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EP3027998B1 - Échangeur de chaleur à évaporateur - Google Patents

Échangeur de chaleur à évaporateur Download PDF

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Publication number
EP3027998B1
EP3027998B1 EP13745400.5A EP13745400A EP3027998B1 EP 3027998 B1 EP3027998 B1 EP 3027998B1 EP 13745400 A EP13745400 A EP 13745400A EP 3027998 B1 EP3027998 B1 EP 3027998B1
Authority
EP
European Patent Office
Prior art keywords
leakage
fluid
heat exchanger
plate
channel
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
EP13745400.5A
Other languages
German (de)
English (en)
Other versions
EP3027998A1 (fr
Inventor
Peter Geskes
David MERCADER QUINTANA
Gerd Schleier
Michael Schmidt
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
Mahle 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 Mahle Behr GmbH and Co KG filed Critical Mahle Behr GmbH and Co KG
Publication of EP3027998A1 publication Critical patent/EP3027998A1/fr
Application granted granted Critical
Publication of EP3027998B1 publication Critical patent/EP3027998B1/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
    • 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
    • F28F3/005—Arrangements for preventing direct contact between different heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements
    • F25B39/024—Evaporators with plate-like or laminated elements with elements constructed in the shape of a hollow panel
    • 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
    • F28F2265/16—Safety or protection arrangements; Arrangements for preventing malfunction for preventing leakage

Definitions

  • the present invention relates to an evaporator heat exchanger for evaporating liquid working medium according to the preamble of claim 1.
  • Such a heat exchanger is known from DE 20 2010 015374 U1 ,
  • thermally ie the energy of the exhaust gas is used for example for heating a passenger compartment or for heating the internal combustion engine or the transmission.
  • thermal energy is also taken from the exhaust gas, it is returned to the internal combustion engine in mechanical form.
  • This method is based on a steam power process in which a particular working fluid is vaporized and overheated in an evaporator and expanded in an adjoining expander, such as a turbine, thereby generating mechanical energy. The evaporation takes place by means of heating via the exhaust gas.
  • the working medium to be evaporated is usually first heated in an evaporator to boiling temperature, then evaporated and then superheated. This can be done in principle in two different locations in a motor vehicle.
  • an evaporator which is used instead of an exhaust gas cooler, heat can be extracted from the exhaust gas in order to evaporate the working medium.
  • the exhaust gas is cooled by the evaporation of the fluid to be evaporated and then returned to the engine together with the fresh air.
  • the main exhaust gas stream should also be used as a heat source in order to evaporate working medium in a so-called main exhaust gas evaporator.
  • Such a main exhaust gas evaporator is usually from the vehicle manufacturers behind the muffler or behind the entire exhaust aftertreatment arranged in the exhaust system.
  • the charge air can be used as a heat source in turbocharged engines.
  • WO 2012/010349 A1 is a generic evaporator heat exchanger for vaporizing liquid working fluid and the use of waste heat of an internal combustion engine known.
  • an introduction of the working medium into the combustion air supplied to the internal combustion engine should be substantially ruled out due to a leak or leakage at the evaporator heat exchanger.
  • at least one first flow channel is formed by at least one first limiting component and at least one second flow channel of at least one second limiting component, wherein at least one of these limiting components is a fluid-conducting connection in the environment or in a receiving space, so that at a leakage at the boundary components Working medium in the environment or in the receiving space can be introduced.
  • Prior art concepts of a gas-fired evaporator heat exchanger contemplate reducing the risk of mixing gas and working fluid. For example, if a fluorinated refrigerant flows into the exhaust gas and is supplied to the internal combustion engine and burned in the latter, hydrofluoric acid is produced, which can escape from an exhaust pipe and cause damage there. If, for example, an alcohol is used instead of this refrigerant, the alcohol in the internal combustion engine would be burned with a leak, which would be noticeable by a sudden increase in the power of the internal combustion engine. This may be difficult to handle, especially for inexperienced drivers.
  • the present invention therefore deals with the problem of providing an improved embodiment for an evaporator heat exchanger of the generic type, in which an undesired mixing of working medium and gas, in particular exhaust gas or charge air, can be excluded.
  • the present invention is based on the general idea of providing a leakage channel or leakage space between a first flow channel carrying a working medium and a second, gas, in particular exhaust gas or charge air, leading flow channel, thereby passing through both the first flow channel and the leakage channel or leakage space form two cover plates and an interposed and profiled fluid disk in a particularly simple design manner.
  • the evaporator heat exchanger according to the invention for evaporating liquid working medium in this case has a housing in which said first flow channel for passing the working medium and the second flow channel for passing the gas are arranged.
  • the first flow channel and at least one leakage channel and / or leakage space are formed by two comparatively strong cover plates and a fluid disk arranged therebetween, whereby a disk package formed from two cover plates and an intermediate fluid disk thus forms the first flow channel and the at least one fluidly separated from it leakage channel or leakage chamber accommodated.
  • the connection between the two cover plates and the interposed fluid disc is cohesively, for example via a solder joint.
  • a second flow channel is arranged between two adjacent disk packages, in which the heat-transferring gas, for example exhaust gas or charge air, flows.
  • the heat-transferring gas for example exhaust gas or charge air
  • the working medium passes from the first flow channel into the leakage channel or into the leakage space and can be removed therefrom without any direct mixing with it the gas flowing in the second flow channel, for example, exhaust gas leads.
  • the leakage channel or the leakage chamber can also be used for discharging gas escaping undesirably from the second flow channel, if, for example, loosening a solder connection between the fluid disk and the cover plate or breaking a wall of the fluid disk leads to a fluidic connection between would lead to the leakage channel and the second flow channel.
  • the gas now flowing into the leakage channel or into the leakage chamber can be removed, thereby avoiding direct mixing with the working medium in the first flow channel.
  • the leakage channel or the leakage chamber thus forms a natural, lying between the two flow channels safety barrier.
  • the leakage channel or the leakage chamber is usually filled with air.
  • the strength of a material of the fluid disk is less than the strength of a cover plate arranged on the fluid disk.
  • This causes a kind of predetermined breaking point of the fluid disk, so that when the evaporator heat exchanger is overloaded in the region of the first flow channel, a passage of the working medium guided in the first flow channel takes place into the leakage channel.
  • the cover plate delimiting the first flow channel and upsets the rib structure arranged, for example, in the second flow channel.
  • a solder seam connecting the fluid disk with this cover plate can thereby be released, whereby a fluidic connection is created between the first flow channel and the leakage channel.
  • the working medium can be removed without mixing with the gas flowing in the second flow channel.
  • a predetermined breaking point can also be formed by a smaller wall thickness or material thickness of the fluid disk in comparison to the cover plates connected thereto. It is always important that, in the event of an overload, the fluid disk first breaks or tears and not the cover plates. In this way, regardless of the type of failure, it can always be ensured that the leakage channel or leakage chamber located between the first and the second flow channel can be used to discharge the working medium or the gas.
  • the leakage channel or the leakage chamber are preferably embossed circumferentially on the fluid disk, larger areas being designated as a leakage space and a smaller one as a leakage channel.
  • the evaporator heat exchanger has a plurality of stacked disk packages, each with a second flow channel arranged therebetween, the leakage channel and / or the leakage space of a fluid disk having a first opening and a plurality of opposing cover plates of two adjacent disk packages each having a second opening , wherein between the second openings a leakage bush to form a (leakage) outlet channel is arranged.
  • the leakage fluid or gas can be reliably discharged from the second flow channel or the working medium from the first flow channel.
  • the housing has a housing opening, which is connected via a housing cover bushing to the first or the second opening in the cover plate of a disk package arranged adjacent to the housing.
  • the housing cover bushing and all other leakage bushings thereby form an outlet channel, also called leakage outlet channel, for the passage of the leakage fluid, wherein on the housing cover bushing a line in the environment or periphery can be attached, in whose area a sensor is arranged, for measuring the pressure and / or the flow and / or a chemical composition of the fluid is formed in the conduit.
  • the outlet channel usually the ambient air pressure prevails. At the same time air is present with usual nature.
  • the fluid disk breaks and / or tears and thus an outlet of working medium from the first flow channel or gas from the second flow channel into the leakage channel
  • the pressure, the temperature and / or the pressure change in this chemical composition, since the leakage fluid, whether exhaust or working fluid, other physical and / or chemical properties than air.
  • the sensor which indicates a leak
  • it can for example control a pump or an exhaust gas recirculation valve conveying the working medium as a function of the signal detected by the sensor.
  • the output of a warning signal which indicates a user of the motor vehicle visually and / or acoustically on a malfunction of the evaporator heat exchanger.
  • the ambient air pressure of approximately 1 bar is usually applied to the sensor. If the evaporator heat exchanger is put into operation, the pressure in the leakage channel or in the leakage chamber rises due to the temperature-induced expansion to about 1-1.5 bar, which is normal. However, if the pressure does not rise, then either the sensor is defective or else the leakage channel or leakage chamber has a leak, via which a pressure reduction takes place can. If the pressure increases significantly during operation of the evaporator heat exchanger, this usually indicates a leakage of the first flow channel or of the second flow channel. The operation of the leakage channel is thus checked at each restart of the motor vehicle, in particular at each cold start.
  • Fig. 1 Has an inventive evaporator heat exchanger 1 for evaporating liquid working medium 2 (see also Fig. 2 to 4 ), a housing 3, in which a first flow channel 4 for passing the working medium 2 and a second flow channel 5 for passing a gas 6 are arranged. A heating of the working medium 2 takes place by a heat transfer of the gas 6, for example, exhaust gas or charge air.
  • the first flow channel 4 is now formed by two cover plates 7 and 8 and an interposed and profiled fluid disk 9, wherein the fluid disk 9 together with the two cover plates 7 and 8 at least one of the two flow channels 4, 5 separate leakage channel 10 and leakage chamber 11 limited.
  • the two cover plates 7, 8 together with a fluid disk 9 arranged therebetween form a disk pack 12, as described, for example, in accordance with FIGS Fig. 2 to 4 illustrated illustrated illustrated.
  • the respective leakage channel 10 and the leakage chamber 11 are arranged laterally next to or at the edge of the first flow channel 5, as in particular the Fig. 5 can be seen.
  • the leakage channel 10 creates a barrier between the two flow channels 4, 5, so that no direct mixing of the working medium 2 with the gas 6 and thus damage to an internal combustion engine can take place.
  • the working fluid to be evaporated flows into the exhaust gas in the event of leakage and, if, for example, a fluorinated refrigerant, such as e.g. R245fa is burned in the internal combustion engine, which produces toxic hydrofluoric acid. This would leak at the exhaust and could cause damage there.
  • a fluorinated refrigerant such as e.g. R245fa is burned in the internal combustion engine, which produces toxic hydrofluoric acid. This would leak at the exhaust and could cause damage there.
  • alcohol e.g.
  • Ethanol or methanol used it would be burned in a leakage of this in the internal combustion engine, which would be reflected in a sudden increase in power of the engine. In particular, inexperienced drivers would be exposed to an increased risk of accidents. Due to the barrier according to the invention in the manner of the leakage channel 10 or the leakage space 11, however, a mixing of the gas 6 with the working medium 2 can be reliably prevented in the event of virtually any failure of the fluid disk 9.
  • the strength of the material for the fluid disk 9 is less than the strength of the cover plates 7, 8 connected to the fluid disk 9, so that the Fluid disk 9 generally represents a kind of predetermined breaking point in the system of the disk package 12.
  • a predetermined breaking point can also be realized by a smaller wall thickness or material thickness of the fluid disk 9 with respect to the wall thickness or material thickness of the cover plates 7, 8.
  • evaporator heat exchanger 1 is shown in the normal operating state in which gas, in particular exhaust gas, flows in the second flow channel 5 and transfers heat to the working medium 2 in the first flow channel 4.
  • gas in particular exhaust gas
  • a rib structure 13 may be arranged in the second flow channel 5, ie between two disk packages 12.
  • a connection of the fluid disk 9 with the two cover plates 7, 8 and also a connection of the rib structure 13 with the respective cover plates 7, 8 takes place preferably cohesively, in particular via a solder joint 14.
  • Fig. 3 now a failure of the fluid disk 9 is shown, in which the mean fluid disk 9 is broken and thereby has led to a deformation or an upward bending of the larger-sized cover plate 7.
  • the deformation of the cover plate 7 in turn leads to a loosening of the solder joint 14, whereby the working medium 2 present in the first flow channel 4 can flow into the leakage channel 10.
  • a fluidic connection with the second flow channel 5 and thus with the gas 6 does not take place.
  • a case is shown in which the fluid disk 9 is also broken due to an overload and thereby has created a fluidic connection between the second flow channel 5 and the leakage channel 10.
  • the gas 6 passing from the second flow channel 5 can be removed via the leakage channel 10, without interfering with the working medium 2 in the first flow channel 4 to mix.
  • both shown cases of failure according to the 3 and 4 Thus, an undesired mixing of the working medium 2 with the gas 6 and the resulting difficulties can be reliably avoided.
  • the fluid disk 9 has a first opening 17, via which the leakage channel 10 or the leakage chamber 11 with a (leakage) outlet channel 18 (see. Fig. 1 ) are connected.
  • a plurality of oppositely disposed cover plates 7, 8 of two adjacent disk packs 12 additionally each have a second opening 19, wherein between two second openings 19, a leakage bush 20 for forming the outlet channel 18, in particular the leakage outlet channel 18, is arranged.
  • the first openings 17 are aligned with the second openings 19 and the leakage bushings 20 and thereby form the outlet channel 18th
  • the cover plates 7, 8 each have a third opening 21 for the passage of the working medium 2 through the first flow channel 4, wherein the third openings 21 between opposite cover plates 7, 8 of two adjacently arranged disc packets 12 respectively a fluid bushing 22 are connected to each other and the fluid bushings 22 have an at least partially circumferential, separated from the first flow channel 4 Fluidbuchsenringkanal 23 which is connected to the leakage channel 10 and / or the leakage chamber 11 of the fluid disk 9 of the disk package 12. This can also be done a backup against from the fluid sockets 22 undesirable emerging working medium 2 are created.
  • the third openings 21 together with the fluid bushes 22 arranged therebetween and the fluid supply 15 or fluid discharge 16 arranged in alignment therewith form a corresponding fluid supply channel 24 or fluid discharge channel 25 in the fluid disks 9.
  • Fig. 7 is a sectional view through the evaporator heat exchanger 1 according to the invention in the region of the Fluidzu Foodkanals 24 and the Fluidab technologicalkanals 25 shown.
  • the uppermost fluid bushing 22 is welded to the housing 3 via a welded joint 26 in a fluid-tight manner. Between each two adjacent fluid bushings 22, a disk pack 12 with two cover plates 7, 8 and interposed or soldered fluid disk 9 can be seen.
  • Fig. 8 a sectional view through the evaporator heat exchanger 1 according to the invention in the region of the outlet channel 18 is shown, wherein the uppermost leakage bushing 20 in turn welded fluid-tight manner with the housing 3 via a welded joint 26.
  • the individual disk packs 12, in turn consisting of the two cover plates 7, 8 and the fluid disk 9 arranged therebetween, are soldered in a fluid-tight manner both to one another and to the individual leakage bushings 20 via a respective solder joint 14.
  • the uppermost leakage bushing 20 is also referred to as a housing cover bushing 27.
  • a further outside the evaporator heat exchanger 1 further line 28 closes (see. Fig. 1 ) into the environment or the periphery.
  • a sensor 29 may be provided which is used to measure the pressure and / or the flow and / or a chemical composition of the fluid in the conduit 28, ie in particular in the leakage channel 10 and in the outlet channel 18th is trained.
  • control and / or regulating device 30 which is used to evaluate a signal detected by the sensor 29, in particular the pressure, the flow and / or chemical composition of the fluid, in particular the leakage fluid, in the line 28 and for the control / Control of the working medium conveying and not shown pump or a likewise not shown exhaust gas recirculation valve is formed in response to the detected signal.
  • the ambient air pressure of approximately 1 bar is applied to the sensor 29, provided that the evaporator heat exchanger 1 is switched off and has ambient temperature. This is according to the Fig. 9 shown by the curve A. If the evaporator heat exchanger 1 is put into operation, the pressure within the line 28 or within the leakage channels 10 increases due to the temperature-induced expansion of the air to about 1 to 1.5 bar, which according to the Fig. 9 is shown with the curve B. If the evaporator heat exchanger 1 is put into operation and the pressure does not rise, which also with the curve A in Fig. 9 is shown, either the sensor 29 is defective or the line 28 and the leakage channel 10 have a leak.
  • the pressure increases significantly when the working medium 2 enters the leakage channel 10, which according to the Fig. 9 is shown with the curve C, and slightly less, if the fluid disk 9 tears in the direction of the second flow channel 5 and thus a passage of gas 6 in the leakage channel 10 takes place, which according to the Fig. 9 is shown with the curve D.
  • the operation of the leakage channel 10 can be checked at each restart of the engine or the system, which also a high reliability can be guaranteed. Also, due to the curve can be closed directly on the failure mode.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (11)

  1. Echangeur de chaleur à évaporateur (1) servant à évaporer un milieu de travail (2) liquide, avec un boîtier (3), dans lequel un premier canal d'écoulement (4) servant à acheminer le milieu de travail (2) et un deuxième canal d'écoulement (5) servant à acheminer un gaz (6) sont disposés, dans lequel de la chaleur peut être transférée du gaz (6) au milieu de travail (2),
    dans lequel le premier canal d'écoulement (4) est formé par deux plaques de recouvrement (7, 8) et un disque de fluide (9) disposé entre ces dernières et profilé,
    cependant
    le disque de fluide (9) délimite, conjointement avec les deux plaques de recouvrement (7, 8), dans le même temps au moins un canal de fuite (10) et/ou un espace de fuite (11) séparé des deux canaux d'écoulement (4, 5).
  2. Echangeur de chaleur à évaporateur selon la revendication 1,
    caractérisé en ce
    que l'au moins un canal de fuite (10) et/ou l'au moins un espace de fuite (11) sont disposés latéralement à côté ou côté bord du premier canal d'écoulement (4).
  3. Echangeur de chaleur à évaporateur selon l'une quelconque des revendications précédentes,
    caractérisé en ce
    - que la résistance d'un matériau du disque de fluide (9) est inférieure à la résistance d'une plaque de recouvrement (7, 8) disposée au niveau du disque de fluide (9), et/ou
    - que le disque de fluide (9) présente une épaisseur de paroi ou une épaisseur de matériau inférieure à celle des plaques de recouvrement (7, 8) respectivement disposées au niveau du disque de fluide (9).
  4. Echangeur de chaleur à évaporateur selon l'une quelconque des revendications précédentes,
    caractérisé en ce
    que respectivement deux plaques de recouvrement (7, 8) forment avec un disque de fluide (9) disposé entre ces dernières une pile de disques (12), qui présente au moins un, de préférence deux, canaux de fuite (10) circulant au moins en partie dans la zone de bord.
  5. Echangeur de chaleur à évaporateur selon la revendication 4,
    caractérisé en ce
    - que l'échangeur de chaleur à évaporateur (1) présente plusieurs piles de disques (12) empilées les unes sur les autres avec respectivement un deuxième canal d'écoulement (5) disposé entre ces dernières,
    - que le canal de fuite (10) et/ou l'espace de fuite (11) d'un disque de fluide (9) présente une première ouverture (17),
    - que plusieurs plaques de recouvrement (7, 8) disposées les unes en regard des autres de deux piles de disques (12) adjacentes présentent respectivement une deuxième ouverture (19), dans lequel une douille de fuite (20) servant à réaliser un canal d'évacuation (18), en particulier un canal d'évacuation de fuite (18), est disposée entre les deuxièmes ouvertures (19).
  6. Echangeur de chaleur à évaporateur selon la revendication 5,
    caractérisé en ce
    que la première ouverture (17) est également reliée directement à la douille de fuite (20).
  7. Echangeur de chaleur à évaporateur selon l'une quelconque des revendications 4 à 6,
    caractérisé en ce
    que plusieurs plaques de recouvrement (7, 8) présentent respectivement une troisième ouverture (21) servant à acheminer le milieu de travail (2) à travers le premier canal d'écoulement (4), dans lequel les troisièmes ouvertures (21) sont reliées entre elles respectivement par une douille de fluide (22) entre des plaques de recouvrement (7, 8) se faisant face de deux piles de disques (12) disposées de manière adjacente l'une par rapport à l'autre et la douille de fluide (22) présente un canal annulaire de douille de fluide (23) circulant au moins en partie, séparé du premier canal d'écoulement (4), lequel est relié au canal de fuite (10) et/ou à l'espace de fuite (11) du disque de fluide (9) de la pile de disques (12).
  8. Echangeur de chaleur à évaporateur selon la revendication 6 ou 7,
    caractérisé en ce
    que le boîtier (3) présente une ouverture de boîtier, qui est reliée, par l'intermédiaire d'une douille de fuite de boîtier (20, 27), à la première et/ou à la deuxième ouverture (17, 19) dans la plaque de recouvrement (7, 8) d'une pile de disques (12) disposée de manière adjacente au boîtier (3).
  9. Echangeur de chaleur à évaporateur selon la revendication 8,
    caractérisé en ce
    que la douille de fuite de boîtier (27) et toutes les autres douilles de fuite (20) forment le canal de sortie (18) servant à acheminer le fluide, dans lequel un conduit (28) peut être installé dans les environs ou en périphérie au niveau de la douille de fuite de boîtier (27), lequel présente un capteur (29), qui est réalisé pour mesurer la pression et/ou le débit et/ou une composition chimique du fluide dans le conduit (28).
  10. Echangeur de chaleur à évaporateur selon l'une quelconque des revendications 4 à 9,
    caractérisé en ce
    - qu'une structure nervurée (13) est disposée dans le deuxième canal d'écoulement (5) entre respectivement deux piles de disques (12), et/ou
    - que le disque de fluide (9) est brasé et/ou soudé entre deux plaques de recouvrement (7, 8).
  11. Echangeur de chaleur à évaporateur selon la revendication 9 ou 10,
    caractérisé en ce
    qu'un dispositif de commande et/ou de régulation (30) est prévu, lequel est réalisé pour analyser un signal détecté par le capteur (29), en particulier la pression, le débit et/ou la composition chimique du fluide dans le conduit (28) et pour commander/réguler une pompe refoulant le milieu de travail (2) et/ou une soupape de retour de gaz d'échappement en fonction du signal détecté.
EP13745400.5A 2013-08-02 2013-08-02 Échangeur de chaleur à évaporateur Not-in-force EP3027998B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2013/066248 WO2015014406A1 (fr) 2013-08-02 2013-08-02 Échangeur de chaleur à évaporateur

Publications (2)

Publication Number Publication Date
EP3027998A1 EP3027998A1 (fr) 2016-06-08
EP3027998B1 true EP3027998B1 (fr) 2017-03-22

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP13745400.5A Not-in-force EP3027998B1 (fr) 2013-08-02 2013-08-02 Échangeur de chaleur à évaporateur

Country Status (4)

Country Link
US (1) US20160178260A1 (fr)
EP (1) EP3027998B1 (fr)
JP (1) JP6313855B2 (fr)
WO (1) WO2015014406A1 (fr)

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CN115930640A (zh) * 2022-11-30 2023-04-07 中国原子能科学研究院 换热器和反应堆的换热系统
EP4477982A1 (fr) * 2023-06-13 2024-12-18 Hanon Systems Echangeur de chaleur à plaques
EP4498028A1 (fr) * 2023-07-24 2025-01-29 Alfa Laval Corporate AB Échangeur de chaleur à plaques brasées avec un système de détection de congélation

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JP2016528465A (ja) 2016-09-15
EP3027998A1 (fr) 2016-06-08
US20160178260A1 (en) 2016-06-23
WO2015014406A1 (fr) 2015-02-05
JP6313855B2 (ja) 2018-04-18

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