EP1769212B1 - Echangeur thermique notamment destine a des vehicules - Google Patents

Echangeur thermique notamment destine a des vehicules Download PDF

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Publication number
EP1769212B1
EP1769212B1 EP05771019.6A EP05771019A EP1769212B1 EP 1769212 B1 EP1769212 B1 EP 1769212B1 EP 05771019 A EP05771019 A EP 05771019A EP 1769212 B1 EP1769212 B1 EP 1769212B1
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EP
European Patent Office
Prior art keywords
heat exchanger
flat tubes
ribs
exchanger according
tubes
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP05771019.6A
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German (de)
English (en)
Other versions
EP1769212A1 (fr
Inventor
Albrecht Dorn
Wolfgang Kramer
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 Behr GmbH and Co KG
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Mahle Behr GmbH and Co KG
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Publication of EP1769212A1 publication Critical patent/EP1769212A1/fr
Application granted granted Critical
Publication of EP1769212B1 publication Critical patent/EP1769212B1/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
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings

Definitions

  • the invention relates to a heat exchanger, in particular for motor vehicles according to the preamble of claim 1.
  • Solch a heat exchanger is, for example JP 2003161589 known.
  • Heat exchangers especially those for motor vehicles, eg. As coolant radiator, intercooler or radiator are known in various constructions, which were each prevailing for certain periods.
  • today's automotive heat exchangers are predominantly made of aluminum, while in the 50's and 60's, they used non-ferrous metal finned tube cooling systems, with brass tubes with thin copper fins joined into a block and soft soldered.
  • the tubes are formed as flat or oval tubes and the ribs as flat, flat sheets with passages, which are "threaded" on the pipes.
  • Such flat tube system with flat ribs is for example in the publication " Heat Transfer and Pressure Drop Characteristics of Flat Tube and Louvered Plate Fin Surfaces "by A. Achaichia and TA Cowell, in Experimental Thermal and Fluid Science 1988, pages 147-157 described.
  • Such a system has a relatively low airside pressure drop due to the aerodynamically favorable tube cross section; disadvantageous, however, is the high weight.
  • the tubes In mechanically joined systems, the tubes often have a circular cross section, in part also an oval or elliptical or flat oval cross section.
  • the tubes are widened mechanically with respect to the ribs and the tubesheets, so that a sufficient pressure is achieved, which produces the required tightness in the tube / bottom connection and the necessary thermal contact in the tube / rib connection.
  • the expansion takes place in part by an olive-shaped mandrel, which causes a plastic deformation of the tube relative to the rib or Boden barn meansn which lie resiliently after expansion on the outer circumference of the tube.
  • Such expansion is relatively easy for pipes with circular cross-section, so-called round tubes possible, because there is a uniform distribution of stress over the circumference.
  • a rib passage for a mechanically joined oval tube system was by the DE-C 34 23 746 known, wherein at the edges of the passages also angled surfaces are provided for spacing.
  • a flat oval rib passage, ie for an elliptical tube with an axial ratio of greater than 3: 1 was by the DE-A 44 04 837 Applicant known, wherein provided for spacing nose formed on the walls of the passages are.
  • the expansion of flat oval tubes for a mechanically joined system is in the DE-C 43 32 768 described by the applicant, wherein the expansion elements are pulled through the oval tubes.
  • the mechanically joined systems say that they are cheap to manufacture, less favorable in performance.
  • the disadvantage is a relatively large pipe wall thickness, which - due to the expansion process - is usually over 0.35 mm for aluminum pipes, while 0.07 mm can not be fallen below for the flat aluminum fin in the rule.
  • the rib passage must maintain its elastic hoop stress after the expansion of the tube, so that the rib thickness can not be minimized arbitrarily.
  • Flat tubes with minimal air resistance are not represented as mechanically joined systems, because no pressure can be generated on the flat straight sides.
  • the block is brazed while maintaining the rib tension in a brazing furnace (all parts consist of aluminum or aluminum alloys).
  • a brazing furnace all parts consist of aluminum or aluminum alloys.
  • the bias of corrugated fins and flat tubes during the soldering process is necessary to achieve a perfect soldering.
  • the corrugated fins in conjunction with outer side members cause a support of the flat tubes, so that they can not bulge under the influence of increased internal pressure.
  • the above-mentioned mechanically joined systems give the soldered systems a higher performance (low air-side pressure drop and very good heat conduction between pipe and ribs), but at higher production costs.
  • limits are set in terms of material thicknesses, with a rib thickness of about 0.05 mm to about 0.07 mm may not be exceeded because of the pressure of the corrugated fins for the soldering - the rib thickness is the distance between adjacent tubes for security against buckling dependent.
  • the cassetting process is also cumbersome and time-consuming because corrugated ribs and flat tubes can not be fitted without aids (fixtures).
  • the Applicant has disclosed another brazed flat tube system with corrugated fins for a coolant radiator of a motor vehicle in which flat tubes having a large depth (in the air flow direction) are used.
  • flat tubes and flat ribs with openings are provided for a soldered block, which are penetrated by the flat tubes, the term "flat tubes” in the description as well as in the claims of the present application also being understood to mean slightly ovalized (domed) flat tubes , ie those with slightly curved longitudinal sides.
  • the plate-shaped ribs are thus threaded onto the flat tubes and soldered to them, for which purpose contact surfaces are provided at the openings of the ribs, through which the cohesive connection after soldering and thus an excellent heat transfer between ribs and flat tubes is produced.
  • ribs and tubes are made of aluminum or aluminum alloys, which are joined together by a brazing process to form a solid block.
  • the flat tubes may have any depth (in the direction of air flow) relative to their width (transverse to the direction of air flow) and may also be formed as folded multi-chamber tubes, bead tubes or straw tubes. Since the tube cross section in the region of the ribs is in each case completely enclosed by a rib, an inflation due to internal pressure is prevented. It also results in the advantage that the tubes can be made with significantly lower wall thickness, since a widening is eliminated.
  • the tubes and / or the ribs are provided with a Lotplatt ist, which is rolled onto the semifinished material.
  • a Lotplatt ist Commonly used are aluminum-silicon alloys for solder plating.
  • the finned tube block in vacuum, in an inert gas atmosphere or by the so-called Nocolok® method, known by the DE-A 26 14 872 to be soldered.
  • the tube ends of the flat tubes can be connected to tube sheets, preferably also by soldering.
  • tube sheets preferably also by soldering.
  • both sides collecting boxes, z. B. made of plastic and mechanically connected Likewise, aluminum boxes are possible, so that results in a single-grade all-metal cooler.
  • the tube sheets can also be mechanically connected to the tube ends by means of a rubber seal, this brings the advantage of improved thermal shock resistance.
  • the contact surfaces of the ribs, which enclose the tube are designed as passages known per se, wherein the passages have a slight conicity.
  • the pipes can be inserted more easily or the ribs can be threaded more easily, and on the other hand results in a resilient system of Rippen graspzuges on the pipe, ie with a certain bias.
  • a self-fixed finned tube block which without further devices, eg. B. clamping means can be soldered.
  • the contact surfaces can also be used as tabs, ie. H. be formed inclined flaps, which create against the flat longitudinal sides and / or the narrow sides of the tubes and thus produce a bias to hold the flat tubes.
  • the contact surfaces are designed so that after soldering results in a closed bond between the rib and flat tube, so that the flat sides of the flat tube are supported by the ribs. Due to the inclination of the tabs or the conicity of the passages results in a Lotspalt, which fills with solder during soldering and forms a solder seam after soldering, which surrounds the tube like a ring and thus causes the required stiffening.
  • the passages or tabs may have at their edges angled surfaces or lobes that serve as spacers - or pronounced lugs, which serve as a stop for an adjacent rib. This eliminates additional spacers when threading the ribs.
  • the ribs are bekiemt, d. H. they have between the flat tubes on gills or gill fields, which - as known per se - serve to improve the heat transfer.
  • so-called turbulence generators can be provided in the ribs.
  • the wall thicknesses of the tubes and / or the ribs are minimized to a minimum.
  • the wall thickness of the flat tubes can thus be chosen smaller than 0.3 mm, preferably smaller than 0.2 mm, since expansion of the tubes no longer takes place and on the other hand, a support of the flat tubes is given by the ribbed package and the soldering.
  • the material thickness of the ribs can be lowered below 0.07 mm, and preferably below 0.05 mm, because a pressure as in corrugated ribs in the invention is not provided.
  • a distance of the axes of the flat tubes or slightly ovalized tubes is at least four times as large as the inside diameter, i. the smaller inner diameter of a pipe. This can reduce the weight and material costs of the heat exchanger.
  • a distance of the axes of the flat tubes or slightly ovalized tubes is at most twenty times, more preferably at most ten times as large as the inside diameter of a tube. As a result, a pressure drop of the heat exchanger can be reduced.
  • Fig. 1 shows a section of a finned tube block 1 in a plan view, ie with a view to a substantially flat or flat formed arranged in the plane of rib 2, which is rectangular in shape and has a leading or leading edge 2a and a trailing or trailing edge 2b; the direction of air flow is indicated by arrows L, but may also be in the reverse direction, indicated by a dashed arrow L.
  • the rib 2 is penetrated by a series of flat tubes 3, which have a depth T ro in the air flow direction and a width B transverse to the air flow direction. The depth of the rib T ri is greater than the depth of the tube, ie the flat tube 3 is enclosed on the inflow and outflow side of the rib 2.
  • the illustrated section of the finned tube block 1 thus represents a single-row flat tube system.
  • the invention is not limited to single-row systems, but also extends to multi-row systems in which the flat tubes in the air flow direction either aligned or offset, that can be arranged on a gap.
  • monoblock configurations in which two or more different heat exchangers are combined to form a block, such. B. in the DE-A 195 43 986 the applicant described.
  • the flat tube cross-sections of the individual heat exchanger, z. B. a coolant radiator and a refrigerant condenser have different cross-sections.
  • Fig. 2 shows the finned tube block 1 in a front view, ie seen in the air flow direction (the scale in Fig. 2 does not match the scale in Fig. 1 ).
  • the continuous ribs 2 are arranged parallel to one another and form a ribbed packet 2 ', which is penetrated by the flat tubes 3.
  • Fig. 3 shows a detail of the finned tube block 1, namely the connection of rib 2 and flat tube 3, which has a longitudinal axis 3 'and is shown with its width B.
  • the ribs 2 are - as mentioned - essentially flat and flat or plate-shaped and extend perpendicular to the tube longitudinal axis 3 '.
  • the ribs 2 have so-called passages or collar 6, which are formed from the material of the ribs 2 by known methods, for. As by slitting, tearing, punching and / or embossing - as partially described in the prior art mentioned above.
  • the collars 6 surround the tube 3 preferably over the entire circumference and provide a mechanical contact between the rib 2 and tube 3 ago.
  • the passages 6 are preferably conical, d. H. they have an acute angle ⁇ relative to the outer wall of the flat tube 3.
  • Such a slope on the one hand favors the threading of the tubes 3 and the threading of the ribs 2 on the tubes 3 and on the other hand an elastic conditioning of the collar 6 on the tubes 3.
  • the collar optionally also shaped noses. 7 (shown in dashed lines), as known from the aforementioned prior art.
  • the height of the collar 6 need not be constant over the entire circumference - sometimes this is not possible depending on the geometry of the flat tube cross-section for punching technical reasons, for example, if the rib spacing a should be greater than half the flat tube width (B / 2).
  • the rib spacing a should be greater than half the flat tube width (B / 2).
  • ribs 2 and tubes 3 are made of aluminum or an aluminum alloy and - which is not shown - with a Lotplatt ist, preferably made of an aluminum-silicon alloy.
  • the plating is applied to the semifinished sheets, which are used as starting material for the ribs. and / or pipe production, rolled as a thin layer.
  • This is - spent substantially without further aids such as fixtures or the like - in a brazing furnace, not shown, and brazed, ie immediately below the melting temperature of the base material of the rib and tube.
  • the solder flows during the soldering process in the conical annular gaps between the pipe 3 and passage 6 (angle ⁇ in Fig. 3 ) and fill them with solder.
  • a corresponding Lotmeniscus or a Lotnaht 8 is in Fig. 5 shown.
  • the flat tube 3 is - as in 4 and 5 represented by the arrows P - completely enclosed by the rib 2 and the passage 6, so that there is a strong support effect in the form of a rigid T-profile. An "inflation" of the flat tube 3 at internal pressure is thus prevented.
  • the pipe 3 may - as mentioned - made of a sheet and be formed as longitudinally welded or folded pipe, with folded multi-chamber pipes, bead or Noppenrohre are possible.
  • the tube 3 as extruded, z. B. multi-chamber tube may be formed, wherein the Lotplatt ist is then preferably on the rib 2 and the collar 6.
  • the thickness d of the fin material can be chosen to be relatively low, d. H. less than 0.07 mm, and preferably less than 0.05 mm. Compared to conventional soldered systems, this means a reduction in the rib thickness and thus a reduction in the weight of the finned tube block.
  • the wall thickness s of the tubes can be chosen relatively low, d. H. lower than the pipe wall thickness in mechanically joined systems.
  • the wall thickness s of the flat tubes 3 is 0.35 mm and less, preferably 0.2 mm and less.
  • the finned tube block 1 On the finned tube block 1 can - which is not shown here - tube plates, also made of an aluminum material, are placed, wherein the tube sheets have passages for receiving the pipe ends of the flat tubes 3, so that the bottoms can be soldered tightly to the pipe ends.
  • plastic boxes On this finned tube block including tube plates plastic boxes can then be placed, which in a known manner with the tube sheet be connected by a flare connection.
  • the collecting boxes can also be made of metal, ie of an aluminum material, so that a whole aluminum heat exchanger can be produced with the finned tube block according to the invention.
  • the soldering of the finned tube block or of the Ganzaluminiumebenesttragers can be carried out by various methods, namely in a vacuum, in an inert gas atmosphere or by the so-called Nocolok® process with a non-corrosive flux.
  • tube sheets as is usual in a mechanically joined finned tube block, can be joined by mechanical connection.
  • the pipe ends are inserted through corresponding openings (passages) in the tube sheet; between passages and pipe ends elastomeric seals are arranged. After passing through the pipe ends they are mechanically widened. This results in a solid, but also elastic compound that withstands higher requirements in terms of pressure and thermal shock resistance.
  • brazed finned tube block 1 can be preferably used as a coolant radiator or intercooler for automobiles.
  • the pressures occurring in the charge air cooling or in the coolant cooling of an internal combustion engine can be controlled by the brazed system according to the invention.

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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)

Claims (17)

  1. Echangeur de chaleur, en particulier pour des véhicules automobiles, comprenant un bloc brasé (1) se composant de tubes plats (3) ou de tubes plats légèrement ovalisés et d'ailettes (2), où les tubes plats (3) peuvent être traversés par un premier milieu et communiquent avec au moins un bac collecteur, et les ailettes (2) peuvent être submergées par un second milieu, où les ailettes (2) sont conçues essentiellement de manière plane et disposées en étant parallèles entre elles, lesdites ailettes présentant également des ouvertures ayant des surfaces de contact (6), faisant que les tubes plats (3) sont logés dans les ouvertures et peuvent être brasés dans la zone des surfaces de contact (6), caractérisé en ce que les surfaces de contact sont configurées comme des passages coniques (6) ou comme des pattes (6) placées en oblique, lesquelles pattes viennent en appui sur les grands côtés et / ou sur les petits côtés des tubes plats (3), où les passages (6) ou les pattes forment, avec les grands côtés et / ou les petits côtés des tubes plats (3), un interstice de brasage conique (α).
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que les tubes plats (3) et les ailettes (2) peuvent être fabriqués en aluminium ou dans des alliages d'aluminium et peuvent être brasés par brasage fort.
  3. Echangeur de chaleur selon la revendication 2, caractérisé en ce que les tubes plats (3) et / ou les ailettes (2) sont plaqué(e)s par brasage, étant doté(e)s de préférence d'un placage brasé à base d'aluminium et de silicium.
  4. Echangeur de chaleur selon la revendication 2 ou 3, caractérisé en ce que les tubes plats (3) et les ailettes (2) peuvent être brasés selon le procédé Nocolok®.
  5. Echangeur de chaleur selon l'une quelconque des revendications 1 à 4, caractérisé en ce que les tubes plats (3) présentent des extrémités tubulaires sur lesquelles sont emboîtées des plaques tubulaires comprenant des passages formés dans les plaques.
  6. Echangeur de chaleur selon la revendication 5, caractérisé en ce que les extrémités tubulaires peuvent être brasées avec les passages formés dans les plaques.
  7. Echangeur de chaleur selon la revendication 5, caractérisé en ce que les extrémités tubulaires sont assemblées mécaniquement avec les passages formés dans les plaques, en particulier au moyen d'un joint d'étanchéité en élastomère.
  8. Echangeur de chaleur selon l'une quelconque des revendications 1 à 7, caractérisé en ce que les surfaces de contact (6) sont configurées comme des entretoises pour les ailettes (2).
  9. Echangeur de chaleur selon la revendication 8, caractérisé en ce que les passages (6) ou pattes présentent des bords coudés ou des ergots formés (7).
  10. Echangeur de chaleur selon l'une quelconque des revendications 1 à 9, caractérisé en ce que les ailettes (2) présentent des ouïes (4) ou des champs d'ouïes et / ou des générateurs de turbulences ou de tourbillons (5).
  11. Echangeur de chaleur selon l'une quelconque des revendications 1 à 10, caractérisé en ce que les ailettes (2) présentent une épaisseur de matériau d où d est ≤ 0,07 mm, de préférence où d est ≤ 0,05 mm.
  12. Echangeur de chaleur selon l'une quelconque des revendications 1 à 11, caractérisé en ce que les tubes plats (3) présentent une épaisseur de paroi s où s est ≤ 0,3 mm, de préférence où s est ≤ 0,2 mm.
  13. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les tubes plats sont configurés comme des tubes ovales plats ayant une section presque elliptique, ayant un grand et un petit demi-axe a, b et ayant un rapport d'axe V = a/b, et en ce que le rapport d'axe V est > 5 : 1.
  14. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les tubes plats sont configurés comme des tubes nervurés soudés.
  15. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les tubes plats sont disposés en formant au moins une rangée.
  16. Echangeur de chaleur selon la revendication 15, caractérisé en ce que les tubes plats sont disposés, dans un agencement à plusieurs rangées, en étant alignés ou décalés les uns par rapport aux autres.
  17. Echangeur de chaleur selon la revendication 15 ou 16, caractérisé en ce que les tubes plats sont disposés en formant deux rangées, où une rangée fait partie d'un premier échangeur de chaleur, en particulier d'un radiateur à liquide de refroidissement, l'autre rangée faisant partie d'un second échangeur de chaleur, en particulier d'un condenseur de fluide frigorigène.
EP05771019.6A 2004-07-12 2005-07-12 Echangeur thermique notamment destine a des vehicules Not-in-force EP1769212B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004033786 2004-07-12
PCT/EP2005/007572 WO2006005594A1 (fr) 2004-07-12 2005-07-12 Echangeur thermique notamment destine a des vehicules

Publications (2)

Publication Number Publication Date
EP1769212A1 EP1769212A1 (fr) 2007-04-04
EP1769212B1 true EP1769212B1 (fr) 2017-05-10

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WO (1) WO2006005594A1 (fr)

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FR3038977B1 (fr) * 2015-07-17 2019-08-30 Valeo Systemes Thermiques Echangeur de chaleur a ailettes comprenant des persiennes ameliorees

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