EP3334615A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur

Info

Publication number
EP3334615A1
EP3334615A1 EP16805381.7A EP16805381A EP3334615A1 EP 3334615 A1 EP3334615 A1 EP 3334615A1 EP 16805381 A EP16805381 A EP 16805381A EP 3334615 A1 EP3334615 A1 EP 3334615A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
coolant
stage
air
channels
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.)
Withdrawn
Application number
EP16805381.7A
Other languages
German (de)
English (en)
Inventor
Jürgen Grünwald
Christian Heneka
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle International GmbH
Original Assignee
Mahle International GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP3334615A1 publication Critical patent/EP3334615A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00321—Heat exchangers for air-conditioning devices
    • B60H1/00328—Heat exchangers for air-conditioning devices of the liquid-air type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00478—Air-conditioning devices using the Peltier effect
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H3/00—Air heaters
    • F24H3/02—Air heaters with forced circulation
    • F24H3/04—Air heaters with forced circulation the air being in direct contact with the heating medium, e.g. electric heating element
    • F24H3/0405—Air heaters with forced circulation the air being in direct contact with the heating medium, e.g. electric heating element using electric energy supply, e.g. the heating medium being a resistive element; Heating by direct contact, i.e. with resistive elements, electrodes and fins being bonded together without additional element in-between
    • F24H3/0429—For vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H3/00—Air heaters
    • F24H3/12—Air heaters with additional heating arrangements
    • 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 present invention relates to a heat exchanger, in particular a heat exchanger for heating a vehicle interior via a cooling circuit of a vehicle with electric or hybrid drive.
  • the invention also relates to a vehicle equipped with at least one such heat exchanger.
  • a room air conditioner is known with the aid of which an air flow can be heated, which in turn serves to heat a living space.
  • the heat required for this purpose is provided via a liquid flow.
  • the room air conditioner has two successively arranged heat exchanger, which in their respective heat exchanger block each have a flow-through air flow through the air channel and a medium through which can flow through the heating medium, which are heat-transmitting and media-separated coupled.
  • the room air conditioner has a two-stage heating of the air flow.
  • a Peltier element is arranged with the aid of which heat can be pumped from the liquid heating medium flow to the air flow or vice versa.
  • a hybrid air conditioning system which is also intended for use on a building.
  • two separate air-to-air heat exchangers are arranged, which are flowed through by a serial air flow to be cooled.
  • the upstream, first through-flow heat exchanger is also flowed through by a first cooling air flow, so that over the first heat exchanger, a pre-cooling of the air flow to be cooled can be achieved.
  • a further cooling takes place in conjunction with a second cooling air flow and in conjunction with thermoelectric converters which are integrated into the second heat exchanger.
  • a cooling device for electrical equipment such as for a computer, which has two separate cooling devices, which are arranged in series in a cooling circuit. It is in the cooling circuit Upstream arranged first cooling device provided to cool the coolant circulating in the cooling circuit to ambient temperature.
  • the second cooling device arranged downstream thereof in the cooling circuit serves to cool the coolant below the ambient temperature, before it is then supplied to the respective electrical component to be cooled.
  • the second cooling device is equipped with electrothermal transducers to improve the cooling effect for the coolant.
  • the present invention is concerned with the problem of providing for a heat exchanger of the type mentioned or for a vehicle equipped therewith an improved embodiment, which is characterized in particular by a small space requirement and by a high operating comfort, even if the heat available strong varied.
  • the invention is based on the general idea to form two heat transfer stages in the heat exchanger block of the heat exchanger, which are arranged one behind the other with respect to the air flow.
  • the formation of two heat transfer stages in one and the same heat exchanger block leads to a particularly compact design for the heat exchanger. Furthermore, this design also leads to a first heat exchanger stage having the air inlet side of the heat exchanger block, while a second heat exchanger stage has an air outlet side of the heat exchanger block.
  • the two heat exchanger stages are arranged one behind the other with respect to the air flow, such that the first heat exchanger stage is first flowed through by the air flow, while the second heat exchanger stage by the air flow flows through it.
  • a plurality of the air flow through ström bare air channels and a plurality of coolant flow souströmbare coolant channels are provided in the common heat exchanger block and arranged so that they are passed through both heat exchanger stages and heat transfer in both heat transfer stages and media separated coupled.
  • the compact design is also supported by the fact that the arrangement of air ducts and coolant channels in the heat exchanger block is such that during operation of the heat exchanger and the total heat exchanger stages are flowed through in each case according to the cross-flow principle of the coolant and the air.
  • the heat exchanger according to the invention is also provided to arrange only in one of the two heat exchanger stages more thermoelectric modules between the air channels and the coolant channels.
  • thermoelectric modules or converters can convert electrical current into heat and have so-called Peltier elements.
  • the thermoelectric modules can be operated as a heat pump depending on demand, to transfer heat from the coolant flow to the air flow or vice versa.
  • the integration of the thermoelectric modules in only one of the two stages of the heat exchanger results in a particularly advantageous design.
  • the thermoelectric modules are preferably arranged exclusively in the second heat exchanger stage. In principle, however, an embodiment is conceivable in which the thermoelectric modules are arranged exclusively in the first heat exchanger stage.
  • thermoelectric modules only in one or the second heat exchanger stage has the advantage that in the other or first heat exchanger stage direct heat coupling between air ducts and coolant channels can be used for efficient heat transfer, while in the second heat exchanger stage demand-dependent the heat pump function of the thermoelectric Modules can be used.
  • a heat exchanger which has only a single heat exchanger stage, which is equipped with thermoelectric If the thermoelectric converters are not active, a significantly improved heat transfer results, since the deactivated thermoelectric converters act more or less as thermal insulators.
  • the first heat exchanger stage and the second heat exchanger stage can adjoin one another in a depth direction of the heat exchanger block.
  • at least two such coolant channels can now run parallel to one another and be arranged one behind the other or next to each other in the depth direction.
  • a plurality of such coolant channels can run parallel to one another in the heat exchanger block and can be arranged one above the other or next to one another in a vertical direction of the heat exchanger block extending perpendicular to the depth direction.
  • the air channels are formed in the heat exchanger block between coolant channels which are adjacent to each other in the height direction. As a result, the air channels and the coolant channels penetrate each other in a projection parallel to the height direction according to the cross-flow principle.
  • the air ducts may extend continuously from the air inlet side to the air outlet side, wherein the respective continuous air duct has a height measured in the channel height, which is substantially constant along the depth direction and / or in the first heat exchanger stage and in the second Heat exchanger stage is about the same size.
  • a jump in the cross section which leads to an increased flow resistance, is avoided.
  • the totality of all air ducts defines an air path which passes through the heat exchanger block or through the heat exchanger. Appropriately, this air path now has in the first heat exchanger stage and in the second heat exchanger stage about the same flowed through by the air flow cross-section.
  • thermoelectric module and a coolant channel can be arranged in the second heat exchanger stage between two air ducts adjacent in the height direction. This results in a particularly compact design.
  • the arrangement has only a single such thermoelectric module and the coolant channel.
  • the respective air duct is then coupled via this thermoelectric module only with one of the coolant channels adjacent thereto.
  • the arrangement comprises two such thermoelectric modules and the coolant channel, which is arranged in the height direction between these two thermoelectric modules. This results in the vertical direction of a layered construction, in which an air duct on a thermoelectric module, a coolant channel on this, followed by another thermoelectric module and only on this another air duct.
  • the respective arrangement may have an arrangement height measured in the height direction which is approximately the same size as a channel height of a coolant channel measured in the height direction, which runs in the first heat exchanger stage and is adjacent to this arrangement in the depth direction. This ensures that in the region of the coolant channels within the first heat transfer stage and within the second heat transfer. Tragerlab about the same space in the height direction is needed.
  • the channel height of a coolant channel in the first heat exchanger stage corresponds to the sum of the channel height of a coolant channel in the second heat exchanger stage and twice the height of such a thermoelectric module. If the coolant channels in the two heat exchanger stages have approximately the same dimensions in the depth direction, the cross-section through which the coolant flows in the coolant channels in the first heat exchanger stage is greater than in the second heat exchanger stage.
  • the coolant channels may extend straight and parallel to each other and parallel to a width direction of the heat exchanger block, which is perpendicular to the height direction and perpendicular to the depth direction. This results in a particularly simple structure for the heat exchanger block, which is inexpensive to implement.
  • the coolant channels may be formed by the coolant flow leading coolant tubes, which extend in the heat exchanger block.
  • the air ducts in the first heat exchanger stage are delimited by the coolant tubes and in the second heat exchanger stage by the thermoelectric modules.
  • the limitation of the air ducts through the coolant pipes or through the thermoelectric modules takes place in the height direction. This measure results in a particularly inexpensive construction for the heat exchanger.
  • the coolant channels in the heat exchanger block may be fluidly connected to one another in such a way that the coolant channels extending in the first heat exchanger stage and those in the second heat exchanger block Transfer stage extending coolant channels are parallel flowed through by the coolant flow.
  • the heat exchanger has a particularly low flow resistance for the coolant flow.
  • a distributor box common to the first heat exchanger stage and the second heat exchanger stage with a coolant inlet and a collecting box with a coolant outlet common to the first heat exchanger stage and the second heat exchanger stage can be provided on the heat exchanger block, the sides of the heat exchanger block facing away from one another in a width direction of the heat exchanger block are arranged and fluidly connected to each other via the coolant channels.
  • the width direction of the heat exchanger block extends perpendicular to the height direction and perpendicular to the depth direction.
  • the coolant channels in the heat exchanger block can be fluidly connected to one another such that the coolant channels extending in the first heat exchanger stage and the coolant channels extending in the second heat exchanger stage can be flowed through in series by the coolant stream.
  • a particularly efficient heat transfer between coolant flow and air flow can be realized.
  • a distributor box assigned to a heat exchanger stage is arranged on the heat exchanger block on a first side with a coolant inlet and a collecting box with a coolant outlet assigned to the other heat exchanger stage, while one fluidically connected to the distributor box and to the collector box via the coolant channels
  • Deflection box is arranged on a second side of the heat exchanger block, which from the first side in a width direction the heat exchanger block faces away.
  • the width direction extends as mentioned perpendicular to the height direction and perpendicular to the depth direction.
  • the heat exchanger in the last-mentioned embodiments can be configured such that it operates on the cross-DC principle.
  • the coolant flow crosses or traverses the air flow, wherein the coolant flow from the first heat transfer stage to the second heat transfer stage also runs in DC with respect to the air flow, ie as the air flow flows first through the first heat transfer stage and then through the second heat transfer stage.
  • a vehicle according to the invention which is equipped with an electric drive or with a hybrid drive and which is preferably a road vehicle, has a cooling circuit in which a coolant circulates and which serves to cool at least one component of the vehicle which is in operation Vehicle warms up.
  • a heat exchanger of the type described above is installed so that the coolant of the cooling circuit can flow through the coolant channels of the heat exchanger.
  • the vehicle is equipped with a blower for generating an air flow, which is passed through the air passages of the heat exchanger and into a vehicle interior inside.
  • a control device is provided with which the thermoelectric modules of the heat exchanger can be controlled so that they work as a heat pump.
  • control device is programmed or designed such that it activates the thermoelectric modules more or less strongly for heating the air flow as a function of the temperature of the coolant and depending on a deviation or difference between desired temperature and actual temperature of the vehicle interior. If the temperature of the coolant is high enough, heating of the air flow can be achieved even without connecting the thermoelectric modules. chen. On the other hand, when starting the vehicle cold, it may be necessary to heat the airflow exclusively via the thermoelectric modules. Likewise, virtually any number of mixed operating states are possible in which the control device energizes the thermoelectric modules more or less strongly in order to obtain a combination of passively transmitted coolant heat flow, actively pumped coolant heat flow and electrical heating power. Such an actively pumped coolant heat flow is given by the heat pump effect of the thermoelectric modules, which is stronger or weaker when energizing the thermoelectric modules depending on the current boundary conditions.
  • 1 is a greatly simplified, schematic diagram of a schematic diagram of a vehicle with hybrid drive, which is equipped with a heat exchanger,
  • Fig. 2 is a greatly simplified longitudinal section of the heat exchanger
  • 3 and 4 are each a longitudinal section of the heat exchanger as in Fig. 2, but in a rotated by 90 ° cutting plane and in two different embodiments.
  • a vehicle 1 with hybrid drive 2 comprises at least one cooling circuit 3 for cooling at least one component of the vehicle 1.
  • the hybrid drive 2 is designed as a serial hybrid, in which an internal combustion engine 4 drives a module 5, which charges a battery 7 via a power electronics 6.
  • the drive of the vehicle 1 takes place only electrically via at least one electric motor 8 which is supplied with power by the battery 7 and which is connected in a suitable manner to at least one drive wheel 9 of the vehicle 1.
  • the power electronics 6 controls the power supply of the electric motor 8 and the charging of the battery 7.
  • Each of the components mentioned can heat up during operation of the vehicle 1. It is customary to connect the internal combustion engine 4 to a cooling circuit 3. Also, the module 5 may be connected to a cooling circuit 3.
  • the battery 7, the power electronics 6 and the respective electric motor 8 may each be connected to a cooling circuit 3.
  • different cooling circuits 3 can be used here.
  • it may be different circles or sections of a common cooling circuit 3.
  • a heat exchanger 10 is involved, so that in the cooling circuit 3 circulating coolant can also flow through the heat exchanger 10.
  • the vehicle 1 is equipped with a blower 1 1 allows, with the aid of an air flow 12 can be generated, which is also passed through the heat exchanger 10.
  • the heat exchanger 10 there is a heat-transmitting coupling between the air flow 12 and a coolant flow 13.
  • the air flow 12 is supplied to a vehicle interior 14 in order to heat it as needed.
  • the hybrid drive 2 can also be configured as a parallel hybrid or as a power-split hybrid or as a hybrid hybrid.
  • the heat exchanger 10 has a heat exchanger block 15 which has a plurality of parallel air flow 12 by ström bare air passages 16 and a plurality of coolant flow through the flow channel 13 17 coolant channels.
  • the air ducts 16 and the coolant channels 17 are heat-transferring and media-separated coupled in the heat exchanger block 15, so that an efficient heat transfer between the coolant flow 13 and air flow 12 takes place while no mixing of air and coolant takes place.
  • the air channels 16 and the coolant channels 17 are arranged according to FIGS. 1, 3 and 4 in the heat exchanger block 15 according to the cross-flow principle.
  • the heat exchanger 10 or its heat exchanger block 15 has a depth direction T defined by the direction of flow through which the air flow 12 passes through the heat exchanger block 15, a height direction H perpendicular to the depth direction T, visible in FIG. 2, and perpendicular to the depth direction T and perpendicular 1, 3 and 4 recognizable width direction B.
  • the flow through the heat exchanger block 15 with the air flow 12 takes place in the depth direction T, while the flow through the heat exchanger block 15 by the coolant flow 13 substantially Chen parallel to the width direction B takes place.
  • the flow paths of air flow 12 and coolant flow 13 intersect in the heat exchanger block 15, whereby the cross-flow principle is realized.
  • the heat exchanger 10 presented here has a first heat exchanger stage 18 and a second heat exchanger stage 19 within one heat exchanger block 15.
  • An air outlet side 21 of the heat exchanger block 15 is assigned to the second heat exchanger stage 19.
  • the air channels 16 and the coolant channels 17 are laid in the heat transfer block 15 so that they passed through both the first heat transfer stage 18 and through the second heat transfer stage 19 are, in such a way that the air channels 16 and the coolant channels 17 in both the first heat transfer stage 18 and in the second heat transfer stage 19 are heat-transmitting and media-separated coupled to each other.
  • both in the first heat exchanger stage 18 and in the second heat exchanger stage 19 there is a heat transfer between the coolant flow 13 and air flow 12, which is achieved by a corresponding routing of the air channels 16 and the coolant channels 17.
  • thermoelectric modules 22 are also arranged in the heat exchanger block 15, in each case between one air channel 16 and one coolant channel 17. These thermoelectric modules 22 can be operated as a heat pump as needed to transfer heat from the coolant stream 13 to the Air flow 12 to transmit.
  • the thermoelectric modules 22 are recognizable only in the second heat exchanger level 19 provided. In the first heat exchanger stage 18 thus no thermoelectric modules 22 are provided.
  • the vehicle 1 is equipped with a control device 23 according to FIG. 1, which is electrically connected via suitable control lines 24 to the thermoelectric modules 22.
  • the control device 23 can also be connected via signal lines 25 with temperature sensors 26, 27.
  • the one temperature sensor 26 determines the temperature of the coolant immediately upstream of the heat exchanger 10.
  • the other temperature sensor 27 determines the actual temperature in the vehicle interior 14.
  • the controller 23 may now be programmed or designed so that it depends on a desired temperature for the Vehicle interior 14, which may also be referred to as a target temperature, controls the heating of the air flow 12 or controls. In this case, depending on the current temperature of the coolant and depending on the current target / actual deviation of the temperature of the vehicle interior 14, it can switch on the thermoelectric modules 22 more or less strongly.
  • the two heat exchanger stages 18, 19 are arranged one behind the other in the depth direction T, so that they adjoin one another in the depth direction T.
  • a plurality of coolant channels 17 are arranged one above the other or according to FIG. 2 next to each other.
  • the coolant channels 17 each extend parallel to one another.
  • the air channels 16 are also in the height direction H parallel to each other and arranged one above the other or side by side.
  • the air channels 16 are each provided between two coolant channels 17, which are adjacent to each other in the height direction H.
  • H air channels 16 and coolant channels 17 alternate in the height direction H from each other.
  • the air ducts 16 extend continuously from the air inlet side 20 to the air outlet side 21 through the heat exchanger block 15.
  • Each individual air channel 16 has a channel height 28 measured in the height direction H which is constant along the depth direction T.
  • the channel height 28 in the first heat exchanger stage 18 is the same size as in the second heat exchanger stage 19th
  • the air channel 16 and coolant channel 17 alternate directly and immediately in the height direction H, so that in each case a coolant channel 17 is arranged between two air channels 16 adjacent in the height direction H.
  • an arrangement 29 is arranged between two adjacent in the height direction H air channels 16, each consisting of two thermoelectric modules 22 and a coolant channel 17.
  • the coolant channel 17 is arranged in the height direction H between the two thermoelectric modules 22.
  • the respective arrangement 29 has an arrangement height 30 measured in the height direction H.
  • the arrangement height 30 is the same as a channel height 31, which is likewise measured in the height direction H and belongs to that coolant channel 17, that in the first heat transfer stage 18 thereto in the depth direction T is adjacent.
  • the coolant channels 17 and the air channels 16 each extend in a straight line and parallel to one another.
  • the coolant channels 17 may expediently be formed by coolant tubes 32, which guide the coolant flow 13 and which are located in the heat exchanger block. lock 15 run.
  • the Kuhlstoffrohre 32 may also extend parallel to the width direction B, which can be seen from the sectional views of FIGS. 3 and 4.
  • In the coolant channels 16 can be arranged in the usual way, not shown here turbulators to improve the heat transfer.
  • the air passages 16 are delimited within the first heat exchanger stage 18 by the coolant tubes 17 and within the second heat exchanger stage 19 by the thermoelectric modules 22.
  • the air ducts 16 turbulators or fins may be arranged in the usual way to improve the heat transfer.
  • the thermoelectric modules 22 may be provided with cooling fins at their outer sides exposed to the air flow 12 in order to improve the heat transfer.
  • the coolant channels 17 in the heat exchanger block 15 are fluidly connected to one another such that the coolant channels 17 extending in the first heat exchanger stage 18 and the coolant channels 17 extending in the second heat exchanger stage 19 are flowed through in parallel by the coolant stream 13.
  • This parallel connection is designated 34 in FIG.
  • Fig. 4 shows an embodiment in which a series circuit or series circuit 35 is realized.
  • the coolant channels 17 are fluidly connected to one another in the heat exchanger block 15 such that the coolant channels 17 running in the first heat exchanger stage 18 and those running in the second heat exchanger stage 19 Coolant channels 17 serially, so are successively flowed through by the coolant flow 13.
  • the coolant channels 17 in the first heat exchanger stage 18 are flowed through in parallel by the coolant.
  • the coolant channels 17 in the first heat exchanger stage 18 and in the second heat exchanger stage 19 are flowed through in the same direction.
  • the coolant channels 17 of the first heat exchanger stage 18 and the second heat exchanger stage 19, on the other hand, flow in opposite directions through the coolant.
  • the parallel circuit 34 is achieved in the embodiment shown in Fig. 3 by means of a junction box 36 which is provided on the heat exchanger block 15 together for both heat exchanger stages 18, 19. Further, a common collection box 37 is provided on the heat exchanger block 15, which is also associated with two heat exchanger stages 18, 19. Distributor box 36 and collection box 37 are arranged with respect to the width direction B on opposite sides 41, 42 of the heat exchanger block 15. Furthermore, distribution box 36 and collection box 37 via the coolant channels 17 and the coolant tube 33 are fluidly connected to each other.
  • the distribution box 36 has a coolant inlet 38. In contrast, the collection box has a coolant outlet 39.
  • the series circuit 35 is also realized by means of a junction box 36, which has the coolant inlet 38, and a collecting tank 37, which has the coolant outlet 39, in conjunction with a deflection box 40.
  • the distribution box 36 is on the one or first side 41 of the heat exchanger block 15 and thereby only one of the heat exchanger stages 18, 19, here the first heat exchanger stage 18 assigned.
  • the collecting boxes 37 is also disposed on the first side 41 of the heat exchanger block 15 and the other, here associated with the second heat transfer stage 19.
  • the deflecting box 40 is disposed on the other or second side 42 of the heat exchanger block 15, which faces in the width direction B of the first side 41 and facing away therefrom.
  • the deflection box 40 is assigned to both heat exchanger stages 18, 19.
  • the deflection box 40 is in fluid communication with the distribution box 36 via the coolant channels 17 extending in the first heat transfer stage 18, while it is in fluid communication with the collection box 37 via the coolant channels 17 extending in the second heat transfer stage 19.
  • the air channels 16 and the coolant channels 17 are arranged within the heat exchanger block 15 so that adjusts a flow according to the cross-DC principle. Accordingly, the coolant first flows through the first heat exchanger stage 18 and then through the second heat exchanger stage 19.
  • an arrangement according to the cross-countercurrent principle is also conceivable.

Abstract

La présente invention concerne un échangeur de chaleur (10) comprenant un bloc d'échangeur de chaleur (15) qui comporte plusieurs conduits d'air (16) pouvant être traversés parallèlement par un flux d'air (12) et plusieurs conduits de réfrigérant (17) pouvant être traversés par un flux de réfrigérant (13), lesquels sont accouplés les uns autres de manière à transmettre la chaleur et de manière à maintenir les milieux séparés, les conduits d'air (16) et les conduits de réfrigérant (17) étant disposés dans le bloc d'échangeur de chaleur (15) selon le principe des flux croisés. Une forme de construction particulièrement compacte peut être obtenue lorsqu'un premier étage d'échangeur de chaleur (18) doté d'un côté d'entrée d'air (20) et un deuxième étage d'échangeur de chaleur (19) doté d'un côté de sortie d'air (21) sont disposés à l'intérieur du bloc d'échangeur de chaleur (15), lorsque les conduits d'air (16) et les conduits de réfrigérant (17) sont guidés à travers le premier étage d'échangeur de chaleur (18) et à travers le deuxième étage d'échangeur de chaleur (19) de telle sorte qu'ils soient accouplés les uns autres de manière à transmettre la chaleur et de manière à maintenir les milieux séparés dans le premier étage d'échangeur de chaleur (18) et dans le deuxième étage d'échangeur de chaleur (19), et lorsque des modules thermoélectriques (22) ne sont disposés que dans le deuxième étage d'échangeur de chaleur (19) entre les conduits d'air (16) et les conduits de réfrigérant (17).
EP16805381.7A 2015-12-02 2016-11-30 Échangeur de chaleur Withdrawn EP3334615A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015224082.7A DE102015224082B4 (de) 2015-12-02 2015-12-02 Wärmeübertrager
PCT/EP2016/079302 WO2017093328A1 (fr) 2015-12-02 2016-11-30 Échangeur de chaleur

Publications (1)

Publication Number Publication Date
EP3334615A1 true EP3334615A1 (fr) 2018-06-20

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP16805381.7A Withdrawn EP3334615A1 (fr) 2015-12-02 2016-11-30 Échangeur de chaleur

Country Status (5)

Country Link
US (1) US20180345754A1 (fr)
EP (1) EP3334615A1 (fr)
CN (1) CN108290473A (fr)
DE (1) DE102015224082B4 (fr)
WO (1) WO2017093328A1 (fr)

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EP3842723A1 (fr) 2019-12-23 2021-06-30 Hamilton Sundstrand Corporation Échangeur de chaleur fractal à deux étages

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DE102015224082B4 (de) 2022-01-13
DE102015224082A1 (de) 2017-06-08
US20180345754A1 (en) 2018-12-06
WO2017093328A1 (fr) 2017-06-08

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