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
  • 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
  • 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
  • F28F9/0202—Header boxes having their inner space divided by partitions
• • 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
  • 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
  • F28F9/04—Arrangements for sealing elements into header boxes or end plates
  • F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
  • F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
• • 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
  • 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
  • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
  • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
  • F28F21/089—Coatings, claddings or bonding layers made from metals or metal alloys
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F2275/00—Fastening; Joining
  • F28F2275/04—Fastening; Joining by brazing
  • F28F2275/045—Fastening; Joining by brazing with particular processing steps, e.g. by allowing displacement of parts during brazing or by using a reservoir for storing brazing material
• • 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
  • F28F9/04—Arrangements for sealing elements into header boxes or end plates
  • F28F9/06—Arrangements for sealing elements into header boxes or end plates by dismountable joints

Definitions

• Heat exchanger in particular for a motor vehicle
• the invention relates to the field of heat exchangers.
• the invention relates more particularly to heat exchangers able to be traversed by a refrigerant fluid having a relatively high operating pressure, as is the case with natural gases such as carbon dioxide designated CO 2 , having a pressure of superior operation to refrigerant gases used in state-of-the-art solutions.
• Such heat exchangers find particular application in motor vehicles. They may in particular constitute a gas cooler in which the cooling 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 referred to as "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 too cold, their autonomy can decrease strongly and if they are subjected to too high temperatures, there is a risk of thermal runaway up to the destruction of the battery or the vehicle.
• a coolant generally coolant comprising a mixture of brine, which circulates in a heat exchanger in contact with the battery or batteries.
• the cooling liquid can thus bring heat to the battery or batteries to heat them, this heat having been absorbed by the cooling liquid for example during the heat exchange with the C0 2 flowing in the gas cooler.
• the coolant can also, if necessary, absorb the heat emitted by the battery or batteries to cool them and remove this heat at one or more other heat exchangers.
• Such heat exchangers can also be used like any other gas cooler in an air conditioning circuit.
• cooling fluid such as C0 2 under a very high pressure, generally greater than 100 bar, with a burst pressure which can reach, for example, up to 340 bar, implies that heat exchangers such as gas coolers can withstand such high pressures.
• 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 the second fluid such as the cooling liquid. Plate heat exchangers known from the prior art do not allow to withstand such high pressures.
• heat exchangers comprising a stack of tubes interconnected by at least one collector of the first fluid, in particular the refrigerant fluid on each side of the tubes, and the second fluid, for example, are known from the prior art. in liquid form, can circulate around the tubes in an envelope connected to a water box.
• the heat exchangers can in particular be assembled by soldering.
• a solder material is generally provided on different elements of the heat exchanger.
• the solder material that melts can plug the channels in which is intended to circulate at least one fluid, including the refrigerant.
• the present invention aims to improve the solutions of the state of the art and to at least partially solve the disadvantages described above by providing a heat exchanger whose assembly by soldering is improved.
• the subject of the invention is a heat exchanger for a heat exchange between at least a first fluid and a second fluid, in particular for a motor vehicle:
• the heat exchanger comprising a plurality of heat exchange tubes respectively defining at least one circulation channel of the first fluid, the heat exchanger having at least partially a coating capable of melting so as to ensure the joining of elements of the heat exchanger during soldering assembly.
• the heat exchanger comprises a plurality of first frames for receiving heat exchange tubes, and the first frames respectively have at least one recess at an inner corner receiving a corner of a tube of heat exchange, for the flow of the coating during brazing of the heat exchanger, so as to prevent the coating clogging the circulation channels of the first fluid of the heat exchange tubes.
• the coating present to ensure the junction between the elements of the heat exchanger assembly is not likely to come clog, when it melts, the circulation channels of the first fluid.
• the surplus solder material flows through the recess or recesses provided on one or more inner corners of the frames near the corners of the ends of the heat exchange tubes instead of risking entering the traffic channels of the first fluid accessible at the ends of the heat exchange tubes.
• the frames designate a part, or an assembly of parts, which can be rigid, delimiting a closed space or not. In this space can be positioned, in our example, heat exchange tubes. It will be noted that the heat exchange bundle, which comprises a plurality of heat exchange tubes, is distinct from the frames.
• the heat exchanger may further comprise one or more of the following features taken alone or in combination.
• each first frame has four recesses respectively arranged at an inner corner of the first frame.
• the heat exchanger comprises at least one manifold of the first fluid
• the first frames comprise means of fluid communication between the header and the heat exchange tubes and at least one recess is arranged near the means for setting fluid communication.
• the first frames respectively have at least one edge facing one end of a heat exchange tube shaped in a pattern defining a series of arches, and at least one setback is made in the extension of an arch extremmale.
• the heat exchanger comprises a plurality of second frames alternate with the first frames for receiving 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 flows. only coolant.
• the superimposed frames make it possible to create the flow path of the first refrigerant fluid, when the frames are brazed together, and likewise the superposed frames make it possible to create the coolant flow path, in particular on two opposite sides of the bundle. heat exchange.
• Such a heat exchanger has a better mechanical strength compared to the solutions of the prior art and very good resistance to high pressures, especially due to the circulation of C0 2 as a refrigerant gas.
• the second frames respectively have at least one groove on at least one edge of the second frame extending substantially perpendicular to the direction of flow of the first fluid. This further prevents the coating from clogging the flow channels defined by the heat exchange tubes when the coating melts and migrates during soldering.
• the width of the groove is substantially equal to the width of the recess.
• FIG. 1 is a perspective view of a heat exchanger according to the invention
• FIG. 2 schematically represents a first frame of the heat exchange bundle receiving two heat exchange tubes
• FIG. 3 is a view of the first single frame of FIG. 2,
• FIG. 4 is a partial sectional view of a first frame showing a recess for the flow of a coating capable of melting during soldering;
• FIG. 5 is another perspective view of a stack of first frames and second frames of the heat exchange bundle of the heat exchanger of FIG. 1;
• FIG. 6 is a partial perspective view showing a reservoir for the flow of a coating capable of melting during brazing provided on a second frame
• FIG. 7 is a side sectional view of a second frame having a reservoir on each side.
• 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 parts, a coating intended to melt to ensure the joining of elements of the heat exchanger during the heat exchange. soldering assembly, as will be detailed later.
• the heat exchanger 1 according to the invention is particularly suitable for the circulation of at least one fluid having a high operating pressure, in particular greater than 100 bar.
• the first fluid is a refrigerant intended to circulate at high pressure such as C0 2 , also designated R744 according to the industrial nomenclature.
• the heat exchanger 1 can in particular be a gas cooler in which the cooling fluid such as CO 2 is cooled by a second fluid for example in liquid form, such as cooling liquid comprising a mixture of brine.
• the second fluid such as the coolant can also be cooled by the first fluid such as C0 2 , such a heat exchanger is then commonly referred to as "Water chiller" in English.
• the heat exchanger 1 comprises a heat exchange bundle 3 for heat exchange between the first fluid and the second fluid.
• the heat exchange bundle 3 has a generally parallelepipedal shape.
• the circulation of the first and second fluids is advantageously countercurrent in the heat exchange bundle 3.
• the introduction and the evacuation of the first fluid in the heat exchange bundle 3 or outside the heat exchange bundle 3 is shown schematically by way of example by the arrows Fli for the introduction and Fl 0 for the evacuation.
• the introduction of the second fluid into the heat exchange bundle 3 and the evacuation of the second fluid out of the heat exchange bundle 3 is shown schematically by way of example by the arrows F2i for the introduction and F2o for 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 both fluids, as will be described further in detail thereafter.
• the heat exchange bundle 3 comprises a plurality of heat exchange tubes 5 (see FIG. 2) stacked so as to alternately define first circulation channels 7 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 made in the form of flat tubes, advantageous in terms of space.
• the flat tubes 5 have a generally rectangular general shape, with a length for example of the order of 32 mm and a thickness of about one 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 of stacking heat exchange tubes 5.
• Each heat exchange tube 5 defines a predetermined number of first circulation channels 7 for the first fluid, in particular circulating microchannels 7 for the first fluid.
• the first channels or microchannels 7 extend here substantially longitudinally, in a substantially "I" or rectilinear shape.
• the first circulation channels or microchannels 7 for the first fluid allow the flow of the first fluid respectively extend in a direction parallel to the longitudinal direction of the heat exchange tubes 5.
• the first fluid can follow a circulation in a so-called "I” flow but also a two-pass circulation called "U” circulation as will be described later.
• the second circulation channels 9 for the second fluid may be shaped to allow circulation in a so-called “I” flow but also a circulation in two passes called “U” circulation as will be described later.
• Turbulators 11 of 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 may be carried by an element 12 distinct from the heat exchange tubes 5.
• turbulators 11 may be formed on the heat exchange tubes 5, for example by deformations such as corrugations of the tubes of heat exchange. heat exchange 5 which protrude into the second circulation channels 9 for the second fluid.
• Interlayers 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 a alternating stack of first frames 13 and second frames 15. At least some second frames 15 form the spacers.
• the stack is here substantially vertically.
• Each first frame 13 is able to receive 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.
• first frames 13 and the second frames 15 are described in more detail below.
• closure plates 17, 18 in particular at least one bottom closure plate 17 and at least one top closure plate 17, 18, can be arranged on either side of the stacking of the first frames 13 and the second frames 15, so as to close the heat exchange bundle 3.
• the heat exchanger 1 further comprises at least one manifold 19 of the first fluid arranged in fluid communication with the first circulation channels 7.
• the collecting box 19 is according to the illustrated example arranged on an upper closure plate 18 disposed at the top of the heat exchange bundle 3.
• the heat exchanger 1 further comprises at least two inlet and fluid outlet pipes 21 for introducing and evacuating the second fluid.
• the two tubes 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 tubes 21 can be arranged on the other side of the heat exchange bundle 3, thus allowing a counter-current circulation of two fluids.
• the manifold 19 is arranged on the left while the pipes 21 are arranged on the right.
• the first frames 13 may be at least partially made of aluminum.
• the first frames 13 present:
• first frames 13 with respect to the general direction of flow of the first fluid, namely that the first frames 13 have:
• the general direction of flow of the first fluid means the direction of the flow in "I” in the case of a flow in one pass 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 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 side edges 13A, 13B, forming narrow 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 heat exchange tubes 5 is here confused.
• These first frames 13 have the same thickness as the heat exchange tubes 5 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. In other words, it is the thickness in the direction of stacking frames 13, 15.
• the heat exchange tubes 5 can be maintained in the respective first frames 13 before superposition of the various frames 13, 15.
• each first frame 13 may be adapted to receive a single heat exchange tube 5 allowing a flow in one pass of the first fluid.
• each first frame 13 has a housing 130 for receiving an associated heat exchange tube 5.
• each first reception frame 13 is able to receive two heat exchange tubes 5.
• the heat exchange bundle 3 then has two rows of heat exchange tubes 5: first heat exchange tubes and second heat exchange tubes.
• two adjacent tubes in a first frame 13 communicate with each other at one end so as to allow two-pass circulation of the first fluid.
• the heat exchange bundle 3 thus has at least one reversal zone of the first fluid, that is to say, allowing the first fluid having circulated in a heat exchange tube 5 to circulate to another heat exchange tube 5, namely the adjacent heat exchange tube 5 received in the same first frame 13.
• Fluidic communication at one end of two adjacent heat exchange tubes 5 received in a first frame 13 is advantageously provided by a second frame 15 as will be described in more detail later.
• the first frames 13 comprise means for placing in fluid communication 131 the first circulation channels 7 of the heat exchange tubes 5 with the manifold 19.
• the fluid communication means 131 define two rows respectively associated with a row of heat exchange tubes 5.
• first communication means 131 ensure the fluidic communication of the first heat exchange tubes 5 or in other words a first row of first heat exchange tubes 5 with the manifold 19.
• second communication establishment means 131 ensure the fluidic communication of the second heat exchange tubes 5 or in other words the second row of second heat exchange tubes 5 with the manifold 19.
• the first frames 13 present respectively a predefined number of recesses 131 forming the means for setting 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 7 of the heat exchange tubes 5.
• These recesses 131 are here provided on two opposite edges 13A, 13B of the first frames 13 which are facing the ends of the heat exchange tubes 5. These are the lateral edges of the first frames 13.
• 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 13A, 13B which is opposite the ends of the heat exchange tubes 5 received in the same first frame 13.
• the arches are provided over the entire width of the set of heat exchange tubes 5 that the first frame 13 can receive, here two heat exchange tubes 5.
• Arch is understood to mean the group formed by an arch arch 132 connecting two feet of arch 133. In this series of arches, two adjacent arch arches 132 are connected by a common arch foot 133.
• a recess 131 is delimited by an arch, in other words each recess 131 is made between two adjacent arch feet 133 and is delimited by these two arches 133 and the arch arch 132 connecting them .
• the space remaining between one end of the heat exchange tube 5 and an arch arch 132 makes it possible to define a through opening for setting into fluid communication.
• the diameter of a through opening is of the order of 0.5 mm.
• each first frame 13 advantageously comprises at least one stress absorption zone on at least one lateral edge 13A, 13B opposite 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 may be made 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 133 provide this function of stress absorption legs.
• the arches are 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 arches 133 still allow to define brazing areas with the second frames 15 as will be described later.
• 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 loop 134 which when a heat exchange tube 5 is arranged in the first frame 13 defines a through through opening allowing the flow of the second fluid.
• FIG. 1 illustrates a first embodiment of FIGS. handles 134 of substantially rounded shape
• Figures 2, 3 and 5 illustrate a second embodiment of the handles 134 whose contour is more rectilinear shape.
• any other form of the handles 134 may be considered.
• the handles 134 allow to define the guides for the passage of the second fluid.
• this through opening has a diameter of the order of 2mm.
• the ratio between the diameter of a passage opening of the second fluid and the diameter of a through opening 131 of fluidic communication allowing the flow of the first fluid is in this example of the order of 4.
• each first frame 13 is arranged in alignment with the handles 134 of the other first frames 13 of the heat exchange bundle 3 so as to allow the flow of the second fluid through the bundle 3.
• each first receiving frame 13 has, according to the embodiment illustrated in FIGS. 2 and 3, at least one partition wall 135 which compartmentalizes the first reception frame 13.
• This partition wall 135 is here arranged in the extension of a foot of arch 133.
• each first receiving frame 13 has a partition wall 135, for example substantially central, which compartmentalizes the first receiving frame 13 in two housings 130 to each receive a heat exchange tube 5.
• the partition wall 135 is thus arranged between two heat exchange tubes 5 when they are placed in the first frame 13.
• the partition wall 135 extends in this example over the entire length of the exchange tubes thermal 5 received in the first frame 13.
• the partition wall 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 cutting stamping in a simple manner.
• FIG. 1 An enlarged portion of a first frame 13 is illustrated in FIG.
• the elements of the heat exchange bundle 3, and in particular the first frames 13 and the second 15, at least partially have a coating capable of melting when the assembly passes into the furnace for soldering and to migrate so as to plug the gaps between the parts of the heat exchanger 1 .
• the coating is commonly referred to as "cladd" in the field of brazing metal parts, in particular aluminum.
• the coating is added to the core of the parts, such as the first frames 13 and second frames 15, during manufacture, for example by cold rolling. It may be a non-limiting example of a coating comprising aluminum and silicon.
• the percentage of the coating is for example of the order of 5% to 10% of the material of a frame 13, for example.
• the percentage of the coating is chosen small enough not to weaken the elements of the heat exchange bundle 3, including the first frames 13 and the second 15, after brazing.
• the first frames 13 respectively have at least one recess 139 at an inner corner receiving a corner of a heat exchange tube 5, that is to say on a corner of the inner edge of a first frame 13, which is opposite with a heat exchange tube 5 when the latter is arranged in the first receiving frame 13.
• Such a recess 139 is provided to allow the flow of the coating during brazing of the heat exchanger 1, thus preventing the coating from clogging the first channels or microchannel circulation 7 of the heat exchange tubes 5.
• this roughening 139 takes into account a compromise not to weaken the first frame 13 while being able to collect a sufficient amount of the coating that migrated during soldering.
• this recess 139 is substantially equal to the width of a groove 154 provided for a similar purpose on a second frame 15 as described below.
• the first frames 13 respectively have four recesses 139 respectively arranged at each of the four interior corners of a first frame 13.
• the recess or recesses 139 are arranged close to the fluid communication connection means 131.
• At least one recess 139 is made in the extension of an extreme arch, that is to say of the first or last arch of the succession of arches.
• the second frames 15 may be at least partially made of aluminum.
• the second frames 15 When the second frames 15 receive turbulators 11, the second frames 15 are said frames-turbulators or turbulators frames.
• the second frames 15 have: two opposite edges extending parallel to the direction of the first circulation channels 7 of the first fluid, in other words here in parallel with the longitudinal direction of the heat exchange tubes 5, and
• the general direction of flow of the second fluid means the direction of the circulation in "I” in the case of a circulation in a pass 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 generally similar shape 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 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 side edges of the first frames 13.
• the second frames 15 extend on the same length and on the same width as the first frames 13.
• the outer contours of the first frames 13 and second frames 15 are substantially identical so that the alternating stack 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 is meant the width defined between the inner walls of the opposite longitudinal edges.
• the lateral edges of the second frames 15 may be slightly larger than the lateral edges of the first frames 13, so that the ends of the heat exchange tubes 5 received in the first frames 13 stacked with the second frames 15, rest on the border peripheral peripheral edges of the second frames 15.
• the second frames 15, 15 'thus define an internal length L 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, 15 '.
• the second frames 15 can be made by stamping cut.
• a plurality of second so-called interposed frames 15 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 furthermore comprise a second end frame (not shown) optionally arranged between a first frame 13 and a closure plate 17, in particular the closure plate. 17.
• a second end frame can be put in place for reasons of mechanical strength.
• Each second frame 15 may be shaped for one-pass circulation of the second fluid.
• each second frame 15 defines a second circulation channel 9 for the second fluid.
• the second circulation channel 9 here extends in a substantially "I" shape.
• the second frames 15 allow circulation in two passes of the second fluid.
• the second frames 15 each comprise a bar 150 arranged inside the second frame 15 so as to separate two flow passes for the second fluid. It is therefore an internal bar 150.
• the bar 150 makes it possible to shape the second circulation channel 9 substantially in a "U" shape.
• a circulation of the second fluid in addition to two passes in a second frame 15 and for this purpose more than one bar 150 inside the second frame 15 which would be, by way of non-limiting example, arranged in an offset manner and opposite to each other.
• the bar 150 extends longitudinally inside a second frame
• the bar 150 thus 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. In other words, the bar 150 extends from a side edge of a second frame 15 towards the opposite side edge but without reaching this opposite side edge.
• the bar 150 is 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 towards the opposite side edge, leaving a space.
• the inner bar 150 therefore extends longitudinally from a lateral edge of a second frame 15 over a length l less than the internal length L of the second frame 15.
• the inner bar 150 does not extend over the entire internal width of the second frame 15. More specifically, the inner bar 150 has a width smaller than the internal width of the second frame 15.
• the inlet and the outlet of the flow path for the second fluid are thus defined on each side of the bar 150.
• the bar 150 may also be called tongue.
• the bar 150 is substantially of the same thickness as the second frame 15.
• the bar 150 is for example arranged substantially centrally. More specifically, the bar 150 is arranged substantially in the center of a second frame 15 in the width direction of the second frame 15. In this way, the bar 150 divides the second frame 15 into two parts of the same size.
• each second frame 15 may have an internal length L in a range of about 30mm to 500mm.
• the heat exchange tubes 5 or mono-tubes received in the first frames 13 may rest on the bars 150 of the second frames 15 vis-à-vis.
• the inner bars 150 of the second frames 15 are opposite partitions 135 of first frames 13 made according to the embodiment illustrated in FIGS. 2 and 3.
• the second frames 15, in particular the second intermediate frames 15, have guides 151 for the passage of the first fluid allowing it to flow in the stack of the first reception frames 13 and the second frames 15, in particular spacers.
• the guides 151 are here made in the form of through-passage orifices 151 arranged in alignment with the recesses 131 forming fluid communication with the first reception frames 13, delimited here by the succession of arches.
• the through orifices 151 are thus arranged on at least one lateral edge of a second frame 15, here a second intermediate frame 15.
• the number of throughthrough orifices 151 is adapted as a function of the number of recesses 131 and therefore the number of first circulation channels 7 of the heat exchange tubes 5.
• the second end frame when present, is made similar to a second intermediate frame, except that the second end frame does not have through holes 151 for the passage of the first fluid.
• the second frames 15 respectively have means for fluid communication 152 of 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 second frames 15 respectively have a predefined number of through openings 152 of fluid communication. These through openings 152 are here arranged on the longitudinal edges of the second frames 15 and are aligned with each other in the direction of the height of the heat exchange bundle 3. The through openings 152 open respectively to the inside 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 left, in a complementary manner to the arrangement of the tubes 21 on the same side of the heat exchange bundle 3, here on the right with reference to the arrangement shown in FIG. 1.
• the through openings 152 define a fluid inlet 152 to the inner 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 define the through openings 152.
• the loops 153 of the second frames 15 are made similarly to the loops 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.
• FIG. 1 illustrates a first embodiment of the loops 153 of substantially rounded shape
• FIG. 5 illustrates a second exemplary embodiment. handles 153 whose contour is more rectilinear shape.
• the loops 134 of the first frames 13 are made according to the first embodiment
• the loops 153 of the second frames 15 are made similarly according to the first embodiment.
• the handles 153 of the second frames 15 are made similarly according to the second embodiment.
• any other form of the handles 153 may be considered.
• the opening delimited by a first loop is arranged in fluid communication with a first pipe 21 and the opening defined by a second loop is arranged in fluid communication with a second pipe 21.
• the heat exchanger 1 is preferably assembled by brazing.
• the second frames 15 are intended to be soldered to the first frames 13.
• the longitudinal edges of the second frames 15 are intended to be assembled by soldering to the longitudinal edges of the first frames 13 and the lateral edges of the second frames 15 are intended to be assembled by soldering with the arches 133 provided on the edges of the first frames 13.
• the second frames 15 respectively have at least one tank 154, better visible in Figure 6, capable of collecting the coating or "cladd” during brazing of the heat exchanger 1.
• Each tank 154 is here arranged on a lateral edge of a second frame 15.
• a tank 154 is provided on each lateral edge of a second frame 15.
• Each tank 154 is then situated opposite a lateral edge 13 A 13B of a first receiving frame 13 on which opens an end 50, 52 of a heat exchange tube 5.
• the coating disposed on the first frames 13 and the second frames 15 opposite melts and migrates so as to plug the gaps between the parts of the heat exchanger 1 and flows into the tanks 154, thus preventing the melted and migrated coating from clogging the first circulation channels or microchannels 7 of the heat exchange tubes 5.
• the tank or reservoirs 154 are provided on each side of a second intermediate frame arranged between two first frames 13.
• the reservoir (s) 154 may be arranged on only one face of this second end frame, namely on the face opposite a heat exchange tube 5, and not on the opposite face of the second end frame, vis-à-vis a closure plate 17.
• Each tank 154 can be made by local reduction of material of a second frame 15.
• the depth p of a tank 154 must be chosen large enough to collect the coating, which is for example of the order of 5% to 10% of the material of the second frame 15, and small enough not to weaken the mechanical strength. second frame 15.
• the tank 154 may have a depth p of the order of 0.5 mm.
• the tank 154 is in the form of a groove 154 extending substantially perpendicular to the direction of flow of the first fluid in the heat exchange tubes 5, here in the direction of the width of a second frame 15.
• the tank 154 extends facing the entire end of a heat exchange tube 5, in other words over the entire width of a tube or of each heat exchange tube 5.
• the width of the groove 154 on a second frame 15 is substantially equal to the width of the recess. 139 on a first frame 13.
• the second frames 15, in particular the second intermediate frames may also be shaped to put into fluid communication two heat exchange tubes 5 received in the same first frame 13 according to the embodiment of the first frames 13 illustrated in FIGS. 2 and 3.
• each second frame 15, in particular an intermediate frame advantageously has at least one overturning orifice 155 (see FIG. 5) which is fluid communication with both a first and a second fluid communication means 131, here a first and a second recess 131, first frames 13 on either side of the second spacer frame.
• each turning 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 opens out of a first heat exchange tube 5 undergoes a reversal in the overturning orifice 155 and then flows 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 overturning orifices 155 provided on the second frames 15, in particular spacers.
• Each overturning orifice 155 is here provided between through-through orifices 151 on at least one lateral edge of each second frame 15, in particular a spacer.
• Each overturning 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 overturning orifice 155 has a longitudinal shape extending perpendicularly to the longitudinal edges of the second frame 15, especially intermediate.
• each turning orifice 155 arranged opposite a first receiving frame 13 extends longitudinally on either side of the partition wall 135 of this first receiving frame 13.
• the turning orifice 155 has a substantially oblong shape.
• the turning orifice 155 is dimensioned so as to have a section for the overturning of the first fluid at least equal to the passage section of a heat exchange tube 5.
• a two-pass circulation referred to as a "U" of the first fluid in a first receiving frame 13 according to the second, third or fourth embodiment, and a two-pass circulation, is additionally provided. said "U" of the second fluid in a second frame 15 according to the second embodiment.
• the heat exchanger 1 is then double "U" circulation.
• the heat exchanger 1 comprises a stack of first frames 13 receiving the heat exchange tubes 5 and preferably second frames 15 which can receive turbulators 11. These are simple elements and can be easily assembled by soldering .
• the recesses 139 at the inside corners of the first frames 13 form a flow passage for the coating when the latter melts and migrates during brazing, thus avoiding clogging the first channels or microchannels 7 circulation for the first fluid in the heat exchange tubes 5.

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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)

Applications Claiming Priority (2)

Publications (2)

Family

ID=55451384

Family Applications (1)

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Family Cites Families (3)

• 2015
  • 2015-12-21 FR FR1562889A patent/FR3045805B1/fr not_active Expired - Fee Related
• 2016
  • 2016-12-16 WO PCT/FR2016/053497 patent/WO2017109349A1/fr active Application Filing
  • 2016-12-16 EP EP16829106.0A patent/EP3394546B1/de active Active

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