EP4141371A1 - Luftgekühlter wärmetauscher - Google Patents

Luftgekühlter wärmetauscher Download PDF

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Publication number
EP4141371A1
EP4141371A1 EP21192542.5A EP21192542A EP4141371A1 EP 4141371 A1 EP4141371 A1 EP 4141371A1 EP 21192542 A EP21192542 A EP 21192542A EP 4141371 A1 EP4141371 A1 EP 4141371A1
Authority
EP
European Patent Office
Prior art keywords
air
heat exchanger
tube
cooled heat
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Withdrawn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
EP21192542.5A
Other languages
English (en)
French (fr)
Inventor
Wilhelmus Franciskus Schoonen
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.)
Dhes BV
Original Assignee
Dhes BV
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 Dhes BV filed Critical Dhes BV
Priority to EP21192542.5A priority Critical patent/EP4141371A1/de
Priority to EP22765156.9A priority patent/EP4392728A1/de
Priority to PCT/EP2022/073382 priority patent/WO2023025750A1/en
Publication of EP4141371A1 publication Critical patent/EP4141371A1/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Withdrawn legal-status Critical Current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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/003—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by using permeable mass, perforated or porous materials
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
    • F25J1/0005—Light or noble gases
    • F25J1/001—Hydrogen
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • F25J1/0296—Removal of the heat of compression, e.g. within an inter- or afterstage-cooler against an ambient heat sink
    • 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
    • F28D7/14—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 both tubes being bent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/04—Compressor cooling arrangement, e.g. inter- or after-stage cooling or condensate removal
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/30—Compression of the feed stream
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0047—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for hydrogen or other compressed gas storage tanks
    • 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
    • F28F2250/08—Fluid driving means, e.g. pumps, fans

Definitions

  • the present invention relates to an air cooled heat exchanger, in particular an air cooled heat exchanger for cooling compressed hydrogen.
  • Air cooled heat exchangers often comprise a serpentine arrangement of tubes through which a medium flows that is to be cooled, wherein outer surfaces of the tubes are cooled by air flow during operation. These outer surfaces of the tubes are often provided with fins for enlarging the air contact area of the tubes such that heat transfer between the tubes and the air flow is facilitated.
  • air cooled heat exchangers may become relatively large for achieving sufficient heat transfer and as such these heat exchangers may be less suitable for applications where space is limited.
  • these U-shaped tubes may cause an increase in friction between the medium and inner surfaces of the U-shaped tubes. This increase in friction may in turn lead to heating of the medium as it flows through the U-shaped tubes, thereby reducing the overall cooling efficiency of the air cooled heat exchanger.
  • the present invention seeks to provide an air cooled heat exchanger that at least in part solves the problems of the prior art.
  • the air cooled heat exchanger of the present invention allows for a compact and cost competitive design whilst exhibiting improved heat transfer efficiency.
  • the air cooled heat exchanger is particularly advantageous for industrial applications such as cooling of compressed hydrogen for example.
  • an air cooled heat exchanger as defined above, comprising a hollow shell provided with a tube inlet for receiving a medium to be cooled and a tube outlet for discharging the medium, wherein the shell houses a tube arrangement connecting the tube inlet to the tube outlet.
  • the shell is filled with a thermally conductive, air permeable material which is in tight engagement with the tube arrangement, and wherein the shell is provided with an air inlet for receiving air and an air outlet for discharging the air, wherein thermally conductive, air permeable material then fluidly connects the air inlet to the air outlet.
  • the thermally conductive, air permeable material inside the hollow shell provides a number of advantages.
  • Second, the thermally conductive, air permeable material provides for heat accumulation, for example, so that a more continuous and consistent thermal exchange is provided with less short term variance.
  • the thermally conductive, air permeable material allows for higher heat transfer through the air then the tube arrangement, thereby ensuring that maximum cooling of the medium is achieved.
  • the thermally conductive air permeable material comprises a compacted arrangement of metal particles.
  • the compacted metal particles provide for snug and tight embedding of the tube arrangement in the metal particles to achieve optimal heat transfer between the tube arrangement and the thermally conductive air permeable material.
  • the metal particles are able to tightly embed the tube arrangement irrespective of the layout and routing complexity thereof.
  • the metal particles may be copper alloy particles to achieve high thermal conductivity.
  • the metal particles may be substantially spherical and/or substantially irregularly shaped.
  • the spherical or irregularly shaped particles can be chosen so as to achieve a desire level of compaction of metal particles, e.g. shell filling factor, level of heat accumulation, air permeability etc.
  • the thermally conductive, air permeable material may be a porous solid material rather than a granular type of material such as the metal particles mentioned above.
  • a porous solid material may be advantageous to provide for higher levels of accumulation, for example, or higher thermal conductivity of the air permeable material.
  • FIG. 1 a schematic top view of an air cooled heat exchanger 1 according to an embodiment of the present invention is depicted, where in Figure 2 a schematic cross sectional view of the air cooled heat exchanger 1 is depicted according to an embodiment. It is noted that both figures 1 and 2 are schematic in nature and do not reflect true proportions of various depicted features and elements.
  • the air cooled heat exchanger 1 comprises a hollow shell 2 provided with a tube inlet 3 for receiving a medium M to be cooled and a tube outlet 4 for discharging the medium M.
  • the medium M may be gaseous hydrogen that needs to be cooled for example.
  • the hollow shell 2 houses or encloses a tube arrangement 5 that connects the tube inlet 3 to the tube outlet 4.
  • the tube arrangement 5 may be embodied in various ways for reasons set forth later below. For now, the tube arrangement 5 for carrying the medium M from the tube inlet 3 to the tube outlet 4 may be routed to achieve a particular heat transfer behaviour.
  • the shell 2 is filled with a thermally conductive, air permeable material 6 in tight engagement with the tube arrangement 5. That is, the thermally conductive, air permeable material 6 tightly embeds the tube arrangement 5 and makes snug contact therewith.
  • the shell 2 is further provided with an air inlet 7 for receiving air A and an air outlet 8 for discharging the air A, wherein the thermally conductive air permeable material 6 fluidly connects the air inlet 7 to the air outlet 8.
  • the air A may be ambient air requiring no special treatment before introduction into the air inlet 7, thereby reducing complexity of the air cooled heat exchanger 1 and costs thereof.
  • the shell 2 is tightly filled with the thermally conductive, air permeable material 6 and by virtue of the air permeability of the material, the air A is able to travel through the shell 2 from the tube inlet 3 to the tube outlet 4.
  • the thermally conductive, air permeable material 6 inside the hollow shell 2 provides for a number of advantages.
  • a surface area for thermal exchange between the tube arrangement 5 and the air A flowing through the shell 2 is greatly increased to optimize thermal exchange between the medium M and the air A as they flow through the tube arrangement 5 and the shell 2 respectively.
  • the thermally conductive, air permeable material 6 provides for heat accumulation, e.g. "thermal mass", allowing a more continuous and consistent thermal exchange to be provided with less short term variance.
  • the thermally conductive, air permeable material 6 allows for high heat transfer by the air A than the tube arrangement 5 is able to provide, thereby ensuring that maximum cooling of the medium M is achieved.
  • the thermally conductive air permeable material 6 comprises a compacted arrangement of metal particles 9.
  • the compacted metal particles 9 may be seen as having a fine granular structure for snug and tight embedding of the tube arrangement 5 in the metal particles 9 to achieve optimal heat transfer between the tube arrangement 5 and the thermally conductive air permeable material 6.
  • the metal particles 9 are able to tightly embed the tube arrangement 5 irrespective of the layout and routing complexity thereof.
  • the metal particles 9 may be copper alloy particles to achieve high thermal conductivity.
  • the metal particles 9 are substantially spherical and/or substantially irregularly shaped.
  • Such spherical or irregularly shaped particles 9 can be chosen so as to achieve a desired level of compaction, a desired shell filling factor of metal particles 9, a level of heat accumulation, higher or lower levels of air permeability of the compacted metal particles and so forth.
  • the metal particles have a width "w" and/or height "h" of at most 3 mm, e.g. 2 mm. This allows for a sufficiently high surface area for thermal exchange, improved thermal accumulation and to provide sufficient air permeability through the shell 2 when the air A travels from the tube inlet 3 to the tube outlet 4.
  • the thermally conductive air permeable material 6 is a porous solid material.
  • a porous solid material may be advantageous to provide for, e.g., higher levels of accumulation and/or thermal conductivity of the air permeable material 6.
  • the porous solid material may comprise brass, e.g. solid brass having a porous structure that provides small channels for the air A to travel through the shell 2.
  • the porous solid material may be cast around the tube arrangement 5, for example, to achieve good contact therewith for optimal heat transfer.
  • the shell 2 may be a toroidal or cylindrical shell 2, wherein the tube arrangement 5 comprises a plurality of tubes 10 forming a wounded tube bundle that extends through the toroidal or cylindrical shell 2 around a centre C thereof.
  • the tube arrangement 5 comprises a plurality of tubes 10 forming a wounded tube bundle that extends through the toroidal or cylindrical shell 2 around a centre C thereof.
  • the wounded tube bundle avoids sharp U-bends that may increase flow resistance considerably, so the toroidal or cylindrical shell 2 allows for a wounded tube arrangement 5 that minimizes friction along inner walls thereof and as such unwanted heating of the medium M is minimized when it flows from the tube inlet 3 to the tube outlet 4.
  • a toroidal shell 2 may comprise an upper and lower surface 2a, 2b which are rounded, e.g. circular, as well as a rounded/circular side surface 2c.
  • a cylindrical shell 2 may have upper and lower surfaces 2a, 2b that are substantially flat, and wherein the side surface 2c will be substantially straight in vertical direction.
  • both the toroidal and cylindrical shell 2 provide for a the tube arrangement 5 having the plurality of tubes 10 forming a continuously wounded tube bundle with mild and gentle bends around the centre C.
  • flow friction along inner walls of the tube arrangement 5 may be minimized by increasing an inner diameter D of the toroidal or cylindrical shell 2.
  • the toroidal or cylindrical shell 2 has an inner diameter D of at least 150 mm. This diameter ensures that internal friction in the wounded tube bundle is kept to a minimum.
  • the inner diameter D can of course be enlarged to meet particular cooling and/or efficiency requirements.
  • the inner diameter D may be 300 mm or larger, e.g. about 400 mm, depending on a required cooling capacity of the air cooled heat exchanger 1.
  • the shell 2 is provided with one or more further tube inlets 3' for receiving a further medium M' to be cooled and a corresponding number of one or more further tube outlets 4' for discharging the further medium M', wherein the tube arrangement 5 connects each of the one or more further tube inlets 3' to a corresponding further tube outlet of the one or more further tube outlets 4'.
  • This embodiment is particular advantageous when different mediums M, M' need to be cooled and/or when particular mediums M, M' are provided at different pressures and/or flow speeds and so forth.
  • the tube inlets 3, 3' and tube outlets 4, 4' may tangentially enter and exit the shell 2, respectively, to minimize sharp bends to decrease internal flow friction and thus heating of the medium M, M'.
  • the tube arrangement 5 in the shell 2 remains fully embedded in the thermally conductive air permeable material 6 to achieve optimal cooling.
  • the air cooled heat exchanger 1 still provides for a compact form factor for a toroidal or cylindrical shell 2 with minimal internal friction as the tube arrangement 5 carrying the various mediums M, M' maintains the wounded tube bundle with gentle, long bends in correspondence with the inner diameter D as mentioned earlier.
  • the air cooled heat exchanger 1 may further comprise an air blower 11 connected to the air inlet 7, wherein the air blower 11 is configured for providing the air A to the air inlet 7.
  • the air A for cooling is provided by the air blower 11, e.g. a fan-based air blower, and wherein the air A is urged through the thermally conductive, air permeable material 6 filling the shell 2.
  • the shell 2 may be provided with one or more further air inlets 7' for receiving further air A' and one or more further air outlets 8' for discharging the further air A', wherein the thermally conductive air permeable material 6 fluidly connects the air inlet 7 and the one or more further air inlets 7' to the air outlet 8 and the one or more further air outlets 8'.
  • the one or more further air inlets 7'and further air outlets 8' allow for increased cooling capacity of the tube agreement 5. To do so it is advantageous to evenly distribute the air inlet 7 and the one or more further air inlets 7' along the shell 2, as well as evenly distributing the air outlet 8 and the one or more further air outlets 8' along the shell 2. By evenly distributing all air inlets 7, 7'and all air outlets 8, 8', the air A and further A' may traverse the shell 2 over longer distances for improved thermal transfer.
  • one or more further air blowers 11' may be provided each of which is connected to a corresponding further air inlet of the one or more further air inlets 7', and wherein each of the one or more further air blowers 11' is configured for providing the further air A' to the corresponding further air inlet of the one or more further air inlets 7'.
  • the one or more further air blowers 11' e.g. fan based
  • a toroidal or cylindrical shell 2 there is provided an embodiment wherein the air inlet 7 and the one or more further air inlets 7' are provided on the lower surface 2b of the shell 2 and wherein the air outlet 8 and the one or more further air outlets 8' are provided on the upper surface 2a of the shell 2.
  • the air A and further air A' traverse the toroidal or cylindrical shell 2 optimally in vertical directional for maximized heat transfers.
  • the air inlet 7 and the one or more further air inlets 7' may be evenly distributed along a circumference/perimeter of the toroidal or cylindrical shell 2 as well as the air outlet 8 and the one or more further air outlets 8' may be evenly distributed along a circumference/perimeter of the toroidal or cylindrical shell 2.
  • the air inlets 7, 7' and air outlets 8, 8' may be arranged in alternating fashion around the circumference/perimeter as shown in Figure 1 .
  • the air inlet 7 and the one or more further air inlets 7' may be mutually spaced apart over a common, maximized inlet angle " ⁇ ", so that the air A and further air A' is evenly introduced into the toroidal or cylindrical shell 2. So in the depicted embodiment with one further air inlet 7', the air inlet 7 and the further air inlet 7' are spaced apart over an inlet angle ⁇ of 180°.
  • the air outlet 8 and one or more further air outlets 8' may be mutually spaced apart over a common, maximized outlet angle " ⁇ ". So in the depicted embodiment with one further air outlet 8', the air outlet 8 and the further air outlet 8' are spaced apart over an outlet angle ⁇ of 180° as depicted.
  • circumferential/peripheral distance between air inlets 7, 7' and air outlets 8, 8' may be maximized as well to ensure that the air A and further A' travels from an air inlet 7, 7' to an air outlet 8, 8' along a maximum distance to maximize heat transfer.
  • the air inlet 7 and the air outlet 8 may be arranged on opposing sides of a toroidal or cylindrical shell 2 to allow the air A to completely traverse the shell 2.
  • the air inlet 7 and further air inlet 7' may be arranged on opposing sides of a toroidal or cylindrical shell 2 and wherein the air outlet 8 and the further air outlet 8' may also be arranged on opposing sides of the shell 2.
  • the tube inlet 3 and the one or more further tube inlets 3' may be positioned on the shell 2 in various ways. The same applies to the tube outlet 4 and the one or more further tube outlets 4'.
  • the tube inlet 3 and the one or more further tube inlets 3' may be connected to the shell proximal to the upper surface 2a, and wherein the tube outlet 4 and the one or more further tube outlets 4' may be connected to the shell 2 proximal to the lower surface 2b.
  • This embodiment allows the tube arrangement 5 to be formed as a helically wounded tube bundle extending from all tube inlets 3, 3' proximal to the upper surface 2a of the shell 2 to all tube outlets 4, 4' proximal to the lower surface 2b of the shell 2.
  • the air cooled heat exchanger 1 of the present invention is advantageous for industrial applications such as cooling of compressed hydrogen gas.
  • the air cooled heat exchanger 1 may be utilized in hydrogen refuelling stations which compress gaseous hydrogen to a required pressure for dispensing the hydrogen gas into a vehicle.
  • compression may raise the temperature of the hydrogen gas well over 100 °C (Celsius) and so cooling of the hydrogen will be required before it can be dispensed.
  • FIG. 3 a schematic view of a hydrogen gas cooling process is depicted, wherein the cooling process utilizes an air cooled heat exchanger 1 as depicted.
  • a process may be used to describe a general method for cooling a gaseous medium M using the air cooled heat exchanger 1 as explained above.
  • the method involves the step of compressing the medium M using a compressor 12. Once compressed, the method continues with the step of feeding the compressed medium M to the tube inlet 3 of the air cooled heat exchanger 1 at a first temperature T1.
  • the first temperature T1 will be higher than the temperature of the gaseous medium M entering the compressor 12 as the compression will have raised the temperature.
  • the method then comprises the step of feeding air A to the air inlet 7 of the air cooled heat exchanger 1.
  • air A is introduced into the air inlet 7 and travels through the shell 2 filled with the thermally conductive, air permeable material 6, where the air A discharges through the air outlet 8.
  • the air A e.g. ambient air A, may be provided by an air blower 11.
  • the method involves discharging the compressed medium M through the tube outlet 4 at a second temperature T2, wherein the second temperature T2 is lower than the first temperature T1.
  • the air cooled heat exchanger 1 cools the medium M as it traverses the tube arrangement 5 toward the tube outlet 4.
  • the final step then involves feeding the discharged compressed medium M to a further heat exchanger 13 for further cooling to a third temperature T3, the third temperature T3 being lower than the second temperature T2.
  • the further heat exchanger 13 allows the medium M to be further cooled.
  • the further heat exchanger 13 may comprise an inlet 14 for receiving the medium M and an outlet 15 for discharging the medium M.
  • the further heat exchanger 13 may comprise a further tube arrangement connecting the inlet 13 and the outlet 14, and wherein the medium M entering the inlet 14 travels through the further tube arrangement which is subjected to further cooling.
  • the method provides a two stage cooling process, which is advantageous as the air cooled heat exchanger 1 may not be able to sufficiently cool the medium M from the second temperature T2 to the third temperature T3.
  • the further heat exchanger 13 need not utilize air as a coolant inside the further heat exchanger 13.
  • the further heat exchanger 13 may utilize mechanical cooling to achieve the third temperature T3.
  • a secondary cooling loop 16 may be used comprising a secondary tube arrangement 17 configured for a condenser type cooling cycle.
  • the further tube arrangement inside the further heat exchanger 13 is then arranged for heat transfer with the secondary tube arrangement 17 which also traverses through the further heat exchanger 13.
  • the medium M may be gaseous hydrogen, wherein the first temperature T1 lies above 100 °C, wherein the second temperature T2 lies between 100 °C and 10 °C, and wherein the third temperature T3 lies below 10 °C.
  • the first temperature T1 may be around 150 °C
  • the second temperature T2 may be around 40 °C
  • the third temperature T3 may be around 6 °C.
  • the first temperature T1 may be around 150 °C
  • the second temperature T2 may be around 65 °C
  • the third temperature T3 may be around 5 °C.
  • the medium e.g. hydrogen
  • the medium may be precooled using relatively little energy, before the medium enters the further heat exchanger 13. In doing so, the overall efficiency may be improved.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Dispersion Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP21192542.5A 2021-08-23 2021-08-23 Luftgekühlter wärmetauscher Withdrawn EP4141371A1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP21192542.5A EP4141371A1 (de) 2021-08-23 2021-08-23 Luftgekühlter wärmetauscher
EP22765156.9A EP4392728A1 (de) 2021-08-23 2022-08-23 Luftgekühlter wärmetauscher
PCT/EP2022/073382 WO2023025750A1 (en) 2021-08-23 2022-08-23 Air cooled heat exchanger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP21192542.5A EP4141371A1 (de) 2021-08-23 2021-08-23 Luftgekühlter wärmetauscher

Publications (1)

Publication Number Publication Date
EP4141371A1 true EP4141371A1 (de) 2023-03-01

Family

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP21192542.5A Withdrawn EP4141371A1 (de) 2021-08-23 2021-08-23 Luftgekühlter wärmetauscher
EP22765156.9A Pending EP4392728A1 (de) 2021-08-23 2022-08-23 Luftgekühlter wärmetauscher

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP22765156.9A Pending EP4392728A1 (de) 2021-08-23 2022-08-23 Luftgekühlter wärmetauscher

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EP (2) EP4141371A1 (de)
WO (1) WO2023025750A1 (de)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3415316A (en) * 1967-04-11 1968-12-10 Olin Mathieson Modular units and use thereof in heat exchangers
US3776303A (en) * 1971-04-27 1973-12-04 Olin Corp Heat exchanger
WO2015079391A1 (en) * 2013-11-29 2015-06-04 Ncr Logistica S.R.L. A heat exchanger and a method of realising it
WO2017080573A1 (en) * 2015-11-09 2017-05-18 Franke Technology And Trademark Ltd Heat exchanger
US20180320957A1 (en) * 2015-10-27 2018-11-08 Linde Aktiengesellschaft Low-temperature mixed--refrigerant for hydrogen precooling in large scale

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3415316A (en) * 1967-04-11 1968-12-10 Olin Mathieson Modular units and use thereof in heat exchangers
US3776303A (en) * 1971-04-27 1973-12-04 Olin Corp Heat exchanger
WO2015079391A1 (en) * 2013-11-29 2015-06-04 Ncr Logistica S.R.L. A heat exchanger and a method of realising it
US20180320957A1 (en) * 2015-10-27 2018-11-08 Linde Aktiengesellschaft Low-temperature mixed--refrigerant for hydrogen precooling in large scale
WO2017080573A1 (en) * 2015-11-09 2017-05-18 Franke Technology And Trademark Ltd Heat exchanger

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Publication number Publication date
WO2023025750A1 (en) 2023-03-02
EP4392728A1 (de) 2024-07-03

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