WO2024052110A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2024052110A1
WO2024052110A1 PCT/EP2023/072970 EP2023072970W WO2024052110A1 WO 2024052110 A1 WO2024052110 A1 WO 2024052110A1 EP 2023072970 W EP2023072970 W EP 2023072970W WO 2024052110 A1 WO2024052110 A1 WO 2024052110A1
Authority
WO
WIPO (PCT)
Prior art keywords
channels
channel group
heat exchanger
films
pressure
Prior art date
Application number
PCT/EP2023/072970
Other languages
German (de)
English (en)
Inventor
Steffen Grohmann
Malte Dirks
Friederike Boehm
Thomas Gietzelt
Georg RABSCH
Jonas ARNSBERG
Original Assignee
Karlsruher Institut für Technologie
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 Karlsruher Institut für Technologie filed Critical Karlsruher Institut für Technologie
Publication of WO2024052110A1 publication Critical patent/WO2024052110A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0037—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/048—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of ribs integral with the element or local variations in thickness of the element, e.g. grooves, microchannels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/06—Fastening; Joining by welding
    • F28F2275/061—Fastening; Joining by welding by diffusion bonding

Definitions

  • the invention relates to a heat exchanger, preferably a micro heat exchanger, with a first high-pressure channel group and a second low-pressure channel group, each with a large number of channels in a film stack according to the first patent claim.
  • the heat exchanger is preferably a co-current, counter-current or cross-current micro heat exchanger.
  • Heat exchangers of the type mentioned at the beginning are generally known in technology. They have a heat transfer area in which a fluid flow in one channel group is tempered by a fluid flow in another channel group.
  • Each of the channel groups has a large number of channels which are preferably connected in parallel over their entire length and preferably also run in parallel.
  • the channels in each channel group are preferably arranged parallel to one another and preferably in a straight line on one plane.
  • the two channel groups are arranged alternately in levels with or without intermediate layers without channels, i.e. H .
  • the fluid flow is cooled or heated by heat transfer to the overlapping areas of the two channel groups, which thus form the heat transfer areas.
  • the entirety of the channels of a channel group preferably forms a passage through the heat exchanger.
  • DE 37 09 278 C2 discloses examples of micro heat exchangers and their production, in which the microchannels are incorporated into metal foils on one side as a large number of parallel grooves. The films are then placed on top of each other and connected to one another by gluing, soldering or welding, with the film sides structured with grooves each resting against one of the neighboring films.
  • One embodiment provides for the grooves to be covered by an unstructured film side.
  • Alternative embodiments provide microchannels whose cross sections extend from grooves into two adjacent films, with the outer film surfaces of these two films remaining unstructured.
  • heat exchangers with a parallel alignment of all microchannels, i.e. H .
  • microstructured heat exchanger which consists of a stack of diffusion-welded foils structured on one side.
  • microchannels are incorporated into each of the films and have an approximately semicircular shape. By stacking two mirror-inverted foils face-to-face, almost round flow cross-sections can be achieved.
  • a further embodiment provides for a monodirectional stacking sequence, whereby the semicircular channel cross sections incorporated into the films are each open in one direction and are covered by a smooth, unstructured surface of the adjacent film.
  • one object of the invention is to propose a heat exchanger which is particularly suitable for improved heat transfer of different volume flows and pressures in the channel groups.
  • a heat exchanger with the features of claim 1.
  • Subclaims reflect advantageous embodiments.
  • a heat exchanger with two channel groups, a first high-pressure channel group and a second low-pressure channel group, each with a large number of channels between an inlet and an outlet area is proposed. Consequently, the channels form a fluidly continuous connection between the inlet and outlet areas, each of which is only connected to one of the two channel groups.
  • the channels in each channel group are arranged in their own levels.
  • the channel groups are separated from each other on the fluid side and are each placed in their own foils.
  • the foils are assembled into a stack of foils.
  • low-pressure and high-pressure channel groups each describe a first and a second channel group, which are fluidically separated from one another, including the associated inlet and outlet areas.
  • the low-pressure channel group is only designed for a lower pressure than the high-pressure channel group, basically independent of the absolute pressure.
  • An inlet area is a volume fluidically upstream of a channel group or part of a channel group. It serves as a distribution structure for a fluid from a fluid source (inlet) opening into the volume into the aforementioned channel group or part of the channel group.
  • an outlet area of a channel group or part of a channel group is a fluidically downstream volume into which the channels open and are forwarded into a fluid sink (outlet).
  • each channel group preferably one inlet and outlet area at a time. It is essential that the channels of the first channel group, the high-pressure channel group, are incorporated level by level as grooves in at least one first film of a first pair of films with two first films lying flat on top of each other, the grooves starting from a contact surface of the two first films on top of each other extend into the at least one, preferably both first films, but do not penetrate the first two films.
  • each of the grooves has a semicircular cross section in both first foils, so that when they are placed together, the grooves combine to form a channel with a round flow cross section.
  • Such a design has a relatively high proportion of film material around the channels, which in turn advantageously ensures high dimensional stability of the film pair even at increased pressures.
  • the channels of the second low-pressure channel group are formed at each level by openings with webs arranged between them, each incorporated into one, preferably only one, second film at each level.
  • the channels penetrate the films to their full thickness and form slots in the films that are initially open on both sides, which are covered on both sides when the film stack is joined by a first film of a first pair of films or a closing film.
  • These perforated films thus represent a frame around the slots, with the individual channels being formed by the slots and being separated from one another in one plane by webs.
  • Such a design is characterized by a lower proportion of film material around the channels than in the high-pressure channel group out of .
  • the second group of channels preferably has a flow cross section which exceeds the cross section of the webs between the channels by at least two times, more preferably at least five times or ten times.
  • the film stack comprises an alternating stacking of second films and a first pair of films, with the top and/or bottom layer of the film stack being formed by a final film or a first pair of films.
  • the top and/or bottom layer of the film stack being formed by a final film or a first pair of films.
  • a preferred embodiment of the first high-pressure channel group provides for its level-by-level incorporation through grooves in both first foils of the first foil pair, the grooves extending from the contact surface of the first two foils to one another in a mirror image into both first foils and more preferably round channel cross-sections with the aforementioned form advantages.
  • each of the first and second levels has a large number of channels arranged next to one another, continuous and separated from one another on the fluid side, advantageous for high penetrability of the heat exchanger volume with the two channel groups. This applies in particular or alternatively if the channels for each channel group are optionally arranged and connected in parallel.
  • the channels per channel group each preferably have a uniform length and/or over their entire channel length a constant flow cross section, which means that the same flow and heat transfer can be achieved in all channels of a channel group.
  • the proposed heat exchanger is basically both a cocurrent or countercurrent heat exchanger, in which all channels of both channel groups are arranged at least in sections parallel to one another to form a cocurrent or countercurrent heat exchanger, and as a crossflow heat exchanger, in which the channels of the first high-pressure channel group and which of the second low-pressure channel group are arranged at least in sections, preferably completely, each at an angle to one another, thus crossing each other to form a cross-flow heat exchanger, can be designed and implemented.
  • the inlet and outlet areas are each preferably arranged in levels at the end of the channels in the respective level.
  • the channels of a level are preferably connected only to one and the same inlet area and one and the same outlet area. For this purpose, they are preferably also arranged in this level and more preferably fluidly connected to the inlet and outlet areas of the same channel group on other levels via the respective inlet area and the respective outlet area via a connecting line.
  • the inlet and outlet areas of the first and second channel groups be formed by depressions or grooves in at least one first film of the respective first pair of films or. through openings, grooves or depressions in the respective second foils.
  • all levels, i.e. H All foils with channels between one inlet and one outlet area per channel group, identical dimensions and materials. They are preferably identical in channel groups; They therefore lead to identical flow conditions in the planes in groups of channels.
  • the inlet and outlet areas of the first and second channel groups are preferably each connected to one another separately on the fluid side in such a way that they each form a common inlet and a common outlet for the high-pressure channel group and the low-pressure channel group of the heat exchanger.
  • the proposed heat exchanger is preferably a micro heat exchanger, which is characterized in the context of the invention in that the channels of both channel groups are designed as microchannels of two microchannel groups as grooves or foil openings with the narrowest flow cross sections between 0.001 mm 2 or 0.01 mm 2 and 10 mm 2 or 1 mm 2 are preferably incorporated into metal foils and these metal foils are joined together to form a foil stack, preferably by means of diffusion welding.
  • the films themselves have a preferred thickness between 0.25 and 5 mm, more preferably between 0.5 and 1.5 mm.
  • the foils are preferably metal foils, preferably made of stainless steel or copper. It is important that the materials used are chemically inert to the heat transfer fluid flowing through the channels. A large number of substances come into consideration as fluids, which are preferably present in the liquid or gaseous form or in the two-phase state (liquid/gaseous form).
  • the fluids can be pure substances or mixtures of substances.
  • the invention therefore solves the problem by means of different flow cross sections of high-pressure and low-pressure channel groups to optimize pressure losses and heat transfer in preferably microstructured heat exchangers, in particular by incorporating the low-pressure channel groups into perforated foils (so-called low-pressure frames, second foils) and on one side , preferably directly adjacent to the adjacent (first) foils of the high-pressure channel group on both sides.
  • perforated foils so-called low-pressure frames, second foils
  • the development of the second foils with the low-pressure channel groups can e.g. B. by punching out sheet metal, laser cutting or milling.
  • the low-pressure flow paths closed by the adjacent foils are always only achieved by combining low-pressure frames with two foils stacked face-to-face (two first foils or a first foil and a final foil), which face outwards Low-pressure frames have smooth joining surfaces for diffusion welding and which form the high-pressure flow paths from the etched channels inside.
  • the low-pressure flow cross section can be adjusted for a given channel width and number and thus the low-pressure side pressure loss can be minimized and the overall energy efficiency of the foil-frame heat exchanger can be maximized.
  • the thickness of the second foils and thus the frame height is preferably less than or equal to 5 mm and/or less than or equal to a factor of 2-3 of the thickness (i.e. two to three times the thickness) of the first pair of foils for the high-pressure channels , more preferably less than or equal to a factor of 5-10 of the thickness of the first pair of foils for the high-pressure channels.
  • the minimum frame height is preferably equal to the thickness of the first pair of foils.
  • the preferably parallel channels in the low-pressure frame are separated from each other by webs, the width and distance of which are determined in particular by manufacturing requirements such as. B. be determined by the preferred diffusion welding. Since the webs are connected to the adjacent rear walls of the first high-pressure films, for example. B.
  • the proposed heat exchangers with low-pressure frames have a fundamentally improved heat transfer behavior and at the same time an additional degree of freedom, which allows for significantly different pressure losses of the flow paths and thus allows the overall energetic optimization of the microstructured heat exchanger with the highest possible power density.
  • foil frame heat exchangers have a basically monolithic design via the foil stack, i.e. H .
  • the first and second foils and thus the entire heat exchanger preferably consist of only a single material. This avoids thermal stresses caused by different thermal expansion coefficients, which is particularly advantageous in low-temperature applications with large temperature gradients.
  • the proposed heat exchangers are particularly suitable for process engineering applications with compressible media where pressure losses have a significant influence on process efficiency. This is particularly the case in the area of low absolute pressures. Processes in refrigeration and cryogenics in particular offer a large area of application.
  • Heat exchangers have a significant influence on the energy efficiency of process engineering applications.
  • the energy efficiency of heat exchangers is mostly determined by the temperature differences of the heat transfer.
  • pressure loss also plays an important role.
  • heat transfer can be improved by increasing the flow velocities; as a result of the increasing pressure losses
  • the flow cross section of the second low-pressure channel group can be adapted to the requirements of the application in such a way that, with improved heat transport, pressure losses in the flow passages can be achieved at the same time, which can differ by one to two orders of magnitude .
  • FIG. la to c schematic cross-sectional views of conventional co-current and/or countercurrent heat exchangers with two channel fractions as a foil stack (prior art),
  • FIG. 2a and b schematic sectional views of co-current and/or countercurrent heat exchangers with two modified channel fractions
  • FIG. 3a to d several detailed views of a second film (low-pressure frame) with a number of parallel channels with inlets and outlets,
  • FIG. 4a to c various exemplary embodiments of a countercurrent heat exchanger for uses preferably in refrigeration and cryogenics as well
  • Fig. 5 is a schematic exploded drawing of the one shown in FIG. 4a shown exemplary embodiment.
  • Fig. la shows an embodiment in which each channel 3 in two adjacent foils 2 of a foil pair (plane) is formed by two opposite grooves 2 with semicircular cross sections.
  • the semicircular cross sections are composed of round channel cross sections.
  • the foils of a foil pair are preferably made of a metal, preferably stainless steel or copper or another material with high thermal conductivity and low tendency to corrosion compared to a heat transfer medium to be conducted through the channels. At least the two foils of each foil pair are diffusion welded or brazed together (material connection), which, in conjunction with a round channel cross section, is particularly suitable for the passage of media with high pressures.
  • Fig. lb and c represent alternative exemplary embodiments in which each channel 3 is formed only by a groove 2 in a film 1, the grooves each being covered level by level by a smooth surface 4 of an adjacent film.
  • these smooth surfaces are formed by the unstructured flat surface of an adjacent film with channels, whereby a stack of similar films is formed.
  • Fig. lc reveals an embodiment in which, as in Fig. la two film surfaces structured with grooves are arranged one above the other, but are separated from one another by an unstructured intermediate film 5.
  • the two grooves do not set as in Fig. la shown as channel halves together to form a channel, but each form their own channels separated from each other by the intermediate film.
  • Fig. 2a and b show cross sections of exemplary embodiments of heat exchangers proposed to solve the aforementioned task with a low-pressure channel group 6 and a high-pressure channel group 7 as a foil stack.
  • the channels of the low-pressure channel group are shown as openings in individual foils (low-pressure frame, second foil), which are covered on both sides by an adjacent foil (belonging to the first foils).
  • the wall of each channel of the low-pressure channel group has a cross-section three adjacent layers formed; These channels border directly on both sides of two first foils of the high-pressure channel group in an advantageous manner for heat transfer.
  • the channels in each channel group are arranged and interconnected parallel to one another.
  • Fig. 2a shows an exemplary embodiment of a film stack in which the levels with the high-pressure channel groups, as in FIG. la shown, are designed particularly advantageously for high pressure applications with round channel cross sections extending over a pair of foils 9 (two first foils 8).
  • the levels arranged in between with the low-pressure channel groups 6 are represented in the example by perforated individual foils 10 (low-pressure frames), the openings 11 being covered on both sides by a smooth surface 4 of one of the aforementioned foil pairs with the high-pressure channel groups.
  • Fig. 2b shows a further exemplary embodiment with particularly short heat transfer paths between the high-pressure and low-pressure channel groups.
  • the low-pressure channel groups 6 are as in Fig. 2a is represented by perforated individual foils 10 (low-pressure frame, second foil), the openings 11 being covered on both sides by an adjacent first foil 8 of the foil pair 9 of the high-pressure channel group 7.
  • the channels of the high-pressure channel groups are incorporated as rectangular grooves in only a first film of the film pair and in continuation of the aforementioned openings and are covered by an unstructured cover film 12 (second of the first two films) that is flat on both sides. Cover film and films structured with grooves form the pair of films (first two films).
  • this as well as the rectangular cross sections of the channels of the high-pressure channel groups and the unstructured cover film promote a particularly large area share of the channel cross sections in the cross section of the (first) pair of films and thus the shortest possible heat transfer paths between the high-pressure and low-pressure channel groups.
  • Fig. 3a to d shows several schematic detailed views of a perforated film 10 as a second film (low-pressure frame) with a number of parallel openings 11 as channels.
  • Fig. 3c and d contain sectional views of the second film along the line shown in FIG. 3a shown section line AA.
  • the channels (openings 11) each open at their ends into a busbar 13 and 14 as inputs and outputs. outlet from or which are arranged as grooves transversely to the openings and connect them fluidly.
  • fluidic connections 15 and 16 are made from the busbars 13 and . 14 for an introduction or Drainage of the media to be conducted through the low-pressure channel group is provided.
  • These fluidic connections are - as shown - preferably proposed as openings through the second film, these openings being arranged one above the other in at least several adjacent films in the entire film stack and continuing to form an inlet and discharge channels crossing the films. Inlet and discharge channels also connect busbars arranged one above the other.
  • Fig. 4a to c show various exemplary embodiments of a countercurrent micro heat exchanger for uses preferably in refrigeration and cryogenic technology in general (Fig. 4a and b) as well as for the temperature control of power supplies for superconductivity applications 23 (Fig. 4c).
  • the countercurrent heat exchangers shown each have two end connection areas 17, each with two connections for the extension area of the high-pressure and low-pressure channel groups 18 arranged between them.
  • Fig. 5 shows an example of a schematic exploded drawing of the first and second films 8 and 8 respectively. 10 in a stack of foil one in Fig. 4a shown exemplary embodiment. The extent of a high-pressure channel group on a first film 27 and a low-pressure channel group on a second film 28 are shown. While the channels of both channel groups run parallel in layers in the central extension area 18, in the two end connection areas 17 they pivot out in channel groups into a connection volume each and open into or out of it. out of . The expanded connection volume (stacked openings) in the drain area is clearly visible, shown in the connection area shown on the right.
  • the second perforated film 10 is closed at the top with a cover film 25 that is flat on one side.
  • Fig. 4a shows an embodiment in which the connections for the drains for the low-pressure channel group 19 and the high-pressure channel group 21 are opposite their inlets 20 and . 22 are significantly expanded.
  • Such a configuration is particularly suitable for micro heat exchangers in which the media tempered in the channels experience an increase in volume (e.g. during a reaction or evaporation) or only a low flow resistance can be tolerated when the media is drained away.
  • This embodiment is characterized by that shown in FIG. 3a to d described breakthroughs through the foil stack, which are connected as fluidic connections to the aforementioned connections.
  • Fig. 4b shows a further embodiment in which the connections for the discharge lines for the low-pressure channel group 19 and the high-pressure channel group 21 are opposite their inlets 20 b. 22 were not or insignificantly changed in cross-section.
  • the aforementioned fluidic connections and the busbars between the high-pressure and low-pressure channel groups 18 and the connections 19 to 22 are replaced here by distribution chambers 24 attached directly to the side of the foil stack.
  • Each of the four distribution chambers preferably flow into all channels of a channel group off or on and are each fluidly connected to one of the four connections 19 to 22.
  • Fig. 4c shows a further embodiment in which the connections for the discharge lines for the low-pressure channel group 19 and the high-pressure channel group 21 are opposite their inlets 20 b.
  • the foil stack consists of an electrically highly conductive material, preferably copper, and has power connections 23, so that the electrical current preferably flows parallel to the channels in the central extension region 18.
  • This embodiment is particularly suitable for temperature control of power supply lines for superconductivity applications in order to efficiently transport the electrical current from room temperature to the cryogenic operating temperature of the superconductor.

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

Abstract

L'invention concerne un échangeur de chaleur comprenant un premier groupe de canaux haute pression (7) et un second groupe de canaux basse pression (6) avec une pluralité respective de canaux (3), les canaux (3) de chaque groupe de canaux étant disposés sur leur propre niveau respectif, les groupes de canaux (6, 7) sont introduits dans leurs propres films respectifs d'une manière séparée par voie fluidique et ceux-ci sont combinés pour former un empilement de films, les canaux du premier groupe de canaux à haute pression étant incorporés en couches et par l'intermédiaire de rainures (2) dans les premières paires de films (9), deux premiers films se trouvant l'un au-dessus de l'autre, les canaux du second groupe de canaux basse pression étant formés en couches par des ouvertures traversantes (11) avec des bandes disposées entre elles dans un second film (10) respectif et étant recouverts des deux côtés par un premier film (8) d'une première paire de films (9) ou un film de fermeture, et l'empilement de films comprenant un empilement alterné de seconds films (10) et de la première paire de films (9).
PCT/EP2023/072970 2022-09-06 2023-08-22 Échangeur de chaleur WO2024052110A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022122518.6A DE102022122518A1 (de) 2022-09-06 2022-09-06 Wärmeübertrager
DE102022122518.6 2022-09-06

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WO2024052110A1 true WO2024052110A1 (fr) 2024-03-14

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3709278C2 (fr) 1987-03-20 1989-03-02 Kernforschungszentrum Karlsruhe Gmbh, 7500 Karlsruhe, De
KR100991113B1 (ko) * 2010-04-14 2010-11-01 한국기계연구원 마이크로채널 열교환기
KR20120075838A (ko) * 2010-12-29 2012-07-09 한국원자력연구원 초고온가스 원자로용 열교환기
US20170309354A1 (en) * 2014-09-22 2017-10-26 Korea Atomic Energy Research Institute Heat exchanger and nuclear power plant comprising same

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011113045A1 (de) 2011-09-10 2013-03-14 Karlsruher Institut für Technologie Kreuzstrom-Wärmeübertrager
KR101376531B1 (ko) 2012-11-22 2014-03-19 주식회사 코헥스 천연가스 추진선박용 액화천연가스 기화 시스템

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3709278C2 (fr) 1987-03-20 1989-03-02 Kernforschungszentrum Karlsruhe Gmbh, 7500 Karlsruhe, De
KR100991113B1 (ko) * 2010-04-14 2010-11-01 한국기계연구원 마이크로채널 열교환기
KR20120075838A (ko) * 2010-12-29 2012-07-09 한국원자력연구원 초고온가스 원자로용 열교환기
US20170309354A1 (en) * 2014-09-22 2017-10-26 Korea Atomic Energy Research Institute Heat exchanger and nuclear power plant comprising same

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