the steel preferably has a high elasticity with a uniform thickness. It is preferably 0.12 mm.
  • a suitable one The material is X2CrTi12 with the material no. 1.4512.
  • the material has a tensile strength Rm of 380 to 560 N / mm 2.
  • the yield strength Rp02 is around 280 to 290 N / mm.
  • the elongation A 80% in practice reaches values over 25%. In particular, the elongation is 30% and in particular is over 34%.
  • Other common materials are 1.4404 (austenitic stainless steel) or 1.4521 (ferritic stainless steel).
  • the special feature of the structure of the heat exchanger 10 according to the invention is the geometry of the fins 1.
  • the fins 1 have slots 4 arranged regularly.
  • the slots 4 have the shape of elongated holes with completely rounded ends. All slots 4 are straight, of equal length and of uniform width. They are arranged in a polygonal shape, in this case hexagonal or honeycomb. The polygon described is an even hexagon.
  • the cooling tubes 13 or openings 2 are arranged one behind the other in rows R1, R2, R3.
  • the rows R1, R2, R3 etc. are each offset transversely to the previous row.
  • the slots 4 have a length L1.
  • the length L1 is slightly smaller than the diameter D1 of the circular opening 2.
  • the length L1 is 7.5 mm compared to the diameter D1 of 8 mm.
  • the width B1 of the slots 4 is 1.5 mm.
  • the ratio of length L1 to width B1 of the slots 4 is therefore 5: 1. All neighboring slots are at an angle W of 120 ° to each other.
  • the distance between the central longitudinal axis MLA of a slot 4 from a center M of an opening 2 is denoted by D2 in FIG. 1.
  • This distance D2 corresponds to the diameter D1 of the openings 2.
  • a slot 4 is always exactly in the middle between two of the openings 2. All openings 2 are located centrally in the individual honeycombs formed by the slots 4.
  • Figure 1 also shows that in the direction of flow (arrow P) of the gas lying edge sides 5, 6 are sawtooth-shaped.
  • a larger sheet metal plate was divided, specifically in the area of deformation points 7. These deformation points 7 are always delimited by a slot 4 which points in the flow direction P.
  • the deformation points 7 are located where three slots 4, which are offset by 120 ° to one another, are adjacent with their ends.
  • the deformation points 7 are located at corner points of the polygon. With regard to the edge sides 5, 6, it is only the slots 4 which run parallel to the flow direction P. Since these edge-side deformation points 7 are subject to particularly high thermal loads, it is provided that no more resistant deformation points are created here than those which are arranged between the star-shaped ones Slots 4 are arranged.
  • the recess 8 can be produced very easily by using a punching tool that removes the actual core area of the deformation point 7.
  • FIG. 3 shows the deformation point 7 in an enlarged representation.
  • the limits of the deformation point 7 are identified by the dashed line.
  • the lines delimit the area in which the highest material stresses occur.
  • the three slots 4 define an inner circle 9 between them, which is enclosed by the star-shaped region of the deformation point 7. If the inner circle 9 is removed by a punching tool that is slightly shifted upward in the image plane of FIG. 3, the punching tool engages in the two upper slots 4.
  • the punching tool for removing the deformation point 7 and thus for separating the sheets preferably has a somewhat larger diameter.
  • the width B1 of the slots 4 is equal to the diameter D4 of the rounded ends of the slots 4.
  • the Central area 9 has this diameter D4.
  • the recess 8 is placed in such a way that a width B2 (FIG. 1) remains.
  • B2 is approximately one third of the width of the slot 4, that is to say approximately 0.5 mm.
  • the deformation point 7 at its narrowest point B3 (FIG. 3) is narrower than the width B1 of the slots 4.
  • FIG. 4 shows a heat exchanger 1 for cooling hot gases.
  • the heat exchanger shown has a gas inlet 11 and a gas outlet 12 at a distance from the gas inlet 11. Between the gas inlet 11 and the
  • a large number of cooling tubes 13 running in parallel are arranged in the gas outlet 12.
  • the cooling tubes 13 are surrounded by the fins 1, as explained above.
  • FIG. 4 shows that the heat exchanger 10 has a plurality of groups 14-17 connected in series.
  • the groups 14-17 are successively flowed through by the hot gas to be cooled.
  • the cooling water which flows through the cooling tubes 13 is deflected between two successive groups 14-17.
  • baffles 19 - 22 are located outside a housing 18 which surrounds the cooling tubes 13 and the fins 1.
  • the heat exchanger 10 shown is inserted into a further housing, not shown in any more detail. Cooling water is, for example, in the image plane from above first group 14 fed.
  • the cooling water then flows through the cooling pipes 13 from top to bottom and emerges below the first group 14.
  • All guide plates 19 - 22 are configured identically. They can be surrounded with elastomeric seals in order to provide a seal with respect to the surrounding, further housing and to avoid bypass flows of the cooling water.
  • Figure 5 shows a perspective view of the heat exchanger 10, partially in section.
  • the first group 14 is shown without the upper tube plate 23 shown in FIG. 4, so that the view of the individual cooling tubes 13 and the fins 1 is clear.
  • the ribs 1 are arranged in a stacked arrangement.
  • Via an inflow funnel 24 which increases in the direction of flow, the gas flow supplied is conducted as uniformly as possible onto the inflow surface formed by the ribs 1.
  • the gas stream flows between the adjacent fins 1 and flows around the cooling tubes 13. This process is repeated from the first to the last group 14-17. From the illustration in FIG.
  • FIGS. 7 to 9 show three further exemplary embodiments of fins for the said heat exchangers.
  • the same reference numerals are used for the essentially identical components as for the exemplary embodiment in FIGS. 1 to 3.
  • the embodiment of Figure 7 differs from that of Figure 1 in width and length. While a total of six rows of tubes are arranged one behind the other in the embodiment of FIG. 1, in the embodiment of FIG. 7 there are only four and also a maximum of four cooling tubes in width.
  • the arrangement and shape of the slots 4 and the deformation points and the openings 2 is, however, identical.
  • FIG. 1 shows additional cutouts at the deformed points in the edge area on the flowed-over edge side 5 and the opposite edge side 6, these are not present in the exemplary embodiment in FIG.
  • the margins 5 and 6 are rounded to a certain extent.
  • the cutouts which lead to pointed protrusions in the example of FIG. 1 were smoothed, so that the course of the edge sides 5, 6 no longer has any sharp jumps or kinks in the course.
  • FIG. 8 represents an alternative to this.
  • the rib 1 shown is provided with additional cutouts 25 in the region of its edge side 5 against which it flows. They are arranged where those slots 4 end, which run in the flow direction according to the arrow P and are thus parallel to the inflow direction or perpendicular to the edge side 5.
  • the sawtooth-like course of the edge side 5 is interrupted by the additional cutouts 25 in the area of the slots 4.
  • the slots 4 open out via the cutouts 25 into the sawtooth-like edge side 5.
  • the cutouts 25 are produced by punching out the end regions of the slots 4 pointing to the edge side 5. As a result, the deformation point denoted by 7 in FIG. 1 is omitted and is replaced by a circular recess 25.
  • the diameter of the recess 25 is larger than the width B1 of the slot 4.
  • the diameter is approximately twice as large as that Width B1. This results in the transition from the inflow edge side 5 to the slot 4, concave widenings of the entry area of the slot 4.
  • These widened cutouts 25 have the effect that the thermally induced stresses in the inflow area of the rib 1 are again significantly reduced, in particular because here the highest Temperatures prevail and material fatigue can occur earlier than on the opposite edge side 5 facing away from the flow.
  • the exemplary embodiment in FIG. 9 differs from that in FIGS. 1, 7 and 8 by slots 4 of different lengths. Those slots 5 which point in the direction of flow and thus run parallel to the flow (arrow P) are longer than the other, opposite one another in pairs Slots 4. It is still a hexagonal arrangement of slots 4. However, the said hexagons are no longer uniform, but stretched in the direction of flow P. It is pointed out that the distance between the rows R1, R2, R3 (see FIG. 1) has not changed. Only the proportions of the slots 4 have been changed. While the slots 4 running in the direction of flow are somewhat longer than in the exemplary embodiment in FIGS. 1, 7 and 8, the slots 4 running diagonally to the direction of flow P are somewhat shorter. The angular positions of the individual slots 4 to one another have not changed. They are still arranged in a star shape with an angle of 120 ° to each other.
  • deformation regions 7 are no longer symmetrical.
  • the longer slit 4 of the three slits 4 meeting one another engages somewhat more deeply into the deformation point 7.
  • the center of the deformation point 7 is thereby shifted somewhat from the central position to one of the adjacent openings 2. In this case, it is those openings 2 which are arranged one behind the other in the direction of flow P.
  • the pairs of opposing slots 4 in terms of their length, the Position the center of the deformation point 7 as required. It can also be seen that the width of the slots 4 is greater than a minimum width of the respective deformation point 7.
  • the inflow edge side 5 is partially rounded. Where the slots 4 running parallel to the flow direction P are arranged, the deformation point 7 which is usually present there is severed transversely to the flow direction. There is an area of the edge side 5 which is perpendicular to the inflow direction P.
  • the slots 4 adjacent to the edge side 5 are not open to the edge side 5 as in the exemplary embodiment in FIG. 8, but are closed. It is optionally possible to provide additional cutouts, as shown in FIG. 7.
  • the deformation point 7 On the opposite edge side 6, which faces away from the flow direction P, there are rounded regions in the region of the openings 2, as is also shown in FIG.
  • the slots 4 adjacent to the edge side 6 end in a deformation point 7, which is also part of the edge side 6.
  • the deformation point 7 In contrast to the flow side 5, the deformation point 7 is not cut off transversely to the flow direction P, but has a concave indentation 26.
  • the deformation point 7 is thus somewhat stronger in this area than on the inflow edge side 5, which can be seen from the corner flanks of the concave indentation 26.
  • the inflow edge side 5 therefore behaves less flexurally in the area of the deformation points 7 there than the deformation points 7 on the opposite, downstream edge side 6.

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

Abstract

L'invention concerne un échangeur de chaleur pour le refroidissement de gaz, comprenant une entrée de gaz et une sortie de gaz et plusieurs tubes de refroidissement, qui sont disposés entre l'entrée de gaz et la sortie de gaz, ainsi que des nervures (1), au moins une telle nervure (1) étant traversée par plusieurs des tubes de refroidissement, les nervures (1) comprenant des fentes (4) qui sont disposées à distance d'ouvertures (2) pour la réception des tubes de refroidissement. Les fentes (4) sont disposées en forme hexagonale, les fentes (4) respectives d'un hexagone entourant une ouverture (2) à une distance D3 de l'ouverture (2), chaque fente (4) se terminant avec au moins une extrémité sur un point de déformation (7) de la nervure (1).
EP19734679.4A 2018-07-19 2019-06-19 Échangeur de chaleur Active EP3824240B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018117457.8A DE102018117457A1 (de) 2018-07-19 2018-07-19 Wärmetauscher
PCT/DE2019/100570 WO2020015777A1 (fr) 2018-07-19 2019-06-19 Échangeur de chaleur

Publications (2)

Publication Number Publication Date
EP3824240A1 true EP3824240A1 (fr) 2021-05-26
EP3824240B1 EP3824240B1 (fr) 2022-05-11

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Family Applications (1)

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EP19734679.4A Active EP3824240B1 (fr) 2018-07-19 2019-06-19 Échangeur de chaleur

Country Status (8)

Country Link
US (1) US11262139B2 (fr)
EP (1) EP3824240B1 (fr)
JP (1) JP6979547B2 (fr)
KR (1) KR20210002745A (fr)
CN (1) CN112313467B (fr)
DE (1) DE102018117457A1 (fr)
DK (1) DK3824240T3 (fr)
WO (1) WO2020015777A1 (fr)

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Publication number Priority date Publication date Assignee Title
US11774187B2 (en) * 2018-04-19 2023-10-03 Kyungdong Navien Co., Ltd. Heat transfer fin of fin-tube type heat exchanger
FR3092657B1 (fr) * 2019-02-12 2021-02-19 Valeo Systemes Thermiques Dissipateur thermique pour carte electronique d’un groupe moto-ventilateur de vehicule automobile
JP7328115B2 (ja) * 2019-10-11 2023-08-16 リンナイ株式会社 熱交換器

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KR20210002745A (ko) 2021-01-08
JP6979547B2 (ja) 2021-12-15
CN112313467B (zh) 2021-07-27
JP2021523342A (ja) 2021-09-02
EP3824240B1 (fr) 2022-05-11
DK3824240T3 (da) 2022-07-04
CN112313467A (zh) 2021-02-02
US11262139B2 (en) 2022-03-01
DE102018117457A1 (de) 2020-01-23
WO2020015777A1 (fr) 2020-01-23

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