EP2232183B1 - Échangeur de chaleur, en particulier radiateur pour des véhicules automobiles - Google Patents

Échangeur de chaleur, en particulier radiateur pour des véhicules automobiles Download PDF

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Publication number
EP2232183B1
EP2232183B1 EP08859570.7A EP08859570A EP2232183B1 EP 2232183 B1 EP2232183 B1 EP 2232183B1 EP 08859570 A EP08859570 A EP 08859570A EP 2232183 B1 EP2232183 B1 EP 2232183B1
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EP
European Patent Office
Prior art keywords
coolant
row
flow
region
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
EP08859570.7A
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German (de)
English (en)
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EP2232183A2 (fr
Inventor
Michael Kohl
Miriam Lozano-Aviles
Thomas Strauss
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 EP2232183A2 publication Critical patent/EP2232183A2/fr
Application granted granted Critical
Publication of EP2232183B1 publication Critical patent/EP2232183B1/fr
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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
    • F28D1/053—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
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage 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
    • 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
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • 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
    • F28D2021/0091—Radiators
    • F28D2021/0096—Radiators for space heating

Definitions

  • the invention relates to a heat exchanger according to the preamble of claim 1.
  • Heat exchangers in particular radiators for motor vehicles, are flowed through on the primary side by a liquid medium, in particular coolant, and act on the secondary side by ambient air, which is supplied to the vehicle cabin.
  • Known radiators have an existing of pipes and ribs block in which enters the air to be heated and exits on the back again.
  • a problem with the heating of the air in the radiator block is that the air outlet temperatures on the air outlet surface are not the same everywhere, so that strands of different air temperature occur in the heated air. This is disadvantageous for a targeted heating of the interior.
  • a radiator which is usually formed Chareihig or Mateflutig
  • different flow patterns are known, the simplest form is a parallel flow, in which all tubes are flowed through in the same direction.
  • a U-shaped flow through the radiator wherein in a coolant box, a partition wall (transverse partition wall) is arranged. Since this deflection of the coolant takes place transversely to the air flow direction, it is called a deflection "in the width”. Based on both media streams, coolant and air, this is called a cross flow.
  • the coolant cools down, so that the air is heated more strongly on the inlet side radiator half than on the outlet side half, which leads to the mentioned strandiness.
  • the coolant in relation to the air flow in cocurrent or countercurrent to lead ie the coolant is deflected in a multi-row radiator from one row to the adjacent row.
  • a longitudinal partition is required, which separates adjacent rows on one side. This is called redirection "in the deep”.
  • DC or countercurrent It is known that can achieve better efficiencies with the countercurrent.
  • a disadvantage, in particular with wider radiators that the coolant must be distributed over the full width on the inlet side - this can cause the outer tubes are flowed through at a slower coolant inlet, which also affects the air outlet temperature unfavorable.
  • the DE 44 31 107 C1 has been known a radiator for motor vehicles, which operates on the countercurrent principle.
  • the coolant is deflected in one or more stages from the air outlet side in the direction of the air inlet side. This can be a higher heat transfer performance can be achieved.
  • the pamphlets US 2003/0041610 A1 and EP 1460 363 A2 disclose a heat exchanger according to the preamble of claim 1.
  • the liquid medium enters a first region, the inlet region, and is deflected within this air outlet side series into a second region, wherein both the first and the second region may have partial regions.
  • the coolant entering the first row of flow channels is deflected at least once in width.
  • the coolant is deflected from the first to the second, ie the air inlet side row, wherein all the flow channels of the second row are flowed through in the same direction.
  • the coolant is also in the second, d. H. the windward row at least once deflected. Overall, the coolant flow is thus deflected twice in width and once in depth. Due to the opposing flow of coolant in both rows of tubes, the air outlet temperature profile can be homogenized even more.
  • the entry region in the first row is arranged centrally, while the second region comprises two sub-regions, which are arranged symmetrically next to the first region.
  • the incoming coolant stream is thus divided after the first pass and deflected in opposite directions in the width of the heat exchanger.
  • the coolant flows exiting from the two partial areas are deflected in the depth and distributed to the second row in such a way that all flow channels are flowed through in the same direction.
  • This achieves a symmetrical air outlet temperature profile, i. H. Any deviations from a homogeneous temperature distribution occur symmetrically. Alternatively it can be deflected in the second row in the width.
  • the flow cross sections of the first and the second region are the same, d. H.
  • the same flow velocities occur in the flow channels of the first and second regions, ie. H. seen across the entire width.
  • the flow cross section of the second region is particularly preferably greater than that of the first region, with the result that there is a delay in the flow in the flow channels of the second region. This compensates for the cooling of the liquid medium, so that a homogeneous air outlet temperature distribution is obtained as an advantage.
  • the flow cross section of the second row is adapted to the flow cross section of the second region of the first row, in such a way that the entire flow cross section of the second row is either equal to or greater than the entire flow cross section of the second region.
  • an expansion of the Flow cross section due to the further cooling of the liquid medium, an expansion of the Flow cross section.
  • either the same flow rate in the second row as in the second range can be achieved or a delay of the flow - with the result that more heat can be released into the air and a lower pressure drop occurs.
  • an extension of the flow cross-section can be carried out with the result of a reduced flow velocity.
  • the heat exchanger is designed as a radiator of a heating system for motor vehicles, d. H.
  • the flow channels are formed as tubes, preferably as flat tubes or multi-chamber tubes, which are flowed through by the coolant and between which corrugated ribs are preferably arranged as secondary surfaces.
  • the flat tube cross sections of the second row - depending on the flow pattern - the same a greater or lesser depth than the flat tubes of the first row.
  • a greater cooling of the coolant and thus a higher heat transfer performance can be achieved.
  • the radiator according to the invention preferably comprises headers or containers, d. h an inlet box, via which the coolant enters, an outlet box, via which the coolant exits, or a coolant inlet and outlet box or a deflection box.
  • Fig. 1 shows a schematic representation of a first embodiment of the invention, namely a flow model for a double-row radiator 1, of which only tubes 2 (without ribs) of a first row 3 and a second row 4 are shown.
  • a longitudinal partition wall 5 with two transverse partition walls 6, 7 in the inlet region of the tubes 2 and a further, continuous longitudinal partition 8 in the lower region of the block 1 are partially shown.
  • the tubes 2 are, as indicated by flow arrows, flows through a coolant, which is branched off from a cooling circuit, not shown, of an internal combustion engine of a motor vehicle.
  • the radiator block 1 is used to heat air, which flows through the block 1 according to the arrow L and not shown ribs between the tubes 2, so-called secondary surfaces, overflowed.
  • the heated air is supplied to the cabin of the motor vehicle.
  • the first row 3 of the radiator block 1, also referred to below as block 1 for short, is subdivided into three regions due to the partitions 5, 6, 7, a first region 9 being contained within the partitions 5, 6, 7 and a second region 10 two partial areas 10a, 10b, on both sides of the transverse partition walls 6, 7 are arranged.
  • the first region 9, also called inlet region comprises four tubes 2, while the two partial regions 10a, 10b each comprise two tubes 2.
  • the coolant enters the tubes 2 via the inlet region 9 according to the arrows E and flows through them from top to bottom (the terms above and below refer to the illustration in the drawing).
  • the coolant flow is divided, in each case to the outside - within the first row 3 - deflected and then enters the tubes 2 of the portions 10 a, 10 b to flow through them from bottom to top.
  • the deflection of the coolant is indicated by the arrows UB, UB means deflection in width.
  • the two diverted in the depth of coolant partial flows are distributed to all tubes 2 (in the illustrated embodiment 8) of the second row 4 and flow through this from top to bottom.
  • the deflection of the coolant in the width corresponding to the arrows UB is through the continuous longitudinal partition wall 8 - in conjunction with a coolant box, not shown, as in subsequent Fig. 6a, 6b shown - allows.
  • the flow pattern described above corresponds to a cross-counterflow, based on coolant and air flow.
  • the first row 3 is the air outlet side row, also referred to below as the leeward row
  • the second row of tubes 4 is the air inlet side row, also referred to below as the windward row.
  • the coolant thus enters the leeward row 3 in the block 1, is first deflected in width and then in depth, with all the tubes 2 of the windward row 4 are flowed through in the same direction.
  • This flow through the radiator block 1 causes a largely homogeneous Air outlet temperature, ie after the exit of the air from the first row 3.
  • Fig. 2 shows a schematic representation of the radiator block 1 according to Fig. 1 in a view from above of the tubes 2, which are arranged in the two rows 3 and 4.
  • the air flow direction is again indicated by an arrow L.
  • the flow direction of the coolant is represented by dot symbols 11 and cross symbols 12, wherein the dot symbols 11 represent an upward flow direction (out of the drawing plane) and the cross symbols represent a coolant flow downward, ie into the drawing plane.
  • the tubes 2 of the inlet region 9 are marked with a clamp a, the tubes 2 of the two partial regions 10a, 10b with clamps b1, b2 and the tubes 2 of the series 4 with a clamp c.
  • the letters a, b1, b2, c stand for the respective number of tubes.
  • the cross sections of the tubes 2 are formed as flat tube cross sections and each have a depth T1 in the first row 3 and a depth T2 in the second row 4.
  • the entire depth of the block 1 is marked T.
  • T the relationship a ⁇ (b1 + b2).
  • b1 + b2 a
  • the same flow velocity for the coolant as in the tubes 2 of the inlet region 9 results in the tubes 2 of the outer partial regions 10a, 10b.
  • the flow cross section becomes for the second region but slightly increased, so that a delay of the coolant flow is achieved. This also contributes to a homogenization of the air outlet temperature profile.
  • the preferred depth dimension T2 for the second row 4 is in the range between 0.5 T1 and T1.
  • Fig. 2a shows two equivalent embodiments for the aforementioned and illustrated tubes 2, each having a flat tube cross-section.
  • Fig. 3 shows a second unclaimed example, wherein like reference numerals are used for like parts.
  • the block 1 again has two rows 3, 4 of flat tubes 2, the first row 3 being subdivided into a first area 13, the entry area, and a second area 14.
  • the inlet region 13 is divided by a longitudinal partition wall 15 and a transverse partition wall 16.
  • the coolant enters according to the arrows E in the tubes 2 of the inlet region 13, is then according to the arrows UB in the width, ie deflected within the row 3 and then flows through the tubes 2 of the second region 14 from bottom to top.
  • the coolant is deflected in the depth, corresponding to the arrows UT and distributed to all tubes 2 of the second row 4, which are all flowed through in the same direction from top to bottom. Thereafter, the coolant exits the block 1. Even with this flow pattern results in a homogeneous air outlet temperature profile.
  • Fig. 4 shows a third, unclaimed example, wherein the same reference numerals are again used for the same parts.
  • a first region 17 with two outer subregions 17a, 17b and a middle second region 18 are provided here.
  • the partial areas 17a, 17b are each divided by longitudinal dividing walls 19a, 19b and by transverse dividing walls 20a, 20b, between which a connecting tube 21 is arranged.
  • the coolant enters according to the arrows E - partly via the connecting pipe 21 - in the tubes 2 of the sections 17a, 17b, flows through them from top to bottom, then, according to the arrows UB, deflected in width and flows through the middle tubes.
  • Fig. 5a and Fig. 5b show a structural design of a radiator 22, according to the first embodiment according to Fig. 1 and Fig. 2 equivalent. However, there is the difference that the coolant inlet, characterized by an arrow E, below and the coolant outlet, characterized by an arrow A, above takes place.
  • This representation corresponds to the preferred mounting position of the radiator 22 in the motor vehicle.
  • the radiator 22 includes a radiator block 23, also called a short block, a lower header or coolant box 24 and an upper header or coolant box 25.
  • the lower header 24 has an inlet nozzle 24a and the upper coolant box, also called outlet box, has an outlet nozzle 25a on.
  • the block 23 comprises - as in the embodiment according to Fig. 1 and Fig.
  • the arrow I symbolizes the incoming coolant flow in the first region
  • the arrows IIa, IIb symbolize the diverted in width partial streams
  • the arrow III symbolizes the coolant flow in the second, ie the windward tube row.
  • the arrows UB, UT show the deflection of the coolant flow I in the width and the deflection of the partial flow IIb in depth.
  • the direction of flow of the air is represented by an arrow L, ie one can see the air outlet side of the radiator block 23.
  • the illustrated installation position of the radiator 22 with the above-arranged coolant outlet 25a is chosen because of the better ventilation of the radiator 22.
  • Fig. 5b shows the radiator 22 in an exploded view, ie the lower inlet box 24, the upper outlet box 25 and the block 23 are shown separately.
  • the interior of the inlet box 24, in particular the inlet region 26 divided off by a longitudinal and two transverse partition walls 26a, 26b, 26c, can be seen.
  • the coolant inlet stream is shown in block 23 by three arrows pointing upwards.
  • the deflection in the width is carried out according to the arrows UB (here, a non-visible longitudinal partition wall is arranged in the upper coolant tank 25).
  • the diversion in depth takes place in the lower coolant box 24 according to the arrows UT.
  • the flow in the windward row is indicated by five arrows pointing upwards.
  • Fig. 6a and Fig. 6b show for clarity again the radiator 22 according to FIGS. 5a, 5b in explosive representations, in Fig. 6a overlooking the air outlet side 23a and in Fig. 6b overlooking the air inlet side 23b.
  • the flow direction of the air is represented by arrows L.
  • the same reference numerals are used for the same parts. From this representation, the different flow on the lee side 23a and on the windward side 23b of the radiator block 23 clearly. In the former case, a coolant flow takes place in opposite directions, in the second case in the same direction.
  • Fig. 6b is a longitudinal partition wall 27 can be seen, which the longitudinal partition wall 8 in the embodiments according to Fig. 1 to Fig. 4 equivalent.
  • Fig. 7a shows a top view of the radiator block 23 accordingly Fig. 5a to Fig. 6b ,
  • the block 23 has two rows 28, 29 of two-chamber tubes 30, 31.
  • the flow direction of the coolant is again represented by dot and cross symbols.
  • the air flow direction is indicated by an arrow L. Between two rows of tubes 28, 29, the longitudinal partition wall 27 is indicated.
  • Fig. 7b shows a view of the radiator block 23 from below with first row of tubes 28 and second row of tubes 29 and with the inlet region 26 (first area) and partitions 26a, 26b, 26c.
  • the number of tubes in the individual areas, ie in the first and second area and in the second row 29 are represented by the dimension arrows a, b1, b2, c.
  • the number of tubes shown in the drawing or the dimensional ratios correspond to a preferred embodiment.
  • fifteen tubes 30 are provided in the first region a, and nine tubes in the second regions b1, b2, respectively.
  • Fig. 7c shows the tubes 30, 31 of the first row 28 and the second row 29 in an enlarged view
  • the depth dimensions T1 apply to the tubes 30 and T2 for the tubes 31 and T for the entire block depth.
  • the width of the tubes is indicated by B.
  • the drawing is drawn to scale for a preferred embodiment, ie, the depth dimension T2 of the second row 29 is smaller than the depth dimension T1 of the first row 28.
  • the number of tubes 30, 31 in both rows 28, 29 is - like the FIGS. 7a, 7b show - the same.
  • the entire flow cross section of the tubes 31 in the second row 29 is dimensioned such that, after the deflection in the depth, a further delay of the coolant flow results. Thus one reaches on the air inlet side an increased temperature difference and thus a performance gain.
  • the depth dimension T2 is selected in a range of 0.5 T1 to 1.0 T1.
  • the radiator according to the invention or its flat tubes have the following dimensions:
  • the tube width B is in a range of 0.5 to 4.0 mm, preferably in a range of 0.8 to 2.5 mm.
  • the material thickness (tube wall thickness) s of the flat tubes is in a preferred range of 0.10 to 0.50 mm.
  • the depth T of the block is in a range of 10 to 100 mm, preferably in a range of 20 to 70 mm.
  • stepwise expansion of the flow cross section in each case after the deflection in the width and / or the deflection in depth, results in conjunction with the delay of the coolant flow and a lower pressure drop on the coolant side, which reduces the power requirement for the coolant pump.
  • Fig. 8 shows a further embodiment of the invention in the form of a double row radiator 32, wherein the coolant is deflected in both the first and in the second row of tubes in width.
  • the entry of the coolant into the radiator 32 is indicated by an arrow E and the exit the coolant from the radiator 32 is indicated by an arrow A.
  • the direction of flow of the air through the radiator 32 is indicated by two arrows L, ie air and coolant are guided in cross-counterflow to each other.
  • the radiator 32 has a first, leeward pipe row 33 and a second windward pipe row 34 and an upper coolant tank 35 and a lower coolant box 36, in which open the (not provided with reference numbers) pipe ends.
  • the coolant first enters an inlet region, represented by arrows I, into the first row of tubes 33, is deflected outwards in the lower coolant box 36, corresponding to the arrows UB in width, enters the two outer sections, flows through them down to the top, according to the arrows IIa, IIb, and is in the upper coolant box 35 in the depth, corresponding to the arrows UT, deflected.
  • windward pipe row 34 there is a flow from top to bottom - which is not shown here - a new deflection in the width, a flow from bottom to top and finally marked by the arrow A outlet of the coolant.
  • the regions I, IIa, IIb in the front and in the rear row 33, 34 are respectively flowed through in opposite directions.
  • Fig. 9a shows the radiator 32 from Fig. 8 in an exploded view, wherein the same reference numerals are used for the same parts.
  • the flow of the coolant is represented by arrows in the tubes and the coolant boxes 35, 36.
  • the two rows of tubes 33, 34 have a plurality of flat tubes 37, between which are not provided with reference numbers corrugated fins are arranged.
  • the ends of the flat tubes 37 are connected to tube sheets 38, 39, preferably by soldering.
  • the tube plates 38, 39 are connected to the coolant boxes 35, 36, preferably by soldering.
  • a longitudinal partition wall 40 is arranged, which separates the first and the second row of tubes 33, 34, so that in the lower coolant box 36 each for the first and second row of tubes 33, 34 can be made a deflection in width, as by the Arrows UB1, UB2, each can take place in the opposite direction.
  • the upper coolant box 35 are two extending over both rows of tubes transverse partitions 41, 42 and arranged between the transverse partition walls 41, 42 extending longitudinal partition wall 43. Due to this arrangement of the partitions 40, 41, 42, 43 results in the flow pattern of the coolant shown by the arrows.
  • the coolant flows in the first and second rows 33, 34 respectively in the opposite direction, as well as in the lower coolant box 36.
  • the first row 33 a deflection in the width from the inside to the outside
  • the second row 34 a deflection in width from the outside to the inside.
  • Fig. 9b shows the radiator 32 in a section in which the two rows of tubes 33, 34, the two coolant boxes 35, 36, the entry of the coolant by an arrow E, the exit of the coolant by an arrow A and the flow direction of the air by an arrow L are shown.
  • the countercurrent principle is clearly visible here.
  • FIG. 10a shows a plan view (view from above) on the two rows of tubes 33, 34, here called R1, R2.
  • the two transverse partitions 41, 42 in conjunction with the longitudinal partition wall 43 in the form of an H.
  • the flow direction of the coolant through the flat tubes 37 is represented by dot and cross symbols.
  • the number of tubes in the individual sections of the rows of tubes R1, R2 is represented by the sections a, b1, b2, c.
  • the sum of the tubes b1 and b2 is greater than the number of tubes a, ie (b1 + b2)> a.
  • section a has fifteen tubes and sections b1 and b2 each have nine tubes, resulting in an increase in the flow area of three tube sections. This results in a reduction of the flow velocity in sections b1 and b2.
  • Fig. 10b shows a view from below of the tube ends of the tube rows R1 and R2, between which the longitudinal partition wall 40 is arranged.
  • the entire width of the rows of tubes R1, R2 is indicated by c - this area is not divided by transverse walls, so that in both rows R1, R2 a deflection in the width can be made.
  • Fig. 10c shows an enlarged section of the two rows of tubes R1, R2, each with five flat tubes 37a, 37b, whose immersion in the depth (in the air flow direction) is designated in each case with T1 and T2.
  • the total depth of the two rows of tubes (the block) is indicated by T.
  • the depth T2 of the flat tubes 37b can be greater than the depth T1 of the flat tubes 37a selected - this with the same tube width B and the same number of tubes.
  • the tube width B is in a range of 0.5 to 4.0 mm, preferably 0.8 to 2.5 mm.
  • the material thickness of the flat tubes 37a, 37b is in the range of 0.10 to 0.50 mm.
  • the overall depth T (mesh or block depth) is 10 to 100 mm, preferably 25 to 70 mm.
  • two rows of flat tubes 37a, 37b which are designed as two-chamber tubes, are shown.
  • Fig. 11 shows a further embodiment of the invention with a radiator 44, which of the flow pattern of the embodiment according to Fig. 10a, 10b equivalent.
  • a constructive variant provides for a lateral inflow of the coolant via an inflow pipe 45, via which the coolant is supplied from the outside into the central inflow region 46.
  • an outflow pipe (not shown) can be provided for the outflow region located downstream of the inflow region 46 in the plane of the drawing. be provided.
  • Such a laterally arranged coolant connection may be advantageous due to the installation situation in the vehicle.
  • Fig. 12 shows a further unclaimed example with a radiator 47, which externally arranged inflow regions 48, 49 (portions), which communicate with each other via a connecting pipe 50.
  • the coolant entering via the inlet connection 51 is thus distributed to both inflow chambers 48, 49.
  • the situation is analogous to the discharge side, not shown, ie in the second row of pipes.

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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)
  • Air-Conditioning For Vehicles (AREA)

Claims (9)

  1. Echangeur de chaleur (1) comprenant précisément deux rangées (3, 4 ; 28, 29 ; 33, 34) de conduits d'écoulement (2 ; 30, 31, 37) qui peuvent être traversés par un milieu liquide, et comprenant des surfaces secondaires disposées entre les conduits d'écoulement (2 ; 30, 31, 37) et baignées d'air, où le milieu liquide et l'air sont guidés suivant des flux croisés circulant dans des sens opposés, et la première rangée (3 ; 28, 33) est disposée sur le côté de sortie d'air, la deuxième rangée (4 ; 29, 34) étant disposée sur le côté d'entrée d'air, caractérisé en ce que le milieu liquide entre dans une première zone (a) de la première rangée (3 ; 28, 33), ledit milieu liquide est redirigé, à l'intérieur de la première rangée (3 ; 28, 33), dans une deuxième zone (b1, b2), et, en sortant de la deuxième zone (b1, b2) de la première rangée (3 ; 28, 33), est redirigé dans la deuxième rangée (4 ; 29, 34), où la première zone (9, a ; 26) est disposée au milieu, et en ce que la deuxième zone comprend deux zones partielles (b1, b2, 10a, 10b) qui sont disposées des deux côtés de la première zone (a, 9 ; 26).
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que le milieu liquide est redirigé au moins une fois à l'intérieur de la deuxième rangée (4, 29, 34) .
  3. Echangeur de chaleur selon la revendication 1 ou 2, caractérisé en ce que la deuxième rangée (R2) présente deux zones partielles extérieures (b1, b2) et une zone de sortie (a) placée au milieu, et en ce que le milieu liquide sortant des deux zones partielles (b1, b2) est redirigé, de l'extérieur vers l'intérieur, dans la zone de sortie (a).
  4. Echangeur de chaleur selon l'une quelconque des revendications 1 à 3, caractérisé en ce que les conduits d'écoulement sont conçus comme des tubes plats (30, 31 ; 37, 37a, 37b).
  5. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'échangeur de chaleur est conçu comme un radiateur (22, 32, 44, 47) d'un système de chauffage ou de climatisation d'un véhicule automobile.
  6. Echangeur de chaleur selon la revendication 5, caractérisé en ce que le radiateur (22, 32, 44, 47) présente des réservoirs (24, 25, 35, 36) pour l'entrée et / ou la sortie et / ou pour la redirection de flux du milieu liquide, respectivement du liquide de refroidissement.
  7. Echangeur de chaleur selon la revendication 6, caractérisé en ce que des parois de séparation, en particulier des parois de séparation transversales et / ou longitudinales (5, 6, 7 ; 15, 16 ; 19a, 19b, 20a, 20b, 26a, 26b, 26c ; 40, 41, 42, 43) sont disposées dans les réservoirs (24, 25, 35, 36).
  8. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que chaque zone (a, b1, b2, c) de conduits d'écoulement présente une section d'écoulement spécifique à la zone, et en ce que les sections d'écoulement se modifient en aval d'une redirection de flux.
  9. Echangeur de chaleur selon revendication 8, caractérisé en ce que les sections d'écoulement augmentent de façon graduelle dans la direction d'écoulement du liquide de refroidissement, de sorte que la vitesse d'écoulement du liquide de refroidissement diminue.
EP08859570.7A 2007-12-10 2008-11-04 Échangeur de chaleur, en particulier radiateur pour des véhicules automobiles Not-in-force EP2232183B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102007059672 2007-12-10
DE102008017485 2008-04-03
PCT/EP2008/009271 WO2009074196A2 (fr) 2007-12-10 2008-11-04 Échangeur de chaleur, en particulier radiateur pour des véhicules automobiles

Publications (2)

Publication Number Publication Date
EP2232183A2 EP2232183A2 (fr) 2010-09-29
EP2232183B1 true EP2232183B1 (fr) 2018-09-12

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EP08859570.7A Not-in-force EP2232183B1 (fr) 2007-12-10 2008-11-04 Échangeur de chaleur, en particulier radiateur pour des véhicules automobiles

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US (1) US8695689B2 (fr)
EP (1) EP2232183B1 (fr)
CN (1) CN101889186A (fr)
DE (1) DE102008055624A1 (fr)
WO (1) WO2009074196A2 (fr)

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Also Published As

Publication number Publication date
EP2232183A2 (fr) 2010-09-29
CN101889186A (zh) 2010-11-17
WO2009074196A3 (fr) 2009-08-27
DE102008055624A1 (de) 2009-06-18
US8695689B2 (en) 2014-04-15
WO2009074196A2 (fr) 2009-06-18
US20110036546A1 (en) 2011-02-17

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