EP1864068B1 - Échangeur thermique à aération - Google Patents

Échangeur thermique à aération Download PDF

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Publication number
EP1864068B1
EP1864068B1 EP06706574A EP06706574A EP1864068B1 EP 1864068 B1 EP1864068 B1 EP 1864068B1 EP 06706574 A EP06706574 A EP 06706574A EP 06706574 A EP06706574 A EP 06706574A EP 1864068 B1 EP1864068 B1 EP 1864068B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
ventilation device
coolant
heat
radiator
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
EP06706574A
Other languages
German (de)
English (en)
Other versions
EP1864068A1 (fr
Inventor
Holger Auchter
Michael Müller
Matthias Traub
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
Original Assignee
Behr GmbH and Co KG
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 Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1864068A1 publication Critical patent/EP1864068A1/fr
Application granted granted Critical
Publication of EP1864068B1 publication Critical patent/EP1864068B1/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
    • F28D1/053—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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/18—Safety or protection arrangements; Arrangements for preventing malfunction for removing contaminants, e.g. for degassing

Definitions

  • the invention relates to a heat exchanger for at least one heat transport medium, as used for example as a radiator for heating in the vehicle interior of a motor vehicle incoming air.
  • the invention further relates to a coolant circuit and an air treatment device for motor vehicles using such a heat exchanger.
  • Heat exchangers are used, inter alia, in motor vehicles for different tasks.
  • heat exchangers for engine cooling in a broader sense z. B. used as a coolant radiator, oil cooler, exhaust gas cooler and intercooler.
  • Another common application of heat exchangers in motor vehicles is the temperature of the air supplied into the passenger compartment.
  • heat exchangers z. B. in the form of evaporators, condensers (or gas coolers), internal heat exchangers and radiators used.
  • heat exchangers now exist in a wide variety of designs and types of installation. If at least one at least partially liquid heat transport medium is used in heat exchangers, as it is z. As is the case with coolant radiators or radiators, if necessary, the problem of air accumulation in the heat exchanger, which may possibly adversely affect the throughput or the uniform distribution of the heat transfer medium in the heat exchanger. This is especially true for standing installed heat exchangers.
  • One possibility is to set up the heat exchanger, for example by means of a flat installation position or a corresponding arrangement of flow or return openings, in such a way that air accumulating in the heat exchanger can escape from the heat exchanger or can be removed, for example. when the system is not even accumulated.
  • a problem with such established heat exchangers is that certain installation methods (such as, for example, vertical installation of the heat exchanger) or specific designs of the supply openings for the heat transport medium are in fact excluded.
  • this is often problematic especially in motor vehicles, since the space in the front part of the motor vehicle is usually very tight and certain configurations of the heat exchanger due to the other engine compartment modules are partially unavoidable.
  • Another possible solution is to allow a certain amount of air accumulation in the heat exchanger and to rely on the fact that at a certain throughput of heat transfer medium, the gas collections are entrained in the heat exchanger from the heat transfer medium through the heat exchanger.
  • the problem here is that in particular at low throughputs of heat transport medium the Efficiency of the heat exchanger can be reduced by the accumulation of air from both the absolute performance as well as the uniformity of heat dissipation. In particular, the latter can lead to thermal stresses and be disadvantageous due to the uneven heat distribution on the radiator surface, especially in the treatment of air for the passenger compartment.
  • Another problem is that the radiators tend to cause noise due to the accumulation of gas, which is disadvantageous in particular with components arranged in the vehicle interior (such as, for example, in the case of the radiator of an air conditioning system).
  • the DE 100 41 121 A1 discloses a heat exchanger having a flow and a return and at least one venting device, wherein the venting device is arranged at a distance from at least one return opening in the heat exchanger.
  • the present invention is therefore based on the object, a heat exchanger with at least one venting device such that the known problems in known prior art heat exchangers are at least partially eliminated or at least mitigated.
  • it makes the invention the task, a To propose heat exchangers, which is simple and inexpensive to design and manufacture, and still allows the greatest possible ventilation without an excess of unwanted noise occurs.
  • venting device for at least one heat transport medium with at least one flow, at least one return and at least one venting device, that the venting device is spaced from at least one return opening in the heat exchanger.
  • the venting device can in particular be designed as a recess, and according to the invention is embodied in a partition wall of the heat exchanger which is normally present anyway, preferably in an upper region of a partition wall. It has surprisingly been shown that such an arrangement of the ventilation device can ensure a particularly advantageous ventilation of the heat exchanger. Up to now it has been assumed that an arrangement of the venting devices in the immediate vicinity of the return line is advantageous since it allows the gas accumulations to be sucked off particularly effectively.
  • the ventilation device it is preferable to also form the ventilation device at a distance from at least one feed opening in the heat exchanger.
  • a kind of additional "vent circuit" are created especially in the upper part of the radiator, which in particular passes through the critical areas of the heat exchanger and thereby vent the heat exchanger particularly effective. It is of course important to ensure that the throughput of this additional vent circuit selected relatively low so that the efficiency of the heat exchanger does not decrease significantly.
  • the distance between at least one ventilation device and at least one flow opening and / or between at least one ventilation device and at least one return opening is at least 10 mm, preferably at least 15 mm, particularly preferably at least 20 mm and in particular at least 25 mm.
  • the proposed values have proved favorable.
  • other numerical values are conceivable. In particular, even with other numerical data occurring in this document, at (half) intervals and discrete values, all numerical values are to be regarded as disclosed and applicable in any desired manner.
  • At least one flow opening and at least one return opening are arranged adjacent to one another. This can ensure a compact construction and a simple assembly, but also a particularly effective ventilation.
  • At least one venting device is arranged at a distance from the direct connecting path between at least one feed opening and at least one return opening.
  • the venting device is arranged as far as possible from the direct connection path between the feed opening and the return opening.
  • the invention can be used particularly advantageously in connection with vertically arranged heat exchangers with advantageously at least one, preferably overhead, coolant box. Particularly in such heat exchangers, gas accumulations are easily generated, which can be eliminated particularly effectively using the present invention.
  • a UT deflection is a so-called downward deflection of the heat transport medium in depth.
  • the "depth" refers to the direction of flow of the second fluid, in particular air to be heated for a vehicle interior.
  • a particularly advantageous embodiment of the proposed invention results when at least one venting device is designed in the form of one or more openings.
  • openings can have any shape.
  • Circular, semicircular, lenticular, square, rectangular, concave, semi-lenticular and / or slot-like recesses (in each case horizontally, vertically and / or obliquely guided) have proved to be useful.
  • lengths of 5 to 15 mm, preferably 6 to 12 mm, in particular 8 to 10 mm may prove to be favorable.
  • the openings are made as an expression, which is advantageously formed in a coolant box, preferably in an overhead coolant box of the heat exchanger.
  • the openings are particularly preferably provided in a contact region between the partition wall and the coolant box wall, in particular in an overhead region of the coolant box.
  • the opening may be located in the region of an optionally existing connecting seam of the coolant box.
  • At least one ventilation device has at least one flow-limiting device, which is designed in particular as a baffle plate, as a tube, as a molded-on flange and / or as a hydrodynamic flow-limiting device.
  • the proposed radiator should, at least in areas where it can lead to gas accumulation, as possible no sharp edges and other construction geometries, which can lead to unwanted noise.
  • the noise can be further reduced by the currents occurring in particular from the speed and / or throughput can be reduced.
  • the term "hydrodynamic flow restricting device” is to be understood quite generally as meaning devices in which a hydrodynamic dynamic pressure of the heat transport medium flowing through the heat exchanger is used to limit other flow paths, in particular of the material flowing through the venting devices.
  • At least one ventilation device as an external ventilation device outside the heat exchanger body and / or the coolant reservoir.
  • the venting device can for example be arranged as far away from the passenger compartment or in areas where only a few noises occur or the resulting noise is transmitted to a reduced extent in the motor vehicle interior.
  • This flange region can be provided for example with a certain distance from the heat exchanger in the flow or return line.
  • this distance between flange and radiator - and thus the distance of the venting device to the radiator - is usually relatively small, and is usually 10-50 mm, e.g. 10 mm, 15 mm, 20 mm, 25 mm, 30 mm, 40 mm or 50 mm.
  • the coolant circuit has the corresponding advantages in analog form.
  • the air treatment device for motor vehicles with at least one heat exchanger according to one of the aforementioned embodiments.
  • the air treatment device which may, for example, additionally comprise an evaporator for cooling incoming air, then has the described advantages in an analogous form.
  • the proposed device can be made particularly effective in this case.
  • FIG. 1 a radiator 1 known per se for heating air is shown, which in the present case is supplied to a motor vehicle interior.
  • the flow direction of the air is in FIG. 1 schematically indicated by an arrow A.
  • the air flow can be performed in any way in the cross-flow or in the countercurrent countercurrent.
  • the illustrated radiator 1 is a standing arranged, so-called UT radiator.
  • the radiator 1 has at its upper end 2 and its lower end 3 each have a coolant box 4, 5, which also serves as a manifold for the coolant flowing therethrough.
  • the upper coolant box 4 is divided by a schematically indicated partition 6 in a front, the lead 9 adjacent front portion 7 and a rear, the return 10 having rear portion 8.
  • each corrugated fins 12 which improve the heat transfer to the air flowing through A.
  • the corrugated fins 12 may be provided in a conventional manner to improve the heat transfer to the air flowing through A with a structuring.
  • FIG. 2 is the in FIG. 1 illustrated radiator 1 shown schematically in cross section to explain the way of flowing through the radiator 1 coolant in more detail.
  • the coolant flows to the flow 9 via a flow opening 15 in the front part 7 of the upper coolant tank 4 a.
  • the coolant box 4 has a partition wall 6, which separates the coolant box 4 into a front region 7 and a rear region 8. Starting from the front region 7, the coolant flows along the direction of the arrow B through the front lying areas 13 of the flat tubes 11 toward the bottom 3 of the radiator 1.
  • the flat tubes 11 are - as explained in more detail below - designed such that in the region of the flat tubes 11th essentially no flow transverse to the longitudinal extent of the flat tubes 11 takes place.
  • the coolant exits from the front part 13 of the flat tubes 11 in the lower coolant box 5.
  • the coolant is deflected in the "depth” C and enters the rear portion 14 of the flat tubes 11, where it flows in the opposite direction D up 2 to the upper coolant box 4.
  • the flow path is indicated by arrows C, D.
  • FIGS. 3A and 3B For the sake of completeness, possible embodiments of flat tubes 11 are shown, as they are for the in the FIGS. 1 and 2 shown radiator 1 can be used.
  • This in FIG. 3A shown flat tube 11 has a plurality of passages 17 for the coolant and can be prepared for example by extrusion.
  • Flat tube 11 shown can be made for example by bending or forming and then welding or soldering a solder-plated sheet.
  • This flat tube 11 is divided by a central web 19 into two separate chambers 18.
  • gas bubbles can accumulate especially in the upper region 2 of the upper coolant box.
  • gas bubbles which form in the flow 9 facing the front part 7 of the coolant box 4, without corresponding ventilation devices not or hardly removed from this front portion 7 of the upper coolant box 4.
  • the gas bubbles can disturb the function of the radiator 1.
  • the flow cross section for the coolant flowing through can be narrowed in the front region 7 of the upper coolant box 4 for the coolant flowing through it, so that the heating power of the radiator 1 can decrease.
  • FIG. 4 For this purpose, several suitable, provided with appropriate ventilation devices partitions 6 are shown.
  • FIG. 4A In this case, a partition wall 6 is first shown, which is formed continuously and, for example, in connection with an external ventilation device 21 (see FIG. 8 ) can be used.
  • an external ventilation device 21 see FIG. 8
  • partitions 6 according to the Figures 4B to 4L is the venting device, however, each executed in the form of a differently shaped recess 22.
  • the recesses 22 are formed as round, semicircular, oval or semi-oval recesses 22. Although only a single recess 22 is shown in the figures, it is also possible to provide a plurality of recesses, which are preferably arranged along the upper edge of the partition wall 6. Typical dimensions are 1, 2, 3 or 4 mm (round or half round) or 1, 2 or 3 mm for the shorter axis and 2, 3, 4 mm for the longer axis (oval or half oval) at.
  • a rectangular or square recess 22 are provided.
  • a plurality of recesses 22 can also be provided, whereby different shapes can also be mixed. This naturally also includes the following exemplary embodiments. Typical dimensions for the long sides are 1, 2, 3 or 4 mm.
  • n-angular recesses especially triangles, in different position and orientation.
  • the values 5, 6, 7, 8, 9 and 10 have proven to be particularly useful.
  • the n-comers can not be just regular (isosceles) n-comers, but arbitrary, general n-comers.
  • the recess is formed as a concave, lenticular formation 22, which may be particularly preferably formed in the radius region of the partition wall.
  • the radius of the lens preferably corresponds essentially the radius of the partition.
  • other radii - in extreme cases also a straight line - are conceivable in this context.
  • FIGS. 4I and 4J shown that only part of the lens after FIG. 4H is removed from the partition 6 and, for example, only the lower half ( Fig. 4I ) or the upper half ( Fig. 4J ) Will get removed.
  • slot-shaped recesses as in FIGS. 4K and 4L is indicated.
  • 1, 2, 3 or 4 mm are available as the slot width, and the lengths 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11 or 12 mm.
  • the in Figure 4K Of course, shown angle of 45 ° can take other values.
  • a value of 1, 2, 3, 4 or 5 has proven particularly useful for the number of openings.
  • the partition walls 6 provided with openings 22 can of course also be combined with external ventilation devices 21. It is also possible to combine different opening shapes 22 with each other.
  • FIG. 9 a venting device is shown, which is designed as an expression 37 in the upper wall 39 of the upper coolant box 4.
  • the expression 37 can be generated, for example, by deforming the wall 39.
  • an opening 38 between the partition wall 6 and the upper wall 39 of the coolant box 4. Due to the opening 38 is a connection between the front region 7 and rear area 8, through which accumulating gas bubbles can be removed.
  • the partition 6 in the region of the expression 37 of the upper wall 39 of the coolant box 4 no recess.
  • FIG. 5 a presently designed as a baffle plate 23 flow limiting device is shown.
  • a parallel to the partition wall 6 extending strip material 25 is arranged, which is held for example via a retaining web 24.
  • side walls not shown here are arranged, so that there is a total trough-like design of the baffle plate 23.
  • This flow E depends on the coolant throughput through the radiator 1.
  • a large coolant flow rate 1 results in a relatively high pressure difference between the flow 9 and return 10 and thus between the front part 7 and the rear part 8 of the upper coolant tank 4, which would have a correspondingly high throughput through the recess 22 to result.
  • This high throughput can be alleviated by the described hydrodynamic effect become.
  • the throughput through the recess 22 can be reduced, and thus, in particular, the speed of passing gas and / or coolant can be reduced. This can in particular have a noise-reducing effect.
  • FIG. 6A, 6B a further flow-limiting device in the form of a flange or a projection 26 is shown, at the lower end 27 of a venting device 28 is formed.
  • a further flow-limiting device in the form of a flange or a projection 26 is shown, at the lower end 27 of a venting device 28 is formed.
  • advantages may arise, in particular due to the hydrodynamic effect which may occur, as described above.
  • the projection 26 may possibly be produced in a particularly simple and cost-effective manner by deforming material processing of the partition wall 6.
  • FIG. 7 is another conceivable embodiment of a flow-limiting device in the form of a centrally arranged with a recess (not visible in the figure) tube 29.
  • the tube 29 is present in the form of a "twisted S" bent so that the inlet 31 horizontally, the outlet 32nd the tube 29, however, is vertical, so that hydrodynamic effects can be used particularly advantageous.
  • a holding web 30 may be provided for the tube 29.
  • FIG. 8 Finally, a part of a cooling circuit is still sketched, in which an external ventilation device 21 is provided, which is presently arranged at the (possibly local) highest point 33 of the cooling circuit.
  • the radiator 1 may be connected in any manner with (eg FIGS. 4B to 4L ) or without (according to FIG. 4A ) Inner venting devices may be formed.
  • the external venting device 21 has in the present embodiment shown via a thin connecting channel 36 which connects the flow line 34 with the return line 35.
  • the flange can - as usual with radiators - even at a smaller distance, such as at a distance of 10-50 mm, be arranged by the radiator.
  • the flange may also be integrated in the radiator. As a rule, only the distance between the forward and / or return opening 15, 16 and the connecting channel 36 is essential.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)

Claims (15)

  1. Echangeur de chaleur (1) pour au moins un milieu servant au transport de la chaleur, comportant au moins une entrée (9), au moins un retour (10) et au moins un dispositif de ventilation (21, 22, 38), où le dispositif de ventilation (23, 36, 38) est disposé dans l'échangeur de chaleur en étant espacé d'au moins une ouverture de retour (16),
    caractérisé en ce qu'au moins un dispositif de ventilation (22) est configuré dans une paroi de séparation (6), de préférence dans une zone supérieure (2) d'une paroi de séparation (6) de l'échangeur de chaleur (1).
  2. Echangeur de chaleur selon la revendication 1,
    caractérisé en ce que le dispositif de ventilation (21, 22, 38) est configuré dans l'échangeur de chaleur en étant espacé d'au moins une ouverture d'entrée (15).
  3. Echangeur de chaleur selon la revendication 1 ou 2,
    caractérisé par un intervalle d'au moins 10 mm, de préférence d'au moins 15 mm, en particulier de préférence d'au moins 20 mm, en particulier d'au moins 25 mm entre au moins un dispositif de ventilation (21, 22, 38) et au moins une ouverture d'entrée (15) et / ou entre au moins un dispositif de ventilation (21, 22, 38) et au moins une ouverture de retour (16).
  4. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins une ouverture d'entrée (15) et au moins une ouverture de retour (16) sont disposées en étant voisines l'une de l'autre.
  5. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins un dispositif de ventilation (21, 22, 38) est disposé en étant espacé du trajet de communication direct situé entre au moins une ouverture d'entrée (15) et au moins une ouverture de retour (16).
  6. Echangeur de chaleur selon l'une quelconque des revendications précédentes, qui est configuré comme un échangeur de chaleur (1) disposé verticalement et qui comprend, de façon avantageuse, au moins une boîte à eau (4) placée de préférence en haut (2).
  7. Echangeur de chaleur selon l'une quelconque des revendications précédentes, qui présente une déviation (5) se produisant au niveau d'un point bas (UT) et / ou est configuré comme un radiateur (1).
  8. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins un dispositif de ventilation (22, 38) est configuré sous la forme d'une ou de plusieurs ouvertures.
  9. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins un dispositif de ventilation (38) est configuré dans une boîte à eau (4), de préférence dans une boîte à eau (4) de l'échangeur de chaleur (1), placée en haut (2).
  10. Echangeur de chaleur selon l'une quelconque des revendications précédentes, dans lequel au moins un dispositif de ventilation (22) présente un dispositif de limitation d'écoulement (23, 26, 29) qui est configuré, en particulier, comme une plaque déflectrice (25), comme un tube (29), comme une bride moulée (26) et / ou comme un dispositif hydrodynamique (F) de limitation de l'écoulement.
  11. Echangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins un dispositif de ventilation est configuré comme un dispositif de ventilation externe (21) placé à l'extérieur du corps de l'échangeur de chaleur (1) et / ou de la boîte à eau (4).
  12. Echangeur de chaleur selon la revendication 11,
    caractérisé en ce qu'au moins un dispositif de ventilation externe est situé dans une zone de bride (21) configurée le cas échéant de manière distincte.
  13. Circuit de liquide de refroidissement comprenant au moins un échangeur de chaleur (1) selon l'une quelconque des revendications 1 à 12.
  14. Dispositif de traitement de l'air pour des véhicules automobiles, présentant au moins un échangeur de chaleur (1) selon l'une quelconque des revendications 1 à 12.
  15. Echangeur de chaleur, circuit de liquide de refroidissement ou dispositif de traitement de l'air selon l'une quelconque des revendications précédentes,
    caractérisé en ce qu'au moins un dispositif de ventilation (21, 22, 38) est configuré, par rapport à au moins un ensemble (1, 4) du circuit du milieu servant au transport de la chaleur et / ou par rapport à la totalité du circuit du milieu servant au transport de la chaleur, dans la zone d'un emplacement (33) placé en hauteur (2), localement du point de vue géodésique, et / ou sensiblement dans la zone de l'emplacement placé tout en haut, du point de vue géodésique.
EP06706574A 2005-03-18 2006-02-02 Échangeur thermique à aération Not-in-force EP1864068B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005013035 2005-03-18
PCT/EP2006/000904 WO2006097162A1 (fr) 2005-03-18 2006-02-02 Échangeur thermique à aération

Publications (2)

Publication Number Publication Date
EP1864068A1 EP1864068A1 (fr) 2007-12-12
EP1864068B1 true EP1864068B1 (fr) 2010-06-02

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP06706574A Not-in-force EP1864068B1 (fr) 2005-03-18 2006-02-02 Échangeur thermique à aération

Country Status (7)

Country Link
US (1) US20080230215A1 (fr)
EP (1) EP1864068B1 (fr)
CN (1) CN101142458B (fr)
AT (1) ATE470120T1 (fr)
DE (1) DE502006007093D1 (fr)
ES (1) ES2346146T3 (fr)
WO (1) WO2006097162A1 (fr)

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KR101213564B1 (ko) * 2009-03-26 2012-12-18 가부시키가이샤 덴소 냉기 저장형 열교환기
JP5913913B2 (ja) * 2011-11-07 2016-04-27 サンデンホールディングス株式会社 室内側凝縮器
US10088241B1 (en) * 2012-05-16 2018-10-02 Engendren Corporation Multi-mode heat exchange system for sensible and/or latent thermal management

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CN101142458B (zh) 2010-09-29
US20080230215A1 (en) 2008-09-25
ATE470120T1 (de) 2010-06-15
EP1864068A1 (fr) 2007-12-12
CN101142458A (zh) 2008-03-12
DE502006007093D1 (de) 2010-07-15
WO2006097162A1 (fr) 2006-09-21
ES2346146T3 (es) 2010-10-11

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