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
  • 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
  • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
• • 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
  • F28D7/022—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 two or more media in heat-exchange relationship being helically coiled, 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
  • 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
  • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
  • F28D2021/0066—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications with combined condensation and evaporation

Definitions

• the invention relates to the recovery of cold in the regasification of cryogenic liquids, in particular liquefied natural gas
• LNG Liquefied Natural Gas at -162 ° C and 1 bar atmospheric pressure
• LN2 Liquefied Nitrogen
• L02 Liquefied Oxygen
• the heat exchanger is for, although relatively small in comparison to the fuel energy, so valuable
• Natural gas can be transferred under atmospheric pressure after cooling to -162 ° C and subsequent removal of the heat of condensation from the gaseous to the liquid phase. This is the reduction of the volume on the
• Liquefied natural gas can thus be stored in an attractive manner and transported over long distances.
• the equally costly and value-adding process chain to be realized ranges from extraction and processing via liquefaction, storage, long-distance transport with tankers, re-storage in large tanks and repeated transport to the user until regasification. The end of this chain very often forms one
• satellite system namely a double-walled
• Vacuum-insulated LNG storage without liquefaction facility Vacuum-insulated LNG storage without liquefaction facility.
• the satellite system has a regasification device,
• LNG liquefied natural gas
• PCM Phase Change Material
• the cold of the LNG is transferred to a liquid refrigerant, which is to be used down to the temperature level of about -60 ° C, without pumping phase change and thus remains safe.
• a liquid refrigerant which is to be used down to the temperature level of about -60 ° C, without pumping phase change and thus remains safe.
• Therminol D12 a synthetic liquid based on aliphatic hydrocarbons.
• Heat transfer properties propane is preferably used as the intermediate medium.
• This heat exchanger is expediently designed as a cylinder in vertical alignment and closed at the top and bottom by dished ends.
• the container thus realized contains at least one in the upper part
• this is filled with the intermediate medium, preferably propane, which is securely encapsulated.
• the propane is in the lower part to the level of a boiling liquid and in the upper region above the filling level condensing saturated steam.
• Both surface heat exchangers are designed as tube helices.
• the heat transfer from the upper coiled tubing to the deep-frozen liquid to be evaporated is particularly effective because of the long flow path and the resulting on a circular path secondary flow in the interior of the coiled tubing.
• the largest transport resistance the reduction of which has a particularly positive effect on the entire heat transfer result.
• the use of a turbulator can further reduce this transport resistance.
• in the lower part of the cylindrical container further tube spirals protruding freely from below into the inner space, but at least one coiled tubing, are located.
• the brine gives the evaporation of the
• the cylindrical container is after its evacuation with the
• Intermediate medium preferably propane, taking into account temperature, density and mass sustainably filled so that the upper tube coils remain free at each subsequent operating state, while the lower tube coils of liquid intermediate medium in the boiling state are completely flooded.
• This distance can be calculated with the help of the material values of the intermediate medium. It corresponds approximately to the diameter of the coiled tubing.
• Boiling state are in phase equilibrium.) Approximately 9.6 bar. The density of the liquid is then about 492 kg / m 3 .
• the density of the liquid phase is then about 612 kg / m 3 .
• the following embodiments are related to the regasification of cryogenic liquefied natural gas LNG (Liquefied Natural Gas) stored in a satellite tank farm.
• LNG Liquified Natural Gas
• Heat exchangers for brine temperature levels above -60 ° C and for cooling capacities in the range below 100 kW explained in more detail with reference to drawings.
• the heat exchangers used differ in their design.
• FIG. 1 A heat exchanger according to the invention is shown in FIG. 1 as a section along its vertical system axis.
• a coiled tubing 6 and at the lower dished bottom 3 a coiled tubing 7 is arranged directly or indirectly in each case in freely projecting into the container interior.
• the attachment to the container 1 is realized only on one side.
• the intermediate medium 8 namely propane 8, which is thus securely encapsulated.
• the level 9 of the liquid intermediate medium 8 in the container 1 is adjusted so that the upper tube coil 6 is surrounded in each operating state of gaseous intermediate medium 8.1 and the lower tube coil 7 is flooded with liquid intermediate medium 8.2.
• the two coiled tubing 6 and 7 a
• the container 1 and the tube coils 6 and 7 are advantageously made of stainless steel. Thus, a sufficient Tiefkaltzähmaschine and a high
• Therminol D12 is used as a refrigerant.
• FIG. 2 Another heat exchanger according to the invention is also shown in FIG. 2 as a section along its vertical system axis.
• both the coiled tubing 6 and the coiled tubing 7 are present in multiple arrangement in the container 1 in otherwise analogous construction.
• seven tube coils 6 and 7 are arranged in each case. All other features are taken apart from structural adjustments.
• the inflow 12 of the refrigerant to the coiled tubing 7 is also carried out with the interposition of a manifold 15 directly, while the drain 13 is realized via a further manifold 16 in the lower part of the container 1.
• the two manifolds 16 may alternatively be arranged outside the container 1. It is recommended to use the headers 16 for each one-sided attachment of the coiled tubing 6 and 7 on the container 1. Depending on the conditions of use, the upper and / or lower tube coils 6 and 7 can be connected individually or in bundles.
• Heat exchanger effective heat transfer from the refrigerant to be cooled to the boiling intermediate medium 8.2 in the lower
• the natural circulation of the intermediate medium comes by the dripping of the condensate of the or the upper
• intermediate medium for example propane, gaseous, condensing
• intermediate medium for example propane, liquid or boiling

Landscapes

• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Filling Or Discharging Of Gas Storage Vessels (AREA)
• Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Priority Applications (2)

Applications Claiming Priority (4)

Publications (1)

Family

ID=59010575

Family Applications (1)

Country Status (4)

Cited By (2)

Families Citing this family (3)

Citations (7)

• 2016
  • 2016-05-18 DE DE102016006121.9A patent/DE102016006121A1/de not_active Withdrawn
  • 2016-06-17 WO PCT/DE2016/000253 patent/WO2017114518A1/de unknown
  • 2016-06-17 DE DE112016006090.4T patent/DE112016006090A5/de not_active Withdrawn
  • 2016-06-17 EP EP16742154.4A patent/EP3397912B1/de active Active
  • 2016-12-23 TW TW105142936A patent/TW201730475A/zh unknown

Patent Citations (7)

Also Published As

Similar Documents

Legal Events