NO20200886A1 - Compressor unit - Google Patents

Compressor unit

Info

Publication number
NO20200886A1
NO20200886A1 NO20200886A NO20200886A NO20200886A1 NO 20200886 A1 NO20200886 A1 NO 20200886A1 NO 20200886 A NO20200886 A NO 20200886A NO 20200886 A NO20200886 A NO 20200886A NO 20200886 A1 NO20200886 A1 NO 20200886A1
Authority
NO
Norway
Prior art keywords
compression
stage
compression stage
flow path
connection flow
Prior art date
Application number
NO20200886A
Inventor
Katsuhiro Seyama
Satoshi Tezuka
Kenji Nagura
Original Assignee
Kobe Steel Ltd
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 Kobe Steel Ltd filed Critical Kobe Steel Ltd
Publication of NO20200886A1 publication Critical patent/NO20200886A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B25/00—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/002—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for driven by internal combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
    • F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
    • F04B37/18—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use for specific elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F04B39/042—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod sealing being provided on the piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F04B39/045—Labyrinth-sealing between piston and cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/122—Cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/123—Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/06—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C13/00—Details of vessels or of the filling or discharging of vessels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17D—PIPE-LINE SYSTEMS; PIPE-LINES
    • F17D1/00—Pipe-line systems
    • F17D1/02—Pipe-line systems for gases or vapours
    • F17D1/065—Arrangements for producing propulsion of gases or vapours
    • F17D1/07—Arrangements for producing propulsion of gases or vapours by compression
    • 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
    • F25J1/0025—Boil-off gases "BOG" from storages
    • 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"
    • F25J1/004—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 flash gas recovery
    • 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
    • F25J1/0201—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 using only internal refrigeration means, i.e. without external refrigeration
    • F25J1/0202—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 using only internal refrigeration means, i.e. without external refrigeration in a quasi-closed internal refrigeration loop
    • 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
    • F25J1/0228—Coupling of the liquefaction unit to other units or processes, so-called integrated processes
    • F25J1/0229—Integration with a unit for using hydrocarbons, e.g. consuming hydrocarbons as feed stock
    • F25J1/023—Integration with a unit for using hydrocarbons, e.g. consuming hydrocarbons as feed stock for the combustion as fuels, i.e. integration with the fuel gas 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
    • 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
    • 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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2265/00—Effects achieved by gas storage or gas handling
    • F17C2265/03—Treating the boil-off
    • F17C2265/032—Treating the boil-off by recovery
    • F17C2265/037—Treating the boil-off by recovery with pressurising
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/24—Multiple compressors or compressor stages 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
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/30—Compression of the feed stream
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/60—Processes or apparatus involving steps for increasing the pressure of gaseous process streams the fluid being hydrocarbons or a mixture of hydrocarbons

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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)
  • Combustion & Propulsion (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Ocean & Marine Engineering (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Description

COMPRESSOR UNIT
Technical Field
[0001]
The present invention relates to a compressor unit that compresses a target gas, which is a boil of gas generated in an LNG storage tank on a ship.
Background Art
[0002]
Various compressor units that sequentially increase the pressure of a boil of gas generated from a liquefied natural gas (LNG) have been developed (see JP 2018-118721 A, JP 2011-517749 A, JP 6371930 Bl, and JP 2018-128039 A). For example, the compressor units disclosed in these patent literatures have five compression stages.
[0003]
The pressure of a target gas is higher in the later compression stage. Consequently, a large load is applied to a seal member used for the last compression stage.
Summary of Invention
[0004]
An object of the present invention is to reduce a load on a seal member.
[0005]
A compressor unit according to one aspect of the present invention is installed in a ship and is configured to compress a target gas that is a boil of gas generated in an LNG storage tank of the ship. The compressor unit includes five compression stages that have a reciprocating system and sequentially increase a pressure of the target gas, a crank mechanism that drives a piston of each of the compression stages, and a stage connection flow path that connects a fourth compression stage to a fifth compression stage. The fourth compression stage is configured to have a double acting system in which a front-side space and a rear-side space inside of a cylinder are compression chambers and to discharge the target gas having a pressure of equal to or higher than 100 barG to the stage connection flow path. The fifth compression stage is configured to have a single acting system in which a front-side space inside of a cylinder forms a compression chamber for compressing the target gas whereas a rear-side space forms a non-compression chamber, the frontside space and the rear-side space being partitioned by a piston to which a piston ring is attached or in which a labyrinth seal is formed. The fifth compression stage includes a seal member that prevents the target gas from leaking from the cylinder to a side of the crank mechanism. The noncompression chamber of the fifth compression stage is open to the stage connection flow path.
[0006]
A compressor unit according to another aspect of the present invention is installed in a ship and is configured to compress a target gas that is a boil of gas generated in an LNG storage tank of the ship. The compressor unit includes six compression stages that have a reciprocating system and sequentially increase a pressure of the target gas, a crank mechanism that drives a piston of each of the compression stages, and a stage connection flow path that connects a fifth compression stage to a sixth compression stage. The fourth compression stage and the fifth compression stage have a tandem system in which a cylinder of the fifth compression stage is disposed on a cylinder of the fourth compression stage. The rear-side space in the cylinder of the fourth compression stage is a compression chamber. The fifth compression stage is configured to discharge the target gas having a pressure of equal to or higher than 100 barG from a compression chamber of the fifth compression stage to the stage connection flow path. The sixth compression stage is configured to have a single acting system in which a front-side space inside of a cylinder forms a compression chamber for compressing the target gas whereas a rear-side space forms a non-compression chamber, the frontside space and the rear-side space being partitioned by a piston to which a piston ring is attached or in which a labyrinth seal is formed. The sixth compression stage includes a seal member that prevents the target gas from leaking from the cylinder to a side of the crank mechanism. The noncompression chamber of the sixth compression stage is open to the stage connection flow path.
[0007]
The compressor unit described above can reduce a load on the seal member of the last compression stage.
[0008]
The purposes, features and advantages of the compressor unit described above will become more apparent from the following detailed description and the accompanying drawings.
Brief Description of Drawings
[0009]
FIG. 1 is a schematic view of a compressor unit;
FIG. 2 is a schematic view of a compressor constituting the compressor unit;
FIG. 3 is a schematic view of a part of the compressor unit;
FIG. 4 is a schematic cross-sectional view of a seal member of the compressor unit;
FIG. 5 is a schematic view of the compressor unit;
FIG. 6 is a graph of results of simulation illustrating a relationship between a pressure of a target gas and a reliquefaction rate;
F I G. 7 is a schematic view of the compressor unit;
FIG. 8 is a schematic diagram of a compressor unit;
FIG. 9 is a schematic diagram of the compressor unit;
FIG. 10 is a schematic diagram of a compressor unit;
FIG. 11 is a schematic cross-sectional view of a compression stage in the compressor unit; and
FIG. 12 is a schematic cross-sectional view of the compression stage in the compressor unit.
Description of Embodiments
[0010]
(First Embodiment)
FIG. 1 is a schematic view of a compressor unit 100. FIG. 2 is a schematic view of a compressor 500 constituting the compressor unit 100. The compressor unit 100 will be described with reference to FIG. 1 and FIG. 2.
[0011]
The compressor unit 100 is installed in a ship (not illustrated) that has an LNG storage tank 101 storing a liquefied natural gas (LNG). The compressor unit 100 is configured to compress a target gas that is a boil off gas generated in the LNG storage tank 101. The pressure of the boil of gas generated in the LNG storage tank 101 is approximately 1 bar to 1.5 bar (absolute pressure). In the following description, "barG" is used to indicate a pressure as a gauge pressure. The compressor unit 100 is configured to increase the pressure of the target gas to 300 barG or higher and 350 barG or lower and supplies the target gas whose pressure has been increased to a predetermined demand destination (for example, ship engine).
[0012]
The compressor unit 100 includes a flow path 110 in which a target gas flows to a demand destination, the compressor 500, and a plurality of coolers 282 to 285. In FIG. 1, the compressor unit 100 is illustrated as a device that includes components illustrated within a two-dot chain frame line.
[0013]
As illustrated in FIG. 2, the compressor 500 includes first to fifth reciprocating compression stages 201 to 205, a crank mechanism, a crankcase 301, and six cross guides 303. The compressor 500 includes two first compression stages 201. The second compression stage 202 is a compression stage next to the first compression stages 201. The third compression stage 203 is a compression stage next to the second compression stage 202. The fourth compression stage 204 is a compression stage next to the third compression stage 203. The fifth compression stage 205 is a last compression stage. The first to fifth compression stages 201 to 205 are disposed in the flow path 110 so as to sequentially increase the pressure of a target gas. The compression ratio of each of the compression stages 201 to 205 is designed to be 2 to 3.5. The crank mechanism is used as a drive source common to the first to fifth compression stages 201 to 205. The crank mechanism is housed in the crankcase 301. The cross guides 303 are attached to the crankcase 301 (see FIG. 2).
[0014]
The upstream end of the flow path 110 is connected to an upper part of the LNG storage tank 101 so as to allow a boil of gas generated in the LNG storage tank 101 to enter the flow path 110. A downstream end of the flow path 110 is connected to the demand destination.
[0015]
The flow path 110 includes a storage tank connection flow path 111, stage connection flow paths 271 to 274, a demand destination connection flow path 114, and a reliquefaction line 106. T he storage tank connection flow path 111 is connected to the LNG storage tank 101 and guides a boil off gas to the compressor unit 100. The storage tank connection flow path 111 includes a main pipe 111C extending from the LNG storage tank 101 through a re liquefaction facility 300 illustrated in FIG. 5 and two branch parts 111 A, 11 IB branching from the main pipe 111C as illustrated in FIG. 1. The branch parts 111 A and 11 IB are connected to two first compression stages 201 , respectively.
[0016]
The stage connection flow path 271 connects the first compression stage 201 to the second compression stage 202. The stage connection flow path 271 includes a main pipe 113C connected to the second compression stage 202 and two branch parts 113A, 113B branching from the main pipe 113C to the two first compression stages 201. These branch parts 113A, 113B are connected to the first compression stages 201, respectively.
[0017]
The stage connection flow path 272 connects the second compression stage 202 to the third compression stage 203. The stage connection flow path 273 connects the third compression stage 203 to the fourth compression stage 204. The stage connection flow path 274 connects the fourth compression stage 204 to the fifth compression stage 205, The coolers 282 to 284 are disposed in the stage connection flow paths 272 to 274, respectively in order to cool the target gas compressed in the second to fifth compression stages 202 to 205. To cool the target gas discharged from the first compression stage 201, a cooler may also be disposed in the stage connection flow path 271, if necessary.
[0018]
The demand destination connection flow path 114 is a flow path connecting the fifth compression stage 205 to the demand destination. The demand destination connection flow path 114 includes the cooler 285.
[0019]
The reliquefaction line 106 branches off from the demand destination connection flow path 114 on a downstream side of the cooler 285. The reliquefaction line 106 is used to supply at least a part of the target gas having passed through the cooler 285 to the reliquefaction facility 300.
[0020]
The two first compression stages 201 are connected to the branch parts 111 A, 111 B, 113 A, 113B so as to be parallel to each other. The second to fifth compression stages 202 to 205 are serially connected.
[0021]
As illustrated in FIG. 2, the crank mechanism is configured to change a rotation of a crankshaft to linear reciprocating movements of the crossheads. The crankshaft is driven by a motor 302. The crosshead is used as a connector to a piston rod 213 of each of the first to fifth compression stages 201 to 205.
[0022]
The six cross guides 303 are arranged in a horizontal direction with an interval therebetween, and project in a direction substantially orthogonal to the horizontal direction (more specifical ly, upward in direction of gravity in present embodiment). The crosshead described above reciprocates in the cross guide 303.
[0023]
A closing part 306 is disposed in each cross guide 303. A through-hole for passing the piston rod 213 is formed at the center of the closing part 306. The piston rod 213 connects a piston 212 reciprocating in each of the first to fifth compression stages 201 to 205 to the corresponding crosshead. An inert gas (for example, nitrogen) is supplied to an inner space above the closing part 306 in the cross guide 303 in order to improve the safety of the compressor unit 100.
[0024]
The first to fifth compression stages 201 to 205 are built at positions of the cross guides 303 arranged in the horizontal direction. The first compression stage 201, the fourth compression stage 204, the fifth compression stage 205, the second compression stage 202, the third compression stage 203, and the first compression stage 201 are arranged in this order from a side of the motor 302. The arrangement order of the first to fifth compression stages 201 to 205 is not limited to this case.
[0025]
The first to fifth compression stages 201 to 205 are connected by the flow path 110 so as to achieve piping connection illustrated in FIG. 1. FIG. 2 schematically illustrates an arrangement of the first to fifth compression stages 201 to 205 and in practice, the first to fifth compression stages 201 to 205 are arranged close to each other.
[0026]
The first compression stage 201 includes, in addition to the piston 212 and the piston rod 213 described above, a cylinder 211, a pair of suction valves 214, and a pair of discharge valves 215.
[0027]
The cylinder 211 includes a sleeve 216 that is substantially coaxial with the cross guide 303, a rear head 217 that is attached to an open end of the sleeve 216 on a side of the crank mechanism, and a front head 218 that closes the other open end of the sleeve 216. A through-hole and a recess that is substantially coaxial with the through-hole are formed at the central position of the rear head 217. The recess of the rear head 217 is open to the side of the crank mechanism.
[0028]
The piston 212 is housed in a housing space of the cylinder 211 that is surrounded by the sleeve 216, the rear head 217, and the front head 218. In the cylinder 211, a compression chamber 221 for compressing a target gas is formed in a space between an end surface of the piston 212 on the side of the crank mechanism and the rear head 217 (hereinafter, referred to as "rear-side space"). A compression chamber 222 for compressing a target gas is formed in a space between an end surface of the piston 212 opposite to the crank mechanism and the front head 218 (hereinafter referred to as "front-side space"). That is, the first compression stage 201 has a double acting system in which the compression chambers 221, 222 are respectively formed on both sides of the piston 212.
[0029]
The paired suction valves 214 are attached to suction ports formed at positions corresponding to the compression chambers 221, 222. When the pressure of a target gas in the compression chambers 221, 222 is equal to or lower than a pressure on the upstream side of the suction valves 214, the suction valves 214 allow the target gas to flow into the compression chambers 221, 222.
[0030]
The paired discharge val ves 215 are attached to discharge ports formed at positions corresponding to the compression chambers 221, 222. When the pressure of a target gas in the compression chambers 221, 222 is equal to or higher than a pressure on the downstream side of the discharge valves 215, the discharge valves 215 allow the target gas to flow from the compression chambers 221, 222.
[0031]
The piston rod 213 is connected to the end surface of the piston 212 on the side of the crank mechanism and the crosshead of the crank mechanism. The piston rod 213 passes through the rear head 217, extends to the side of the crank mechanism in the cross guide 303, and is inserted into the through-hole in the closing part 306.
[0032]
The first compression stage 201 includes a wiper 231 and an oil slinger 232 in order to prevent a lubricating oil used for lubricating the crank mechanism from entering the compression chambers 221, 222 through an outer peripheral part of the piston rod 213.
[0033]
The wiper 231 is an annular seal member surrounding the piston rod 213. The wiper 231 is fixed to the closing part 306. An inner peripheral part of the wiper 231 contacts the outer peripheral part of the piston rod 213. The wiper 231 prevents a lubricating oil from flowing along the outer peripheral part of the piston rod 213 and moving to the cylinder 211.
[0034]
The oil slinger 232 is an annular plate member. The oil slinger 232 is fixed to the piston rod 213 between the wiper 231 and the rear head 217. If a little amount of a lubricating oil flows over the wiper 231 , the oil slinger 232 prevents the lubricant from entering the cylinder 211.
[0035]
The first compression stage 201 includes a plurality of piston rings 243 attached to an outer peripheral part of the piston 212 in order to prevent a target gas from flowing between the compression chambers 221 and 222, and a sea! member 242 that prevents the target gas from leaking from the compression chamber 221 into the cross guide 303. Each of the piston rings 243 is a contact seal member that contacts the cylinder 211 at its outer peripheral part to seal a space between the piston 212 and an inner surface of the cylinder 211. The piston ring 243 is also an oilfree (in other words, unlubricated) seal member in which a lubricating oil is not supplied to the piston ring 243.
[0036]
FIG. 4 illustrates a schematic cross-section of the seal member 242. The seal member 242 is an oil-free (in other words, unlubricated) seal member in which a lubricating oil is not supplied to rings 249.
[0037]
As illustrated in FIGS. 2 to 4, the seal member 242 is a so-called rod packing, and includes a plurality of cases 244, the rings 249, and a holder 294. The cases 244 and the rings 249 surround the piston rod 213 in the rear head 217.
[0038]
The cases 244 are housed in the recess of the rear head 217 between the rear head 217 and the piston rod 213. Each of the cases 244 includes a substantially circular bottom part 251 and a peripheral wall 252 that projects from an outer edge of the bottom part 251 to the side of the crank mechanism. A through-hole into which the piston rod 213 is inserted is formed at a substantial center of the bottom part 251. The rings 249 are housed inside of the case 244 (that is, radially inside of peripheral wall 252).
[0039]
These rings 249 are arranged in an axial direction of the piston rod 213. An inner peripheral part of the ring 249 contacts the outer peripheral part of the piston rod 213 under a pressure of a target gas in the compression chamber 221. That is, the ring 249 functions as a contact seal member to seal the space between the piston rod 213 and the rear head 217.
[0040]
The holder 294 is disposed closer to the side of crank mechanism than the cases 244. The holder 294 is fixed to the rear head 217 by a bolt or the like (not illustrated). The case 244 is thus held.
[0041]
The second to fourth compression stages 202 to 204 are substantially common to the first compression stage 201 except that the diameter of the piston 212 and the inner diameter of the cylinder 211 are smaller than those in the first compression stage 201. That is, the piston ring 243 and the seal member 242 in the second to fourth compression stages 202 to 204 are also contact and oil-free piston ring and seal member. In addition, the second to fourth compression stages 202 to 204 also have the double acting system.
In the fifth compression stage 205, as illustrated in FIG. 2 and FIG. 3, the diameter of the piston 212 and the inner diameter of the cylinder 211 are smaller than those in the first to fourth compression stages 201 to 204. In the cylinder 211 of the fifth compression stage 205, the compression chamber 222 is formed in the front-side space, as in the first compression stage 201.
[0043]
On the other hand, in the rear-side space, a pipe member 119 is connected to the position of a suction valve without the suction valve being interposed (see FIG. 3). The pipe member 119 does not include a check valve. The pipe member 119 is connected to the stage connection flow path 274. Consequently, the rear-side space communicates with the stage connection flow path 274, in other words, the rear-side space is open to the stage connection flow path 274. The rear-side space is thus a non-compression chamber 223 that is not used for compressing a target gas. That is, unlike the first to fourth compression stages 201 to 204, the fifth compression stage 205 has a single acting system in which only the front-side space is the compression chamber 222.
[0044]
The fifth compression stage 205 includes the piston rings 243 and the seal member 242. The piston rings 243 in the fifth compression stage 205 are oil-free piston rings (that is, lubricating oil is not supplied to piston rings 243) as in the first compression stage 201, and seals the space between the piston 212 and the inner surface of the cylinder 211.
[0045]
The seal member 242 of the fifth compression stage 205 is a contact seal member in which the inner peripheral part of the ring 249 contacts the outer peripheral part of the piston rod 213, as in the first compression stage 201. The seal member 242 is also an oil-free seal member (that is, lubricating oil is not supplied to rings 249).
[0046]
The number of sets of the cases 244 and the rings 249 in the seal member 242 of the fifth compression stage 205 is larger than the number of sets of the cases 244 and the rings 249 in the seal member 242 of the first compression stage 201. A part of the seal m ember 242 of the fifth compression stage 205 projects from the rear head 217 to the side of the crank mechanism. The axial length of the seal member 242 of the fifth compression stage 205 is thus longer than that of the seal member 242 of the first compression stage 201. The seal area of the seal member 242 in the fifth compression stage 205 is larger than the seal area of the seal member 242 in the first compression stage 201. Consequently, a target gas with higher pressure can be sealed. Other configurations of the fifth compression stage 205 are similar to those of the first compression stage 201.
[0047]
As illustrated in FIG. 5, the reliquefaction facility 300 is used to liquefy a target gas supplied through the reliquefaction line 106. The reliquefaction facility 300 includes a heat exchanger 310, a flash tank 320, a Joule-Thomson valve 333, a connection pipe 331 , and a return pipe 332. The main pipe 111 C is connected to the heat exchanger 310, and the target gas flowing from the LNG storage tank 101 can flow into the heat exchanger 310. The reliquefaction line 106 is also connected to the heat exchanger 310, and a part of the target gas discharged from the fifth compression stage 205 can flow into the heat exchanger 310.
[0048]
The Joule-Thomson valve 333 is disposed on a downstream side of the heat exchanger 310 in the reliquefaction line 106. The downstream end of the reliquefaction line 106 is connected to an upper part of the flash tank 320. The connection pipe 331 is connected to the upper part of the flash tank 320 and the main pipe 111 C so as to cause the target gas in the flash tank 320 to flow into the main pipe 111 C of the storage tank connection flow path 111. The return pipe 332 connects a lower part of the flash tank 320 to a lower part of the LNG storage tank 101. The return pipe 332 may include a pump for conveying an LNG to the LNG storage tank 101.
[0049]
Next, an operation of the compressor unit 100 and a flow of a target gas will be described below.
[0050]
When the motor 302 illustrated in FIG. 2 is operated, the crosshead of a crank mechani sm is linearly reciprocated. Power of the crosshead is transmitted via the piston rods 213 of the first to fifth compression stage 201 to 205 to the pistons 212 of the first to fifth compression stages 201 to 205. As a result, these pistons 212 are also linearly reciprocated.
[0051]
The target gas generated in the LNG storage tank 101 illustrated in FIG.l flows in the storage tank connection flow path 111 to be sucked in the first compression stage 201 and sequentially compressed in the first to fifth compression stages 201 to 205. The high-temperature target gas immediately after being discharged from the second to fifth compression stages 202 to 205 passes through the coolers 282 to 284 to be cooled to a normal temperature (for example, 40°C). The target gas immediately after being compressed in the fifth compression stage 205 is also cooled to a normal temperature by the cooler 285. A part of the target gas cooled by the cooler 285 flows into the reliquefaction line 106, whereas the remaining target gas is supplied to a demand destination.
[0052]
In the compression chambers 221, 222 of the fourth compression stage 204 illustrated in FIG. 3, the pressure of the target gas is increased to a pressure equal to or higher than 100 barG and equal to or lower than 150 barG. In the compression chamber 222 of the fifth compression stage 205, the pressure of the target gas is further increased to a pressure equal to or higher than 300 barG and equal to or lower than 350 barG. In the non-compression chamber 223 of the fifth compression stage 205, the pressure is kept at a pressure substantially equal to the pressure in the stage connection flow path 274 (pressure equal to or higher than 100 barG and equal to or lower than 150 barG).
[0053]
As illustrated in FIG. 5, the normal-temperature target gas flowing into the reliquefaction line 106 exchanges heat with the low-temperature target gas (for example, -162°C) flowing in the main pipe 111 C of the storage tank connection flow path 111 in the heat exchanger 310. After being cooled by the heat exchanger 310, the target gas flowing in the reliquefaction line 106 is depressurized to a predetermined pressure by the Joule-Thomson valve 333, and is partially liquefied in the flash tank 320. The liquefied target gas is returned to the LNG storage tank 101 through the return pipe 332.
[0054]
FIG. 6 is a graph of results of simulation illustrating a relationship between a pressure of a target gas and a reliquefaction rate. It is assumed in this simulation that the pressure of a target gas discharged from the compressor 500 is in the range of 50 barG to 300 barG, the temperature of the target gas is 40°C. and 4,000 kg/h of the target gas is entirely reliquefied. In addition, it is assumed that the amount of heat exchange with a boil off gas generated in the LNG storage tank 101 in heat exchanger 310 is 400 kW, and the target gas flowing from the heat exchanger 310 is depressurized to 3 barG by the Joule-Thomson valve 333. Here, the reliquefaction rate is a ratio of the amount of a liquid in the flash tank 320 (kg/h) to 4,000 kg/ of the target gas.
[0055]
The reliquefaction rate of the target gas changes depending on the pressure of the target gas flowing into the reliquefaction line 106. It is found that as the pressure of the target gas flowing into the reliquefaction line 106 increases, the reliquefaction rate of the target gas also increases. For example, it is found that the reliquefaction rate is 10% when the discharge pressure of the compressor 500 is equal to or higher than 100 barG. In general, the reliquefaction rate is preferably equal or more than 10%. When the discharge pressure of the compressor 500 is 300 barG, it is found that the reliquefaction rate increases to approximately 33%. Based on the results of the simulation, it is found that the reliquefaction line 106 is disposed most preferably on the downstream side of the fifth compression stage 205 having a pressure of 300 barG to 350 barG in the compressor unit 100 illustrated in FIG. 1.
[0056]
The first embodiment of the present invention has been described above. According to the compressor unit 100, the rear-side space (that is, space on side of crank mechanism in cylinder 211) in the fifth compression stage 205 is connected to the stage connection flow path 274 through the pipe member 119, so that the non-compression chamber 223 is formed. The pressure of the noncompression chamber 223 is thus kept at a pressure substantially equal to the discharge pressure of a target gas in the fourth compression stage 204.
[0057]
In the fifth compression stage 205, if the pressure of the rear-side space is equal to the pressure of a compression chamber, a large load is applied to the seal member 242 because the diference between a suction pressure and a discharge pressure is larger than that in other compression stages 201 to 204. As the rear-side space is the non-compression chamber 223 in the compressor unit 100, the load on the seal member 242 is reduced and the life of the seal member 242 is extended.
[0058]
As the first to fourth compression stages 201 to 204 have a double acting system in the compressor unit 100, it is possible to achieve a target gas throughput.
[0059]
As the piston rings 243 and the seal members 242 of the first to fifth compression stages 201 to 205 are oil-free piston rings and seal members, it is possible to prevent a lubricating oil from being mixed with the target gas. It is thus possible to prevent the lubricating oil from entering the reliquefaction line 106.
[0060]
FIG. 7 illustrates another example of the compressor unit 100. Based on the simulation of FIG. 6, when the discharge pressure is equal to or higher than 100 barG, the reliquefaction rate is equal to or more than 10%. Consequently, the reliquefaction line 106 may branch from the stage connection flow path 274 between the fourth compression stage 204 and the fifth compression stage 205, the stage connection flow path 274 having a pressure of 100 barG or higher.
[0061]
(Second Embodiment)
FIG. 8 illustrates a part of a compressor unit 100 according to a second embodiment. The compressor unit 100 further includes a sixth compression stage 206. In the present invention, in order to prevent a crank mechanism from increasing in size, a fourth compression stage 204 and a fifth compression stage 205 have a tandem system. A common piston rod 213 is used in the fourth compression stage 204 and the fifth compression stage 205.
[0062]
In the following description, the piston of the fourth compression stage 204 is denoted by reference numeral "212A". The cylinder of the fourth compression stage 204 is denoted by reference numeral ''211 A". The piston of the fifth compression stage 205 is denoted by reference numeral "212B". The cylinder of the fifth compression stage 205 is denoted by reference numeral "211B". The piston of the sixth compression stage 206 is denoted by the symbol "212C". The cylinder of the sixth compression stage 206 is denoted by reference numeral "211C". The configuration of the first to third compression stages 201 to 203 is the same as the configuration of the first to third compression stage 201 to 203 in the first embodiment.
[0063]
The cylinder 211 A of the fourth compression stage 204 has a tubular shape as a whole.
The lower end of the cylinder 211 A in the fourth compression stage 204 is closed by a rear head 217. The upper end of the cylinder 211A in the fourth compression stage 204 opens upward at the center of the upper end. The rear-side space (that is, space between piston 212A and rear head 217) is a compression chamber 221.
[0064]
A plurality of piston rings 243 are attached to an outer peripheral part of the piston 212A. The piston ring 243 is an oil-free piston ring. To prevent a target gas from leaking from the compression chamber 221 to a side of the crank mechanism (that is, inner space of corresponding cross guide 303), a contact and oil-free seal member 242 is disposed in the rear head 217 attached to the lower end of the cylinder 211 A.
[0065]
The cylinder 211B of the fifth compression stage 205 is disposed on the cylinder 211 A of the fourth compression stage 204. The cylinder 211B has a tubular shape as a whole. The inner diameter of the cylinder 21 IB in the fifth compression stage 205 is smaller than the inner diameter of the cylinder 211A in the fourth compression stage 204. The upper end of the cylinder 21 IB is closed by a front head 218.
[0066]
The piston 212B of the fifth compression stage 205 projects upward from an upper end surface of the piston 212A of the fourth compression stage 204 into the cylinder 21 IB of the fifth compression stage 205 through an opening in the upper end of the cylinder 211 A in the fourth compression stage 204. The front-side space (that is, space between piston 212B and front head 218) of the fifth compression stage 205 is a compression chamber 222 for compressing a target gas. The piston rings 243 are attached to the outer peripheral part of the piston 212B. The piston ring 243 is an oil-free piston ring.
[0067]
The front-side space (that is, space between piston 212 A and piston 212B) of the fourth compression stage 204 is open to a stage connection flow path 274 (flow path connecting fourth compression stage 204 to fifth compression stage 205) through a pipe member 119A.
Consequently, this space is a non-compression chamber 223 that is not used for compressing a target gas.
[0068]
The piston 212A of the fourth compression stage 204 and the piston 212B of the fifth compression stage 205 are driven by a reciprocating movement of the common piston rod 213. The target gas having a pressure of equal to or higher than 100 barG and equal to or lower than 150 barG is discharged from the fifth compression stage 205.
[0069]
In the sixth compression stage 206, an upper end and a lower end of the cylinder 211C are closed by a front head 218 and a rear head 217, respectively. The piston 212C of the sixth compression stage 206 is disposed in the cylinder 211C. The front-side space (that is, space between front head 218 and piston 212C) is the compression chamber 222 for compressing a target gas. As the pipe member 119B is connected to a stage connection flow path 275, the rear-side space (that is, space between rear head 217 and piston 212C) is a non-compression chamber 223.
Namely, the sixth compression stage 206 has a single acting system. In the sixth compression stage 206, the pressure of the target gas is increased to a pressure equal to or higher than 300 barG and equal to or lower than 350 barG.
[0070]
The piston rings 243 are attached to an outer peripheral part of the piston 212C in the sixth compression stage 206. These piston rings 243 are also oil-free piston rings. The contact and oilfree seal member 242 is disposed in the rear head 217 of the sixth compression stage 206.
[0071]
A suction valve 214 and a discharge valve 215 are attached to positions of the cylinders 211A, 211B, 211C corresponding to the compression chambers 221, 222 of the fourth to sixth compression stages 204 to 206.
[0072]
A flow path 110 includes the stage connection flow path 275 that connects the fifth compression stage 205 and the sixth compression stage 206. A cooler 285 is attached in the stage connection flow path 275.
[0073]
A reliquefaction line 106 branches from the stage connection flow path 275 on a downstream side of the cooler 285 to be extended to a reliquefaction facility 300 (see FIG. 5).
[0074]
A demand destination connection flow path 114 extends from the discharge valve 215 of the sixth compression stage 206 to a demand destination. The compressor unit 100 includes a cooler 286 that is attached in the demand destination connection flow path 114 in order to cool the target gas compressed in the sixth compression stage 206.
[0075]
While the compressor unit 100 is driven, the target gas cooled by the cooler 283 (see FIG.
1) flows into the compression chamber 221 of the fourth compression stage 204. The target gas is compressed in the compression chamber 221 of the fourth compression stage 204 and then flows into the stage connection flow path 274. The target gas is cooled by a cooler 284 and then flows into the compression chamber 222 of the fifth compression stage 205.
[0076]
After being compressed in the compression chamber 222 of the fifth compression stage 205, the target gas flows into the stage connection flow path 275 and is cooled by the cooler 285. A part of the target gas cooled by the cooler 285 is supplied to the reliquefaction facility 300 through the reliquefaction line 106. The remaining target gas flows into the compression chamber 222 of the sixth compression stage 206 through the stage connection flow path 275. After being compressed in the compression chamber 222 of the sixth compression stage 206, the target gas flows into the demand destination connection flow path 114 and is cooled by the cooler 286. The target gas is then supplied to the demand destination.
[0077]
In the second embodiment, as the rear-side space is connected to the stage connection flow path 275 through the pipe member 119B, the rear-side space is the non-compression chamber 223 in the sixth compression stage 206. Consequently, the load on the seal member 242 is reduced and the life of the seal member 242 is extended as compared with a case where the rear-side space is a compression chamber.
[0078]
In the fourth compression stage 204 and the fifth compression stage 205, as the front-side space (space between pistons 212A and 212B) of the fourth compression stage 204 is connected to the stage connection flow path 274 through the pipe member 119A, the front-side space is the noncompression chamber 223. As compared with a case where the front-side space is connected to the stage connection flow path 273 connecting the fourth compression stage 204 to the third compression stage 203 and thus the front-side space is a non-compression chamber, the difference between the pressure of the fifth compression stage 205 before the piston 212B and the pressure of the fifth compression stage 205 after the piston 212B can be reduced, and the load on the piston ring 243 disposed on the piston 212B can be reduced.
[0079]
In the second embodiment, the reliquefaction line 106 may branch from the demand destination connection flow path 114 as illustrated in FIG. 9.
[0080]
(Third Embodiment)
FIG. 10 is a schematic view of a compressor unit 100 according to a third embodiment. In the third embodiment, a lubricating oil is supplied to piston rings 243 and a seal member 242 of a sixth compression stage 206. That is, the sixth compression stage 206 is a lubricated compression stage. However, the oil-free piston rings 243 and the oil-free seal member 242 are used in the first to fifth compression stages 201 to 205, as in the second embodiment.
[0081]
A stage connection flow path 275 includes a flow path section 108 extending in a horizontal direction, a flow path section 109 extending upward from a downstream end of the flow path section 108, and a flow path section 107 connected to an upper end of the flow path section 109 and extending in the horizontal direction. The downstream end of the flow path section 107 is connected to a suction valve 214 of the sixth compression stage 206. A pipe member 119B connects a non-compression chamber 223 of the sixth compression stage 206 to the flow path section 107. A reliquefaction line 106 branches off from the stage connection flow path 275 in the flow path section 108.
[0082]
The stage connection flow path 275 includes a check valve 261, an on-off valve 262, and an oil filter 263. The check valve 261 is attached in the flow path section 107. The on-off valve 262 and the oil filter 263 are attached in the flow path section 108. The on-off valve 262 is disposed on a downstream side of a connection position of the flow path section 108 and the reliquefaction line 106. The oil filter 263 is disposed on a downstream side of the on-off valve 262. The on-off valve 262 is opened when the compressor unit 100 is driven and is closed when the compressor unit 100 is stopped.
[0083]
In the compressor unit 100, even if the target gas in the sixth compression stage 206 flows back into the stage connection flow path 275, the target gas does not flow back to an upstream side of the check valve 261. The lubricating oil mixed with the target gas thus remains in a portion between the check valve 261 and the suction valve 214 of the sixth compression stage 206. In addition, if the lubricating oil flows back over the check valve 261, the lubricating oil is caught by the oil filter 263. It is thus possible to reliably prevent the lubricating oil from flowing into the reliquefaction line 106. Moreover, the on-off valve 262 is closed when the compressor unit 100 is stopped. Consequently, it is possible to reliably prevent the lubricating oil from flowing into the reliquefaction line 106.
[0084]
The disclosed embodiments are to be considered in all respects as illustrative and not restrictive. The scope of the present invention is defined not by the description above but by the claims, and is intended to include all modifications within the scope and meaning equivalent to the claims.
[0085]
According to the embodiments described above, the piston ring 243 (that is, contact seal) is used in each compression stage. However, a labyrinth seal (non-contact seal) may be formed on the piston 212 instead of the piston ring 243. For example, a large number of labyrinth grooves 245 may be formed in an outer peripheral surface of the piston 212 as illustrated in FIG. 11. The labyrinth grooves 245 are formed with intervals therebetween in a longitudinal direction of the piston 212.
[0086]
According to the embodiments described above, the seal member 242 is attached to the lower end of the cylinder 211 via the rear head 217. However, the rear head 217 is not always necessary. For example, the seal member 242 may be directly attached to the lower end of the cylinder 211 as illustrated in FIG. 12. In this case, the seal member 242 closes the lower end of the cylinder 211.
[0087]
In the first embodiment, an on-off valve that is closed only when the compressor unit 100 is stopped may be disposed in the pipe member 119. Even in this case, the non-compression chamber 223 of the fifth compression stage 205 communicates with the stage connection flow path 274 at least when the compressor unit 100 is driven. This description is applicable to the pipe members 119A, 119B illustrated in FIGS. 8 to 10.
[0088]
In the third embodiment, a lubricating oil may be supplied to only either of the piston ring 243 and the seal member 242 in the sixth compression stage 206. The on-off valve 262 may be disposed at any position on the downstream side of the connection position of the stage connection flow path 275 and the reliquefaction line 106.
[0089]
According to the embodiments described above, the compressor unit 100 includes two first compression stages 201. However, the compressor unit 100 may include a single first compression stage 201.
[0090]
According to the embodiments described above, two first compression stages 201 are connected in parallel. When the compressor unit 100 includes each of the second to sixth compression stages 202 to 206 in plural, the second, third, fourth, fifth, and sixth compression stages 202 to 206 may be respectively connected in parallel.
[0091]
The embodiments described above mainly includes a compressor unit having the following configuration.
[0092]
A compressor unit according to one aspect of the embodiments described above is installed in a ship and is configured to compress a target gas that is a boil off gas generated in an LNG storage tank of the ship. The compressor unit includes five compression stages that have a reciprocating system and sequentially increase a pressure of the target gas, a crank mechanism that drives a piston of each of the compression stages, and a stage connection flow path that connects a fourth compression stage to a fifth compression stage. The fourth compression stage is configured to have a double acting system in which a front-side space and a rear-side space inside of a cylinder are compression chambers and to discharge the target gas having a pressure of equal to or higher than 100 barG to the stage connection flow path. The fifth compression stage is configured to have a single acting system in which a front-side space inside of a cylinder forms a compression chamber for compressing the target gas whereas a rear-side space forms a non-compression chamber, the front-side space and the rear-side space being partitioned by a piston to which a piston ring is attached or in which a labyrinth seal is formed. The fifth compression stage includes a seal member that prevents the target gas from leaking from the cylinder to a side of the crank mechanism. The non-compression chamber of the fifth compression stage is open to the stage connection flow path.
According to the configuration described above, the rear-side space of the fifth compression stage is a non-compression chamber, and thus the load on the seal member is reduced.
[0094]
Regarding the configuration described above, the compressor unit may further include a demand destination conneetion flow path that connects the fifth compression stage to a demand destination of the target gas and a reliquefaction line that branches from the stage connection flow path or the demand destination connection flow path so as to guide at least a part of the target gas discharged into the stage connection flow path or the demand destination connection flow path to a reliquefaction facility. The fourth compression stage or the fifth compression stage may be configured to discharge the target gas to the stage connection flow path so as to reliquefy 10% or more of the target gas supplied to the reliquefaction facility.
[0095]
According to the configuration described above, the target gas is eficiently reliquefied.
[0096]
The compressor unit according to another aspect of the embodiments described above is installed in a ship and is configured to compress a target gas that is a boil of gas generated in an LNG storage tank of the ship. The compressor unit includes six compression stages that have a reciprocating system and sequentially increase a pressure of the target gas, a crank mechanism that drives a piston of each of the compression stages, and a stage connection flow path that connects a fifth compression stage to a sixth compression stage. The fourth compression stage and the fifth compression stage have a tandem system in which a cylinder of the fifth compression stage is disposed on a cylinder of the fourth compression stage. A rear-side space in the cylinder of the fourth compression stage is a compression chamber. The fifth compression stage is configured to discharge the target gas having a pressure of equal to or higher than 100 barG from a compression chamber of the fifth compression stage to the stage connection flow path. The sixth compression stage is configured to have a single acting system in which a front-side space inside of a cylinder forms a compression chamber for compressing the target gas whereas a rear-side space forms a noncompression chamber, the front-side space and the rear-side space being partitioned by a piston to which a piston ring is attached or in which a labyrinth seal is formed. The sixth compression stage includes a seal member that prevents the target gas from leaking from the cylinder to a side of the crank mechanism. The non-compression chamber of the sixth compression stage is open to the stage connection flow path.
[0097]
According to the configuration described above, the rear-side space of the sixth compression stage is a non-compression chamber, and thus the load on the seal member is reduced.
[0098]
Regarding the configuration described above, the compression chamber of the fifth compression stage may be partitioned from a front-side space in the cylinder of the fourth compression stage by a piston to which a piston ring is attached or in which a labyrinth seal is formed. The compression chamber of the fourth compression stage may be partitioned from the front-side space in the cylinder of the fourth compression stage by a piston to which a piston ring is attached or in which a labyrinth seal is formed. The front-side space in the cylinder of the fourth compression stage may be a non-compression chamber that is open to another stage connection flow path that connects the fourth compression stage to the fifth compression stage.
[0099]
According to the configuration described above, the front-side space in the fourth compression stage is connected to the stage connection flow path, and thus is a non-compression chamber. As compared with a case where the front-side space is connected to the stage connection flow path connecting the fourth compression stage to the third compression stage and thus the frontside space is a non-compression chamber, the difference between the pressure of the fifth compression stage before the piston and the pressure of the fifth compression stage after the piston can be reduced, and the load on the piston ring disposed on the piston of the fifth compression stage can be reduced.
[0100]
Regarding the configuration described above, the compressor unit may further include a demand destination connection flow path that connects the sixth compression stage to a demand destination of the target gas and a reliquefaction line that branches from the stage connection flow path or the demand destination connection flow path so as to guide at least a part of the target gas discharged into the stage connection flow path or the demand destination connection flow path to a reliquefaction facility. The fifth compression stage or the sixth compression stage may be configured to discharge the target gas to the stage connection flow path so as to reliquefy 10% or more of the target gas supplied to the reliquefaction facility.
[0101]
According to the configuration described above, the target gas is efficiently reliquefied.
[0102]
Regarding the configuration described above, all compression stages may be oil-free compression stages.
[0103]
According to the configuration described above, the reliquefaction line can be provided without considering mixing of an oil into the reliquefaction line.
[0104]
Regarding the configuration described above, the compressor unit may further include a check valve that is disposed on the stage connection flow path that connects the fifth compression stage to the sixth compression stage and an oil filter that is disposed on an upstream side of the check valve on the stage connection flow path that connects the fifth compression stage to the sixth compression stage. The sixth compression stage may be a lubricated compression stage, and other compression stages may be oil-free compression stages. The reliquefaction line may branch from the stage connection flow path on an upstream side of the check valve and the oil filter.
[0105]
According to the configuration described above, the sixth compression stage is a lubricated compression stage, but the check valve is disposed on the stage connection flow path. It is thus difficult for an oil to flow back to the stage connection flow path and flow into the reliquefaction line. If the oil passes through the check valve, the oil passing through the check valve is caught by the oil filter. Consequently, it is possible to prevent the oil from flowing into the reliquefaction line.
[0106]
Regarding the configuration described above, the compressor unit may further include an on-off valve that is disposed on a downstream side of the reliquefaction line and closes the stage connection flow path that connects the fifth compression stage to the sixth compression stage when the compressor unit is stopped.
[0107]
According to the configuration described above, the on-off valve is disposed on the stage connection flow path, and thus it is possible to prevent an oil from flowing into the reliquefaction line when the compressor unit is stopped.
[0108]
The techniques described in the above embodiments are appropriately used in a compressor unit mounted on a ship.

Claims (8)

Claims
1. A compressor unit that is installed in a ship and compresses a target gas that is a boil off gas generated in an LNG storage tank of the ship, the compressor unit comprising:
five compression stages that have a reciprocating system and sequentially increase a pressure of the target gas;
a crank mechanism that drives a piston of each of the compression stages; and
a stage connection flow path that connects a fourth compression stage to a fifth compression stage, wherein
the fourth compression stage is configured to have a double acting system in which a frontside space and a rear-side space inside of a cylinder are compression chambers and to discharge the target gas having a pressure of equal to or higher than 100 barG to the stage connection flow path, the fifth compression stage is configured to have a single acting system in which a frontside space inside of a cylinder forms a compression chamber for compressing the target gas whereas a rear-side space forms a non-compression chamber, the front-side space and the rear-side space being partitioned by a piston to which a piston ring is attached or in which a labyrinth seal is formed,
the fifth compression stage includes a seal member that prevents the target gas from leaking from the cylinder to a side of the crank mechanism, and
the non-compression chamber of the fifth compression stage is open to the stage connection flow path.
2. The compressor unit according to claim 1, further comprising:
a demand destination connection flow path that connects the fifth compression stage to a demand destination of the target gas; and
a reliquefaction line that branches from the stage connection flow path or the demand destination connection flow path so as to guide at least a part of the target gas discharged into the stage connection flow path or the demand destination connection flow path to a reliquefaction facility, wherein
the fourth compression stage or the fifth compression stage is configured to discharge the target gas to the stage connection flow path so as to re liquefy 10% or more of the target gas supplied to the reliquefaction facility.
3. A compressor unit that is installed in a ship and compresses a target gas that is a boil off gas generated in an LNG storage tank of the ship, the compressor unit comprising:
six compression stages that have a reciprocating system and sequentially increase a pressure of the target gas;
a crank mechanism that drives a piston of each of the compression stages; and
a stage connection flow path that connects a fifth compression stage to a sixth compression stage, wherein
the fourth compression stage and the fifth compression stage have a tandem system in which a cylinder of the fifth compression stage is disposed on a cylinder of the fourth compression stage,
a rear-side space in the cylinder of the fourth compression stage is a compression chamber, the fifth compression stage is configured to discharge the target gas having a pressure of equal to or higher than 100 barG from a compression chamber of the fifth compression stage to the stage connection flow path,
the sixth compression stage is configured to have a single acting system in which a frontside space inside of a cylinder forms a compression chamber for compressing the target gas whereas a rear-side space forms a non-compression chamber, the front-side space and the rear-side space being partitioned by a piston to which a piston ring is attached or in which a labyrinth seal is formed,
the sixth compression stage includes a seal member that prevents the target gas from leaking from the cylinder to a side of the crank mechanism, and
the non-compression chamber of the sixth compression stage is open to the stage connection flow path.
4. The compressor unit according to claim 3, wherein
the compression chamber of the fifth compression stage is partitioned from a front-side space in the cylinder of the fourth compression stage by a piston to which a piston ring is attached or in which a labyrinth seal is formed,
the compression chamber of the fourth compression stage is partitioned from the front-side space in the cylinder of the fourth compression stage by a piston to which a piston ring is attached or in which a labyrinth seal is formed, and
the front-side space in the cylinder of the fourth compression stage is a non-compression chamber that is open to another stage connection flow path that connects the fourth compression stage to the fifth compression stage.
5. The compressor unit according to claim 3 or 4, further comprising:
a demand destination connection flow path that connects the sixth compression stage to a demand destination of the target gas; and
a reliquefaction line that branches from the stage connection flow path or the demand destination connection flow path so as to guide at least a part of the target gas discharged into the stage connection flow path or the demand destination connection flow path to a reliquefaction facility, wherein
the fifth compression stage or the sixth compression stage is configured to discharge the target gas to the stage connection flow path so as to reliquefy 10% or more of the target gas supplied to the reliquefaction facility.
6. The compressor unit according to any one of claims 1 to 4, wherein all compression stages are oil-free compression stages.
7. The compressor unit according to claim 5, further comprising:
a check valve that is disposed on the stage connection flow path that connects the fifth compression stage to the sixth compression stage; and
an oil filter that is disposed on an upstream side of the check valve on the stage connection flow path that connects the fifth compression stage to the sixth compression stage, wherein
the sixth compression stage is a lubricated compression stage, and other compression stages are oil-free compression stages, and
the re liquefaction line branches from the stage connection flow path on an upstream side of the check valve and the oil filter.
8. The compressor unit according to claim 7, further comprising an on-off valve that is disposed on a downstream side of the reliquefaction line and closes the stage connection flow path that connects the fifth compression stage to the sixth compression stage when the compressor unit is stopped.
NO20200886A 2019-08-23 2020-08-07 Compressor unit NO20200886A1 (en)

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