EP3635320A1 - Dispositif de récupération de chaleur d'un fluide chauffant - Google Patents

Dispositif de récupération de chaleur d'un fluide chauffant

Info

Publication number
EP3635320A1
EP3635320A1 EP18728066.4A EP18728066A EP3635320A1 EP 3635320 A1 EP3635320 A1 EP 3635320A1 EP 18728066 A EP18728066 A EP 18728066A EP 3635320 A1 EP3635320 A1 EP 3635320A1
Authority
EP
European Patent Office
Prior art keywords
fluid
tube
channel
flow channel
heat exchanger
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.)
Granted
Application number
EP18728066.4A
Other languages
German (de)
English (en)
Other versions
EP3635320B1 (fr
Inventor
Jens Gockel
Hilmar LÄMMER
Christian Urban
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.)
Volkswagen AG
Original Assignee
Volkswagen AG
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 Volkswagen AG filed Critical Volkswagen AG
Publication of EP3635320A1 publication Critical patent/EP3635320A1/fr
Application granted granted Critical
Publication of EP3635320B1 publication Critical patent/EP3635320B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • F02M26/32—Liquid-cooled heat exchangers
    • 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
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/25—Layout, e.g. schematics with coolers having bypasses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/06—Derivation channels, e.g. bypass

Definitions

  • the invention relates to a device for heat recovery from a heating fluid, which flows through a Schufid Force in operation of a Schufidermaschineers having a
  • Main flow channel in this case the main flow channel and the secondary flow channel each have at least one inlet and at least one downstream of the inlet formed outlet to the flow by means of the heating fluid, in the
  • a challenge of modern motor vehicle construction consists in the noble goal of constantly minimizing the fuel consumption and, associated therewith, the pollutant emissions of an internal combustion engine present in the motor vehicle.
  • One way to use the waste heat is to recover the existing thermal energy in the exhaust.
  • the steam generator in this case has a housing with an inlet and an outlet region, wherein within and coaxial with the housing extending from the inlet to the outlet region, tubular
  • This feedthrough line is also slotted at its lying in the inlet and outlet end portions, so that in the
  • Passage line arranged a spiral tube, which is flowed through by a fluid to be evaporated. That in one embodiment for increasing the heat transfer Disc-like ribs having spiral tube serves as a heat transfer block, via which the existing thermal energy in the exhaust gas is transferred to the fluid to be evaporated.
  • a control valve is arranged within the steam generator, in the exact inside of the feedthrough line, by means of which, depending on the position of the control flap, the feedthrough line is present in a closed or opened state.
  • the control flap is arranged in the inlet region, wherein the exhaust gas passes through the slotted end region of the feedthrough line in the intermediate space between the feedthrough line and the housing and flows over the spiral tube when the feedthrough line is closed.
  • Block flap moving flap shaft must have a high length in order to reach into the interior of the feedthrough line. This requires low manufacturing tolerances of the valve shafts and their storage, which leads in conjunction with the temperatures reached in the exhaust system to delay and malfunction of the blocking flap.
  • DE 10 201 1 056 212 A1 comparably designed arrangements for the recovery of heat energy from an exhaust gas for heating transmission oil, in which the control valve within the feedthrough line, but is arranged in the outlet, and the feedthrough line also in the
  • Outlet area has openings for the transition of the exhaust gas in the intermediate region between feedthrough line and housing wall. According to DE 10 2012 204 126 A1, the feedthrough line is also closed by means of the control flap.
  • DE 10 2012 105 588 A1 a substantially the function of DE 10 201 1 056 212 A1 corresponding arrangement for the recovery of heat energy known, which also serves to heat transmission oil. This is in contrast to those disclosed by DE 10 2012 204 126 A1 and DE 10 201 1 056 212 A1
  • the arrangement shows separate, but adjacent and coaxial with each other, extending annular chambers for receiving coolant and gear oil, wherein within the coolant chambers several mat-like and longitudinally of the array rectilinear tube bundles are arranged, which are traversed by exhaust gas over Openings in the feedthrough line in a front-side intermediate area between
  • Feedthrough line and housing is passed.
  • the tube bundles have a plurality of individual tubes, which are substantially both parallel to each other and parallel to the
  • the invention has the object, a device of the type mentioned in such a way that compared to the prior art simplifies the design, allows coarse manufacturing tolerances and thereby
  • a device for heat recovery from a heating fluid wherein the heating fluid flows through a Schufid Dimension during operation of a Schufluidermaschineers.
  • the device has a channel closure element and a
  • Heat exchanger assembly wherein the heat exchanger assembly also has a surrounded by a bypass duct main flow channel.
  • main flow channel and the secondary flow channel each have at least one inlet and at least one outlet formed downstream of the inlet
  • Heat exchanger arrangement arranged.
  • the device for heat recovery is thus arranged in the Schufluid Consumer, wherein upstream of the device, at least the inlet of the
  • Main flow channel fluidly connected to a first portion of the Schufluid Consumeres and further the device downstream of the closure device in turn may open in a second portion of the Schufluid Consumeres.
  • the heating fluid is discharged downstream of the closure device in a post-treatment plant or the environment.
  • the length of the main flow channel would be limited downstream by the channel closure element in its longitudinal extent, wherein downstream of the channel closure element in turn would join the Schufluid Consumer.
  • the main flow channel and the Schufluid Consumer are made in one piece and thus the main flow channel a portion of the
  • the heat exchanger arrangement of the device taken alone has no
  • the heat exchanger assembly of the device should also preferably work in countercurrent principle, d. H. the flow direction of heating fluid and working fluid are opposite to each other.
  • d. H the flow direction of heating fluid and working fluid are opposite to each other.
  • DC principle it is also conceivable an embodiment in the DC principle.
  • the closure element should have at least two states, the
  • Closure element preferably also should be able to take between these two states further continuously or discretely changeable intermediate states.
  • One of the at least two states could be described here by a maximum opening rate, ie a counterpressure in the main flow channel caused by the closure element Heat exchanger arrangement is minimal, the heating fluid is thus prevented only in a minimal way at the flow through the main flow channel.
  • no or substantially a minimum volumetric flow rate of the heating fluid would flow through the secondary flow passage, whereby the main flow passage acts as a bypass of the bypass passage.
  • a second of the at least two states could be
  • Counterpressure in the main flow channel would be maximum.
  • the heating fluid would thus be hindered in the maximum of the flow through the main flow channel, whereby no or a minimum volume flow rate of the heating fluid would flow through the main flow channel and a maximum volume flow rate of the bypass flow channel.
  • the necessary actuation of the closure element would be realized, for example via an electric or pneumatic actuator.
  • the described opening rate is determined here from the ratio of the permeable cross-sectional area of the main flow channel to the total cross-sectional area of the
  • Heating fluid existing thermal energy or heat transferred via the heat transfer element in the working fluid should at least be heated, but preferably evaporated.
  • the working fluid should also be part of a subsequent cycle in which it could serve in a gaseous state, for example, the drive of a generator.
  • the closure element can be designed as a flap, in particular as an exhaust flap, wherein the angular position of the flap or the exhaust flap should determine its opening rate.
  • the flap or exhaust flap in a first state of maximum opening rate, could be aligned at a rotation angle of 0 degrees or 180 degrees to the flow direction of the heating fluid or corresponding to the longitudinal direction of the main flow channel.
  • a second state ie in the state of minimum opening rate, would be a
  • the heating fluid may in particular be designed as an exhaust gas, which flows through the exhaust gas tract, in particular the exhaust gas tract of an internal combustion engine, wherein the
  • the Schwarzetrig would therefore the exhaust tract, in particular the exhaust gas tract of the internal combustion engine, such as. B. an internal combustion engine of a motor vehicle, correspond.
  • the working fluid should be formed as a fluid, which passes through the transferred from the heating fluid through the heat transfer element heat from the liquid to the gaseous phase, so it can be evaporated.
  • the secondary flow channel of the heat exchanger arrangement is connected fluid-permeable exclusively via the inlet of the secondary flow channel to the main flow channel of the heat exchanger arrangement.
  • Heat exchanger arrangement is simplified and this thus a reduced
  • the fluid-permeable compound in this context means a permeable compound, which is permeable at least for fluids and gases. However, permeability to solids is not excluded. It is also to be taken for granted that energy can also be transmitted via this fluid-permeable connection.
  • An embodiment of the invention can also be regarded as advantageous if the secondary flow channel is connected in a fluid-permeable manner via the outlet of the secondary flow channel to a closure bypass channel having an inlet and an outlet.
  • the heating fluid does not accumulate in the secondary flow channel, which positively prevents a possible overheating of the heat transfer element and / or the working fluid flowing in the heat transfer element.
  • the closure bypass channel is fluid-permeably connected to the heating fluid tract via the outlet of the closure bypass channel downstream of the channel closure element, then it is possible for the heating fluid which has flowed out of the secondary flow channel into the closure bypass channel to be returned to the heating fluid tract, whereby no counterpressure in the closure bypass channel and / or in the
  • the main flow channel is formed by a fluid tube enclosed by a housing, wherein the housing encloses the fluid tube orthogonal to the longitudinal direction of the fluid tube.
  • the housing encloses the fluid tube orthogonal to the longitudinal direction of the fluid tube.
  • the fluid tube may be pronounced in the simplest case as a cylinder tube.
  • the fluid tube should not be completely, but only orthogonal to and enclosed in the longitudinal direction of the fluid tube of the housing, so that the inlet and the outlet of the skin flow channel forming end faces of the fluid tube are not enclosed by the housing.
  • Such a configuration offers in promising manner, a little error-prone basic structure of the heat exchanger assembly.
  • the inlet of the secondary flow channel is formed by at least one opening formed in the wall of the fluid pipe, said opening should be in a region of the fluid pipe, which is enclosed by the housing and thereby the Main flow channel fluidly connected to the bypass channel.
  • the opening can assume any shape, for example a circular, oval or even elliptical shape. It is also conceivable that the opening is in the form of a slot. In addition to a single opening, however, an embodiment with a plurality of openings is preferred, wherein these may be arranged spaced apart in the circumferential direction of the fluid pipe.
  • the heat exchanger assembly is located.
  • at least the two end regions of the housing should be fluid-impermeably connected to the fluid tube, wherein the connection can be made cohesively and also non-positively and / or positively.
  • the length of the bypass duct would be determined by this configuration on the longitudinal extent of the housing, in particular by the spacing of the end portions of the housing.
  • the closure bypass channel is designed as at least one overflow pipe, which is arranged downstream of the heat exchanger arrangement on the housing of the heat exchanger assembly and the Schufluid Consumer and thereby connects the bypass channel on the outlet side, bypassing the channel closure element with the Schufluid Consumer, so that the heating fluid can flow from the bypass duct in the Schufluid Consumer.
  • the overflow pipe should be arranged so that a first end face of the overflow pipe upstream of the housing of the heat exchanger assembly and a second end face of the overflow pipe downstream is fluidly connected to the Schufluid Consumer.
  • the overflow pipe could also be partially parallel to the main flow channel and / or KniWeid Consumer run.
  • the lock bypass channel in the form of an outside of the
  • Main flow channel and / or the Schuffluid Force arranged overflow advantageously offers a structurally and manufacturing technology easier to implement structure as, for example, a within the main flow channel and / or Bankfluid Thermales, z. B. in the form of a tube-in-tube design, arranged overflow pipe.
  • the heat exchanger element is designed as a spiral tube through which the working fluid flows and / or ribs are formed on an outer lateral surface of the spiral tube and in the longitudinal direction of the tube at least partially against the central axis of the tube is arranged.
  • Heat transfer element as a coiled tubing offers against a possible
  • Embodiment with several straight and substantially parallel to each other and parallel to the main and secondary flow channel extending individual tubes the advantage that adjusts no unequal distribution of the flow rate of the heating fluid.
  • An embodiment of the Rohheirl to the effect that ribs are formed on the outer circumferential surface increases the heat flow from the heating fluid into the working fluid, whereby the efficiency of heat transfer can be increased.
  • the ribs it is conceivable for the ribs to be formed by applying to the tube, which carries the ribs at least in sections, an endless band spirally wound in the longitudinal direction of the tube, which is the section length
  • connection between the endless belt forming the ribs and the pipe can be formed cohesively, wherein the production of the material bond can be carried out using a welding process, in particular a laser welding process.
  • Such a described tube may in one embodiment, for example, a
  • Outside diameter of eight millimeters with a wall thickness of 0.75 millimeters and the rib-forming endless belt has a width of five millimeters and a thickness of 0.5 millimeters.
  • Another advantageous embodiment of the device can be designed in that between the fluid tube and the tube coil and / or between the tube coil and the housing a the fluid tube and / or the tube spiral orthogonal to the longitudinal direction of the
  • Fluid pipe surrounding, deformable intermediate insert is arranged, with which the fluid tube and the tube coil and / or the coiled tubing and the housing are in contact.
  • the intermediate insert in this case is elastically and / or plastically deformable and is present for example as a woven, knitted and / or knitted fabric.
  • Conceivable are felt mats and / or fiber mats, such.
  • glass fiber mats and in particular silicate glass fiber mats can also be generally planar and flat in general, with such a trained
  • the intermediate insert could also be in the form of a hollow cylinder, quasi in the form of a flexible tube or a cuff, so that it can be pushed onto the fluid tube and / or interposed between the tube coil and the housing.
  • the intermediate insert can also be present as a solid material.
  • the intermediate insert may be formed as an insulating element and / or a sealing element, whereby on the one hand, the heat flow into the environment and optionally in the main flow channel, ie, for. As the fluid pipe can be minimized. For this it is considered advantageous if the
  • Rib interstices formed helical rib channel along the ribs
  • the intermediate element serves to compensate for tolerances between fluid pipe and coiled tubing and / or coiled tubing and housing.
  • Fig. 1 is a perspective view of the device
  • Fig. 2 is a first sectional view of the device
  • Fig. 3 is a second sectional view of the device
  • Fig. 4 is an illustration of a tube formed with ribs.
  • FIG. 1 shows a perspective view of a development of the invention
  • Device 1 for heat recovery from a heating fluid. This heating fluid flows through the Schufid Consumer 2 during operation of a Schufluidermaschineers.
  • the device 1 has the
  • the heat transfer element 1 1 is in this case formed as a tube coil 22 from the spirally extending tube 23. The volume flow of the heating fluid through the
  • Main flow channel 6 and / or the secondary flow channel 5 is arranged as a function of the opening rate of the downstream of the heat exchanger arrangement 4 Channel closure element 3 adjustable. Moreover, the secondary flow channel 5 is exclusively via the inlet 7 of the secondary flow channel 5 with the main flow channel 6
  • Heat exchanger element 1 1 heated in the working fluid.
  • the heating fluid after passing through the secondary flow passage 5, flows back into the bypass passage 14
  • Figure 2 also shows a development of the device 1, wherein this is shown in section.
  • the device 1 again shows the channel closure element 3 and the
  • Heat exchanger assembly 4 The heat exchanger assembly 4 has the from
  • Main flow channel 6, the inlet 9 and the outlet 10 and the secondary flow channel 5, the inlets 7 and 8 have the outlet.
  • the main flow channel 6 is formed by the fluid pipe 16 enclosed by the housing 15, the housing 15 enclosing the fluid pipe 16 orthogonal to the longitudinal direction 17 of the fluid pipe 16.
  • the secondary flow channel 5 exclusively via the inlets 7 of the
  • Heat transfer element 1 1 arranged.
  • the heat transfer element 1 1 is formed as a tube coil 22 which extends spirally around the fluid tube 16.
  • the coiled tubing 22 orthogonal to the longitudinal direction 25 of the fluid tube 16 enclosing, deformable intermediate insert 27 is arranged, with which also the coiled tubing 22 and the housing 15 are in contact.
  • the channel closure element 3 is arranged downstream of the outlets 10, 8 of the main flow channel 6 and the secondary flow channel 5, which is formed in this development as a flap and thereby determines the angular position of the valve closure element 3 designed as a flap whose opening rate.
  • FIG. 2 also shows that the secondary flow channel 5 via its outlet 8 to the inlet 12 of the closure bypass channel 14 and the closure bypass channel 14 again via its outlet 13 downstream of the channel closure element 3 with the Schufluid Thermal second
  • the closure bypass channel 14 is formed as shown as the overflow pipe 21. This overflow pipe 21 is also downstream of the
  • Heat exchanger assembly 4 and its second end face downstream is fluidly connected to the Walkerfluid Consumer 2.
  • the overflow pipe 21 extends in a section parallel to the main flow channel 6 and the Schufluid Thermal Second
  • the device 1 is shown in contrast to Figure 2 with the valve closure element 3 designed as a flap in its first state with correspondingly maximum opening rate.
  • the flow of the heating fluid through the main flow channel 6 is thus maximum.
  • FIG. 4 describes a development of the basically spiral-shaped tube 23, which forms the tube helix 22 shown in FIGS. 1 to 3.
  • the ribs 26 are formed by applying to the tube 23 a cut-to-length, endlessly spiraling spiral around the tube 23 in the longitudinal direction 25 of the tube 23.
  • Heat exchanger arrangement 24 lateral surface

Landscapes

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

Abstract

L'invention concerne un dispositif (1) de récupération de chaleur d'un fluide chauffant, lequel traverse un conduit (2) de fluide chauffant lors du fonctionnement d'un générateur de fluide chauffant, comportant un élément de fermeture (3) de canal ainsi qu'un agencement échangeur de chaleur (4), l'agencement échangeur de chaleur (4) comportant un canal d'écoulement principal (6) entouré d'un canal d'écoulement auxiliaire (5), le canal d'écoulement principal (6) et le canal d'écoulement auxiliaire (5) comportant ici chacun au moins une entrée (7, 9) ainsi qu'au moins une sortie (8, 10) réalisée en aval de l'entrée (7, 9) pour l'écoulement au moyen du fluide chauffant, au moins un élément (11) échangeur de chaleur pouvant être traversé par un fluide de travail lors du fonctionnement du dispositif (1) étant agencé dans le canal d'écoulement auxiliaire (5) et un courant en volume du fluide chauffant à travers le canal d'écoulement principal (6) et/ou le canal d'écoulement secondaire (5) pouvant être réglé en fonction d'un taux d'ouverture de l'élément de fermeture (3) de canal. L'élément de fermeture (3) de canal est en outre agencé en aval des sorties (8, 10) du canal d'écoulement principal (6) et du canal d'écoulement auxiliaire (5) de l'agencement échangeur de chaleur (4).
EP18728066.4A 2017-06-08 2018-05-22 Dispositif de récupération de chaleur d'un fluide chauffant Active EP3635320B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017209725.6A DE102017209725A1 (de) 2017-06-08 2017-06-08 Vorrichtung zur Wärmerückgewinnung aus einem Heizfluid
PCT/EP2018/063265 WO2018224295A1 (fr) 2017-06-08 2018-05-22 Dispositif de récupération de chaleur d'un fluide chauffant

Publications (2)

Publication Number Publication Date
EP3635320A1 true EP3635320A1 (fr) 2020-04-15
EP3635320B1 EP3635320B1 (fr) 2021-07-07

Family

ID=62455444

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18728066.4A Active EP3635320B1 (fr) 2017-06-08 2018-05-22 Dispositif de récupération de chaleur d'un fluide chauffant

Country Status (4)

Country Link
EP (1) EP3635320B1 (fr)
DE (1) DE102017209725A1 (fr)
RU (1) RU2727499C1 (fr)
WO (1) WO2018224295A1 (fr)

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RU196876U1 (ru) * 2020-01-31 2020-03-18 Тамара Ивановна Носова Устройство для подогрева жидкостей двигателя внутреннего сгорания
CN112595146B (zh) * 2020-12-29 2023-09-12 乔治洛德方法研究和开发液化空气有限公司 管道壳体由换热设备构成的高温流体运输管道、适用的换热设备以及换热方法
CN112577338B (zh) 2020-12-30 2023-07-25 乔治洛德方法研究和开发液化空气有限公司 内部安置有换热设备的高温流体运输管道，适用的换热设备及换热方法

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KR101317373B1 (ko) 2011-12-09 2013-10-10 현대자동차주식회사 열교환기
DE102012204126A1 (de) 2012-03-15 2013-09-19 Eberspächer Exhaust Technology GmbH & Co. KG Dampferzeuger für einen Rankine-Prozess
RU132877U1 (ru) * 2013-03-26 2013-09-27 Общество с ограниченной ответственностью "Краснодарский Компрессорный Завод" Вертикальный межступенчатый газоохладитель
DE102014106386B4 (de) * 2014-05-07 2016-08-11 Benteler Automobiltechnik Gmbh Abgaswärmetauscher mit Bypassrohr

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WO2018224295A1 (fr) 2018-12-13
DE102017209725A1 (de) 2018-12-13
EP3635320B1 (fr) 2021-07-07

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