EP2757336B1 - Échangeur de chaleur avec transfert de chaleur optimisé et dispositif de chauffage doté d'un tel échangeur de chaleur - Google Patents

Échangeur de chaleur avec transfert de chaleur optimisé et dispositif de chauffage doté d'un tel échangeur de chaleur Download PDF

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Publication number
EP2757336B1
EP2757336B1 EP14151370.5A EP14151370A EP2757336B1 EP 2757336 B1 EP2757336 B1 EP 2757336B1 EP 14151370 A EP14151370 A EP 14151370A EP 2757336 B1 EP2757336 B1 EP 2757336B1
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European Patent Office
Prior art keywords
channel
fluid
sub
heat exchanger
module
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EP14151370.5A
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German (de)
English (en)
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EP2757336A3 (fr
EP2757336A2 (fr
Inventor
Halil Ufuk Oezboga
Mustafa Tuerkelli
Cenk Acar
Hürrem Murat Altay
Turgut Oruc Yilmaz
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Robert Bosch GmbH
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Robert Bosch GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • 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
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F28D21/0005—Recuperative heat exchangers the heat being recuperated from exhaust gases for domestic or space-heating systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • 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
    • F28D2021/0024—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for combustion apparatus, e.g. for boilers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/02—Heat exchange conduits with particular branching, e.g. fractal conduit arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/10—Particular layout, e.g. for uniform temperature distribution
    • 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
    • F28F2265/10—Safety or protection arrangements; Arrangements for preventing malfunction for preventing overheating, e.g. heat shields

Definitions

  • the invention relates to a heat exchanger according to the preamble of claim 1 and a heating device with such a heat exchanger according to claim 10.
  • Heat exchangers are used to transfer heat from a first heat carrier to a second heat carrier.
  • different fluids are used as heat transfer, which should not be in contact or even mixed.
  • the fluids are guided in separated from a separator fluid channels.
  • the separator has good heat conduction properties and the largest possible surface area to the fluids.
  • Each module consists of two interconnected plates of rectangular basic shape, between which a second fluid channel for a liquid fluid is formed. This also extends from a fluid inlet to a fluid outlet, wherein fluid inlet and fluid outlet are arranged diagonally opposite.
  • second fluid channel ribs are arranged between the plates, which are to conduct the fluid.
  • first ribs extend in a first direction.
  • second ribs which are arranged at an angle to the first ribs.
  • third ribs which run parallel to the first ribs.
  • the second fluid channel is branched by the ribs behind the fluid inlet into a plurality of sub-channels.
  • a disadvantage is the thermal unequal loading of the module and thus of the heat exchanger.
  • a hot combustion gas eg 2000 K
  • both the first and the second fluid have their maximum temperature.
  • This leads to thermal stresses in the heat exchanger, which can lead to deformation and material damage.
  • there may be a phase change of the fluid in the second fluid channel from liquid to gaseous.
  • the pressure in the second fluid channel increases, there are noise developments in the formation of gas bubbles, the gas bubbles can cause damage to pumps used and corrosion inside the module is enhanced.
  • WO2008 / 107760 A2 discloses another modular heat exchanger having a plurality of stacked modules, and a heater having such a heat exchanger.
  • the object of the invention is therefore to provide a heat exchanger and a heater with which a high efficiency of heat transfer from a first fluid to a second fluid is achieved, the heat exchanger as compact, material-saving, lightweight and inexpensive manufacturable and yet a long has maintenance-free life.
  • the invention relates to a heat exchanger comprising a first fluid channel for a first fluid having a fluid inlet and a fluid outlet and a second fluid channel for a second fluid having a fluid inlet and a fluid outlet, the second fluid channel being branched behind its fluid inlet into a first and second partial channel, wherein the first and the second sub-channel are merged before the fluid outlet of the second fluid channel to a collecting channel which extends in a first portion transversely to the first fluid channel (or whose collecting channel flow of the second fluid transversely to a Main flow direction of the first fluid in the first fluid passage extends) and closer to the fluid inlet of the first fluid channel is arranged as the first sub-channel and the second sub-channel, the first sub-channel in a second section transverse to the first fluid channel and this second section closer to the fluid inlet of the first fluid channel is arranged as the second sub-channel, wherein the second fluid channel is formed within a substantially flat first module and that the second sub-channel is delimited by herringbone embosse
  • the course of the fluid channels according to the invention prevents overheating of the second fluid in the second fluid line and the second fluid line as such, in particular at the thermally heavily loaded fluid inlet of the first fluid channel.
  • the thermal stress acting on the heat exchanger (the thermal stresses) is low and this has a long service life.
  • the collecting channel by means of which the full volume of the fluid to be heated is conducted past the thermally most heavily loaded inlet opening of the first fluid channel at high speed.
  • the length of the first portion of the collection channel should be greater than three quarters of the maximum diameter of the adjacent first fluid channel.
  • first sub-channel By lying behind the collecting channel first sub-channel fluid is directly passed to the inlet temperature, which can absorb a correspondingly high heat by a high temperature gradient to the fluid in the first fluid channel.
  • the length of the second section should be greater than two-thirds of the maximum diameter of the adjacent first fluid channel.
  • the cooling of the fluid inlet of the first fluid channel is particularly high.
  • a substantially parallel arrangement of the first portion of the collecting channel to the second portion of the first sub-channel is useful.
  • the flow rate may be reduced, so that a temporally long heat absorption can take place in order to extract a maximum of heat from the fluid in the first fluid channel.
  • the second sub-channel is then preferably arranged in the condensation region of the first fluid channel. The efficiency of the heat recovery with the heat exchanger is correspondingly high.
  • the heat exchanger can be used particularly well as a gas-liquid heat exchanger.
  • the first fluid channel then forms a gas channel and the second fluid channel is a fluid channel.
  • the second fluid channel is formed within a substantially flat first module.
  • modules are ideally suited to design a heat transfer performance of the heat exchanger in a stacked arrangement by the number of identical modules, especially in rectangular basic shape.
  • the heat exchanger is then a plate heat exchanger. Since only a few tools and component variants for a large number of possible heat transfer services are necessary, a heat exchanger produced in this way can be provided in a particularly cost-effective manner.
  • the fluid inlets and the fluid outlets of the second fluid channel preferably point in the stacking direction. They can then flow continuously between the modules.
  • Adjacent modules preferably have sealing surfaces which correspond to one another in the region of the fluid entries of the second fluid channel and / or in the region of the fluid exits of the second fluid channel. Additional sealants are not required.
  • the fluid inlet of the second fluid channel should be arranged geodetically lower in the operating position than the fluid outlet.
  • the first fluid channel then adjoins the outer surface of the module.
  • it is formed between the first module and an adjacently spaced, identical or construction-like, second module.
  • adjacent modules should have corresponding sealing surfaces along the first fluid channel. Accordingly, then no separate sealing means are provided here.
  • the first module consists of two plates, between which the second fluid channel is formed, wherein the two plates are positively or materially connected to each other.
  • Such modules are particularly inexpensive to produce. At least one of the plates then predetermines the course of the second fluid channel by structured shaping (embossing, profiling). In this plate, the pattern of the second fluid channel should be embossed before connecting to the second plate. As plates in particular sheets are used. After assembly, the second fluid channel is then completely formed. Thus, at least one plate has elevations of the second fluid channel on the outside of the first module. The contact area to the first fluid channel and the heat transfer are correspondingly large. to reinforce these advantages, both plates should preferably have a structured shape corresponding to the second fluid channel.
  • a full-surface connection between the plates can be created by welding them in a vacuum oven.
  • the welding agent used is preferably nickel.
  • copper can also be used.
  • the exposed copper sites should then be subsequently nickel coated.
  • the vacuum furnace is also suitable for deep drawing the second fluid channel into the plates.
  • the first module from a plate, wherein the plate along a bending region, which is arranged in the region of the fluid inlet of the first fluid channel, folded or bent and two (structured, embossed) plate areas comprises the surface lie on one another and between which the second fluid channel is formed.
  • the two plate sections then correspond, so to speak, to the previously described two plates, with the exception of one-piece production by means of folding.
  • the main advantage of such a design is the high thermal load capacity of the bending area. This is significantly higher than a joined connection. The high thermal stress in the region of the fluid inlet of the first fluid channel can thus hardly lead to damage to the module.
  • the bending region preferably directly adjoins the first section of the collecting channel. As a result, the already temperature-resistant bending region is additionally cooled particularly well.
  • the first module consists of high-alloy stainless steel.
  • stainless steel By using stainless steel, the corrosion of the heat exchanger is low. A long life without maintenance is achieved.
  • the first section of the collecting channel and / or the second section of the first partial channel may have a circular cross section.
  • an embodiment is particularly preferred, according to which the first section of the collecting channel and / or the second section of the first sub-channel an oval Cross-section with two narrow end faces and two wide longitudinal sides. The longitudinal sides should be aligned along the first fluid channel. The narrow end faces are then aligned substantially transversely to the first fluid channel.
  • This design results in a module with a lower overall height, whereby more compact installation dimensions can be achieved.
  • the ratio of the surface of the first portion of the collecting channel and / or the second portion of the first sub-channel to its volume is greater, so that a higher heat transfer is achieved.
  • a combustion chamber can be formed with the modules themselves.
  • the modules on the side of the fluid inlet of the first fluid channel with lateral legs, so that the module is U-shaped.
  • additional fluid channels e.g., the collection channel
  • end cover plates / end modules which cover the entire U-shape, then results in a one-sided open chamber, which adjoins the fluid inlet of the first fluid channel.
  • This chamber can be designed as a combustion chamber, with a burner would connect upstream on the open side.
  • At least one rotary element is formed with a deflection surface having a slope relative to the channel profile. Due to the rotational excitation of the fluid flowing through it is mixed and requires a more effective cooling of the first fluid. The possible heat absorption from the first fluid channel is so particularly high. By impressing obliquely to the channel course pointing notches, these are also extremely inexpensive to produce.
  • the flow resistance of the first sub-channel deviates by a maximum of 10% from the flow resistance of the second sub-channel.
  • a relatively large fluid throughput should take place in the first subchannel.
  • the flow resistance of the first sub-channel should tend to be even slightly smaller than the flow resistance of the second sub-channel. At least 50% of the fluid flows through the first subchannel.
  • the volume of the first sub-channel smaller than the volume of the second sub-channel. Consequently, with essentially the same flow cross section, the residence time of the fluid in the first subregion is short. by virtue of the high volume in the second sub-channel, the residual heat of the first fluid in the first fluid channel can be effectively absorbed here, since a large heat transfer surface can be achieved, in particular by significantly longer or wider flow channels.
  • the volume of the second sub-channel is even greater than the sum of the volumes of the first sub-channel and the collecting channel. This makes it possible to achieve that the fluid in the first fluid channel in the region of the collecting channel and the first subchannel can be cooled to approximately condensation temperature, while the condensation finally takes place in the region of the second subchannel.
  • the first subchannel can be branched into a plurality of individual subchannels. These individual part channels of the first sub-channel should then run substantially parallel adjacent to each other.
  • this has a flow resistance which is greater than the resulting flow resistance of the parallel flow resistances of the first and second subchannel or has a flow cross section which is smaller than the total flow cross section of the parallel connected first and second subchannels.
  • the second sub-channel is herringbone-shaped.
  • the herringbone-shaped formation of the second sub-channel has a feed channel formed in or on a first module plate, from which branch off branch channels form herringbone.
  • the flushing of the individual branch channels is then carried out by convection currents and opens into branch channels and a feed channel, which are formed in or on a second module plate.
  • the feed channels should in this case be substantially adjacent to each other and aligned transversely to the first fluid channel.
  • the second subchannel in the manner of plate heat exchangers is delimited by herringbone embossed regions of the plates forming the module.
  • the invention further relates to a heating device having a combustion chamber comprising a heating gas supply and a Schugasab founded which is fluidly connected to a fluid inlet of a first fluid passage of a heat exchanger as described above, and with a heat transfer medium leading fluid circuit in which the heat exchanger with the fluid inlet and the fluid outlet of the second Fluid channel is integrated. Therefore the heat exchanger functions as a gas-liquid heat exchanger.
  • the heat exchanger is ideally suited to cool the very hot heating gases (combustion gases, sometimes up to 2000 K hot with fossil fuel-fired combustion chamber) of the combustion chamber, without being damaged. This is achieved, in particular, by preventing boiling of the fluid in the collecting channel and in the first sub-channel through the special channel guide of the second fluid channel.
  • the fluid circuit may, for example, contain a radiator, so that the fluid can release the absorbed heat at a destination again.
  • a feed pump should be arranged in the fluid circuit.
  • water-containing fluid has proved to be particularly suitable as a fluid. This is preferably kept in the fluid circuit under a pressure of more than 1 bar, so that the boiling temperature is above the normal level.
  • a development of the heater provides that the first module is U-shaped, wherein the first module with its cavity (this is the interior of the U-shape) at least partially surrounds the combustion chamber and the collection channel U-shaped in the combustion chamber-nahen Areas of the first module runs.
  • a heating device is provided which provides an almost completely water-cooled combustion chamber, thereby causing very low heat losses and is characterized by a high heat transfer efficiency.
  • the Fig. 1 and 2 show perspective views of a heat exchanger 1.
  • This consists of a first module 30, a second module 40 and other modules 41, which are stacked in a stacking direction R on each other. It is therefore a plate heat exchanger.
  • each substantially planar module 30, 40, 41 of the heat exchanger 1 accommodates in each case a second fluid channel 20 for a second fluid, in particular for water W, with a fluid inlet 21 and a fluid outlet 22.
  • the fluid inlet 21 is geodetically lower than the fluid outlet 22.
  • the fluid inlet 21 and the fluid outlet 22 of the second fluid channel 20 point in the stacking direction R. In this way, the fluid inlets 21 and the fluid outlets 22 of the second fluid channels 20 of the modules 30, 40, 41 are flow-connected to one another in the stacking direction R.
  • the modules 30, 40, 41 have corresponding sealing surfaces in the area of the fluid inlet 21 and fluid outlet 22 of the second fluid channel 20, so that no additional sealing means are required.
  • the modules 30, 40, 41 have corresponding sealing surfaces along the first fluid channel 10.
  • the second fluid channel 20 branches behind the fluid inlet 21 into a first 23 and second sub-channel 24. Else elsewhere, the first 23 and the second sub-channel 24 open in front of the fluid outlet 22 of the second fluid channel 20 into a common collection chamber 28, whereby they are brought together again to a collection channel 25.
  • the collecting channel 25 runs transversely to the first fluid channel 10 at least in a first section A1. In addition, it is arranged closer to the fluid inlet 11 of the first fluid channel 10 than the first sub-channel 23 and the second sub-channel 24.
  • the length of the first section A1 is greater than three-quarters maximum diameter of the adjacent first fluid channel 10th
  • the first sub-channel 23 extends transversely to the first fluid channel 10 in a second section A2.
  • the length of the second section A2 is greater than two-thirds of the maximum diameter of the adjacent first fluid channel 10.
  • this second section A2 is closer to the fluid inlet 11 of the first fluid channel
  • the first portion A1 of the collecting channel 25 is adjacent and parallel to the second portion A2 of the first sub-channel 10.
  • Both the first portion A1 of the collecting channel 25 and the second portion A2 of the first sub-channel 23 have a circular Cross-section S. It can further be seen that the first sub-channel 24 is branched into two single-part channels, which run essentially parallel to one another.
  • the second sub-channel 24 is formed herringbone-shaped, for which he has a feed channel 26, branch off from the herringbone branch channels 27.
  • the feeding channel 26 is aligned substantially transversely to the first fluid channel 10.
  • the branch channels 27 extend diagonally, or rather rather longitudinally, to the first fluid channel 27.
  • the volume V1 of the first sub-channel 23 is smaller than the volume V2 of the herringbone branched second sub-channel 24.
  • the volume V2 of the second sub-channel 24 is even greater than the sum of the volumes V1, V3 of the first sub-channel 23 and the collecting channel 25th It can also be easily recognized that the flow resistance W3 of the collecting channel 25 is greater than the resulting flow resistance of the parallel-connected flow resistances W1, W2 of the first and second sub-channels 23, 24.
  • the second sub-channel 24 is in the illustrated embodiment of the second fluid channel 20 Condensation region of the first fluid channel 10th
  • Fig. 5 recognizes the structure of the module 30 of two plates 31, 32, between which the second fluid channel 20 is formed.
  • the two plates 31, 32 are integrally connected to each other and each have a second fluid channel 20 corresponding, structured shape, which is raised on the outside of the plates 31, 32.
  • the module 30 according to Fig. 6 from a single plate 31, 32, wherein the plate 31, 32 is folded along a bending region 34, which is arranged in the region of the fluid inlet 11 of the first fluid channel 10.
  • the thus formed two plate portions 31, 32 lie flat against each other, so that the second fluid channel 20 is formed between them.
  • both plate regions 31, 32 have a structured shaping corresponding to the second fluid channel 20, which is raised on the outside.
  • the bending region 34 directly adjoins the collecting channel 25.
  • Fig. 7 is a section through a first section A1 of a collecting channel 25 of a module 30 to see.
  • the first section A1 of the collecting channel 25 has an oval cross section S with two narrow end faces S1, S2 and two wide longitudinal sides S3, S4.
  • the narrow end faces S1, S2 are aligned substantially transversely to the first fluid channel 10, as can be seen from the trimmed first and second plates 31, 32.
  • rotational elements 50 are each formed with a deflection surface 51.
  • Each deflection surface 51 has a slope relative to the passageway, so that water flowing through W is forced into a rotation.
  • Fig. 8 shows a U-shaped heat exchanger 1.
  • the modules 30, 40, 41 are provided on the side of the fluid inlet 11 of the first fluid channel 10 with lateral legs 63, so that the modules 30, 40, 41 are U-shaped. In these legs 63 additional fluid channels extend to the cooling.
  • R end-side end modules 60, 61 which cover the entire U-shape of the modules 30, 40, 41, results in a unilaterally open chamber 62, which adjoins the fluid inlet 11 of the first fluid channel 10 and directly used as a combustion chamber 62 is.
  • the end modules 60, 61 have additional fluid channels so that they can be cooled over the entire surface. It can also be seen above the center inserted viewing holes in the front first end module 60th

Claims (11)

  1. Echangeur de chaleur (1) comprenant un premier canal (10) pour un premier fluide, avec une entrée de fluide (11) et une sortie de fluide (12), et un deuxième canal (20) pour un deuxième fluide, avec une entrée de fluide (21) et une sortie de fluide (22), le deuxième canal de fluide (20) étant ramifié en un premier et un deuxième canal partiel (23, 24) en aval de son entrée de fluide (21),
    le premier et le deuxième canal partiel (23, 24) se réunissant en amont de la sortie de fluide (22) du deuxième canal de fluide (20) en un canal de collecte (25) qui s'étend dans une première partie (A1) transversalement par rapport au premier canal de fluide (10) et est disposé plus près de l'entrée de fluide (11) du deuxième canal de fluide (10) que le premier canal partiel (23) et le deuxième canal partiel (24),
    le premier canal partiel (23) s'étendant dans une deuxième partie (A2) transversalement par rapport au premier canal de fluide (10) et cette deuxième partie (A2) étant disposée plus près de l'entrée de fluide (11) du premier canal de fluide (10) que le deuxième canal partiel (24),
    caractérisé en ce que
    le deuxième canal de fluide (20) est formé à l'intérieur d'un premier module (30) essentiellement plat et
    en ce que le deuxième canal partiel (24) est délimité par des parties gaufrées en arêtes de poisson par une plaque qui forme le premier module (30) ou par les plaques (31, 32) qui forment le premier module (30).
  2. Echangeur de chaleur (1) selon la revendication 2, caractérisé en ce que le premier module (30) est constitué de deux plaques (31, 32) entre lesquelles est formé le deuxième canal de fluide (20), les deux plaques (31, 32) étant reliées l'une à l'autre en correspondance mécanique ou en correspondance de matière.
  3. Echangeur de chaleur (1) selon la revendication 2, caractérisé en ce que le premier module (30) est constitué d'une plaque (31, 32), la plaque (31, 32) étant repliée le long d'une partie de flexion (34) disposée au niveau de l'entrée de fluide (11) du premier canal de fluide (10) et comprenant deux parties de plaque (31, 32) disposées à plat l'une au-dessus de l'autre et entre lesquelles est formé le deuxième canal de fluide (20).
  4. Echangeur de chaleur (1) selon l'une des revendications précédentes, caractérisé en ce que le premier module (30) est constitué d'acier inoxydable fortement allié.
  5. Echangeur de chaleur (1) selon l'une des revendications précédentes, caractérisé en ce que la première partie (A1) du canal de collecte (25) et/ou la deuxième partie (A2) du premier canal partiel (23) présentent une section transversale (S) ovale présentant deux côtés frontaux étroits (S1, S2) et deux côtés longitudinaux larges (S3, S4).
  6. Echangeur de chaleur (1) selon l'une des revendications précédentes, caractérisé en ce qu'au moins un élément de rotation (50) doté d'une surface de renvoi (51), qui présente une pente par rapport à l'évolution du canal, est formé dans le canal de collecte (25) et/ou dans le premier canal partiel (23).
  7. Echangeur de chaleur (1) selon l'une des revendications précédentes, caractérisé en ce que la résistance à l'écoulement (W1) du premier canal partiel (23) s'écarte d'au plus 10 % de la résistance à l'écoulement (W2) du deuxième canal partiel (24).
  8. Echangeur de chaleur (1) selon l'une des revendications précédentes, caractérisé en ce que le volume (V1) du premier canal partiel (23) est plus petite que le volume (V2) du deuxième canal partiel (24).
  9. Echangeur de chaleur (1) selon l'une des revendications précédentes, caractérisé en ce que la résistance à l'écoulement (W3) du canal de collecte (25) est supérieure à la résistance à l'écoulement résultante des résultantes des résistances à l'écoulement (W1, W2) branchées en parallèle du premier et du deuxième canal partiel (23, 24).
  10. Dispositif de chauffage présentant :
    a) une chambre de combustion (62) qui comprend une amenée de gaz chaud et une évacuation de gaz chaud et raccordée à écoulement à une entrée de fluide (11) d'un premier canal de fluide (10) d'un échangeur de chaleur (1) selon l'une des revendications précédentes et
    b) un circuit de fluide conduisant un fluide caloporteur, dans lequel l'échangeur de chaleur (1) est intégré avec l'entrée de fluide (21) et la sortie de fluide (22) du deuxième canal de fluide (20).
  11. Dispositif de chauffage selon la revendication 12, caractérisé en ce que le premier module a la forme d'un U, le premier module englobant au moins en partie par son creux la chambre de combustion et le canal de collecte (25) s'étendant en forme de U dans les parties du premier module proches de la chambre de combustion.
EP14151370.5A 2013-01-18 2014-01-16 Échangeur de chaleur avec transfert de chaleur optimisé et dispositif de chauffage doté d'un tel échangeur de chaleur Active EP2757336B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
TR201300671 2013-01-18

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EP14151370.5A Active EP2757336B1 (fr) 2013-01-18 2014-01-16 Échangeur de chaleur avec transfert de chaleur optimisé et dispositif de chauffage doté d'un tel échangeur de chaleur

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EP3040670A1 (fr) * 2015-01-05 2016-07-06 VALEO AUTOSYSTEMY Sp. Z. o.o. Échangeur de chaleur, notamment un condenseur ou un refroidisseur de gaz
SE542079C2 (en) 2017-05-11 2020-02-18 Alfa Laval Corp Ab Plate for heat exchange arrangement and heat exchange arrangement

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FR2737557B1 (fr) * 1995-07-31 1997-09-12 Valeo Climatisation Tube a circulation en u pour echangeur de chaleur et son procede de fabrication
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Publication number Priority date Publication date Assignee Title
FR3129715A1 (fr) * 2021-11-30 2023-06-02 Valeo Systemes Thermiques Systeme de gestion thermique
WO2023099236A1 (fr) * 2021-11-30 2023-06-08 Valeo Systemes Thermiques Systeme de gestion thermique

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EP2757336A2 (fr) 2014-07-23

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