EP2604960A1 - Procédé de fonctionnement d'un compresseur et système et procédé pour la production de flux d'hydrocarbures liquéfié - Google Patents

Procédé de fonctionnement d'un compresseur et système et procédé pour la production de flux d'hydrocarbures liquéfié Download PDF

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Publication number
EP2604960A1
EP2604960A1 EP11193688.6A EP11193688A EP2604960A1 EP 2604960 A1 EP2604960 A1 EP 2604960A1 EP 11193688 A EP11193688 A EP 11193688A EP 2604960 A1 EP2604960 A1 EP 2604960A1
Authority
EP
European Patent Office
Prior art keywords
compressor
refrigerant
guide vanes
inlet guide
hydrocarbon stream
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Withdrawn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
EP11193688.6A
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German (de)
English (en)
Inventor
Michiel Gijsbert Van Aken
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.)
Shell Internationale Research Maatschappij BV
Original Assignee
Shell Internationale Research Maatschappij 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 Shell Internationale Research Maatschappij BV filed Critical Shell Internationale Research Maatschappij BV
Priority to EP11193688.6A priority Critical patent/EP2604960A1/fr
Priority to CA2859147A priority patent/CA2859147C/fr
Priority to CN201280061508.1A priority patent/CN104350345A/zh
Priority to PCT/EP2012/075314 priority patent/WO2013087740A2/fr
Priority to KR1020147018666A priority patent/KR20140112496A/ko
Priority to AU2012324009A priority patent/AU2012324009B2/en
Priority to AP2014007627A priority patent/AP2014007627A0/xx
Priority to US14/365,171 priority patent/US20140311183A1/en
Priority to RU2014128901A priority patent/RU2621591C2/ru
Publication of EP2604960A1 publication Critical patent/EP2604960A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/002—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by varying geometry within the pumps, e.g. by adjusting vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0246—Surge control by varying geometry within the pumps, e.g. by adjusting vanes
    • 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.
    • F25J1/0281—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc. characterised by the type of prime driver, e.g. hot gas expander
    • F25J1/0284—Electrical motor as the prime mechanical driver
    • 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.
    • F25J1/0298—Safety aspects and control of the refrigerant compression system, e.g. anti-surge control
    • 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
    • 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
    • F25J2280/00—Control of the process or apparatus
    • F25J2280/20—Control for stopping, deriming or defrosting after an emergency shut-down of the installation or for back up system

Definitions

  • the present invention relates to a method of producing a liquefied hydrocarbon stream.
  • the present invention relates to a system for producing a liquefied hydrocarbon stream.
  • the present invention relates to a method of operating a compressor.
  • LNG liquefied natural gas
  • natural gas can be stored, and transported over long distances, more readily in the form of LNG than in gaseous form, because as LNG it occupies a smaller volume and does not need to be stored at a high pressure.
  • US pre-grant patent application publication No. 2010/0257895 describes an all electric LNG plant wherein LNG is produced, in which compressors in the form of refrigerant compressors are employed to refrigerate the natural gas.
  • the refrigerant compressors are driven by electric motors.
  • a power plant supplies the electrical power for these motors.
  • the power plant contains a plurality of power generation units, each based on an electric generator driven by a gas or steam turbine.
  • the LNG production process will fail and it can take at least a number of hours before the refrigerant compressor(s) have started up again and before the LNG production process has regained it stability of operation.
  • US 2010/0257895 further proposes that in the event of the failure of a power generation unit in the power plant, the (rotational) speed of the compressor drive will preferably be lowered if a previously determined overall positive load reserve is smaller than the power which was being supplied by the power generation unit before its failure.
  • the quadratic load characteristic curve of a turbine compressor the power drawn from the electric motors reduces as the cube of the rotational speed. Only if the actual energy demand of the LNG plant is not covered even taking into account the reduction in the compressor drive speed, it is expedient to switch off at least one predetermined electrical consumer in the gas liquefaction plant.
  • the present invention provides a method of producing a liquefied hydrocarbon stream, comprising:
  • the invention provides a system for producing a liquefied hydrocarbon stream, comprising:
  • the invention provides a method of operating a compressor, comprising:
  • the present disclosure describes methods and systems for producing a liquefied hydrocarbon stream.
  • a compressor is employed which is driven by an electric motor. At least part of a fluid is compressed in the compressor.
  • the compressor has variable inlet guide vanes of which an angle can be adjusted.
  • the electric motor is powered using a power supply network, and a signal representative of a condition of the power supply network is monitored. From the signal, it is automatically determined whether additional load shedding is needed, by comparing the signal to a predetermined criterion.
  • the variable inlet guide vanes angle are automatically adjusted when the criterion is satisfied and additional load shedding is needed, thereby automatically reducing the loading of the compressor.
  • the power demand can be reduced without relying on reducing the motor speed. Therefore, the presently proposed method of load shedding can be employed irrespective of whether a variable speed electric drive is used or a fixed speed electric drive.
  • inertia of the rotating mass such as rotating parts of the motor, the compressor and the drive shaft, does not influence the response time of a load shedding action.
  • Inlet guide vanes have much less inertia than the rotating parts of the motor/compressor system, and therefore it is envisaged that the response time associated with adjusting the variable inlet guide vanes can be much lower.
  • the compressor is unloaded by adjusting the variable inlet guide vanes angle when the monitored signal indicates that the available power drops below a predetermined value.
  • the condition of the power supply network represented by the signal may thus represent power available on the power supply network relative to power being consumed, whereby the predetermined criterion is satisfied when the available power, according to the monitored signal, drops below a predetermined value.
  • the compressor is provided in the form of a refrigerant compressor, whereby the fluid is a refrigerant fluid, such as may be employed in a system and/or process for producing a liquefied hydrocarbon stream.
  • the proposed load shedding method can also be used to prevent overloading that could result from an increase in ambient temperature. This may be useful particularly if the compressor is provided in the form of a refrigerant compressor employed for compressing at least part of a refrigerant fluid, as may be done in the course of operating a process of producing as liquefied hydrocarbon stream.
  • An increase in ambient temperature generally increases the power demand for liquefying the hydrocarbon stream.
  • the power supply network is powered via one or more gas turbines, the available power will reduce as a result of the increase in ambient temperature.
  • the proposed load shedding method can be used in connection with compressors relying on so-called "island-mode" power generation, where the power supply network is powered by a dedicated power plant, as well as those powered by imported power such as imported power from a domestic grid or from an industrial grid to which other consumers of power are connected as well.
  • the compressor comprises variable inlet guide vanes of which an angle can be adjusted
  • implementation of the proposed load shedding method does not require significant adaptations of equipment. Implementation may be achieved by changing the existing control system which is typically already in place for controlling the inlet guide vane settings, or by adding a dedicated control system.
  • Figure 1 illustrates the method of operating the compressor in the context of a method and system for producing a liquefied hydrocarbon stream.
  • the teachings provided herein below regarding the operation of the compressor are not necessarily restricted to, or limited to, embodiments wherein the compressor is a refrigerant compressor and/or wherein the fluid is a refrigerant fluid.
  • the system illustrated in Figure 1 employs at least one refrigerant circuit, including a first refrigerant circuit 100 arranged to circulate a refrigerant fluid 110.
  • Each of the at least one refrigerant circuits comprises a compressor in the form of a refrigerant compressor 120, for compressing at least part of the refrigerant fluid 110 being circulated in the refrigerant circuit 100.
  • Each refrigerant compressor is engaged with an electric motor 130, typically via a mechanical drive shaft 125 extending between the respective refrigerant compressor 120 and the electric motor 130 to drive the rotor of the respective refrigerant compressor 120 into rotation.
  • the electric motor 130 is connected to a power supply network 400, for powering the electric motor 130.
  • the power supply network comprises a power source, typically in the form of a power plant 410 and a distribution network 420 connected to the power source.
  • the power plant can be of the "island-mode" type, which is a dedicated power plant for powering the hydrocarbon liquefaction facility, or it can be an external power source from which power is imported into the facility.
  • the distribution network 420 may be connected to a power busbar 430, arranged to feed power to the at least one electric motor 130 via a power feed line 140.
  • the at least one refrigerant circuit comprises an optional second refrigerant circuit 200 as well, to circulate a second refrigerant fluid 210. It comprises a second refrigerant compressor 220; a second electric motor 230; a second power feed line 240; and a second mechanical drive shaft 125 all similarly interrelated as described above with reference to the first refrigerant circuit 100.
  • the system depicted in Figure 1 further comprises a heat exchanger train 300.
  • the heat exchanger train 300 is very schematically shown, as many different types of such heat exchanger trains are known in the art.
  • the heat exchanger train 300 is arranged to remove heat from an initially vaporous hydrocarbon stream 10, thereby condensing at least part of the initially vaporous hydrocarbon stream 10 to form a liquefied hydrocarbon stream 90.
  • the heat exchanger train typically comprises at least one heat exchanger that is arranged to accommodate at least said part of the initially vaporous hydrocarbon stream 10 in a mutual heat exchanging relationship with at least part of the refrigerant fluid 110 circulating through the refrigerant circuit 100.
  • the compressor(s) may be of any type that is provided with variable inlet guide vanes, including axial compressors (for example the AN 200 axial compressor manufactured by General Electric) and centrifugal compressors.
  • axial compressors for example the AN 200 axial compressor manufactured by General Electric
  • centrifugal compressors for example the AN 200 axial compressor manufactured by General Electric
  • Inlet guide vanes are often installed on commercially available refrigerant compressors to increase efficiency and to extend the operating envelope.
  • Inlet guide vanes are typically installed on the first compression stage, but for instance in case of integrally geared compressors, with multiple compressor stages, inlet guide vanes can also be installed on one or more subsequent stages such as the second stage.
  • Inlet guide vanes are typically provided in the form of radially positioned aerofoils in the vapour flow of the compressor.
  • the inlet guide vanes are positioned inside the suction duct.
  • Such inlet guide vanes serve to guide the refrigerant vapour into the subsequent compression stage at the most efficient direction onto the vanes or impellers of the subsequent compression stage.
  • Variable inlet guide vanes such as may be employed in the context of the present invention, are normally rotatable about their mounting axes. Under normal operating conditions, different refrigerant entry speeds can be accommodated by rotating the variable inlet guide vanes into different positions. Rotation may be imparted on the variable inlet guide vanes by a vane adjustment mechanism coupled to an actuator.
  • the invention is expressly not limited to any particular type of inlet guidvane geometry and or vane adjustment mechanism.
  • there are various suitable ways for acting on the vanes including rotating ring concepts, lever concepts, hydraulic pistons concepts, all acting on the variable inlet guide vanes.
  • Examples of variable inlet guide vanes and possible mechanisms for adjusting their angle are shown in for instance US patent application publication 2010/0172745 and US patent 7,520,716 .
  • the vapour flows generally inwardly towards the rotating axis of the compressor.
  • US patent application publication 2010/0329898 shows an example wherein the vapour generally flows axially, in the direction along the rotating axis.
  • US patent application publications 2010/0172745 and 2010/0329898 , and US patent 7,520,716 are incorporated in the present disclosure by reference.
  • variable inlet guide vanes of a centrifugal compressor derived from US patent application publication 2010/0172745
  • Figure 2 An embodiment of variable inlet guide vanes of a centrifugal compressor, derived from US patent application publication 2010/0172745 , is shown in Figure 2 as an illustrative non-limiting example. It comprises a vane adjustment mechanism employing a rotating ring 13 provided with a plurality of elongated slots 31, and inlet guide vanes 11 positioned around a circumference of the rotating ring 13.
  • the inlet guide vanes 11 are pivotably attached to a base plate (not shown, in the interest of clarity), such that each one of the inlet guide vanes 11 can pivot around a shaft 45.
  • the inlet guide vanes 11 are each coupled to an end of one of a plurality of lever arms 43 by the shaft 45.
  • Each lever arm 43 is provided with an outwardly protruding pin 35 in a direction perpendicular to a plane of rotation of the lever arms 43 around their shafts 45.
  • Each pin 35 is configured to be positioned within one of the elongated slots 31.
  • the vane adjustment mechanism also includes a rack and pinion drive mechanism 21 configured to drive one of the plurality of inlet guide vanes 11, thereby creating a drive vane 47.
  • the rack and pinion drive mechanism includes a pinion 53 coupled to an elongated shaft 55 of the drive vane 47, which replaces the shaft 45, and a rack 57.
  • the rack 57 includes a plurality of teeth 59 that is configured to engage with a plurality of teeth 61 on the pinion 53, thereby operationally coupling the rack 57 to the pinion 53.
  • An end of the rack 57 is coupled to a drive shaft 23, which may be actuated by for instance hydraulic cylinder (not shown).
  • the drive shaft 23 is arranged to impart a linear motion 24 to the rack 57, which is converted to rotational motion 25 in the pinion 53 thereby rotating drive vane 47 relative to the base plate.
  • Drive vane 47 transfers torque to the rotating ring 13 due to the positioning of each pin 35 on each lever arm 43 within the associate elongated slot 31 of the rotating ring 13 with which the pin 35 interacts.
  • the torque is thereby transmitted to the remaining inlet guide vanes 11, as shown in Figure 2 , whereby the respective inlet guide vanes 11 are caused to synchronously change their angular position by the same amount.
  • the variable inlet guide vanes angle ⁇ compared to a reference position 16 can be adjusted.
  • the radial position is taken to be the reference position 16 as an example, but any suitable reference position can be selected.
  • the system is further provided with a load shedding controller C.
  • the load shedding controller C is arranged to monitor a signal that is representative of the available power on the power supply network relative to the power being consumed, and to adjust the variable inlet guide vanes angle when the available power, as monitored, drops below a predetermined value.
  • the variable inlet guide vanes angle is adjusted to a position wherein the refrigerant compressor is unloaded relative to the loading in a previous condition whereby the variable inlet guide vanes angle was in a previous position.
  • the controller C may interact with the actuator of the compressor 120.
  • a suitable signal to monitor is the network frequency.
  • the network frequency which may be defined as the frequency of the overall system associated with the power network (including the active electric generators and all the running loads that consume power), generally depends directly on the amount of power that the generators can deliver to the system compared to the power being demanded for consumption. Gradual or sudden downward changes in generation capacity result in frequency decline.
  • the network frequency is thus a good indicator for the need of load shedding, which is particularly suitable in combination with island mode power generation.
  • the controller C interacts with the actuator of the compressor 120 so as to halt the drop in network frequency.
  • the signal may suitably be an external signal, generated by the power provider or one of the power providers providing power to the network, to request load shedding.
  • variable inlet guide vanes angle are preferably adjusted whereby the refrigerant compressor is unloaded by a portion of the original load that is equal to or greater than the power generation deficiency.
  • the balance between power generation and the power demand will be restored where after the power network can continue its stable operation.
  • the system may further comprise a process controller PC for controlling the production of the liquefied hydrocarbon stream 90. It may advantageously be arranged to maintain the variable inlet guide vanes at an optimized target angle, to optimize one or both of efficiency and operating envelope of the refrigerant compressor 120 when the available power as monitored is at or above the predetermined value.
  • the load shedding controller C can be a separate dedicated controller unit or it can be integrated with another controller, for instance one that is arranged to control also other aspects of the system, or it can be a hybrid controller whereby selected parts of the load shedding controller C are provided as a separate controller and other parts are provided integrated with the other controller.
  • the other controller can be the process controller PC.
  • the system described above may be operated as follows.
  • the refrigerant fluid 110 is circulated through the refrigerant circuit 100. In the course of this circulating, at least part of the refrigerant fluid 100 is compressed in the refrigerant compressor 120 to form a compressed refrigerant.
  • the refrigerant compressor 120 is driven by the electric motor 130, which typically imparts a rotational motion to the mechanical drive shaft 125 about its longitudinal axis.
  • the electric motor 130 is powered using power from the power supply network 400.
  • the compressed refrigerant is passed to the heat exchanger train 300, where it is typically allowed to expand to a lower pressure and evaporate by receiving heat from at least an initially vaporous hydrocarbon stream 10. In many cases, but this is not a requirement for every type of heat exchanger train 300, the compressed refrigerant is condensed and preferably subcooled before it is allowed to expand to said lower pressure.
  • the evaporated refrigerant is led back from the heat exchanger train 300 to the refrigerant compressor 120, to be recompressed. This completes one cycle in the refrigerant circuit 100.
  • heat is removed from the initially vaporous hydrocarbon stream 10 by at least part of the evaporating refrigerant, by heat exchanging at least said part of the initially vaporous hydrocarbon stream 10 against said at least part of the refrigerant fluid circulating through the refrigerant circuit 100.
  • at least part of the initially vaporous hydrocarbon stream 10 is condensed as a result of removing heat from it by the refrigerant fluid 120 and optional second and further refrigerant fluids, to form the liquefied hydrocarbon stream 90.
  • variable inlet guide vanes are set manually by the operator or automated by the process controller PC and/or a compressor anti surge controller.
  • the variable inlet guide vanes are set at a selected angle, for instance to achieve a desired operating window.
  • variable inlet guide vanes can be maintained at the selected angle or moved to another selected angle as desired as long as the available power as monitored is at or above a predetermined value.
  • the variable inlet guide vanes are maintained at an optimized target angle to optimize one or both of efficiency and operating envelope of the refrigerant compressor as long as the available power as monitored is at or above the predetermined value.
  • the load shedding controller reacts by adjusting the variable inlet guide vanes angle, thereby unloading the refrigerant compressor 120. This can be done by quickly changing the angle to a position different from the selected angle. If the selected angle was at the optimized target angle, which would be the case in preferred embodiments of operation, the unloading of the refrigerant compressor 120 is achieved by deliberately changing the variable inlet guide vanes angle away from the optimized target angle.
  • variable inlet guide vanes which in accordance with convention in the art corresponds to moving the position of the variable inlet guide vanes to increasingly negative angles, whereby 0° corresponds to the optimized target angle.
  • the heat exchanger train 300 in the present specification has been depicted very schematically. It can represent any suitable hydrocarbon liquefaction process, in particular any natural gas liquefaction process producing liquefied natural gas, and the invention is not limited by the specific choice of heat exchanger train.
  • suitable heat exchanger trains are derivable from single refrigerant cycle processes (usually single mixed refrigerant - SMR - processes, such as PRICO described in the paper " LNG Production on floating platforms” by K R Johnsen and P Christiansen, presented at Gastech 1998 (Dubai ), but also possible is a single component refrigerant such as for instance the BHP-cLNG process also described in the afore-mentioned paper by Johnsen and Christiansen); double refrigerant cycle processes (for instance the much applied Propane-Mixed-Refrigerant process, often abbreviated C3MR, such as described in for instance US Patent 4,404,008 , or for instance double mixed refrigerant - DMR - processes of which an example is described in US Patent 6,658,891 , or for instance two-cycle processes wherein each refrigerant cycle contains a single component refrigerant); and processes based on three or more compressor trains for three or more refrigeration cycles (an example is described in US Patent 7,114,35
  • the initially vaporous hydrocarbon stream 10 to be refrigerated, and ultimately preferably liquefied may be derived from any suitable gas stream to be refrigerated and optionally liquefied.
  • An often used example is a natural gas stream, obtained from natural gas or petroleum reservoirs or coal beds.
  • the initially vaporous hydrocarbon stream 10 may also be obtained from another source, including as an example a synthetic source such as a Fischer-Tropsch process.
  • the initially vaporous hydrocarbon stream 10 is a natural gas stream, it is usually comprised substantially of methane.
  • the gaseous hydrocarbon stream 10 comprises at least 50 mol% methane, more preferably at least 80 mol% methane.
  • natural gas may contain varying amounts of hydrocarbons heavier than methane such as in particular ethane, propane and the butanes, and possibly lesser amounts of pentanes and aromatic hydrocarbons.
  • hydrocarbons heavier than methane such as in particular ethane, propane and the butanes, and possibly lesser amounts of pentanes and aromatic hydrocarbons.
  • the composition varies depending upon the type and location of the gas.
  • hydrocarbons heavier than methane are removed as far as needed to produce a liquefied hydrocarbon product stream in accordance with a desired specification.
  • Hydrocarbons heavier than butanes (C4) are removed as far as efficiently possible from the natural gas prior to any significant cooling for several reasons, such as having different freezing or liquefaction temperatures that may cause them to block parts of a methane liquefaction plant.
  • the natural gas may also contain non-hydrocarbons such as H 2 O, N 2 , CO 2 , Hg, H 2 S and other sulphur compounds, and the like.
  • the initially vaporous hydrocarbon stream 10 comprising the natural gas may be (pre-)treated before or during being refrigerated.
  • This (pre-)treatment may comprise reduction and/or removal of undesired components such as CO 2 and H 2 S or other steps such as early cooling, pre-pressurizing or the like. As these steps are well known to the person skilled in the art, their mechanisms are not further discussed here.
  • the initially vaporous hydrocarbon stream 10 comprises natural gas, whereby the liquefied hydrocarbon stream 90 is a liquefied natural gas stream.

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EP11193688.6A 2011-12-15 2011-12-15 Procédé de fonctionnement d'un compresseur et système et procédé pour la production de flux d'hydrocarbures liquéfié Withdrawn EP2604960A1 (fr)

Priority Applications (9)

Application Number Priority Date Filing Date Title
EP11193688.6A EP2604960A1 (fr) 2011-12-15 2011-12-15 Procédé de fonctionnement d'un compresseur et système et procédé pour la production de flux d'hydrocarbures liquéfié
CA2859147A CA2859147C (fr) 2011-12-15 2012-12-13 Systeme et procede de production d'un courant d'hydrocarbure liquefie et procede de fonctionnement d'un compresseur
CN201280061508.1A CN104350345A (zh) 2011-12-15 2012-12-13 用于产生液化烃流的系统和方法以及操作压缩机的方法
PCT/EP2012/075314 WO2013087740A2 (fr) 2011-12-15 2012-12-13 Système et procédé de production d'un courant d'hydrocarbure liquéfié et procédé de fonctionnement d'un compresseur
KR1020147018666A KR20140112496A (ko) 2011-12-15 2012-12-13 액화탄화수소 스트림 제조 장치와 방법, 및 압축기 작동 방법
AU2012324009A AU2012324009B2 (en) 2011-12-15 2012-12-13 System and method for producing a liquefied hydrocarbon stream and method of operating a compressor
AP2014007627A AP2014007627A0 (en) 2011-12-15 2012-12-13 System and method for producing a liquefied hydrocarbon stream and method of operating a compressor
US14/365,171 US20140311183A1 (en) 2011-12-15 2012-12-13 System and method for producing a liquefied hydrocarbon stream and method of operating a compressor
RU2014128901A RU2621591C2 (ru) 2011-12-15 2012-12-13 Система и способ для производства потока сжиженных углеводородов и способ работы компрессора

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11193688.6A EP2604960A1 (fr) 2011-12-15 2011-12-15 Procédé de fonctionnement d'un compresseur et système et procédé pour la production de flux d'hydrocarbures liquéfié

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EP2604960A1 true EP2604960A1 (fr) 2013-06-19

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Publication number Priority date Publication date Assignee Title
IT201600109378A1 (it) * 2016-10-28 2018-04-28 Nuovo Pignone Tecnologie Srl Sistema di liquefazione di gas naturale comprendente un turbocompressore con moltiplicatore integrato
WO2018077935A1 (fr) * 2016-10-28 2018-05-03 Nuovo Pignone Tecnologie Srl Système de liquéfaction de gaz naturel comprenant un turbocompresseur à engrenage intégré
US20220268516A1 (en) * 2019-08-05 2022-08-25 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Cooling and/or liquefying system and method

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AP2014007627A0 (en) 2014-05-31
RU2014128901A (ru) 2016-02-10
AU2012324009B2 (en) 2015-08-06
KR20140112496A (ko) 2014-09-23
WO2013087740A3 (fr) 2015-09-11
RU2621591C2 (ru) 2017-06-06
WO2013087740A2 (fr) 2013-06-20
CA2859147C (fr) 2020-04-28
US20140311183A1 (en) 2014-10-23
CA2859147A1 (fr) 2013-06-20
CN104350345A (zh) 2015-02-11
AU2012324009A1 (en) 2013-07-04

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