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

• Heat exchanger in particular for a motor vehicle
• 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 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 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 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 to the destruction of the battery, or even the motor 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.
• These heat exchangers can in particular be heat exchangers assembled by soldering.
• 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.
• 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 must withstand such high pressures.
• 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 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 simple to achieve and having a small footprint all while having interesting properties to withstand the strong local pressures.
• the subject of the invention is a heat exchanger, in particular for a motor vehicle, said exchanger comprising a heat exchange bundle with a plurality of heat exchange tubes defining circulation channels for a fluid.
• said exchanger comprising a heat exchange bundle with a plurality of heat exchange tubes defining circulation channels for a fluid.
• the heat exchange bundle comprises a plurality of first heat exchange tube receiving frames
• the first receiving frames of the heat exchange tubes respectively comprise at least one stress absorption zone, arranged on at least one edge facing an end of a heat exchange tube and capable of resist mechanical stress.
• Such a heat exchanger has a 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 C0 2 as a refrigerant.
• 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.
• 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:
• the stress absorption zones are formed by a predetermined number of stress absorption legs formed on at least one edge of a first receiving frame opposite one end of an exchange tube thermal and extending towards the end of the heat exchange tube;
• the stress absorption legs extend longitudinally substantially parallel to the flow direction of the fluid in the circulation channels;
• the first frames have a plurality of recesses, and two adjacent stress-absorbing legs extend on either side of a recess;
• the first frames respectively have at least one edge opposite one end of a heat exchange tube shaped in a pattern defining a succession of arches, the arches legs forming the absorption legs of constraints;
• the heat exchanger comprises at least one fluid collection box, and when heat exchange tubes are received in the first frames, arches vaults define with the ends of the heat exchange tubes of the fluidic communication connection openings between the collector box and the heat exchange tubes, so that a fluidic communication opening is arranged between two arches;
• the heat exchanger is assembled by soldering and the stress absorption legs define soldering zones.
• a first fluid is able to circulate in the heat exchange tubes, and the heat exchanger further comprises a plurality of second frames respectively arranged alternately with the first receiving frames of the tubes. of heat exchange, and respectively defining a second circulation channel for a second fluid so as to allow a heat exchange between the first fluid and the second fluid.
• the heat exchange tubes are received and maintained in dedicated first 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 flows. only coolant.
• the second frames have through holes arranged in the alignment of the recesses, so as to allow the flow of the first fluid in the stack of the first frames and second frames.
• the superimposed frames make it possible to create the flow path of 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 of the second fluid, in particular on two opposite sides of the heat exchange bundle.
• FIG. 1 is a perspective view of a heat exchanger according to the invention
• FIG. 2 is a sectional view from below of the heat exchanger of FIG. 1;
• FIG. 3 is a partial perspective view of a stack of first frames and second frames of the heat exchange bundle of the heat exchanger of FIG. 1;
• FIG. 4 schematically represents a first frame of the beam heat exchanger receiving two heat exchange tubes
• FIG. 5 is a view of the first single frame of FIG. 4, and
• FIG. 6 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.
• 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.
• the coating is commonly referred to as "clad" in the field of brazing 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 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 CO 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 the 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 two fluids, or both fluids.
• the heat exchange bundle 3 comprises a plurality of heat exchange tubes 5, visible in FIGS. 2 to 4, stacked so as to alternately define first channels (not visible in the figures) of circulation 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 (not visible in the figures) for the first fluid, in particular micro-flow 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 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 flow in
• 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.
• 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 as illustrated in FIGS. 2 and 3.
• turbulators 11 may be formed on the heat exchange tubes 5, for example by deformations such as corrugations of the heat exchange tubes 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 an alternating stack of first frames 13 and second frames 15.
• At least some second frames 15 form the dividers.
• 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 set forms another stage of the heat exchange bundle 3. These two sets or stages are repeated as many times as necessary depending on 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 in particular at least one bottom closure plate 17 and at least one upper closure plate 18, can be arranged on either side of the wall. stacking of the first frames
• the closure plates 17, 18 are of complementary shape to the shape of the first frames 13 and the second frames 15.
• the heat exchanger 1 furthermore comprises less a 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 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 edges lateral sides 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.
• 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. As previously, 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 maintained in the first respective frames 13 before superposition of the various frames 13, 15.
• Each first frame 13 may receive a heat exchange tube 5 or alternatively at least two heat exchange tubes 5, as illustrated in FIGS. 2 to 5, so that the heat exchange bundle 3 then has the minus 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.
• Fluidic communication at one end of two adjacent heat exchange tubes 5 received in the same 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 of the first fluid with the manifold 19.
• each first frame 13 are advantageously arranged in fluid communication with the fluidic communication means 131 of the other first frames 13 of the heat exchange bundle 3 and with the manifold 19.
• the means for placing in fluid communication 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 fluidic 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.
• These recesses 131 are here provided on two opposite edges 13A, 13B (see FIGS. 4 and 5) of the first frames 13 which are facing 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 .
• 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 tube (s) heat exchange 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 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, otherwise said recess 131 is made between two adjacent arches 133 and is delimited by these two arches 133 and the arch arch 132 connecting them.
• the fluid communication connection means 131 can 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 the first row of first heat exchange tubes with the manifold 19.
• second means of in communication 131 ensure the fluidic communication of the second heat exchange tubes 5 or in other words 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 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 absorption legs constraints.
• 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 make it possible to define soldering 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 loop 134 which, when a heat exchange tube 5 is arranged in the first frame 13, defines a passage through opening allowing the flow of the second fluid.
• the handles 134 allow 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 flow of the second fluid through the bundle 3.
• FIG. 1 illustrates a first embodiment of loops 134 of substantially rounded shape
• FIGS. 2 to 5 illustrate a second exemplary embodiment.
• handles 134 whose contour is more rectilinear shape.
• any other form of the handles 134 may be considered.
• each first receiving frame 13 may have at least one partition wall 135 which compartmentalizes the first receiving frame 13.
• This partition wall 135 is here arranged in the extension of an arch foot 133.
• each first receiving frame 13 has a partition wall 135, for example substantially central, which compartmentalizes the first receiving frame 13 into two housings 130 (see Figure 5) to receive each a heat exchange tube 5.
• Partition wall 135 is therefore arranged between two tubes 5 in the first frame 13.
• the partition wall 135 extends over the entire length of the heat exchange tubes 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.
• 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 channels (not visible in the figures) of circulation of the first fluid in the heat exchange tubes 5, otherwise said here parallel to the longitudinal direction of the heat exchange tubes 5, and
• the second frames 15 with respect to the general direction of flow of the second fluid flowing against the current of the first fluid, namely that the second frames 15 have:
• 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.
• internal length the length defined between the inner walls of the opposite side 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 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 thus 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 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 optionally arranged between a first frame 13 and a closure plate, in particular the bottom closure plate 17.
• second end frame can be put in place for reasons of mechanical strength.
• the second frames allow two-pass circulation 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.
• the strip 150 extends longitudinally inside a second frame 15.
• the strip 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 side edge of a second frame 15 towards the opposite side edge but without reaching the 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 thus 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 inner bar 150 does not extend over the entire internal width of the second frame 15.
• the inner bar 150 has a width smaller than the internal width of the second frame 15.
• the width of the inner bar 150 may be greater than or equal to, preferably greater than, the thickness of the second frame 15. It defines thus on each side of the bar 150, the inlet and the outlet of the flow path for the second fluid.
• 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.
• the bar 150 divides the second frame 15 into two parts of the same size.
• the inner bar 150 extends over a length at least equal to half the internal length of a second frame 15.
• the inner bars 150 of the second frames 15 are opposite partitions 135 of 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 it to flow in the stack of the first reception frames 13 and the second frames 15, especially 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 thus the number of first circulation channels of the heat exchange tubes 5.
• 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.
• Fluidic 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, of 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 direction of the height of the heat exchange bundle 3, in other words in the stacking direction of the various frames 13 , 15.
• 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 right or left, complementary to the arrangement of the tubes 21 on a same side of the heat exchange bundle 3, here to the right with reference to the arrangement shown in FIG.
• 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.
• Figure 1 illustrates a first embodiment of the loops 153 of substantially rounded shape
• Figure 6 illustrates a second embodiment of the invention. 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 defined 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. Furthermore, as said above, 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 soldered to the longitudinal edges of the first frames 13 and the lateral edges of the second frames 15 are intended to to be assembled by soldering with the arches 133 provided on the lateral edges of the first frames 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 as illustrated in FIGS. 2 to 4.
• each second frame 15, in particular the spacer advantageously has at least one overturning orifice 155 (see FIGS. 2 and 6) which is in fluid communication with both first and second fluid communication means 131, here first and second recesses 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 turning orifice 155 is here formed between passage orifices 151 through at least one side edge of each second frame 15, including interlayers.
• 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 facing a first receiving frame 13, extends longitudinally on either side of the partition wall 135 of this first receiving frame 13, as is better visible on 16.
• 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" circulation
• a two-pass circulation referred to as a "U" circulation
• a two-pass circulation called a "U” circulation of the second fluid in a second 15.
• the heat exchanger 1 is then double "U" circulation.
• 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 easily assembled by particular brazing.
• Such a heat exchanger 1 as described above also has a very good resistance to high pressures, in particular due to the circulation of C0 2 , as well as optimized heat exchange performance.
• the conformation of the edges of the first frames 13 receiving the heat exchange tubes 5 with stress absorption zones formed by arch feet 133 makes it possible to obtain a heat exchanger 1 having a better mechanical strength compared to the solutions of the prior art.
• these arch feet 133 advantageously form brazing zones with the second frames 15.

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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)

Applications Claiming Priority (2)

Publications (2)

Family

ID=55411610

Family Applications (1)

Country Status (3)

Family Cites Families (4)

• 2015
  • 2015-12-21 FR FR1562890A patent/FR3045806A1/fr not_active Withdrawn
• 2016
  • 2016-12-16 WO PCT/FR2016/053494 patent/WO2017109347A1/fr active Application Filing
  • 2016-12-16 EP EP16829104.5A patent/EP3394554B1/de active Active

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