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WO2009126353A2 - Détendeurs de gaz liquéfié cryogénique à flux parallèle - Google Patents

Détendeurs de gaz liquéfié cryogénique à flux parallèle Download PDF

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Publication number
WO2009126353A2
WO2009126353A2 PCT/US2009/031556 US2009031556W WO2009126353A2 WO 2009126353 A2 WO2009126353 A2 WO 2009126353A2 US 2009031556 W US2009031556 W US 2009031556W WO 2009126353 A2 WO2009126353 A2 WO 2009126353A2
Authority
WO
WIPO (PCT)
Prior art keywords
cryogenic fluid
chamber
expander
cryogenic
vessel
Prior art date
Application number
PCT/US2009/031556
Other languages
English (en)
Other versions
WO2009126353A3 (fr
Inventor
Joel V. Madison
Original Assignee
Madison Joel V
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 Madison Joel V filed Critical Madison Joel V
Priority to EP09731319.1A priority Critical patent/EP2250454B1/fr
Publication of WO2009126353A2 publication Critical patent/WO2009126353A2/fr
Publication of WO2009126353A3 publication Critical patent/WO2009126353A3/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/005—Adaptations for refrigeration plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F01D17/145—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path by means of valves, e.g. for steam turbines
    • 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
    • F25J1/0032—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 the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
    • F25J1/0042—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 the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by liquid expansion with extraction of work
    • 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
    • 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
    • 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
    • F25J2240/00—Processes or apparatus involving steps for expanding of process streams
    • F25J2240/02—Expansion of a process fluid in a work-extracting turbine (i.e. isentropic expansion), e.g. of the feed stream
    • F25J2240/04—Multiple expansion turbines 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
    • F25J2240/00—Processes or apparatus involving steps for expanding of process streams
    • F25J2240/30—Dynamic liquid or hydraulic expansion with extraction of work, e.g. single phase or two-phase turbine

Definitions

  • the present invention is directed to cryogenic liquefied gas expanders configured within one or more containment vessels with parallel flow through the expanders, where cryogenic fluid enters through a common inlet and is split between a first expander and a second expander, while expanded cryogenic fluid is generated by both expanders and exits through a common outlet.
  • Parallel flow between the liquefied gas expanders is further facilitated by a rotary control valve positioned either between the vessels or within a vessel and between the two liquefied gas expanders.
  • Cryogenic liquids are liquefied gases that are maintained in their liquid state at very low temperatures, typically below -150 0 C or -238 0 F. Different cryogens become liquids under different conditions of temperature and pressure.
  • Industrial facilities that produce, store, transport and utilize such gases make use of a variety of valves, pumps and expanders to move, control and process the liquids and gases.
  • Joule-Thomson (J-T) expansion valves are frequently used to reduce pressure within a system carrying liquefied natural gas (LNG). While J-T valves are important, they have limited value in comparison to certain types of liquefied gas expanders, which are able to reduce pressure while also reducing the enthalpy of the natural gas and generating work.
  • turbine expanders are able to reduce pressure and create rotational momentum that generates shaft torque (which reduces enthalpy). The shaft torque is then used by a generator to produce electrical power.
  • turbine expanders are frequently used to expand liquefied gas from a high pressure to a low pressure, while capturing energy generated by the expansion.
  • single-phase LNG expanders are used to enhance the performance of LNG liquefaction plants.
  • Two-phase LNG expanders are further used to reduce liquefaction costs and increase production, which has the positive benefit of extending the lifetime of depleting gas fields by generating more usable liquid from the field.
  • Figure 1 is a diagrammatic view of a single vessel containing two expanders configured to operate in parallel flow through operation of two external valves;
  • Figure 2 is a diagrammatic view of a single vessel containing two expanders configured to operate in parallel flow through operation of a rotary control valve;
  • Figure 3 is a partial cross-sectional view of a rotary control valve in accordance with the present invention.
  • Figure 4 further illustrates the rotary control valve of Figure 3 when the passages to both the lower expander and the upper expander are open;
  • Figure 5 further illustrates the rotary control valve of Figure 3 when the passages to the lower expander are open and the passages to the upper expander are closed
  • Figure 6 further illustrates the rotary control valve of Figure 3 when the passages to both the lower expander and the upper expander are closed
  • Figure 7 further illustrates the rotary control valve of Figure 3 when the passages to the lower expander are closed and the passages to the upper expander are open;
  • Figure 8 is a cross-sectional view of the multiple expander vessel of Figure 2 further illustrating operation of the rotary control valve of Figure 3 and the interaction between the expanders within the vessel,
  • the present invention is directed to cryogenic liquefied gas expanders, and more particularly to two liquefied gas expanders (herein referred to as "expanders") operating in parallel within one or more containment vessels with parallel flow through the expanders.
  • expanders two liquefied gas expanders
  • Expanders are also used in series and in parallel, where the physical arrangement is in parallel (meaning the expanders are physically located next to one another) and the flow through the expanders is in parallel.
  • expanders are used in parallel in a more compact physical arrangement, such as within a single vessel or in a serial physical arrangement, with parallel flow between the expanders.
  • a serial arrangement, parallel flow design allows for a higher flow capacity without increasing the size of the expanders, the size of the vessel(s), the size of the passages, or the diameter of the generators, thereby eliminating the need for a larger four pole generator.
  • a serial arrangement, parallel flow design also reduces the cost of the expanders (overall), reduces space requirements and reduces disruption of the LNG plant for installation and maintenance.
  • the parallel flow design of the present invention increases operational flexibility. With two expanders operating in parallel within one or more vessels, and through utilization of the rotary control valve discussed below, the range of flow and head that the expanders can operate in is much larger than is possible with a single expander or multiple expanders, running in series or otherwise. For example, in a single or multi-expander design, to turn down flow by some percentage, the operating capacity of the expander(s) must be turned down by a corresponding percentage. Running such expanders at less than 100% or near full capacity, however, compromises the efficiency of the expanders and turning them down by as much as 50% renders the expander(s) inoperable. With the parallel flow design of the present invention, a fifty percent turndown is possible by simply not running one of the expanders and other percentage variations are possible through use of the control valves to selectively restrict flow through the expanders, as further described below.
  • the serial arrangement, parallel flow design of the present invention is also much more compact than prior art designs with similar capacity.
  • the novel rotary control valve of the present invention further enhances the compactness and operational flexibility of the design by eliminating the need for external control valves, as further explained below.
  • Figure 1 provides a simplistic diagrammatic illustration of a single vessel 10 containing an expander 12 in a first chamber 13 and an expander 14 in a second chamber 15, with the,expanders 12 and 14 configured to operate in parallel flow through operation of two external valves 16 and 18 and passageways 17 and 19 between the first chamber 13 and the second chamber 15.
  • Cryogenic fluid entering the vessel 10 at point 20 would be split within the vessel 10, with approximately half of the fluid being directed to expander 12 and half to expander 14.
  • the passageways 17 and 19 can either be formed by a natural divider 22 created between the two chambers 13 and 15 by the vessel 10, as shown in Figure 1, or by positioning a plate or disk (not shown in Figure 1) between the two chambers 13 and 15.
  • the plate or disk of the divider 22 would create the passageways 17 and 19 and could be bolted between the two chambers 13 and 15, or welded, or both bolted and welded, so as to form a seal between the two chambers 13 and 15.
  • the two chambers 13 and 15 could be separate vessels that are joined together by the divider 22 to form a single vessel, so references to a single vessel, herein, are understood to include two vessels operating as a single vessel, and references to chambers are understood to include separate vessels joined together to effectively form a single vessel.
  • the plate or disk between the chambers or vessels would be formed of stainless steel or some other similarly suitable material.
  • the divider 22 and passageways 17 and 19 could be structured in such a way as to look very much like the plate 44 and accompanying passages of the rotary valve illustrated in Figure 3 when positioned so as to enable flow between both chambers at the same time. Unlike the rotary valve, however, where plate 44 (shown in Figure 3) can be turned to create multiple different flow scenarios, , as further described below, the divider 22 would be stationary at all times and only permit full flow between the two chambers 13 and 15.
  • the expanders utilized in any of the various configuration described herein could be single-phase liquefied gas expanders or two-phase liquid-vapor expanders that expand liquid or liquid and vapor, respectively, from high pressure to lower pressure, as well as fixed speed expanders or variable speed expanders, as further explained below.
  • valves 16 and 18 are utilized to regulate the parallel flow between the two expanders 12 and 14.
  • valves 16 and 18 When both valves 16 and 18 are open, fluid flows through expanders 12 and 14 along the illustrated paths. When valve 16 is open, but valve 18 is closed, fluid only flows through expander 12. When valve 16 is closed and valve 18 is open, fluid only flows through expander 14.
  • the combination of valves and expander allows the careful control of the expanders 12 and 14 within the vessel 10. Further flexibility is possible by partially opening/closing the valves 16 and 18 to control the flow • through each expander.
  • This aspect of the present invention makes it possible to control the flow through both variable speed and fixed speed expanders, without having to adjust the speed at which the expanders operate (something which, of course, was not possible with a fixed speed expander).
  • one expander would be located within a first vessel and a second expander would be located within a second vessel, with passageways formed between the two vessels so that expanded fluid created by the first expander is routed to the second vessel and around the outside of the second expander and unexpanded fluid in the first vessel is routed to the second expander in the second vessel.
  • pipes could be utilized to route the unexpanded fluid and the expanded fluid as necessary, a plate or disk as described above could be positioned between the two vessels, or a rotary valve of the type described below could be positioned between the two vessels.
  • the key is that all of the unexpanded fluid enters through the same vessel inlet with some of the unexpanded fluid in the first vessel being routed to the second vessel at the same time that expanded fluid from the first vessel is routed to the second vessel and out through a common vessel outlet, so that fluid.flow between the two vessels is in parallel, regardless of the physical arrangement between the vessels or expanders. This enables vessels to be positioned in a serial arrangement while operating in parallel, versus being positioned in parallel and operating in parallel, which requires significantly more space and is not practical in many installations.
  • Figure 2 discloses a structure similar to that of Figure 1, but in this preferred embodiment of the present invention, instead of two external valves being utilized, and additional passageways between the two chambers, a single rotary valve is used to direct fluid through one or both of the expanders, thereby further compacting the design, saving more space and cost, and reducing issues associated with externalized equipment.
  • a cryogenically submerged motor to operate a valve removes the requirement of making the motor explosion proof and makes motor or valve leakage inconsequential.
  • the vessel 10 contains the two expanders 12 and 14 and a single rotary control valve 30 positioned in-between as a divider.
  • two seals 32 positioned on either side of the valve 30, seal the valve 30 between the expanders 12 and 14 and create two sealed chambers 34 and 36 within the vessel 10, but seals are not required and two vessels could be used in place of a single vessel with two chambers.
  • a cryogenic submerged motor 33 is positioned within chamber 36 to operate the rotary control valve 30, as further illustrated with respect to Figure 3 below.
  • valve 30 in place of seals 32 between the valve 30 and the two chambers 34 and 36 (seals can pose issues at cryogenic temperatures anyway), it may be desirable to use the valve 30 as a form of divider and seal itself, especially since chamber 36 will be at a lower pressure than chamber 34.
  • Making a portion of the plate 44 (discussed below with respect to Figure 3) out of TEFLON like material (that is not affected by the temperatures within the vessel 10) will also help to seal the two chambers 34 and 36. While this may allow some leakage between the two chambers 34 and 36, it would be small and therefore not a major issue, and the cryogenic fluid would still be retained within the vessel 10.
  • the rotary control valve 30 is further illustrated in Figure 3, which provides a partial cross-sectional view of the valve 30.
  • Intake assembly 40 to the valve 30 is bolted to the output assembly (not shown in Figure 3) of expander 12.
  • the output fluid of expander 12 is directed to the outlet ports 46 so as to flow around the outside of expander 14.
  • a second set of passages 48 formed in the plate 44 are aligned with the inlet ports 50, vessel input fluid flowing around the outside of expander 12 is routed to the intake passages 52 of the intake assembly 54 of expander 14.
  • the motor 33 rotates a toothed gear 56 that engages the teeth of the plate 44 and rotates the plate 44 to the left or right.
  • the plate 44 effectively operates like a sliding gate that opens or closes the flow passages or passageways at the crossing point between the seals of the two chambers 34 and 36.
  • the plate 44 is positioned so that first set of passages 42 are aligned over the channels 45 of the intake assembly 40 so that fluid can flow out of the expander 12.
  • the second set of passages 48 are aligned over the intake passages 52 of the intake assembly 54 so fluid can flow into expander 14.
  • the plate 44 has been rotated to the left so that the second set of passages 48 are now aligned over the channels 45 of the intake assembly 40, thereby leaving expander 12 open, and the first set of passages 42 are blocked, which also closes expander 14 by blocking the intake passages 52 (represented by the dotted circle).
  • Figure 6 illustrates the plate 44 further rotated to the left, so that the first set of passages 42 and the second set of passages 48 are both closed, thereby blocking the channels 45 and the intake passages 52, and closing both expanders 12 and 14.
  • Rotating the plate 44 once more to the left causes the first set of passages 42 to be aligned with the intake passages 52, thereby opening expander 14, with the second set of passages 48 and the channels 45 being blocked, thereby closing expander 12.
  • the plate 44 can also be partially rotated so as to only partially open/close the flow through the first set of passages 42, the second set of passages 48, or both sets of passages, thereby enabling significant operational flexibility.
  • Cryogenic fluid (either in the form of liquid or liquid/vapor) enters through the vessel intake point 20 and enters an interior of the first chamber 34, where some of the fluid designated by the arrow 60 enters expander 12 (if the expander 12 is on and the valve 30 is open to expander 12), while the remaining fluid flows around the outside of expander 12, which is positioned within the first chamber 34, as designated by the arrow 62 (if the valve 30 to expander 14 is open).
  • the fluid entering the expander 12 is expanded and exits the expander 12, passes through the valve 30 and enters the interior of the second chamber 36, where it flows around the outside of expander 14.
  • the fluid flowing through the interior of the first chamber 34 and around the outside of expander 12 follows the path 62 into the valve 30 and into expander 14, where it is expanded and exits expander 14 at outlet 30.
  • the cryogenic fluid output from the expander 12 merges with the cryogenic fluid output from the expander 14 near the common vessel outlet 38.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)

Abstract

La présente invention concerne un ou plusieurs détendeurs de gaz liquéfié cryogénique conçus dans une ou plusieurs cuves de confinement à écoulement parallèle à travers les détendeurs, le fluide cryogénique entrant par une entrée commune et étant séparé entre un premier détendeur et un second détendeur, pendant que le fluide cryogénique expansé est généré par les deux détendeurs et sort par une sortie commune. L’écoulement parallèle entre les détendeurs de gaz liquéfié est ensuite facilité par une soupape de commande rotative positionnée soit entre les cuves soit entre les chambres d’une cuve et entre les deux détendeurs de gaz liquéfié.
PCT/US2009/031556 2008-01-21 2009-01-21 Détendeurs de gaz liquéfié cryogénique à flux parallèle WO2009126353A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP09731319.1A EP2250454B1 (fr) 2008-01-21 2009-01-21 Détendeurs de gaz liquéfié cryogénique à flux parallèle

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US1191408P 2008-01-21 2008-01-21
US61/011,914 2008-01-21

Publications (2)

Publication Number Publication Date
WO2009126353A2 true WO2009126353A2 (fr) 2009-10-15
WO2009126353A3 WO2009126353A3 (fr) 2009-12-30

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US (1) US20090183505A1 (fr)
EP (1) EP2250454B1 (fr)
WO (1) WO2009126353A2 (fr)

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Publication number Priority date Publication date Assignee Title
US8683824B2 (en) * 2009-04-24 2014-04-01 Ebara International Corporation Liquefied gas expander and integrated Joule-Thomson valve

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See also references of EP2250454A4

Also Published As

Publication number Publication date
EP2250454A2 (fr) 2010-11-17
WO2009126353A3 (fr) 2009-12-30
EP2250454A4 (fr) 2015-10-21
US20090183505A1 (en) 2009-07-23
EP2250454B1 (fr) 2019-03-20

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