EP2994712B1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
EP2994712B1
EP2994712B1 EP14722208.7A EP14722208A EP2994712B1 EP 2994712 B1 EP2994712 B1 EP 2994712B1 EP 14722208 A EP14722208 A EP 14722208A EP 2994712 B1 EP2994712 B1 EP 2994712B1
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EP
European Patent Office
Prior art keywords
heat exchanger
collecting tube
cross
sectional area
side collecting
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.)
Not-in-force
Application number
EP14722208.7A
Other languages
German (de)
English (en)
Other versions
EP2994712A1 (fr
Inventor
Uwe FÖRSTER
Siegfried Tews
Martin Kaspar
Wolfgang Seewald
Christoph Walter
Gottfried DÜRR
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle International GmbH
Original Assignee
Mahle International GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP2994712A1 publication Critical patent/EP2994712A1/fr
Application granted granted Critical
Publication of EP2994712B1 publication Critical patent/EP2994712B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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

Definitions

  • the invention relates to a heat exchanger according to the preamble of claim 1.
  • the WO 2004/040038 describes such a heat exchanger.
  • the invention relates to a motor vehicle with an air conditioner with a heat exchanger.
  • a heat pump In the air conditioning of a motor vehicle for air conditioning of the passenger compartment is increasingly used in addition to the, powered by electrical energy PTC heating elements (Positive Temperature Coefficient), a heat pump.
  • PTC heating elements Physical Temperature Coefficient
  • the condenser of the air conditioning system is used to heat the passenger compartment. This is when using the heat pump in an electric vehicle or hybrid vehicle of great advantage, since it reduces the energy consumption of the air conditioning and thus a greater range of the motor vehicle can be achieved. For example, it could be determined that the use of the heat pump in the air conditioning system, the range reduction is only 50% compared to that for motor vehicles that use only one PTC heating element for heating.
  • the air conditioner usually has a compressor, an evaporator, a condenser and an expansion valve on.
  • the condenser also referred to as a heat exchanger, provides the heat necessary to heat the passenger compartment of the motor vehicle when the heat transfer medium is cooled and liquefied from the superheated gaseous state to a liquefaction temperature.
  • the heat removed from the heat transfer medium or refrigerant in the condenser is discharged to a surrounding cooling medium, for example air.
  • the flow of air through the condenser is achieved by a condenser fan located generally adjacent to the condenser, as the condenser fan sucks in cold air, passes through the condenser, and is available as heated air to the condenser.
  • the heated air can be passed through ducts into the passenger compartment, for example.
  • heat exchangers are used with a double row of heat exchanger tubes.
  • a heat exchanger is known.
  • the heat exchanger has a heat exchanger network comprising flat tubes and corrugated ribs, wherein the flat tubes are each connected on both sides with a collecting box.
  • the collecting box has a lid portion and a bottom portion, wherein the lid portion in cross-section seen perpendicular to its longitudinal extent has an M- or W-shaped configuration.
  • the heat exchanger should be constructed so that it requires the least possible space.
  • the heat exchanger for an air conditioner in a motor vehicle with a heat exchanger network has heat exchanger tubes, in particular flat tubes and at least one collecting box, wherein the collecting box comprises at least one input-side manifold and an output-side manifold, which are in flow communication with the heat exchanger tubes.
  • the heat exchanger is characterized in that the output-side manifold has a cross-sectional area which is smaller than a cross-sectional area of the input-side manifold.
  • the cross-sectional area of the input-side manifold is larger than a cross-sectional area of the deflector-side manifold, and the cross-sectional area of the deflector-side manifold is smaller than the cross-sectional area of the output manifold.
  • the heat exchanger tubes are preferably arranged side by side in two rows.
  • the heat exchanger tubes are preferably arranged aligned in each case and oriented substantially parallel.
  • the heat exchanger has at least one double-row arrangement. It can also be provided more than two juxtaposed rows of heat exchanger tubes.
  • a two-row arrangement may also be present if the two juxtaposed heat exchanger tubes are made in one piece and a partition along the longitudinal extent of the heat exchanger tubes is arranged, so that two separate parallel flow channels are realized in the heat exchanger tube.
  • the input-side manifold and the output-side manifold are preferably arranged on one side of the heat exchanger tubes, in particular flat tubes and in fluid communication with these.
  • the input-side manifold and the output-side manifold are arranged parallel to each other.
  • the heat transfer medium occurs in the operation of the air conditioning system of the motor vehicle in the input-side manifold of the heat exchanger in the gaseous state, flows through the Heat exchanger tubes, in particular flat tubes and exits the heat exchanger through the output-side manifold in a liquid state of matter, since the heat transfer medium is spent by the condensation in the heat exchanger in the liquid state. In the liquid state, the heat transfer medium has a greater density and requires less volume due to its greater density.
  • the output-side manifold can work with a smaller cross-sectional area and thus a smaller volume than the input-side manifold, which must accommodate the refrigerant in the gaseous phase.
  • the cross-sectional area of the outlet-side header pipe is between 20% and 90% of the cross-sectional area of the inlet-side header pipe.
  • the cross-sectional area of the outlet-side header pipe is between 50% and 90% of the cross-sectional area of the inlet-side header pipe.
  • the cross-sectional area of the outlet-side header pipe is between 50% and 70% of the cross-sectional area of the inlet-side header pipe.
  • a transition between the input-side manifold and the output-side manifold by means of a deflection-side manifold can be realized.
  • the transition by means of the deflection-side manifold is in this case a fluid flow transition.
  • the deflection-side manifold is preferably arranged between two flat tubes.
  • the cross-sectional area of the deflection-side manifold lies between that of the input-side manifold and that of the output-side manifold.
  • the flow cross-section of the deflection-side manifold is between that of the input side and the output side manifold.
  • the reduction in the cross-sectional area of the output-side header pipe is achieved by making the shape of the cross-sectional area of the input-side header pipe different from the shape of the cross-sectional area of the output side header pipe.
  • a bottom portion of the input-side and the output-side manifold is preferably the same.
  • the shape or shape of the input-side manifold is substantially round, wherein the output-side manifold has a flattened or elliptical shape.
  • the cross-sectional areas of the output-side and the input-side manifold are static relative to the length of the respective manifold.
  • the cross-sectional area is constant over the entire length of the manifold and does not change.
  • none of the headers tapers relative to its length.
  • the input side manifold and the output-side manifold arranged side by side and / or substantially parallel.
  • the input-side manifold and the output-side manifold are made in one piece and form the collection box.
  • the collecting box and thus the headers are preferably bent from sheet metal.
  • both the output side and the input side manifold can be bent from a separate sheet and joined together after bending, for example, be soldered.
  • a web forms in the heat exchanger between the input-side manifold and the output-side manifold.
  • the web gives the heat exchanger a certain stability and separates the input-side and output-side manifold, wherein along the longitudinal extension of the headers at least one opening is provided, preferably a plurality of passage openings are provided in the web.
  • it can also be provided to bend both manifolds from a sheet, so that a one-piece collection box is formed with two manifolds and a formed between the output side and the input side manifold web.
  • a motor vehicle having an air conditioning system which comprises a heat exchanger with heat exchanger tubes arranged in two rows, in particular flat tubes and collecting tank having manifolds whose outlet-side manifold has a smaller cross-sectional area than its inlet-side manifold. Due to the smaller cross-sectional area, it is avoided, despite the smaller amount of refrigerant, that a pressure loss occurs in the outlet-side header.
  • FIG. 1 shows a schematic perspective view of a portion of a known double row heat exchanger 10.
  • the heat exchanger 10 is part of an air conditioner (not shown) of a motor vehicle (not shown).
  • the structure of the heat exchanger 10 in FIG. 1 should show the basic structure of the two-row heat exchanger 10.
  • the heat exchanger 10 has substantially parallel arranged behind one another heat exchanger tubes 12, which are formed as flat tubes 12.
  • Each flat tube 12 is in fluid communication with a first, input-side manifold 16 or a second, output-side manifold 18 of the manifold 14.
  • the flat tubes 12 are arranged in alignment in two adjacent rows 20 and 22.
  • a two-row arrangement of flat tubes is also feasible by two flat tubes are integrally formed and have a longitudinal partition wall.
  • two flow paths for the heat transfer medium can be realized in an integrally constructed flat tube.
  • a web 24 is formed, which separates the first manifold 16 and the second manifold 18 and extends over the length 26, or longitudinal extent 26 of the manifolds 16, 18 as an intermediate wall 24.
  • the flat tubes 12 in the respective row 20, 22 are arranged with their broad side 28 one behind the other along the length 32 in alignment and substantially parallel to each other.
  • the flat tubes 12 of the rows 20 and 22 are each also arranged with their thick side 30 side by side substantially parallel.
  • a two-column matrix results from along the headers 16 and 18 aligned behind the other arranged flat tubes 12, which are arranged in each matrix with their wide side 28 in succession in the respective matrix column and so a double row arrangement of Flat tubes 12 form.
  • the heat exchanger tubes 12 may also have another than rectangular base surface with the broad side 28, which has a greater extension than the thickness 30, for example, a square base with two equal sides 28 and 30. Also square heat exchanger tubes 12 may be aligned and in two Rows are arranged side by side, any other base is conceivable in principle for the heat exchanger tubes 12.
  • the heat exchanger 10 has, in addition to the collecting box 14 preferably a further collecting box (not shown), which also has manifolds or at least deflection-side header pipes.
  • the length 32 of the flat tubes 12 and two times the length 26 of the collecting box 14 essentially define the dimensions of the heat exchanger 10 without connection means (not shown), which serve to connect the heat exchanger 10 to a cooling circuit (not shown) of the air conditioning system of the motor vehicle.
  • openings 34 are provided which realize a fluid connection between the first manifold 16 and the second manifold 18, in particular along the longitudinal extent of the manifolds 16 and 18.
  • an opening 34 in FIG. 1 shown.
  • a deflection can also be done in the second collection box, not shown. Even though the second collection box is not shown in FIG FIG.
  • the collection box 14 ' may be configured the same as the collection box 14, for example, the manifolds 16 and 16' and 18 and 18 'may have the same shape, but it may also be different from the collection box 14.
  • the cross-sectional areas of the headers 16, 16 'and 18, 18' may each be the same or different.
  • the second collection box 14 ' can also be provided simple deflection-side header pipes.
  • heat transfer medium flowing from the first row 20 of the flat tubes 12 into the second row 22 of the flat tubes 12 can pass through the collecting box 14 'or through the deflection-side header pipes.
  • intermediate walls may be provided in the manifolds 16 and 18 at different locations transverse to the flow direction of the heat transfer means, closing the flow path in the respective manifold 16 and / or 18 and 16 'and / or 18' and the heat transfer means in operation Forcing flat tubes 12 of the first row 20, for example, in flat tubes 12 of the second row 22 through openings 34 or in the second collection box 14 ', not shown, and vice versa.
  • the headers 16 and 18 are bent from sheet metal and connected together at the web 24, for example soldered to form a stable structure.
  • the input-side manifold 16 and the output side manifold 18 in one piece as a collection box 14 before.
  • the collecting box 14, 14 ' can also be made of prefabricated pipes by connecting the same.
  • the first manifold 16 and the second manifold 18 having a same cross-sectional area 36, 38 and of the same shape shown as it is known per se.
  • the input-side collecting pipe 16 and the output-side collecting pipe 18 have a different cross-sectional area 36, 38, the cross-sectional area 36 of the input-side collecting pipe being larger than the cross-sectional area 38 of the output-side collecting pipe. Examples are in the Figures 5 . 6 and 7 shown.
  • the design of the collecting tank 14 with manifolds 16, 18 with different sized cross-sectional areas 36 and 38 can in this case on the shown construction of the heat exchanger 10 of FIGS. 1 . 2 . 3 and 4 be applied.
  • the ends of the headers 16 and 18 are provided with a cover (not shown).
  • One end of the manifold 16 is provided with a spud (not shown) which is an inlet port (not shown) for the heat transfer medium or refrigerant.
  • One end of the outlet-side header pipe 18 has an outlet opening and is connected to a connecting piece (not shown).
  • FIG. 2 shows the portion of the heat exchanger 10 from FIG. 1 in a cross-sectional view perpendicular through the manifolds 16 and 18 in a plane parallel to the flat tubes 12.
  • the flat tubes 12 are each connected to the manifolds 16 and 18, so that a fluid connection is realized.
  • the collecting box 14 is bent from a sheet metal, wherein the Sheet metal forms an outer wall 39 of the headers 16 and 18 and the two ends of the sheet form the substantially parallel web 24.
  • the two ends are connected to each other and to the outer wall 39, preferably soldered, so that the collecting box 14 is integrally formed and the collecting pipes 16 and 18 are arranged side by side and extend substantially parallel.
  • FIG. 3 shows in a schematic cross-sectional view in a plane of one of the flat tubes 12, another embodiment of the portion of the heat exchanger 10.
  • the collecting box 14 is made of two sheets and has a cover portion 42 and a bottom portion 44.
  • the lid portion 42 is bent from a sheet and the bottom portion 44 is formed from a second sheet.
  • Lid section 42 and bottom section 44 are fluid tightly interconnected at two interfaces 46 and 48, respectively.
  • the web 24 is formed by the lid portion 42 forming sheet.
  • the web 24 is connected to the bottom portion 44 approximately in the middle portion 47 thereof.
  • FIG. 4 shows in a schematic cross-sectional view along the longitudinal extent of the flat tubes 12, a further embodiment of the portion of the heat exchanger 10, the manifolds 16 and 18 are formed by the lid portion 42 and the bottom portion 44 and a separate web 24 a.
  • FIG. 5 shows a schematic sectional view in a plane perpendicular to the longitudinal extent 26 of the header 14, a further embodiment of the construction of the manifolds 16 and 18.
  • Each manifold 16 and 18 is formed of a separate sheet, preferably bent, which the outer wall 39 of the respective manifold 16, 18 forms.
  • the collecting box 14 is located after the Assembly in one piece.
  • openings are either 16, 18 introduced in the sheet before forming the manifolds, for example, pre-punched or introduced after the molding of the manifolds 16 and 18, for example by laser cutting. It is also possible to use prefabricated metal sheets with openings for connecting the flat tubes 12 and the headers 16, 18. Likewise, prefabricated tubes can be used, which are connected to each other to the collection box 14.
  • FIG. 6 shows a schematic sectional view of the collection box 14 of the heat exchanger 10 according to the invention with the input side manifold 16 and the output side manifold 18.
  • the input side manifold 16 has a larger by about half cross-sectional area 36 as the output side manifold 18, whose cross-sectional area is designated by the reference numeral 38 ,
  • the flow cross-sectional area in the inlet-side flow channel, which is formed by the manifold 16 something between 70% and 50% greater than the flow cross-sectional area of the output side manifold 18.
  • the cross-sectional area 38 of the outlet-side collector tube 18 is always smaller than that of the inlet-side collector tube 16.
  • the ratio of the cross-sectional area 38 to the cross-sectional area 36 is preferably between 0.2 and 0.9. If the cross-sectional area 36 of the input-side collector tube 16 is designated by A1 and the cross-sectional area 38 of the outlet-side collector tube 18 by A2, the following applies: 0.2 ⁇ A 2 / A 1 ⁇ 0.9
  • the ratio is between 0.5 and 0.9.
  • the cross-sectional area 36 of the input-side collecting tube 16 is twice as large as the cross-sectional area 38 of the output-side collecting tube 18 or at least approximately 1.45 times as large. The following applies: 0.5 ⁇ A 2 / A 1 ⁇ 0.7
  • the base surfaces or bottom surfaces 44 of the manifolds 16 and 18 are the same size.
  • the different cross-sectional areas 36, 38 are realized by a different shape of the manifold 18 compared to the manifold 16.
  • the lid portion 42 of the collecting tube 18 is flattened, so that an approximately elliptical shape of the collecting tube 18 is formed.
  • the input-side manifold 16 and the output-side manifold 18 are preferably not symmetrical at least in a portion near the bottom portion 44, i. asymmetrically with respect to a central axis 50.
  • the manifold 16 and the manifold 18 have at a web 24 forming side 52 each have a nearly right angle between the bottom portion 44 and the lid portion 42.
  • a transition between the input-side manifold 16 and the output-side manifold 18 can be realized by means of a deflection-side manifold.
  • the deflection-side manifold has a cross-section, the cross-sectional area between the cross-sectional surfaces 36 and 38 is located.
  • the deflection-side manifold can be preferably realized by a collection box 14 corresponding collection box 14 ', each with a first manifold 16 'and a manifold 18' to the collection box 14 opposite end of the flat tubes 12 is arranged. Both ends of the collecting box 14 'are preferably closed by a fluid-tight cover (not shown).
  • the cross-sectional surfaces 36 and 38 are statically formed over the length 26 of the manifolds 16 and 18, that is, the cross-sectional area 36 and 38 of the manifold 16 and 18 does not change over the longitudinal extent 26, but remains constant.
  • FIG. 8 shows a schematic representation of a principle Verschaltungsart the two-row heat exchanger 10.
  • the heat exchanger 10 has a heat exchanger network, of the in FIG. 8 only schematically flow paths for a heat transfer medium or refrigerant are shown.
  • an input flow channel 60 or input flow path 60 and in the collection tube 18, an output flow channel 62 or output flow path 62 is realized.
  • the in the representation in FIG. 8 substantially horizontally extending flow paths 64a, 64b, 64c, 66a, 66b, 66c and 68a, 68b, 68c extend in the flat tubes 12 and in the diverter-side manifold.
  • the deflection-side collecting pipe is preferably realized in or through the collecting box 14 ', wherein the flow paths 64b, 66b, 68b are respectively realized through an opening 34' in a web 24 'of the collecting box 14'.
  • FIG. 8 There are in FIG. 8 in each case two flat tubes 12 and a deflecting-side collecting tube are arranged in each of the horizontally extending plane 70a, 70b, 70c.
  • the direction of an air flow or air flow passing essentially vertically through the heat exchanger 10 is shown by the arrow 72, which thus represents the air flow direction 72.
  • a profile of the fluid flow of the heat transfer medium or refrigerant is illustrated by the arrows, which are designated by the reference numerals 64, 66 and 68.
  • the fluid flow occurs, as illustrated by the arrow 60, in the inlet opening of the manifold 16 a.
  • the fluid can be distributed over the length 26 of the collecting tube 16 and at the same time flow into the respective flat tube 12 in the three planes 70a, 70b and 70c.
  • the fluid flows through the deflection-side collecting tube and enters in each case the flat tube 12 which implements the flow channel 64c, 66c and 68c.
  • the fluid may be directed through respective partitions and passage openings disposed in the manifold 16 'and 18', respectively, in the respective planes 70a, 70b and 70c, or may be distributed to the planes 70a, 70b and 70c.
  • the fluid flows through the flat tube 12 of the respective plane 70 a, 70 b and 70 c, enters the collecting tube 18 and leaves the heat exchanger 10 through an outlet opening of the collecting tube 18, illustrated by the arrow 62.
  • FIG. 9 shows a further possibility for the fluid flow of the heat transfer medium or refrigerant, which is realized by a different Verschaltungsart arranged in the manifolds 16, 18, 16 ', 18' passage openings and partitions.
  • the fluid flows in gaseous form into the heat exchanger 10 as illustrated by the arrow 60.
  • the fluid can be distributed over the three levels 70a, 70b and 70c in the inlet-side manifold 16 and flows along the flow paths 64a, 66a and 68a in the respective flat tubes 12.
  • the fluid can be distributed in each case to the three levels 70a, 70b and 70c.
  • the fluid can only be deflected in depth in the plane 70c through the diverter-side manifold and then flow through the flow path 66c. After the fluid has flowed through the flat tube 12, the plane 70c, this can enter the manifold 18. Here is a deflection in the width in the plane 70b. The fluid can in the flat tube 12 enter the plane 70b and this in the reverse order in flow path 66b 'in the direction of the manifold 18' flow through.
  • FIGS. 8 and 9 are merely exemplary flow paths possible for the heat transfer medium. Other possible flow paths, which can be realized with the heat exchanger 10 according to the invention, are in the DE 202010000951 U1 are included as a part of this description.

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

Claims (10)

  1. Echangeur de chaleur pour un système de climatisation dans un véhicule automobile comprenant un réseau d'échangeurs de chaleur, lequel réseau présente des tubes d'échangeurs de chaleur (12), en particulier des tubes plats (12) et au moins un bac collecteur (14), où le bac collecteur (14) comprend au moins un tube collecteur (16) côté entrée et un tube collecteur (18) côté sortie, tubes collecteurs qui sont en communication d'écoulement avec les tubes d'échangeurs de chaleur (12), où le tube collecteur (18) côté sortie présente une surface de section (38) qui est plus petite qu'une surface de section (36) du tube collecteur (16) côté entrée, caractérisé en ce que la surface de section (36) du tube collecteur (16) côté entrée est plus grande qu'une surface de section du tube collecteur côté retour de flux, et la surface de section du tube collecteur côté retour de flux est plus petite que la surface de section (38) du tube collecteur (18) côté sortie.
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que la surface de section (38) du tube collecteur (18) côté sortie est comprise entre 20 % et 90 %, de préférence entre 50 % et 90 %, en particulier de préférence entre 50 % et 70 % de la surface de section (36) du tube collecteur (16) côté entrée.
  3. Echangeur de chaleur selon la revendication 1 ou 2, caractérisé en ce qu'une transition entre le tube collecteur (16) côté entrée et le tube collecteur (18) côté sortie peut être réalisée au moyen d'un tube collecteur côté retour de flux.
  4. Echangeur de chaleur selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la forme de la surface de section (36) du tube collecteur (16) côté entrée est différente de la forme de la surface de section (38) du tube collecteur (18) côté sortie, où une surface de fond (44) du tube collecteur (16) côté entrée est identique à la surface de fond (44) du tube collecteur (18) côté sortie.
  5. Echangeur de chaleur selon l'une quelconque des revendications 1 à 4, caractérisé en ce que la surface de section (36) du tube collecteur (16) côté entrée et la surface de section (38) du tube collecteur (18) côté sortie sont statiques par rapport à la longueur (26) du tube collecteur (16) côté entrée et par rapport à la longueur (26) du tube collecteur (18) côté sortie.
  6. Echangeur de chaleur selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le tube collecteur (16) côté entrée et le tube collecteur (18) côté sortie sont disposés en étant l'un à côté de l'autre et / ou en s'étendant pratiquement de façon parallèle.
  7. Echangeur de chaleur selon l'une quelconque des revendications 1 à 6, caractérisé en ce que le tube collecteur (16) côté entrée et le tube collecteur (18) côté sortie sont réalisés de façon monobloc et forment le bac collecteur (14).
  8. Echangeur de chaleur selon l'une quelconque des revendications 1 à 7, caractérisé en ce qu'une partie pleine (24) est disposée entre le tube collecteur (16) côté entrée et le tube collecteur (18) côté sortie, laquelle partie pleine forme une paroi intermédiaire (24) suivant l'étendue longitudinale (26) des tubes collecteurs (16, 18), laquelle paroi intermédiaire présente au moins une ouverture (34) se situant dans l'étendue longitudinale (26) des tubes collecteurs (16, 18).
  9. Echangeur de chaleur selon l'une quelconque des revendications 1 à 8, caractérisé en ce que les tubes d'échangeurs de chaleur (12), en particulier des tubes plats (12), sont disposés les uns à côté des autres, sur deux rangées (20, 22).
  10. Véhicule automobile comprenant un système de climatisation qui présente un échangeur de chaleur (10) selon l'une quelconque des revendications 1 à 9.
EP14722208.7A 2013-05-07 2014-05-07 Échangeur de chaleur Not-in-force EP2994712B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013208396.3A DE102013208396A1 (de) 2013-05-07 2013-05-07 Wärmeübertrager
PCT/EP2014/059334 WO2014180904A1 (fr) 2013-05-07 2014-05-07 Échangeur de chaleur

Publications (2)

Publication Number Publication Date
EP2994712A1 EP2994712A1 (fr) 2016-03-16
EP2994712B1 true EP2994712B1 (fr) 2018-11-21

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EP14722208.7A Not-in-force EP2994712B1 (fr) 2013-05-07 2014-05-07 Échangeur de chaleur

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EP (1) EP2994712B1 (fr)
DE (1) DE102013208396A1 (fr)
WO (1) WO2014180904A1 (fr)

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DE102015215253A1 (de) * 2015-08-11 2017-02-16 Bayerische Motoren Werke Aktiengesellschaft Kühlvorrichtung für Energiespeicher
EP3690377A1 (fr) * 2019-01-29 2020-08-05 Valeo Systemes Thermiques-THS Échangeur de chaleur, boîtier et circuit de conditionnement d'air comprenant un tel échangeur de chaleur

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DE102013208396A1 (de) 2014-11-13
EP2994712A1 (fr) 2016-03-16
WO2014180904A1 (fr) 2014-11-13

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