EP2955469A1 - Für verdampfer geeignete ablenkplatte - Google Patents

Für verdampfer geeignete ablenkplatte Download PDF

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Publication number
EP2955469A1
EP2955469A1 EP14382488.6A EP14382488A EP2955469A1 EP 2955469 A1 EP2955469 A1 EP 2955469A1 EP 14382488 A EP14382488 A EP 14382488A EP 2955469 A1 EP2955469 A1 EP 2955469A1
Authority
EP
European Patent Office
Prior art keywords
baffle
fluid
baffles
stack
shell
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Withdrawn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
EP14382488.6A
Other languages
English (en)
French (fr)
Inventor
José Antonio GRANDE FERNÁNDEZ
Adrián Folgueira Baltar
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.)
BorgWarner Emissions Systems Spain SL
Original Assignee
BorgWarner Emissions Systems Spain SL
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 BorgWarner Emissions Systems Spain SL filed Critical BorgWarner Emissions Systems Spain SL
Priority to EP14382488.6A priority Critical patent/EP2955469A1/de
Publication of EP2955469A1 publication Critical patent/EP2955469A1/de
Withdrawn legal-status Critical Current

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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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0236—Header boxes; End plates floating elements
    • F28F9/0241—Header boxes; End plates floating elements floating end plates
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • 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
    • F28D7/16—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 in parallel spaced relation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/06—Tubular elements of cross-section which is non-circular crimped or corrugated in cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/228—Oblique partitions
    • 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
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements

Definitions

  • the present invention relates to a baffle suitable for evaporators which allows increasing heat transfer in a heat exchanger incorporating a stack of these baffles, since this stack forces a flow of the fluid to be evaporated transverse to the bundle of tubes, particularly according to a helical trajectory with a long path.
  • the helical trajectory of the liquid flow also helps preventing production of stagnation points even in zones where the liquid has not yet evaporated.
  • Baffle manufacture is cost effective because it allows manufacturing by means of stamping.
  • manufacture of a heat exchanger incorporating a stack of such baffles is also cost effective because of the ease of inserting the baffles within the shell of the exchanger and because there is no need to axially fix the position of each baffle along the tubes through which hot gas, transferring the heat required in the phase change of the fluid to be evaporated, circulates.
  • Heat recovery from exhaust gas is aimed at harnessing the heat from the exhaust gas which would otherwise be discharged into the atmosphere.
  • a technique which harnesses said heat from exhaust gases is the technique of incorporating a power cycle where heat transfer from exhaust gases to a specific working fluid is a step within a thermodynamic cycle, the purpose of which is to convert said transferred heat into work.
  • thermodynamic cycle Among the particular ways of transferring heat from exhaust gases to a working fluid which is made to follow a thermodynamic cycle include the use of evaporators causing phase change from liquid to vapor in said working fluid.
  • the working substance or fluid carrying out the power cycle is usually ethanol. Nevertheless, various fluids can be used as a working fluid, where many of them are organic substances (carbon-based). Other fluids that can also be used as a working fluid can be water or ammonia (NH 3 ), in this case inorganic substances.
  • the Rankine cycle is an example of performing a thermal cycle applied for converting transferred heat energy into mechanical energy.
  • an evaporator in a vehicle has restrictions, such as the space available in the engine compartment for installation or the condition of being a device with a low manufacturing cost.
  • One way to reduce the space occupied by said evaporator and/or the cost is by increasing heat exchange capacity, i.e., increasing turbulence or exchange surface comprised in the evaporator over which hot gas circulates.
  • a bundle of tubes is housed in a shell and immersed in the fluid to which heat is transferred or the fluid to be evaporated. The fluid to which heat is transferred circulates between the tubes of the bundle of tubes and the shell of the heat exchanger housing said bundle of tubes.
  • the heat transfer area of the zone through which the working fluid circulates can be increased, such that more heat can be transferred.
  • the limitation of the space that can be occupied by the device, and therefore the space available inside the shell means that the number of tubes cannot be increased to any extent desired.
  • each pair of tubes is formed by an inner tube and an outer tube having a larger diameter, arranged coaxially to one another.
  • a bundle of pairs of tubes thus distributed is housed in a shell such that two possible channels are obtained for the flow of the first fluid. Said two channels are the inside of the inner tubes having a smaller diameter and the space defined between the tubes having a larger diameter and the shell.
  • the space defined between the two bundles of tubes allows passage of the working fluid, i.e., the fluid undergoing phase change.
  • the exchange area between the first fluid and the second fluid is therefore the surface of the inner tubes and the surface of the outer tubes.
  • Documents DE 102011118164 A1 and DE 102010008175 A1 describe a heat exchanger with this configuration. Additionally, the tubes of the exchanger defined in DE 102010008175 A1 further increase heat transfer between the inner tubes and the outer tubes, because the configuration of the tubes changes along the length thereof.
  • baffles in the space existing between the tubes and the inner wall of the shell, for forcing the exchange by increasing convection.
  • These baffles usually incorporate passages in alternating positions, forcing a zig-zag flow.
  • one drawback of such baffles is that they require fixing by means of welding at pre-established points of the bundle of tubes, in addition to the production of stagnation zones behind the baffles where the fluid barely reaches or reaches with a very low speed causing very hot points, which increase thermal fatigue and generates structural damage.
  • the present invention allows increasing heat exchange by improving convection between the second fluid and the outer surface of the exchange tubes, overcoming the problems identified above by establishing a simple configuration for a baffle which is manufactured by stamping, does not require being welded to the bundle of tubes and considerably increases the degree of heat transfer between the working fluid and the bundle of tubes, while at the same time helps to contain vibrations in the tubular bundle without preventing differential expansions and shrinkages between the shell and the tubes, therefore reducing the level of thermal fatigue of the part.
  • a first aspect of the present invention relates to a baffle suitable for evaporators.
  • the evaporator for which is the baffle intended comprises a shell housing a bundle of heat exchange tubes.
  • the bundle of tubes allows passage of the first fluid transferring heat, preferably the exhaust gas of an internal combustion engine.
  • the space through which the second fluid or working fluid receiving heat and undergoing a phase change from liquid to vapor flows is arranged between the tubes of the bundle of tubes and the shell.
  • Conventional working fluids are water, coolants, methanol and ethanol. This second fluid has been identified as a working fluid given its main application of being subjected to a thermal cycle for converting the heat absorbed by said second fluid into mechanical work.
  • the fluid flowing through the bundle of tubes transferring heat will be referred to as the first fluid
  • the fluid circulating between the tubes of the bundle of tubes and the shell will be referred to as the second fluid.
  • the first aspect of the invention relates to a baffle modifying the trajectory of the second fluid causing it to circulate mainly transverse to the bundle of tubes, increasing convection inside the shell.
  • the baffle comprises:
  • the baffle according to the invention has a configuration which allows it to be stacked together with a contiguous baffle, this stacking giving rise to a duct having a helical trajectory for the working fluid.
  • Each of the baffles allows passage of the bundle of tubes, whereby heat exchange occurs, through the plurality of perforations comprised therein.
  • the first fluid flows according to the direction imposed by the direction of the bundle of tubes and the second fluid follows a mainly transverse trajectory along the helical trajectory configured by the baffles.
  • Said helical trajectory is obtained by stacking a plurality of baffles.
  • Each of the baffles has a first support region and a second support region, both regions being spaced from one another. This spacing generates a channel between consecutive baffles.
  • Each baffle contributes to an angular sector of the trajectory of the second fluid. In the embodiments, this angular sector is 360°, assuring continuity between baffles of the helical trajectory along the heat exchanger.
  • Said continuity is established by the edge condition imposed according to the last structural technical feature indicated above, whereby the first edge segment and the second edge segment of the opening are such that they also give rise to the adjacency of the edges in baffles arranged adjacent to one another in the stack. Said condition forces the entire flow to follow the entire helical trajectory, from the inlet until reaching the outlet, with a direction of movement essentially transverse to the tubes.
  • baffle is not interposed perpendicular to the main flow for deflecting said flow, rather it acts as a guide to impose a flow parallel to it, following the described helical trajectory.
  • Stacking of the baffles means that, if the space occupied by the stack is limited at the ends thereof, then it will be unnecessary to fix each of the baffles to the bundle of tubes. In this case, arranging a stop or limiting element maintaining the packing resulting from the compact stack in at least one of the ends of the stack is sufficient.
  • seat rings are included at both ends, which rings are adapted to the helical configuration with which the stack of baffles finishes, such that the baffles of the stack are kept compact and therefore in contact at all times.
  • this heat exchanger only requires inserting a plurality of baffles such as those of the present invention, correctly oriented such that the edges of the openings coincide with one another.
  • the perforations allowing passage of the tubes of the bundle of tubes serve as guides facilitating assembly and orientation of each of the baffles, thus also facilitating the manufacture of the heat exchanger from these baffles.
  • the present invention relates to a baffle (1) for evaporators.
  • Figure 1 shows a perspective view of an embodiment of the baffle (1)
  • Figure 2 shows an elevational view of a stack of three baffles such as those shown in Figure 1 .
  • the evaporator for which the baffle (1) according to the invention, and particularly the baffle (1) according to this embodiment, is suitable comprises, as shown in Figures 3 , 4 and 5 :
  • FIGS. 3 to 5 show an embodiment of the evaporator.
  • the baffles (1) according to the invention are such that the stacking thereof establishes a helical conduit for the second fluid inside the evaporator.
  • FIGS 1 and 6 show the perspective views of a baffle (1) according to different embodiments, manufactured in stamped sheet metal.
  • the baffle (1) is formed by a main plate (1.4) comprising a plurality of perforations (1.3) adapted for passage of the tubes (3) of the bundle of tubes of the exchanger.
  • the main plate (1.4) has a helical warped surface.
  • the helical surface starts from a first edge segment (A1), which in this embodiment extends according to a radial direction and furthermore extends according to the clockwise direction of rotation, considering the particular orientation shown in Figure 1 , until reaching a second edge segment (A2), which also extends according to a radial direction.
  • the perimetral edge of the helical surface segment of the main plate (1.4) extends towards the inner portion, also considering the particular orientation of Figures 1 and 2 , by means of a skirt-like cylindrical surface (1.2). In other words, it extends parallel to the direction defined by stacking a plurality of baffles (1) and which in this embodiment is essentially perpendicular to the main plate (1.4) given the reduced helical feed of the helical surface. Nevertheless, it is possible to carry out the invention with main plates having greater helical pitch. In these cases, the axis defined by the stack continues to be the longitudinal reference.
  • the cylindrical surface (1.2) extends along the entire perimetral edge of the main plate (1.4) with a constant width. According to other embodiments, the cylindrical surface (1.2) extends according to two or more perimetral edge segments of the main plate (1.4). This cylindrical surface (1.2) is intended for being completely or partially supported in the inner wall of the shell (2) of the evaporator.
  • the cylindrical surface (1.2) shows a plurality of grooves (12) parallel to the direction defined by stacking a plurality of baffles (1) such that there is a tab between consecutive grooves.
  • This configuration facilitates inserting the baffles (1) inside the shell (2) and therefore assembling them.
  • Another technical effect of this configuration is the improved adaptation of the periphery of the baffle (1) to the inner surface of the shell (2) at each point such that better sealing between the baffle (1) and the shell (2) is achieved, preventing passage of fluid between both components.
  • the perimetral edge of the main plate (1.4) has a first support region (1.1), which in this embodiment is located on one of the faces of the main plate (1.4).
  • the cylindrical surface (1.2) extends in the opposite direction from the opposite face of the main plate (1.4), such that the free edge of this cylindrical surface (1.2) is the second support region (1.2.1).
  • the cylindrical surface (1.2) establishes a spacing between the first support region (1.1) and the second support region (1.2.1).
  • FIG 2 shows a stack of three baffles (1) according to one embodiment. All the baffles (1) in this stack have the same configuration, so it is not necessary to manufacture different types of baffles (1) according to their axial or longitudinal position, axial or longitudinal direction being understood as the direction defined by stacking. This longitudinal direction is identified in Figure 2 by means of axis X-X'.
  • Each of the baffles (1) comprises an opening (A).
  • this opening (A) is a radial cut of the main plate (1.4) traversing some perforations (1.3). For that reason, the radial cut is not a straight cut but rather interrupted segments of cuts in the material located between the perforations (1.3).
  • the radial cut as well as deformation by stamping generate the first and second edge segment (A1, A2). Deformation by stamping separates the edge segments (A1, A2) from one another according to the stacking direction.
  • stacking causes the overlapping of a plurality of baffles (1) such that the orientations of the openings (A), in the embodiment the orientation is determined by the radial cut, coincide with one another according to the projection of axis X-X'.
  • the helical surface formed by the main plate (1.4) extends 360°, the first edge segment (A1) of a baffle (1) coincides with the second edge segment (A2) of the contiguous baffle, establishing surface continuity defining the main plate (1.4) of both baffles (1).
  • the plurality of main plates (1.4) forms a continuous helical surface, with the perforations (1.3) in alignment for passage of the bundle of tubes (3) through said perforations (1.3), following the stacking direction.
  • the helical surface formed by the stack of baffles (1) establishes a helical path for the second fluid, which is essentially perpendicular to the tubes (3) arranged in the path thereof.
  • the first edge segment (A1) and the second edge segment (A2) are discontinuous. This is the result of generating the opening (A) through a radial cut going through perforations (1.3) during a die-cutting and stamping operation.
  • the tubes (3) going through the perforations (1.3) are surrounded by the edge generated by half the perforation (1.3) of the main plate (1.4) of a baffle (1), and by the edge generated by half the perforation (1.3) of the main plate (1.4) of the contiguous baffle.
  • the cylindrical surfaces (1.2) also result in a continuous cylindrical surface.
  • Figure 2 shows the resulting continuous cylindrical surface and the support of the first support region (1.1) on the second support region (1.2.1).
  • the width of the cylindrical surface (1.2) of each baffle (1) defines the spacing between the baffles (1) and therefore the height of the section of the helical duct generated by stacking.
  • the cylindrical surface (1.2) is still considered a continuous surface with the exception that it has a plurality of grooves (12) on the surface thereof.
  • FIG 3 shows an exploded perspective view of the components of an evaporator according to an embodiment where the bundle of tubes (3) goes through a stack of baffles (1) such as the one described.
  • This drawing clearly shows the cylindrical surface generated by stacking a plurality of baffles (1). As shown in Figure 4 , this cylindrical surface is supported in the inner wall of the shell (2).
  • the stack of baffles (1) is preferably not welded to the tubes (3) although this may be the case in a particular example.
  • a seat ring (9, 11) has been included at each end of the stack of baffles (1) configured according to the helical perimetral shape.
  • the bundle of tubes (3) extends between a first end baffle (4) and a second end baffle (5), both in the shape of a circular plate with a cylindrical seat in the periphery thereof for closing on the inner wall of the shell (2).
  • the bundle of tubes (3) is welded by brazing or any other techniques of attachment, to the end baffles (4, 5).
  • Figures 4 and 5 show a gap between the first end baffle (4) and the seat ring (11) such that between the stack of baffles (1) and said end baffle (4) there is a first chamber (C1) which is accessible to the second fluid through an inlet (2.1) located in this embodiment in the shell (2) and with direct access to the bundle of tubes (3).
  • first chamber (C1) the second fluid is distributed along the transverse section of the bundle of tubes (3) and is forced to enter the helical duct configured by the stack of baffles (1).
  • the access for the entry or exit of the first fluid at this end of the heat exchanger is through a first manifold (10), which in this case is shown with a flange (10.1) for attachment to the duct of the first fluid. Said access will be for the entry or exit depending on if the evaporator works in co-current flow or counter-current flow.
  • said end is the end of the trajectory of the second fluid after said second fluid travelled through the helical path imposed by the stack of baffles (1).
  • Said second fluid expands after the phase change it undergoes along the travel thereof through the heat exchanger, so a second chamber (C2) that is larger than the first chamber (C1) is configured for receiving the evaporated second fluid.
  • This second chamber (C2) is formed inside a second manifold (8) having a larger diameter than the shell (2).
  • This second manifold (8) is not only adapted for receiving the evaporated second fluid but also for housing a third manifold (7) in the central position according to longitudinal axis X-X', receiving the first fluid at the end of the bundle of tubes (3).
  • the core of the heat exchanger formed mainly by the bundle of tubes (3) is connected to the end of the heat exchanger by means of a compressible bellows (6) with axial deformation capacity.
  • the bellows (6) establishes a fluid communication between the end of the third manifold (7) and the end of the second manifold (8).
  • the second chamber (C2) is mainly defined as the space between the third manifold (7) arranged inside the second manifold (8), and said second manifold (8).
  • the outlet (8.1) of the second fluid is located in this second manifold (8).
  • the first fluid firstly exits through the third manifold (7), then going through the compressible bellows (6) and finally leaving the second manifold (8), which is communicated with the duct of the first fluid of the internal combustion engine by means of a flange (8.2).
  • the second fluid is in more direct contact with the shell (2). Heat losses occurring through the shell reduce the effective heat transferred from the first fluid to the second fluid and therefore reduce the overall performance of the heat exchanger.
  • the shell (2) is insulated by being surrounded by an insulating material, such as rock wool.
  • the shell (2) is located inside a second shell such that there is an air chamber between both shells (2) performing the function of thermal insulation, reducing heat leakage.

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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)
EP14382488.6A 2014-12-02 2014-12-02 Für verdampfer geeignete ablenkplatte Withdrawn EP2955469A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14382488.6A EP2955469A1 (de) 2014-12-02 2014-12-02 Für verdampfer geeignete ablenkplatte

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14382488.6A EP2955469A1 (de) 2014-12-02 2014-12-02 Für verdampfer geeignete ablenkplatte

Publications (1)

Publication Number Publication Date
EP2955469A1 true EP2955469A1 (de) 2015-12-16

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EP14382488.6A Withdrawn EP2955469A1 (de) 2014-12-02 2014-12-02 Für verdampfer geeignete ablenkplatte

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018147978A1 (en) * 2017-02-13 2018-08-16 Daikin Applied Americas Inc. Condenser with tube support structure
US11454452B2 (en) * 2017-12-11 2022-09-27 John Cockerill S.A. Heat exchanger for a molten salt steam generator in a concentrated solar power plant (III)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1335506A (en) * 1917-07-16 1920-03-30 Griscom Russell Co Oil-cooler
US1525094A (en) * 1921-03-05 1925-02-03 Griscom Russell Co Multivane cooler
WO2000017593A1 (en) * 1998-09-24 2000-03-30 Serck Aviation Limited Heat exchanger
DE102010008175A1 (de) 2010-02-16 2011-08-18 TheSys GmbH, 72127 Wärmeübertrager und Verfahren zum Betreiben eines Wärmeübertragers
DE102011118164A1 (de) 2010-12-29 2012-07-05 Thesys Gmbh Wärmeübertrager und Verfahren zum Betreiben eines Wärmeübertragers

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1335506A (en) * 1917-07-16 1920-03-30 Griscom Russell Co Oil-cooler
US1525094A (en) * 1921-03-05 1925-02-03 Griscom Russell Co Multivane cooler
WO2000017593A1 (en) * 1998-09-24 2000-03-30 Serck Aviation Limited Heat exchanger
DE102010008175A1 (de) 2010-02-16 2011-08-18 TheSys GmbH, 72127 Wärmeübertrager und Verfahren zum Betreiben eines Wärmeübertragers
DE102011118164A1 (de) 2010-12-29 2012-07-05 Thesys Gmbh Wärmeübertrager und Verfahren zum Betreiben eines Wärmeübertragers

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018147978A1 (en) * 2017-02-13 2018-08-16 Daikin Applied Americas Inc. Condenser with tube support structure
US10371422B2 (en) 2017-02-13 2019-08-06 Daikin Applied Americas Inc. Condenser with tube support structure
US11454452B2 (en) * 2017-12-11 2022-09-27 John Cockerill S.A. Heat exchanger for a molten salt steam generator in a concentrated solar power plant (III)

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