EP3394554B1 - Wärmetauscher, insbesondere für ein kraftfahrzeug - Google Patents

Wärmetauscher, insbesondere für ein kraftfahrzeug Download PDF

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Publication number
EP3394554B1
EP3394554B1 EP16829104.5A EP16829104A EP3394554B1 EP 3394554 B1 EP3394554 B1 EP 3394554B1 EP 16829104 A EP16829104 A EP 16829104A EP 3394554 B1 EP3394554 B1 EP 3394554B1
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EP
European Patent Office
Prior art keywords
frames
fluid
heat
heat exchange
heat exchanger
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.)
Active
Application number
EP16829104.5A
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English (en)
French (fr)
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EP3394554A1 (de
Inventor
Sébastien JACOPE
Jérôme MOUGNIER
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Valeo Systemes Thermiques SAS
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Valeo Systemes Thermiques SAS
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Publication of EP3394554A1 publication Critical patent/EP3394554A1/de
Application granted granted Critical
Publication of EP3394554B1 publication Critical patent/EP3394554B1/de
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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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • F28D9/0081—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 a single plate-like element ; the conduits for one heat-exchange medium being integrated in one single plate-like element
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F28F2225/08—Reinforcing means for header boxes

Definitions

  • the invention relates to the field of heat exchangers and in particular to heat exchangers intended to be traversed by a fluid under high pressure.
  • the invention relates to a heat exchanger corresponding to the preamble of claim 1, and as disclosed by the document FR 2 912 811 .
  • the invention relates more particularly to heat exchangers capable of being traversed by a refrigerant fluid having a relatively high operating pressure, as is the case with natural gases such as carbon dioxide designated by CO 2 , having an operating pressure higher than the refrigerant gases used in the solutions of the state of the art.
  • Such heat exchangers find particular application in motor vehicles. They can in particular constitute a gas cooler in which the refrigerant fluid such as CO 2 is cooled by a second fluid, such as liquid. Conversely, the second fluid can be cooled by the first fluid, for example in gaseous form, the heat exchanger is then commonly designated by “Water chiller” in English.
  • Such heat exchangers can in particular be used in the thermal regulation of one or more batteries of an electric or hybrid vehicle.
  • the thermal regulation of the batteries is an important point because if the batteries are subjected to temperatures that are too cold, their autonomy can decrease sharply and if they are subjected to too high temperatures, there is a risk of thermal runaway which can go up to destruction of the battery, or even of the motor vehicle.
  • a heat transfer fluid in general cooling liquid comprising a mixture of glycol water, which circulates within a heat exchanger in contact with the battery or batteries.
  • the coolant can thus bring heat to the battery or batteries to heat them, this heat having been absorbed by the coolant for example during the heat exchange with the CO 2 circulating in the gas cooler.
  • the coolant can also, if necessary, absorb heat emitted by the battery or batteries in order to cool them and evacuate this heat at the level of one or more other heat exchangers.
  • Such heat exchangers can also be used like any other gas cooler in an air conditioning circuit.
  • These heat exchangers can in particular be heat exchangers assembled by brazing.
  • Heat exchangers are known, for example, comprising a stack of plates allowing the circulation of the first fluid, such as the refrigerant or refrigerant gas, and of the second fluid such as the coolant.
  • heat exchangers are also known from the prior art, comprising a stack of tubes connected together by at least one collector of the first fluid, in particular the refrigerant on each side of the tubes, and the second fluid, for example. in liquid form, can circulate around the tubes in an envelope connected to a water box.
  • the present invention aims to improve the solutions of the state of the art and to at least partially resolve the drawbacks set out above by proposing a heat exchanger which is simple to produce and which has a reduced bulk while at the same time having advantageous properties in order to resist at best strong local pressures.
  • Such a heat exchanger has better mechanical strength compared to the solutions of the prior art and very good resistance to high pressures, in particular due to the circulation of CO 2 as refrigerant.
  • the frames designate a part, or an assembly of parts, which can be rigid, delimiting a closed or not space. In this space can be positioned, in our example, heat exchange tubes.
  • the heat exchange bundle which comprises a plurality of heat exchange tubes, is distinct from the frames.
  • a first fluid is able to circulate in the heat exchange tubes
  • the heat exchanger further comprises a plurality of second frames respectively arranged alternately with the first frames for receiving the tubes heat exchange, and respectively defining a second circulation channel for a second fluid so as to allow heat exchange between the first fluid and the second fluid.
  • the heat exchange tubes are received and maintained in first dedicated frames while the turbulators can be received in the second dedicated frames and thus be superimposed on the heat exchange tubes.
  • the heat exchanger thus comprises a stack of simple elements, namely frames and heat exchange tubes in which the first fluid circulates, such as the refrigerant gas, inserted in the first frames and between which the second fluid circulates. only coolant.
  • the second frames have through passage orifices arranged in alignment with the recesses, so as to allow the flow of the first fluid in the stack of the first frames and of the second frames.
  • the superimposed frames make it possible to create the flow path for the first fluid, when the frames are assembled together, for example by brazing.
  • the superimposed frames advantageously make it possible to create the flow path for the second fluid, in particular on two opposite sides of the heat exchange bundle.
  • the invention relates to a heat exchanger 1 in particular for a motor vehicle, for a heat exchange between at least a first fluid and a second fluid.
  • the first fluid can enter the heat exchanger 1 in gaseous form and the second fluid in liquid form.
  • the heat exchanger 1 has at least partially, that is to say on at least some elements or certain parts, a coating intended to melt to ensure the joining of elements of the heat exchanger during the by brazing.
  • the coating is commonly designated by "clad” in the field of brazing of metal parts, in particular aluminum.
  • the coating is added on the core of the parts, during manufacture, for example by cold rolling. It may be a non-limiting example of a coating comprising aluminum and silicon.
  • the heat exchanger 1 according to the invention is in particular suitable for the circulation of at least one fluid having a high operating pressure, in particular greater than 100 bars.
  • the first fluid is a refrigerant intended to circulate at high pressure such as CO 2 , also designated by R744 according to the industrial nomenclature.
  • the heat exchanger 1 can in particular be a gas cooler in which the refrigerant fluid such as CO 2 is cooled by a second fluid, for example in liquid form, such as coolant comprising a mixture of glycol water.
  • the second fluid such as the coolant can also be cooled by the first fluid such as CO 2 , such a heat exchanger is then commonly designated by "Water chiller" in English.
  • the heat exchanger 1 comprises a heat exchange bundle 3 allowing the heat exchange between the first fluid and the second fluid.
  • the heat exchange bundle 3 has a generally substantially parallelepiped shape.
  • the circulation of the first and second fluids is advantageously done against the current in the heat exchange bundle 3.
  • the introduction and evacuation of the first fluid in the heat exchange bundle 3 or out of the heat exchange bundle 3 is shown schematically by way of example by the arrows F1 I for the introduction and F1 O for the evacuation .
  • the heat exchanger 1, and more precisely the heat exchange bundle 3 can be configured for circulation in at least two passes of one of the two fluids, or even of the two fluids.
  • the heat exchange bundle 3 comprises a plurality of heat exchange tubes 5, visible on the figures 2 to 4 , stacked so as to alternately define first circulation channels (not visible in the figures) for the first fluid in the heat exchange tubes 5 and second circulation channels 9 for the second fluid between the heat exchange tubes 5 .
  • the heat exchange tubes 5 can be produced in the form of flat tubes, advantageous in terms of space.
  • the flat tubes 5 have a substantially rectangular general shape, with a length for example of the order of 32mm and a thickness of the order of a millimeter.
  • the thickness is here considered in the direction of the height of the heat exchange bundle 3, we can also speak of the height of the heat exchange tubes 5. In other words, it is the thickness in the direction d stack of heat exchange tubes 5.
  • Each heat exchange tube 5 defines a predetermined number of first circulation channels (not visible in the figures) for the first fluid, in particular micro-circulation channels for the first fluid.
  • the first channels or micro-channels extend, for example, substantially longitudinally, in a substantially “I” or rectilinear shape.
  • the first circulation channels or micro-channels for the first fluid allowing the flow of the first fluid extend respectively in a direction parallel to the longitudinal direction of the heat exchange tubes 5.
  • the first fluid can follow a circulation in a pass called “I” circulation but also a circulation in two passes called “U” circulation.
  • the second circulation channels 9 for the second fluid can be shaped to allow circulation in a so-called “I” circulation pass but also a circulation in two passes called “U” circulation.
  • Turbulators 11 for the flow of the second fluid are advantageously arranged in the second circulation channels 9, thus improving the heat exchange between the two fluids.
  • the turbulators 11 can be carried by an element 12 separate from the heat exchange tubes 5 as illustrated in the figures 2 and 3 .
  • turbulators 11 can be formed on the heat exchange tubes 5, for example by deformations such as undulations of the heat exchange tubes 5 which project into the second circulation channels 9 for the second fluid.
  • Interleaves are advantageously arranged between the heat exchange tubes 5, and define the pitch between the heat exchange tubes 5.
  • the heat exchange bundle 3 comprises an alternating stack of first frames 13 and second frames 15.
  • At least some second frames 15 form the spacers.
  • the stacking takes place here substantially vertically.
  • Each first frame 13 is capable of receiving at least one heat exchange tube 5 and this assembly forms a stage of the heat exchange bundle 3.
  • the first frames 13 can be designated by tube frames.
  • Each second frame 15 can receive turbulators 11 and this assembly forms another stage of the heat exchange bundle 3. These two assemblies or stages are repeated as many times as necessary according to the space available and the performance to be achieved.
  • the first frames 13 and the second frames 15 are described in more detail below.
  • closure plates 17, 18 (see figure 1 ), in particular at least one lower closure plate 17 and at least one upper closure plate 18, can be arranged on either side of the stack of first frames 13 and second frames 15, so as to close the heat exchange bundle 3.
  • the closure plates 17, 18 have a shape complementary to the shape of the first frames 13 and of the second frames 15.
  • the heat exchanger 1 further comprises at at least one manifold 19 of the first fluid arranged in fluid communication with the first circulation channels (not visible in the figures) defined in the heat exchange tubes 5.
  • the manifold 19 is, according to the example illustrated, arranged on an upper closure plate 18 disposed at the top of the heat exchange bundle 3.
  • the heat exchanger 1 also comprises at least two fluid inlet and outlet pipes 21 allowing the introduction and the evacuation of the second fluid.
  • the two pipes 21 are arranged on the same upper closure plate 18 as the manifold 19 for the first fluid.
  • the manifold 19 can be arranged on one side of the heat exchange bundle 3 and the pipes 21 can be arranged on the other side of the heat exchange bundle 3, thus allowing counter-current circulation of the two fluids.
  • the manifold 19 is arranged on the left while the pipes 21 are arranged on the right.
  • First frames called tube frames
  • the first frames 13 can be at least partially made of aluminum.
  • the general direction of flow of the first fluid is understood to be the direction of circulation in “I” in the case of a one-pass circulation of the first fluid, or the direction of the branches of the “U” in the case of 'a circulation in two passes of the first fluid.
  • the first frames 13 are of generally substantially rectangular shape and have two longitudinal edges 13C, 13D, forming long sides, extending substantially parallel to the general direction of flow of the first fluid and two edges lateral 13A, 13B, forming short sides, extending in the width direction, substantially perpendicular to the direction of flow of the first fluid.
  • the longitudinal axis of the first frames 13 and the heat exchange tubes 5 is here combined.
  • These first frames 13 have the same thickness as the heat exchange tubes 5 which they receive, in particular of the order of a few millimeters, for example of the order of 1mm.
  • the thickness is considered in the direction of the height of the heat exchange bundle 3, we can also speak of the height of the first frames 13.
  • the heat exchange tubes 5 can be held in the respective first frames 13 before the different frames 13, 15 are superimposed.
  • Each first frame 13 can receive a heat exchange tube 5 or, as a variant, at least two heat exchange tubes 5, as illustrated in the figures 2 to 5 , so that the heat exchange bundle 3 then has at least two rows of heat exchange tubes 5.
  • each first frame 13 has two housings 130 for receiving in each housing 130 an associated heat exchange tube 5.
  • two adjacent heat exchange tubes 5 arranged in a first frame 13 can communicate with each other at one end.
  • the first frames 13 comprise means for placing in fluid communication 131 the first circulation channels of the first fluid with the manifold 19.
  • each first frame 13 The means for placing in fluid communication 131 of each first frame 13 are advantageously arranged in fluid communication with the means for putting in fluid communication 131 of the other first frames 13 of the heat exchange bundle 3 and with the manifold 19.
  • the fluid communication means 131 provided on the first frames 13 allow, in a simple way, to collect the first fluid and to distribute it, for example in the heat exchange tubes 5 held in these first frames 13. It is no longer necessary to provide the collectors on each side of the tubes as in the known solutions.
  • the first frames 13 respectively have a predefined number of recesses 131 forming the means of fluid communication, in which the ends, in particular the longitudinal ends, of the heat exchange tubes 5 open.
  • the number of recesses 131 is adapted as a function of the number of first circulation channels in the heat exchange tubes 5.
  • recesses 131 are here provided on two opposite edges 13A, 13B (see Figures 4 and 5 ) first frames 13 which are opposite the ends of the heat exchange tubes 5.
  • the first frames 13 are arranged so that their recesses 131 are in fluid communication with the recesses 131 of the other first frames 13.
  • the recesses 131 of the first frames 13 are aligned in the direction of the height of the heat exchange bundle 3 .
  • the recesses 131 are aligned with the manifold 19.
  • At least one lateral edge 13A, 13B of a first receiving frame 13, arranged opposite one end of a heat exchange tube 5, is shaped according to a pattern defining a succession of arches.
  • the arches are advantageously arranged over the entire width of the lateral edge which is opposite one or more ends of the heat exchange tube (s) 5.
  • the arches are provided over the entire width of the set of tubes heat exchange 5 that the first frame 13 can receive, here two heat exchange tubes 5.
  • arch is understood to mean the assembly formed by an arch vault 132 connecting two arch legs 133. In this succession of arches, two adjacent arch vaults 132 are connected by a common arch leg 133.
  • a recess 131 is delimited by an arch, otherwise said each recess 131 is made between two adjacent arch legs 133 and is delimited by these two arch legs 133 and the arch vault 132 connecting them.
  • the fluid communication means 131 can define two rows respectively associated with a row of heat exchange tubes 5.
  • first communication means 131 ensure the fluid communication of the first heat exchange tubes 5 or in other words of the first row of first heat exchange tubes with the manifold 19.
  • second means placing in communication 131 ensures the fluidic communication of the second heat exchange tubes 5 or in other words of the second row of second heat exchange tubes with the manifold 19.
  • each first frame 13 advantageously comprises at least one stress absorption zone on at least one lateral edge 13A, 13B facing one end of a heat exchange tube 5.
  • Such a stress absorption zone is able to withstand mechanical stresses, in particular due to pressure.
  • the stress absorption zones can be produced by a predetermined number of stress absorption legs formed on at least one lateral edge 13A, 13B of a first frame 13 opposite one end of a heat exchange tube 5.
  • the arches are therefore dimensioned taking into account the mechanical strength of the first frame 13 and the flow of the first fluid through the recesses 131 defined by the arches.
  • the arch feet 133 also make it possible to define brazing zones with the second frames 15.
  • the first frames 13 also have guides 134 for the passage of the second fluid.
  • the first frames 13 are respectively shaped with at least one handle 134 which, when a heat exchange tube 5 is arranged in the first frame 13, makes it possible to define a through opening for passage allowing the flow of the second fluid.
  • the handles 134 make it possible to define the guides for the passage of the second fluid.
  • the handles 134 of each first frame 13 are arranged in alignment with the handles 134 of the other first frames 13 of the heat exchange bundle 3 so as to allow the second fluid to flow through the bundle 3.
  • the figures show various embodiments of the handles 134, in particular the figure 1 illustrates a first embodiment of the handles 134 of substantially rounded shape, while the figures 2 to 5 illustrate a second embodiment of the handles 134, the outline of which is more straight.
  • any other form of the handles 134 can be envisaged.
  • each first receiving frame 13 may have at least one partition 135 which compartments the first receiving frame 13.
  • This partition 135 is here arranged in the extension of an arch foot 133.
  • each first receiving frame 13 has a partition 135, for example substantially central, which partitions the first receiving frame 13 into two housings 130 (see figure 5 ) to each receive a heat exchange tube 5.
  • the partition 135 is therefore found arranged between two tubes heat exchange 5 when they are placed in the first frame 13.
  • the partition 135 extends over the entire length of the heat exchange tubes 5 received in the first frame 13.
  • the partition 135 of a first frame 13 can be made in one piece with this first frame 13.
  • Such a first frame 13 can be made by stamping in a simple manner.
  • the second frames 15 can be at least partially made of aluminum.
  • the second frames 15 When the second frames 15 receive turbulators 11, the second frames 15 are called turbulator frames or turbulator-carrying frames.
  • the general direction of flow of the second fluid is understood to be the direction of circulation in “I” in the case of a one-pass circulation of the second fluid, or the direction of the branches of the “U” in the case of 'a circulation in two passes of the second fluid.
  • the second frames 15 are of general shape similar to the first frames 13, here substantially rectangular.
  • the second frames 15 have two longitudinal edges, forming long sides, extending substantially parallel to the longitudinal edges of the first frames 13 and to the general direction of flow of the second fluid, and two lateral edges, forming short sides, extending in the width direction, substantially perpendicular to the direction of flow of the second fluid parallel to the lateral edges of the first frames 13.
  • the second frames 15 extend over the same length and the same width as the first frames 13.
  • the outer contours of the first frames 13 and second frames 15 are practically identical so that the alternating stacking of the first frames 13 and second frames 15 forms a block.
  • each second frame 15 defines an internal width and an internal length.
  • internal width means the width defined between the internal walls of the opposite longitudinal edges.
  • internal length means the length defined between the internal walls of the opposite lateral edges.
  • the side edges of the second frames 15 may be slightly larger than the side edges of the first frames 13, so that the ends heat exchange tubes 5 received in the first frames 13 stacked with the second frames 15, rest on the peripheral edge of the lateral edges of the second frames 15.
  • the second frames 15 therefore define an internal length less than the internal length defined by the interior space of the first frames 13.
  • the second frames 15 have a thickness which is of the order of a few millimeters, for example of the order of 0.5mm to 4mm, preferably of the order of 2mm.
  • the thickness is here considered in the direction of the height of the heat exchange bundle 3, we can also speak of the height of the second frames 15. In other words, it is the thickness in the stacking direction of the frames 13, 15.
  • the second frames 15 can be produced by stamping cutting.
  • a plurality of second frames 15, called intermediate frames, are arranged between two first frames 13 for receiving the heat exchange tubes 5, thus defining the pitch between two stages of heat exchange tubes 5.
  • the heat exchange bundle 3 may further comprise a second end frame optionally arranged between a first frame 13 and a closure plate, in particular the lower closure plate 17.
  • a second end frame can be put in place for reasons of mechanical strength.
  • first frames 13 and second frames 15 are advantageously provided without such an end frame.
  • the second frames 15 allow a circulation in two passes of the second fluid.
  • the second frames 15 each comprise a bar 150 arranged inside the respective second frame 15 so as to separate two circulation passes for the second fluid. It is therefore an internal bar 150.
  • the bar 150 makes it possible to conform the second circulation channel 9 substantially in a "U" shape.
  • the bar 150 extends longitudinally inside a second frame 15.
  • the bar 150 therefore extends in this example substantially parallel to the longitudinal edges of the second frame 15.
  • the bar 150 does not extend over the entire internal length of the second frame 15.
  • the bar 150 extends from a lateral edge of a second frame 15 in the direction of the opposite lateral edge but without reaching this opposite lateral edge.
  • the bar 150 is therefore secured to a lateral edge of a second frame 15 and projects with its free end towards the internal space of the second frame 15 in the direction of the opposite lateral edge, leaving a space.
  • the internal bar 150 therefore extends longitudinally from a lateral edge of a second frame 15 over a length less than the internal length of the second frame 15.
  • the internal bar 150 does not extend over the entire internal width of the second frame 15 either.
  • the internal bar 150 has a smaller width than the internal width of the second frame 15.
  • the width of the internal bar 150 may be greater than or equal, preferably strictly greater, to the thickness of the second frame 15. We define thus on each side of the bar 150, the inlet and the outlet of the flow path for the second fluid.
  • the bar 150 can also be described as a tongue.
  • the bar 150 is substantially the same thickness as the second frame 15.
  • the bar 150 is for example arranged substantially centrally. More precisely, the bar 150 is arranged substantially in the center of a second frame 15 in the width direction of the second frame 15.
  • the bar 150 divides the second frame 15 into two parts of the same size.
  • the internal bar 150 extends over a length at least equal to half the internal length of a second frame 15.
  • the internal bars 150 of the second frames 15 are located opposite the partitions 135 of the first frames 13.
  • the second frames 15, in particular the second intermediate frames 15, have guides 151 for the passage of the first fluid allowing its flow in the stack of the first receiving frames 13 and the second frames 15, especially dividers.
  • the guides 151 are here produced in the form of through-passage orifices 151 arranged in alignment with the recesses 131 for placing the first receiving frames 13 in fluid communication, delimited here by the succession of arches.
  • the through passage holes 151 are therefore arranged on at least one lateral edge of a second frame 15, here of a second intermediate frame 15.
  • the number of through passage openings 151 is adapted as a function of the number of recesses 131 and therefore of the number of first circulation channels of the heat exchange tubes 5.
  • the second frames 15 respectively have means for placing in fluid communication 152 the second circulation channels 9 between them on the one hand and with the pipes 21 for the second fluid on the other hand.
  • the fluid communication means 152 provided on the second frames make it possible to collect the second fluid and distribute it between the heat exchange tubes.
  • the second frames 15 respectively have a predefined number of through openings 152, here two through openings 152, for fluid communication.
  • the through openings 152 are here arranged on the longitudinal edges of the second frames 15 and are aligned with each other in the height direction of the heat exchange bundle 3, in other words in the stacking direction of the different frames 13 , 15.
  • the through openings 152 lead respectively to the interior of a second frame 15.
  • the through openings 152 are arranged on the same side of a second frame 15 in the longitudinal direction, that is to say here to the right or to the left, in a complementary manner to the arrangement of the pipes 21 on a same side of the heat exchange bundle 3, here on the right with reference to the arrangement shown on the figure 1 .
  • the through openings 152 make it possible to define a fluid inlet 152 towards the interior space of the second frame 15 on a longitudinal edge, and a fluid outlet 152 out of the second frame 15 on the opposite longitudinal edge.
  • the second frames 15 have handles 153 which make it possible to delimit the through openings 152.
  • the handles 153 of the second frames 15 are produced in a similar manner to the handles 134 of the first frames 13 and are aligned with these handles 134 which allow the passage of the second fluid through the heat exchange bundle 3.
  • the figures show different embodiments of the handles 153, in particular, the figure 1 illustrates a first embodiment of the handles 153 of substantially rounded shape, while the figure 6 illustrates a second embodiment of the handles 153, the outline of which is more straight.
  • the handles 134 of the first frames 13 are produced according to the first embodiment
  • the handles 153 of the second frames 15 are produced in a similar manner according to the first embodiment.
  • the handles 153 of the second frames 15 are produced in a similar manner according to the second embodiment example.
  • any other form of the handles 153 can be envisaged.
  • the opening delimited by a first handle is arranged in fluid communication with a first tube 21 and the opening delimited by a second handle is arranged in fluid communication with a second tube 21.
  • the heat exchanger 1 is preferably assembled by brazing.
  • the second frames 15 are intended to be assembled by brazing to the first frames 13.
  • the longitudinal edges of the second frames 15 are intended to be assembled by brazing to the longitudinal edges of the first frames 13 and the lateral edges of the second frames 15 are intended to be assembled by brazing with the arch legs 133 provided on the lateral edges of the first frames 13.
  • the second frames 15, in particular the second intermediate frames 15, can also be shaped to put in fluid communication two heat exchange tubes 5 received in the same first frame 13 as illustrated on the figures 2 to 4 .
  • each second frame 15, in particular an intermediate frame advantageously has at least one turning orifice 155 (see figures 2 and 6 ) which is in fluid communication with both a first and a second fluid communication means 131, here a first and a second recesses 131, of the first frames 13 on either side of the second intermediate frame 15.
  • each reversal orifice 155 is arranged between two adjacent heat exchange tubes 5 received in a first frame 13 and in fluid communication with these two heat exchange tubes 5.
  • the first fluid which emerges from a first heat exchange tube 5 undergoes a reversal in the reversal orifice 155 then circulates to a second heat exchange tube 5.
  • the two rows of heat exchange tubes 5 arranged in the first frames 13 then communicate at one end via the reversal orifices 155 provided on the second frames 15, in particular spacers.
  • Each reversal orifice 155 is here formed between passage orifices through 151 on at least one side edge of each second frame 15, in particular intermediate.
  • Each reversal orifice 155 advantageously has a longitudinal shape extending substantially perpendicular to the general direction of flow of the first fluid in the two heat exchange tubes 5.
  • each turning orifice 155 has a longitudinal shape extending perpendicular to the longitudinal edges of the second frame 15, in particular in between.
  • each reversal orifice 155 arranged opposite a first receiving frame 13 extends longitudinally on either side of the partition 135 of this first receiving frame 13, as is better visible on FIG. 16.
  • the reversal orifice 155 has a substantially oblong shape.
  • the reversal orifice 155 is dimensioned so as to have a section for the reversal of the first fluid at least equal to the section of passage of a heat exchange tube 5.
  • the heat exchanger 1 is then dual circulation in "U”.
  • the heat exchanger 1 comprises a stack of first frames 13 receiving one or more heat exchange tubes 5 and second frames 15 advantageously receiving turbulators 11. These are simple elements and can be assembled easily, by brazing in particular.
  • Such a heat exchanger 1 as described above also has very good resistance to high pressures, in particular due to the circulation of CO 2 , as well as optimized heat exchange performance.
  • the shape of the edges of the first frames 13 receiving the heat exchange tubes 5 with stress absorption zones formed by arch legs 133 makes it possible to obtain a heat exchanger 1 having better mechanical strength compared to the solutions of the prior art.
  • these arch legs 133 advantageously form brazing zones with the second frames 15.

Landscapes

  • 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)

Claims (8)

  1. Wärmetauscher (1), insbesondere für ein Kraftfahrzeug, wobei der Tauscher (1) ein Wärmetauscherbündel (3) mit einer Vielzahl von Wärmetauscherrohren (5) enthält, die Strömungskanäle für ein Fluid definieren:
    - wobei das Wärmetauscherbündel (3) eine Vielzahl erster Rahmen (13) zur Aufnahme der Wärmetauscherrohre (5) enthält, und dass
    - die ersten Rahmen (13) zur Aufnahme der Wärmetauscherrohre je mindestens einen Belastungsabsorptionsbereich (133) enthalten, der an mindestens einem Rand (13A, 13B) gegenüber einem Ende eines Wärmetauscherrohrs (5) angeordnet und geeignet ist, mechanischen Belastungen standzuhalten,
    wobei der Wärmetauscher dadurch gekennzeichnet ist, dass die Belastungsabsorptionsbereiche von einer vorbestimmten Anzahl von Belastungsabsorptionsbeinen (133) realisiert werden, die an mindestens einem Rand (13A, 13B) eines ersten Aufnahmerahmens (13) gegenüber einem Ende eines Wärmetauscherrohrs (5) geformt sind und sich in Richtung des Endes des Wärmetauscherrohrs (5) erstrecken.
  2. Wärmetauscher (1) nach dem vorhergehenden Anspruch, wobei die Belastungsabsorptionsbeine (133) sich in Längsrichtung im Wesentlichen parallel zur Fließrichtung des Fluids in den Strömungskanälen erstrecken.
  3. Wärmetauscher (1) nach einem der Ansprüche 1 oder 2, wobei die ersten Rahmen (13) eine Vielzahl von Aussparungen (131) aufweisen, und wobei zwei benachbarte Belastungsabsorptionsbeine (133) sich zu beiden Seiten einer Aussparung (131) erstrecken.
  4. Wärmetauscher (1) nach einem der Ansprüche 1 bis 3, wobei die ersten Rahmen (13) je mindestens einen Rand (13A, 13B) gegenüber einem Ende eines Wärmetauscherrohrs (5) aufweisen, der gemäß einem Muster gestaltet ist, das eine Folge von Bögen definiert, wobei die Bogenfüße (133) die Belastungsabsorptionsbeine bilden.
  5. Wärmetauscher (1) nach den Ansprüchen 3 und 4, der mindestens einen Sammelkasten (19) des Fluids enthält, und wobei, wenn Wärmetauscherrohre (5) in den ersten Rahmen (13) aufgenommen werden, die Wölbungen (132) der Bögen mit den Enden der Wärmetauscherrohre (5) Öffnungen zur Fluidverbindung zwischen dem Sammelkasten (19) und den Wärmetauscherrohren (5) definieren, so dass eine Öffnung zur Fluidverbindung zwischen zwei Bogenfüßen (133) ausgebildet wird.
  6. Wärmetauscher (1) nach einem der Ansprüche 1 bis 5, der durch Löten zusammengebaut wird, und wobei die Belastungsabsorptionsbeine (133) Lötbereiche definieren.
  7. Wärmetauscher (1) nach einem der vorhergehenden Ansprüche, wobei ein erstes Fluid in den Wärmetauscherrohren (5) strömen kann, und der außerdem eine Vielzahl zweiter Rahmen (15) enthält, die je abwechselnd mit den ersten Rahmen (13) zur Aufnahme der Wärmetauscherrohre (5) angeordnet sind und je einen zweiten Strömungskanal (9) für ein zweites Fluid definieren, um einen Wärmeaustausch zwischen dem ersten Fluid und dem zweiten Fluid zu erlauben.
  8. Wärmetauscher nach Anspruch 5 in Kombination mit Anspruch 8, wobei die zweiten Rahmen (15) durchgehende Durchlassöffnungen (151) aufweisen, die in Flucht mit den Aussparungen (131) angeordnet sind, um das Fließen des ersten Fluids in der Stapelung der ersten Rahmen (13) und der zweiten Rahmen (15) zu erlauben.
EP16829104.5A 2015-12-21 2016-12-16 Wärmetauscher, insbesondere für ein kraftfahrzeug Active EP3394554B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1562890A FR3045806A1 (fr) 2015-12-21 2015-12-21 Echangeur thermique, notamment pour vehicule automobile
PCT/FR2016/053494 WO2017109347A1 (fr) 2015-12-21 2016-12-16 Échangeur thermique, notamment pour véhicule automobile

Publications (2)

Publication Number Publication Date
EP3394554A1 EP3394554A1 (de) 2018-10-31
EP3394554B1 true EP3394554B1 (de) 2020-04-08

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Application Number Title Priority Date Filing Date
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Country Status (3)

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EP (1) EP3394554B1 (de)
FR (1) FR3045806A1 (de)
WO (1) WO2017109347A1 (de)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2852383B1 (fr) * 2003-03-11 2017-05-05 Valeo Thermique Moteur Sa Boite collectrice pour echangeur de chaleur a haute pression et echangeur de chaleur comportant cette boite collectrice
FR2864215B1 (fr) * 2003-12-19 2011-07-15 Valeo Climatisation Element de circuit pour echangeur de chaleur
FR2912811B1 (fr) * 2007-02-16 2013-02-08 Valeo Systemes Thermiques Echangeur de chaleur pour fluides a circulation en u
FR2986315B1 (fr) * 2012-01-30 2014-01-10 Valeo Systemes Thermiques Echangeur de chaleur

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
FR3045806A1 (fr) 2017-06-23
WO2017109347A1 (fr) 2017-06-29
EP3394554A1 (de) 2018-10-31

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