US20130153172A1 - Method and apparatus for reducing the impact of motion in a core-in-shell heat exchanger - Google Patents

Method and apparatus for reducing the impact of motion in a core-in-shell heat exchanger Download PDF

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Publication number
US20130153172A1
US20130153172A1 US13/718,275 US201213718275A US2013153172A1 US 20130153172 A1 US20130153172 A1 US 20130153172A1 US 201213718275 A US201213718275 A US 201213718275A US 2013153172 A1 US2013153172 A1 US 2013153172A1
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United States
Prior art keywords
heat exchanger
stream
shell
separation vessel
internal volume
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Abandoned
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US13/718,275
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English (en)
Inventor
Paul R. Davies
Will T. JAMES
Shaun P. GRAVOIS
Olanrewaju M. Oshinowo
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ConocoPhillips Co
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ConocoPhillips Co
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Application filed by ConocoPhillips Co filed Critical ConocoPhillips Co
Priority to AU2012355362A priority Critical patent/AU2012355362B2/en
Priority to CN201280063617.7A priority patent/CN104024776B/zh
Priority to JP2014549209A priority patent/JP6170943B2/ja
Priority to RU2014129909A priority patent/RU2611537C2/ru
Priority to PCT/US2012/070383 priority patent/WO2013096328A1/en
Priority to US13/718,275 priority patent/US20130153172A1/en
Priority to AP2014007702A priority patent/AP2014007702A0/xx
Assigned to CONCOPHILLIPS COMPANY reassignment CONCOPHILLIPS COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: OSHINOWO, Olanrewaju M., GRAVOIS, Shaun P., DAVIES, PAUL R., JAMES, Will T.
Publication of US20130153172A1 publication Critical patent/US20130153172A1/en
Assigned to CONOCOPHILLIPS COMPANY reassignment CONOCOPHILLIPS COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DIETRICH, JORG, KAYSER, STEFAN, WANKE, RUDOLF, BRENNER, STEFFEN
Abandoned legal-status Critical Current

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    • 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
    • F25J5/00—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0017—Flooded core heat exchangers
    • 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
    • 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
    • F25J1/0022—Hydrocarbons, e.g. natural gas
    • 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
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0047—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle
    • F25J1/0052—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle by vaporising a liquid refrigerant stream
    • 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
    • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
    • F25J1/0262—Details of the cold heat exchange system
    • 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
    • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
    • F25J1/0269—Arrangement of liquefaction units or equipments fulfilling the same process step, e.g. multiple "trains" concept
    • F25J1/0271—Inter-connecting multiple cold equipments within or downstream of the cold box
    • F25J1/0272—Multiple identical heat exchangers in parallel
    • 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
    • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
    • F25J1/0275—Construction and layout of liquefaction equipments, e.g. valves, machines adapted for special use of the liquefaction unit, e.g. portable or transportable devices
    • F25J1/0277—Offshore use, e.g. during shipping
    • F25J1/0278—Unit being stationary, e.g. on floating barge or fixed platform
    • 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.
    • 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
    • F25J5/00—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants
    • F25J5/002—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger
    • F25J5/005—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger in a reboiler-condenser, e.g. within a column
    • 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
    • F25J2250/00—Details related to the use of reboiler-condensers
    • F25J2250/02—Bath type boiler-condenser using thermo-siphon effect, e.g. with natural or forced circulation or pool boiling, i.e. core-in-kettle heat exchanger
    • 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
    • F25J2250/00—Details related to the use of reboiler-condensers
    • F25J2250/20—Boiler-condenser with multiple exchanger cores in parallel or with multiple re-boiling or condensing streams
    • 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
    • F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
    • F25J2290/72—Processing device is used off-shore, e.g. on a platform or floating on a ship or barge
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P80/00—Climate change mitigation technologies for sector-wide applications
    • Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier

Definitions

  • This invention relates to a method and apparatus for reducing the effects of motion in a core-in-shell type heat exchanger.
  • Natural gas in its native form must be concentrated before it can be transported economically.
  • the use of natural gas has increased significantly in the recent past due to its environmentally-friendly, clean burning characteristics. Burning natural gas produces less carbon dioxide than any other fossil fuel, which is important since carbon dioxide emissions have been recognized as a significant factor in causing the greenhouse effect.
  • Liquefied natural gas (LNG) is likely to be used more and more in densely-populated urban areas with the increased concern over environmental issues.
  • Abundant natural gas reserves are located all over the world. Many of these gas reserves are located offshore in places that are inaccessible by land and are considered to be stranded gas reserves based on application of existing technology. Existing technical reserves of gas are being replenished faster than oil reserves, making the use of LNG more important to meeting the demands of future energy consumption. In liquid form, LNG occupies 600 times less space than natural gas in its gaseous phase. Since many areas of the world cannot be reached by pipelines due to technical, economic, or political limits, locating the LNG processing plant offshore and utilizing a nautical vessels to directly transport the LNG offshore from the processing plant to the transportation vessel can reduce initial capital expenditure and release otherwise uneconomical offshore gas reserves.
  • Floating liquefaction plants provide an off-shore alternative to on-shore liquefaction plants and alternative to costly subsea pipeline for stranded offshore reserves.
  • a floating liquefaction plant can be moored off the coast, or close to or at a gas field. It also represents a moveable asset, which can be relocated to a new site when the gas field is nearing the end of its production life, or when required by economic, environmental or political conditions.
  • a method for reducing the impact of motion in a heat exchanger includes: (a) flooding the heat exchanger with a vaporizing fluid, wherein the heat exchanger includes an internal volume defined within a shell and a plurality of spaced apart cores disposed within the internal volume of the shell; (b) introducing a hot process feed stream to an upper vessel, wherein the upper vessel is located above the heat exchanger, wherein the upper vessel is connected to the heat exchanger via a plurality of conductor pipes, wherein the conductor pipes include external pipes for connecting the upper vessel and the plurality of spaced apart cores, wherein the conductor pipes further include an internal diameter vapor riser, wherein the internal vapor riser is fixed to the top of the plurality of cores and floats inside the conductor pipe to allow for thermal expansion and contraction of the plurality of cores; (c) delivering the hot feed stream to a core within the internal volume of the shell via the conductor pipes, wherein the hot process feed stream undergoes indirect heat exchange with the vaporizing fluid
  • a method for reducing the impact of motion in a heat exchanger includes: (a) flooding the heat exchanger with a vaporizing fluid, wherein the heat exchanger includes an internal volume defined within a shell and a plurality of spaced apart cores disposed within the internal volume of the shell; (b) introducing a hot process feed stream to a separation vessel, wherein the separation vessel is located above the heat exchanger, wherein the separation vessel is connected to the heat exchanger via a plurality of external pipes; (c) delivering the hot process feed stream to a core within the internal volume of the shell via the external pipes, wherein the hot process feed stream undergoes indirect heat exchange with the vaporizing fluid thereby producing a warm liquid stream and a non-vaporized stream, wherein the non-vaporized stream is a mixture of vapor and liquid; and (d) delivering the non-vaporized stream to the separation vessel to undergo separation.
  • a method for reducing the impact of motion in a heat exchanger includes: (a) flooding the heat exchanger with a vaporizing liquid, wherein the heat exchanger includes an internal volume defined within a shell and a plurality of spaced apart cores disposed within the internal volume of the shell; (b) introducing a hot process feed stream to a separation vessel, wherein the separation vessel is located at an elevation higher than the heat exchanger, wherein the separation vessel includes a liquid outlet and a vapor inlet; (c) delivering the hot feed stream to a core within the internal volume of the shell at or near the top of the core via the liquid outlet, wherein the hot feed stream undergoes indirect heat exchange with the vaporizing fluid thereby producing a warm liquid stream and a non-vaporized stream, wherein the non-vaporized stream is a mixture of vapor and liquid; and (d) delivering the non-vaporized stream to the separation vessel to undergo separation.
  • an apparatus in a further embodiment, includes: (a) a heat exchanger, wherein the heat exchanger includes an internal volume defined within a shell and a plurality of spaced apart cores disposed within the internal volume of the shell, wherein the internal volume is flooded with a vaporizing fluid; and (b) a separation vessel connected to the heat exchanger, wherein the separation vessel is located at higher elevation than the heat exchanger, wherein the separation vessel is connected to the heat exchanger in such a manner so as to deliver a hot feed stream to heat exchanger and the receive a non-vaporizing stream from the heat exchanger.
  • FIG. 1 is a schematic of a core-in-shell heat exchanger, according to one embodiment of the invention involving an external horizontal separator.
  • FIG. 2 is a schematic of a core-in-shell heat exchanger, according to one embodiment of the invention involving a vertical separator.
  • FIG. 3 is a schematic of a core-in-shell heat exchanger, according to one embodiment of the invention involving an external vertical separator.
  • a heat exchanger 10 generally includes a shell 12 and a plurality of spaced apart cores, i.e., a first core 16 , a second core 18 , and a third core 20 within the shell 12 .
  • the plurality of spaced apart cores within the heat exchanger 10 includes at least one core.
  • the heat exchanger is horizontally disposed; however, the heat exchanger may be positioned in any commercially operable manner, such as vertically, for example.
  • the plurality of spaced apart cores within the shell 12 are completely submerged, i.e., flooded, in vaporizing fluid, i.e., a liquid refrigerant.
  • a principle design of the core-in-shell heat exchanger provides cross exchange of a hot process feed stream against the colder vaporizing fluid.
  • the vaporizing fluid resides in a pressure vessel where brazed aluminum compact exchanger cores are mounted and completely submerged in the vaporizing fluid which is at or near its boiling point.
  • the liquid is drawn into the bottom face of the exchanger where it contacts the hotter surfaces within the core.
  • the vaporizing fluid then transfers heat through the exchanger core channels. The majority of the heat transfer is from the latent heat of vaporization of the vaporizing fluid.
  • the hot process feed stream is cooled or condensed as it passes through the opposite side of the channels in the exchanger cores.
  • thermosiphon effect is a passive fluid transfer phenomenon resulting from natural convective thermal forces.
  • the vaporizing fluid is heated and the vaporizing fluid density decreases.
  • fresh liquid is drawn in. This results in a natural circulation of the vaporizing fluid into the core channels induced by the thermal gradient inside the core. Not all vaporizing fluid in the channel is vaporized and a mixture of liquid and vapors typically are transported up through the exchanger core channels and expelled through the top of the core.
  • thermosiphon circulation effect in the core is enhanced or impaired by the external hydraulic pressure (level differences) between the effective liquid levels inside the core versus the liquid level outside the core.
  • the driving force for the transfer of the liquid into the exchanger core is decreased, and the effective heat transfer is reduced.
  • the vaporizing fluid circulation stops due to the loss of the thermosiphon effect which results in the loss of heat transfer. If the heat exchanger is operated with a liquid level higher than the core, i.e., flooded, the heat transferred is impaired further as the vapor produced in the core has to overcome the additional head to escape from the core.
  • an upper vessel 30 is utilized, such as depicted in FIG. 1 .
  • the upper vessel 30 is located above the heat exchanger 10 and includes a plurality of vapor disengaging conductor pipes 32 connecting the upper vessel 30 to the shell 12 of the heat exchanger 10 .
  • the conductor pipes 32 consist of an external pipe connecting the two vessels. Inside the conductor pipes resides an internal smaller diameter vapor riser.
  • the vapor riser not shown in FIG. 1 , is fixed to the top of the core, 16 , 18 , 20 and floats inside the conductor pipe 32 so as to allow for thermal expansion and contraction of the exchanger cores 16 , 18 , 20 .
  • the vapor riser terminates inside the upper vessel 30 above the normal liquid level of the upper vessel 30 .
  • the vapor riser is fastened to the top of the cores 16 , 18 , 20 via a top manifold on the cores 16 , 18 , 20 so as to collect the non-vaporized stream exiting the internal cores 16 , 18 , or 20 .
  • the non-vaporized stream is introduced to the upper vessel 30 .
  • the non-vaporized stream is then separated in the upper vessel 30 so that liquid flows down the annulus (between the outside of the vapor riser and the inside of the conductor pipe) of the conductor pipe 32 into the shell 12 of the heat exchanger 10 via the plurality of conductor pipes 32 .
  • the hot process feed streams are delivered to the plurality of spaced apart cores via externally connecting pipes in order to separately undergo indirect heat exchanger with the vaporizing fluid.
  • the plurality of spaced apart cores each receives a separate hot process feed stream, allowing for simultaneous indirect heat transfer between the vaporizing fluid and the separate hot process feed streams.
  • the vaporizing fluid and the hot process feed stream flow in a cross-current manner in alternating plate and fin channels inside each core.
  • the vaporizing fluid is vaporized in the core resulting in a mixture of vapor and liquid, i.e., the non-vaporized stream, existing the top of the core, which must be disengaged in the upper vessel 30 .
  • the vapor risers are designed such that the non-vaporized stream exiting the core remains a mixed phase stream and are routed inside the inner pipe connected via manifold from the top of the plurality of cores 16 , 18 , 20 of the heat exchanger 10 and terminates inside the upper vessel 30 above the normal liquid level in the upper vessel 30 .
  • the vapor from non-vaporized stream disengages in the upper vessel 30 and is mixed with the vapor from the non-vaporized stream entering the upper chamber 30 .
  • Liquid separates from the hot process feed stream and mixes with the re-circulating liquid from the vapor risers and flows in the outer annulus of the conductor pipes 32 to the bottom of the heat exchanger.
  • the upper vessel includes slosh suppressing baffles to minimize liquid surface movement.
  • a separation vessel 40 can be utilized to overcome the effects of a flooded heat exchanger to ensure disengagement of the non-vaporized stream, as depicted in FIG. 2 .
  • the separation vessel 40 is vertically disposed above the heat exchanger 10 and includes a plurality of conductor pipes 42 connected to the heat exchanger 10 .
  • the non-vaporized stream is introduced to the separation vessel 40 .
  • the vapor and liquid in non-vaporized stream is separated in the separation vessel 40 and the liquid flows through the external separation vessel to the heat exchanger 10 via the plurality of conductor pipes 42 through the bottom of the separation vessel 40 .
  • the vapor risers within the conductor pipes are designed such that the non-vaporized liquid vapor mixture exiting the core remains a mixed two phase stream and are routed inside the inner pipe connected via a manifold from the top of the plurality of cores 16 , 18 , 20 and terminates inside the separation vessel 40 above the normal liquid level in the horizontal return header 43 connected to the vapor space of the separation vessel 40 .
  • the vapor from the plurality of cores 16 , 18 , 20 disengages in the separation vessel 40 and is mixed with the vapor from the non-vaporized stream entering the separation vessel 40 and exits the top of the separation vessel 40 .
  • Re-circulating liquid is returned to the bottom of the shell 10 via the annulus of the conductor pipes or via the bottom of the separation vessel 40 .
  • the hot process feed streams are delivered to the plurality of spaced apart cores via externally connecting pipes in order to separately undergo indirect heat exchanger with the vaporizing fluid.
  • the plurality of spaced apart cores each receives a separate hot process feed stream, allowing for simultaneous indirect heat transfer between the vaporizing fluid and the hot process feed streams.
  • the vaporizing fluid and the hot process feed stream flow in a cross-current manner in alternating plate and fin channels inside each core.
  • the resulting non-vaporized stream is disengaged in the plurality of external pipes 42 .
  • the liquid stream is re-circulated back into the heat exchanger 10 via the external side of the annulus pipe inside the conductor pipe 42 .
  • the vapor stream flows through the external pipes 42 into the separation vessel 40 .
  • a liquid level is maintained in the separation vessel via an external liquid level control valve. Since the separation vessel 40 is vertical, motion suppression may not be required. However, in an embodiment, slosh suppressing baffles are utilized in the separation vessel.
  • a separation vessel 50 located at an elevation higher to or at the same elevation as than the heat exchanger 10 can be utilized to overcome the effects of motion and is an alternative method to flood completely flooding the heat exchanger 10 .
  • the separation vessel 50 is located to the side of the heat exchanger 10 and includes a feed liquid outlet pipe 52 and a plurality of vapor disengaging conductor inlet pipes 54 .
  • a hot process feed stream, i.e., a mixed phase feed stream, is introduced to the separation vessel 50 .
  • the vaporizing fluid is delivered to the heat exchangers 10 from the separation vessel 50 through one or more free drains via the feed outlet pipe 52 .
  • the hot process feed streams are delivered to the plurality of spaced apart cores via externally connecting pipes in order to separately undergo indirect heat exchanger with the vaporizing fluid.
  • the plurality of spaced apart cores each receives a separate feed stream, allowing for simultaneous indirect heat transfer between the vaporizing fluid and the separate feed streams.
  • the vaporizing fluid and the feed stream flow in a cross-current manner in alternating plate and fin channels inside each core.
  • the resulting non-vaporized stream is disengaged in the plurality of vapor inlet pipes 54 .
  • the liquid stream is re-circulated back into the heat exchanger 10 .
  • the vapor stream flows through the vapor disengaging conductor inlet pipes into the separation vessel 50 .
  • a liquid level is maintained in the separation vessel 50 via an external liquid level control valve. Since the separation vessel 50 is vertical, motion suppression may not be required. However, in an embodiment, slosh suppressing baffles are utilized in the separation vessel 50 .

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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)
  • Ocean & Marine Engineering (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
US13/718,275 2011-12-20 2012-12-18 Method and apparatus for reducing the impact of motion in a core-in-shell heat exchanger Abandoned US20130153172A1 (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
AU2012355362A AU2012355362B2 (en) 2011-12-20 2012-12-18 Method and apparatus for reducing the impact of motion in a core-in-shell heat exchanger
CN201280063617.7A CN104024776B (zh) 2011-12-20 2012-12-18 用于减小在芯壳式热交换器中的运动的影响的方法和装置
JP2014549209A JP6170943B2 (ja) 2011-12-20 2012-12-18 シェル内コア熱交換器内の動きの影響を低減するための方法、および装置
RU2014129909A RU2611537C2 (ru) 2011-12-20 2012-12-18 Способ и устройство для уменьшения влияния движения в теплообменнике типа "сердцевина-оболочка"
PCT/US2012/070383 WO2013096328A1 (en) 2011-12-20 2012-12-18 Method and apparatus for reducing the impact of motion in a core-in-shell heat exchanger
US13/718,275 US20130153172A1 (en) 2011-12-20 2012-12-18 Method and apparatus for reducing the impact of motion in a core-in-shell heat exchanger
AP2014007702A AP2014007702A0 (en) 2011-12-20 2012-12-18 Method and apparatus for reducing the impact of motion in a core-in-shell heat exchanger

Applications Claiming Priority (2)

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US201161578144P 2011-12-20 2011-12-20
US13/718,275 US20130153172A1 (en) 2011-12-20 2012-12-18 Method and apparatus for reducing the impact of motion in a core-in-shell heat exchanger

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US13/718,275 Abandoned US20130153172A1 (en) 2011-12-20 2012-12-18 Method and apparatus for reducing the impact of motion in a core-in-shell heat exchanger

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US (1) US20130153172A1 (enExample)
EP (1) EP2795216B1 (enExample)
JP (1) JP6170943B2 (enExample)
CN (1) CN104024776B (enExample)
AP (1) AP2014007702A0 (enExample)
AU (1) AU2012355362B2 (enExample)
ES (1) ES2762736T3 (enExample)
RU (1) RU2611537C2 (enExample)
WO (1) WO2013096328A1 (enExample)

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CA3229821A1 (en) * 2021-09-02 2023-03-09 Conocophillips Company Formed plate core-in-shell and multi-pass exchangers
CN119585584A (zh) * 2022-07-22 2025-03-07 气体产品与化学公司 具有降低的压降的盘管式热交换器

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US2720082A (en) * 1952-02-04 1955-10-11 N A Hardin Multiple unit barge having an expansion chamber communicating with plural storage tanks
US2928254A (en) * 1954-09-20 1960-03-15 Garrett Corp Storage tank for low temperature liquids
GB918920A (en) * 1959-03-04 1963-02-20 Honeywell Regulator Co Improvements in or relating to methods and apparatus for butt welding fine metal filaments
US3103206A (en) * 1961-12-26 1963-09-10 Combustion Eng Shell and tube type vapor generating unit
US3521605A (en) * 1968-07-05 1970-07-28 Blaw Knox Co Forced recirculation evaporator
US3563308A (en) * 1969-04-21 1971-02-16 Stewart Warner Corp Submerged core heat exchanger
GB1299643A (en) * 1969-04-26 1972-12-13 Messer Griesheim Gmbh Evaporator-condenser apparatus
US3583370A (en) * 1969-08-22 1971-06-08 J F Pritchard And Co Shroud for fire-tube boiler
GB1515631A (en) * 1976-01-30 1978-06-28 Raffinage Cie Francaise Tank for storing liquefied gas and utilisation of said tank for storing butane
US5667005A (en) * 1994-04-04 1997-09-16 Jgc Corporation Heat exchanging unit and heat exchanging apparatus
US6158238A (en) * 1996-09-04 2000-12-12 Abb Power Oy Arrangement for transferring heating and cooling power
FR2797943A1 (fr) * 1999-08-24 2001-03-02 Air Liquide Appareil a circulation de fluide
US20010030042A1 (en) * 2000-04-13 2001-10-18 L' Air Liquide, Societe Anonyme Pour L' Etude Et L' Exploitation Des Procedes Georges Claude Reboiler/condenser heat exchanger of the bath type
US6918433B2 (en) * 2000-08-23 2005-07-19 Vahterus Oy Heat exchanger with plate structure
US20050039486A1 (en) * 2002-01-17 2005-02-24 York Refrigeration Aps Submerged evaporator with integrated heat exchanger
JP2003336933A (ja) * 2002-05-17 2003-11-28 Takuma Co Ltd 満液二重管式の蒸発器及びアンモニア吸収式冷凍機
US7073572B2 (en) * 2003-06-18 2006-07-11 Zahid Hussain Ayub Flooded evaporator with various kinds of tubes
US20080041096A1 (en) * 2005-04-06 2008-02-21 Mayekawa Mfg. Co., Ltd. Flooded evaporator
WO2008112549A2 (en) * 2007-03-09 2008-09-18 Johnson Controls Technology Company Heat exchanger
US20100319877A1 (en) * 2009-06-23 2010-12-23 Conocophillips Company Removable Flow Diversion Baffles for Liquefied Natural Gas Heat Exchangers
US20120175091A1 (en) * 2010-12-30 2012-07-12 Linde Aktiengesellschaft Distribution system and heat exchanger apparatus

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015134188A1 (en) * 2014-03-07 2015-09-11 Conocophillips Company Heat exchanger system with mono-cyclone inline separator
AU2015225689B2 (en) * 2014-03-07 2019-01-03 Conocophillips Company Heat exchanger system with mono-cyclone inline separator
US10488104B2 (en) 2014-03-07 2019-11-26 Conocophillips Company Heat exchanger system with mono-cyclone inline separator

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WO2013096328A1 (en) 2013-06-27
EP2795216A4 (en) 2016-05-18
JP2015510572A (ja) 2015-04-09
JP6170943B2 (ja) 2017-07-26
EP2795216A1 (en) 2014-10-29
EP2795216B1 (en) 2019-11-20
AU2012355362B2 (en) 2017-02-02
ES2762736T3 (es) 2020-05-25
RU2014129909A (ru) 2016-02-20
CN104024776B (zh) 2016-08-17
CN104024776A (zh) 2014-09-03
AU2012355362A1 (en) 2014-06-12
RU2611537C2 (ru) 2017-02-28
AP2014007702A0 (en) 2014-06-30

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