EP2679483A1 - Machine d'entraînement à turbine à vapeur, et navire et appareil de liquéfaction de gaz équipés chacun d'une machine d'entraînement à turbine à vapeur - Google Patents

Machine d'entraînement à turbine à vapeur, et navire et appareil de liquéfaction de gaz équipés chacun d'une machine d'entraînement à turbine à vapeur Download PDF

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Publication number
EP2679483A1
EP2679483A1 EP12749246.0A EP12749246A EP2679483A1 EP 2679483 A1 EP2679483 A1 EP 2679483A1 EP 12749246 A EP12749246 A EP 12749246A EP 2679483 A1 EP2679483 A1 EP 2679483A1
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EP
European Patent Office
Prior art keywords
pressure
steam
turbine
low
ahead
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Granted
Application number
EP12749246.0A
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German (de)
English (en)
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EP2679483A4 (fr
EP2679483B1 (fr
Inventor
Masaru Oka
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Mitsubishi Shipbuilding Co Ltd
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Mitsubishi Heavy Industries Ltd
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Publication of EP2679483A4 publication Critical patent/EP2679483A4/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H21/00—Use of propulsion power plant or units on vessels
    • B63H21/02—Use of propulsion power plant or units on vessels the vessels being steam-driven
    • B63H21/06—Use of propulsion power plant or units on vessels the vessels being steam-driven relating to steam turbines
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H23/00—Transmitting power from propulsion power plant to propulsive elements
    • B63H23/02—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing
    • B63H23/10—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing for transmitting drive from more than one propulsion power unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K15/00—Adaptations of plants for special use
    • F01K15/02—Adaptations of plants for special use for driving vehicles, e.g. locomotives
    • F01K15/04—Adaptations of plants for special use for driving vehicles, e.g. locomotives the vehicles being waterborne vessels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
    • F25J1/0022—Hydrocarbons, e.g. natural gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0047—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle
    • F25J1/005—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle by expansion of a gaseous refrigerant stream with extraction of work
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0203—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 a single-component refrigerant [SCR] fluid in a closed vapor compression cycle
    • F25J1/0204—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 a single-component refrigerant [SCR] fluid in a closed vapor compression cycle as a single flow SCR cycle
    • 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
    • F25J1/0282—Steam turbine 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.
    • F25J1/0285—Combination of different types of drivers mechanically coupled to the same refrigerant compressor, possibly split on multiple compressor casings
    • F25J1/0288—Combination of different types of drivers mechanically coupled to the same refrigerant compressor, possibly split on multiple compressor casings using work extraction by mechanical coupling of compression and expansion of the refrigerant, so-called companders
    • 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
    • F25J2230/20—Integrated compressor and process expander; Gear box arrangement; Multiple compressors on a common shaft
    • 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
    • F25J2270/00—Refrigeration techniques used
    • F25J2270/14—External refrigeration with work-producing gas expansion loop
    • F25J2270/16—External refrigeration with work-producing gas expansion loop with mutliple gas expansion loops of the same refrigerant

Definitions

  • the present invention relates to a steam turbine driver including two drive shafts, and a marine vessel and a gas liquefaction apparatus each equipped with the steam turbine driver.
  • Steam turbines including a high-pressure turbine rotated upon supply of superheated steam guided from a boiler, and a low-pressure turbine rotated upon supply of superheated steam discharged from the high-pressure turbine have been known as steam turbines for rotating propellers of marine vessels (e.g., see PTL 1).
  • the high-pressure turbine and the low-pressure turbine are arranged side by side in a beam direction. Rotational output powers respectively obtained from the turbines are combined by a speed reducer to rotate one propeller. Two output shafts for rotating the propeller may be required due to an increase in the size of marine vessels.
  • a steam turbine as disclosed in PTL 2 described below has been proposed.
  • a high-pressure turbine and a low-pressure turbine are arranged side by side in a beam direction.
  • One of output shafts is driven by the high-pressure turbine, and the other of the output shafts is driven by the low-pressure turbine, thereby avoiding an increase in the installation space.
  • the output power of the high-pressure turbine and the output power of the low-pressure turbine inevitably become uneven.
  • the unevenness in the output power is eliminated by providing a shaft generator or an electric motor at each of the output shafts and electrically connecting the shaft generators or the electric motors in the steam turbine disclosed in PTL 2.
  • the steam turbine disclosed in PTL 2 can advantageously eliminate the unevenness in the output power between the respective output shafts, it is necessary to provide the shaft generators or the electric motors, resulting in a facility complication and a cost increase.
  • the present invention has been made in view of such circumstances, and an object thereof is to provide a steam turbine driver which enables using two shafts without causing an increase in installation space, and can further independently drive the two output shafts with a simple configuration, and a marine vessel and a gas liquefaction apparatus each equipped with the steam turbine driver.
  • a steam turbine driver includes: a high pressure-side turbine that is driven upon supply of steam; a first drive shaft that is driven by the high pressure-side turbine; a low pressure-side turbine that is driven upon supply of steam discharged from the high pressure-side turbine; and a second drive shaft that is driven by the low pressure-side turbine, the steam turbine driver further including a pressure control means that controls a pressure of the steam discharged from the high pressure-side turbine and supplied to the low pressure-side turbine.
  • a configuration in which two shafts using a single steam flow are provided is enabled by employing the first drive shaft driven by the high pressure-side turbine, and the second drive shaft driven by the low pressure-side turbine that is driven by supply of the steam discharged from the high pressure-side turbine in the steam turbine driver. Accordingly, the configuration with two shafts can be achieved without causing an increase in installation space.
  • the pressure control means is provided so as to control the pressure of the steam discharged from the high pressure-side turbine and supplied to the low pressure-side turbine.
  • the pressure of the steam flowing into the low pressure-side turbine can be thereby set without being affected by operating conditions of the high pressure-side turbine. Consequently, the output power of the high pressure-side turbine, and the output power of the low pressure-side turbine can be independently controlled.
  • the independent control of the two shafts can be achieved with a simple configuration in which the pressure control means is added as described above.
  • the high pressure-side turbine include a configuration in which a single high-pressure turbine driven by high-pressure superheated steam guided from a boiler is provided, and a configuration in which a medium-pressure turbine driven by superheated steam obtained by reheating exhaust steam from the high-pressure turbine by the boiler is provided in addition to the high-pressure turbine.
  • the output powers of the respective drive shafts of the steam turbine driver may be used for driving a propeller of a marine vessel, may be used as a power source of a compressor for liquefying gas, or may be used for driving a power generator.
  • the pressure control means may include: a steam dump path that branches a portion of the steam discharged from the high pressure-side turbine and guides the portion to a condenser; a pressure reducing valve that reduces the pressure of the steam flowing through the steam dump path; and a control section that controls the pressure reducing valve such that the steam flowing into the low pressure-side turbine has a predetermined pressure.
  • the pressure of the steam guided to the low pressure-side turbine is reduced by guiding a portion of the steam discharged from the high pressure-side turbine to the condenser through the steam dump path.
  • the pressure reducing valve that reduces the pressure of the steam flowing through the steam dump path is controlled by the control section such that the steam flowing into the low pressure-side turbine has a predetermined pressure value. Accordingly, the steam pressure at an inlet of the low pressure-side turbine can be independently controlled irrespective of the exhaust pressure of the high pressure-side turbine.
  • steam guided from a separate system from an exhaust system of the high pressure-side turbine may be supplied to the low pressure-side turbine.
  • the output power of the low pressure-side turbine is increased by supplying superheated steam from the separate system to the low pressure-side turbine.
  • the output power can be thereby adjusted independently from the high pressure-side turbine. Accordingly, the low pressure-side turbine can be stably controlled.
  • Examples of the steam guided from the separate system include utility steam guided from a boiler desuperheated steam line. In this case, the separate system can be made independent from a main turbine system, so that more stable operation can be expected.
  • the low pressure-side turbine may be composed of two low-pressure turbines of a first low-pressure turbine and a second low-pressure turbine provided in parallel with respect to the superheated steam supplied from the high pressure-side turbine, the steam from the separate system being supplied only to the first low-pressure turbine.
  • the low pressure-side turbine is divided into the two low-pressure turbines, and the steam from the separate system is supplied only to the first low-pressure turbine. Accordingly, the controllability of the low pressure-side turbine is improved.
  • a check valve that prevents the steam from flowing reversely from the first low-pressure turbine toward the high pressure-side turbine may be provided in a steam supply path that connects an inlet side of the first low-pressure turbine and an exhaust side of the high pressure-side turbine.
  • the pressure of the steam supplied from the separate system may become higher than the pressure of the superheated steam discharged from the high pressure-side turbine depending on pressure conditions of the superheated steam (that is, depending on a set pressure value of the pressure control means), thereby possibly causing the steam to flow reversely from the first low-pressure turbine toward the high pressure-side turbine.
  • the check valve is provided so as to prevent the reverse flow, so that stable operation is achieved.
  • a marine vessel includes: the steam turbine driver described in any of the above configurations; a first propeller that is rotationally driven by the first drive shaft; and a second propeller that is rotationally driven by the second drive shaft.
  • a twin-screw marine vessel including two propellers can be achieved by using the steam turbine driver capable of independently driving the two shafts by use of the aforementioned steam turbine driver, a marine vessel having excellent installability and cost advantages can be provided.
  • the high pressure-side turbine and the low pressure-side turbine can be applied not only to an ahead turbine, but also to an astern turbine.
  • a gas liquefaction apparatus includes: the steam turbine driver described in any of the above configurations; a first compressor that is rotationally driven by the first drive shaft; a second compressor that is rotationally driven by the second drive shaft; a first cold energy output section that obtains cold energy by expanding a refrigerant compressed by the first compressor; and a second cold energy output section that obtains cold energy by expanding a refrigerant compressed by the second compressor, wherein the first cold energy output section and the second cold energy output section cool and liquefy liquefied gas.
  • the liquefied gas is liquefied by independently driving the two compressors by use of the steam turbine driver capable of independently driving the two shafts, and thereby obtaining two expansion cycles. Accordingly, a gas liquefaction apparatus having excellent installability and cost advantages can be provided.
  • the pressure control means is provided so as to control the pressure of the superheated steam discharged from the high pressure-side turbine and supplied to the low pressure-side turbine, the output power of the high pressure-side turbine and the output power of the low pressure-side turbine can be independently controlled with a simple configuration.
  • Fig. 1 shows a steam turbine driver 1A for use in a twin-screw marine vessel including two propellers.
  • the steam turbine driver 1A includes a starboard engine 3 and a port engine 5.
  • the starboard engine 3 includes an ahead high-pressure turbine (high pressure-side turbine) 7 and an astern turbine 9.
  • Main drive steam as high-pressure superheated steam is guided to the ahead high-pressure turbine 7 from an unillustrated marine boiler through a main steam pipe 8.
  • a main steam valve 10, the opening degree of which is controlled by an unillustrated control section, is provided in the main steam pipe 8 so as to control the output power of the high-pressure turbine 7.
  • the opening degree of the main steam valve 10 is adjusted in ahead motion, and the main steam valve 10 is fully closed in astern motion.
  • the main drive steam as high-pressure superheated steam is guided to the astern turbine 9 from the unillustrated marine boiler in the astern motion.
  • the ahead high-pressure turbine 7 and the astern turbine 9 are mounted onto a single first drive shaft 4.
  • a speed reducer 20 reduces the rotational speed of the output power and transmits the output power to a propeller shaft 24 supported by a thrust bearing 22.
  • An unillustrated starboard-side propeller is mounted to a distal end of the propeller shaft 24 so as to apply a propulsive force to the marine vessel.
  • the port engine 5 includes an ahead first low-pressure turbine (low pressure-side turbine) 11, an ahead second low-pressure turbine (low pressure-side turbine) 13, and an astern turbine 15.
  • the ahead first low-pressure turbine 11, the ahead second low-pressure turbine 13, and the astern turbine 15 are mounted onto a single second drive shaft 14.
  • a speed reducer 21 reduces the rotational speed of the output power and transmits the output power to a propeller shaft 25 supported by a thrust bearing 23.
  • An unillustrated port-side propeller is mounted to a distal end of the propeller shaft 25 so as to apply a propulsive force to the marine vessel.
  • the ahead first low-pressure turbine 11 and the astern second low-pressure turbine are coaxially placed face-to-face with each other such that their expansion processes are parallel to each other.
  • An exhaust steam pipe 27 is connected to an exhaust side of the ahead high-pressure turbine 7.
  • a first supply pipe 29 connected to a steam inlet of the ahead first low-pressure turbine 11, a second supply pipe 31 connected to an inlet of the ahead second low-pressure turbine 13, and a steam dump pipe (steam dump path) 33 connected to an unillustrated condenser are also connected to the downstream side of the exhaust steam pipe 27.
  • a pressure reducing valve 35 the opening degree of which is adjustable within a range from a fully closed state to a fully open state, is provided in the steam dump pipe 33. The opening degree of the pressure reducing valve 35 is controlled by an unillustrated control section.
  • the steam dump pipe 33, the pressure reducing valve 35, and the control section that controls the pressure reducing valve 35 constitute a pressure control means that controls the pressure of superheated steam supplied to the respective low-pressure turbines 11 and 13.
  • a low-pressure drive steam pipe 37 is connected to a steam inlet of the ahead first low-pressure turbine 11.
  • Low-pressure drive steam as utility steam is guided from a boiler desuperheated steam line and supplied to the ahead first low-pressure turbine 11.
  • a low-pressure drive steam valve 38 is provided in the low-pressure drive steam pipe 37. Accordingly, the low-pressure drive steam from the low-pressure drive steam pipe 37 as well as the steam discharged from the ahead high-pressure turbine 7 is supplied to the ahead first low-pressure turbine 11.
  • the steam turbine driver 1A having the above configuration operates as follows.
  • the main drive steam as high-pressure superheated steam is supplied to the ahead high-pressure turbine 7 from the marine boiler to rotationally drive the ahead high-pressure turbine 7.
  • the propeller shaft 24 is driven via the first drive shaft 4 and the speed reducer 20, and the starboard-side propeller is rotated. An ahead thrust is thereby generated.
  • the output power of the starboard-side propeller is adjusted by the opening degree of the main steam valve 10.
  • the superheated steam discharged from the ahead high-pressure turbine 7 flows through the exhaust steam pipe 27, and flows through the first supply pipe 29 and the second supply pipe 31 provided in parallel with each other.
  • the superheated steam flowing through the first supply pipe 29 is guided to the ahead first low-pressure turbine 11 to rotationally drive the ahead first low-pressure turbine 11.
  • the superheated steam flowing through the second supply pipe 31 is guided to the ahead second low-pressure turbine 13 to rotationally drive the ahead second low-pressure turbine 13.
  • the pressure of the superheated steam supplied to the respective low-pressure turbines 11 and 13 as described above is adjusted by the pressure reducing valve 35 provided in the steam dump pipe 33.
  • the amount of steam guided to the condenser through the steam dump pipe 33 is increased by increasing the opening degree of the pressure reducing valve 35, so that the pressure of the superheated steam guided to the respective low-pressure turbines 11 and 13 is lowered.
  • the amount of steam guided to the condenser through the steam dump pipe 33 is reduced by decreasing the opening degree of the pressure reducing valve 35, so that the pressure of the superheated steam guided to the respective low-pressure turbines 11 and 13 is raised.
  • the opening degree control of the pressure reducing valve 35 is performed by the unillustrated control section. The opening degree is adjusted based on a thrust required for the port-side propeller.
  • the propeller shaft 25 is driven via the second drive shaft 14 and the speed reducer 21, and the port-side propeller is rotated. An ahead thrust is thereby generated.
  • the output power of the port-side propeller is adjusted by the opening degree of the pressure reducing valve 35 as described above.
  • the low-pressure drive steam guided from the low-pressure drive steam pipe 37 is supplied to the ahead first low-pressure turbine 11.
  • the pressure of the supplied low-pressure drive steam is controlled by the low-pressure drive steam valve 38.
  • the steam obtained after rotationally driving the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13 is guided to the condenser as exhaust steam.
  • the main drive steam is supplied to the respective astern turbines 9 and 15 to rotationally drive the turbines 9 and 15. Accordingly, the starboard-side propeller and the port-side propeller are rotated in a reverse direction to generate an astern thrust.
  • the steam obtained after rotationally driving the respective astern turbines 9 and 15 is guided to the condenser as exhaust steam.
  • a configuration in which two shafts using a single steam flow are provided is enabled by employing the first drive shaft 4 driven by the ahead high-pressure turbine 7, and the second drive shaft 14 driven by the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13 that are driven by supply of the steam discharged from the high-pressure turbine 7. Accordingly, the configuration with two shafts can be achieved without causing an increase in installation space.
  • the steam dump pipe 33 and the pressure reducing valve 35 are provided so as to control the pressure of the steam discharged from the ahead high-pressure turbine 7 and supplied to the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13. Accordingly, the pressure of the steam flowing into the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13 can be set without being affected by operating conditions of the ahead high-pressure turbine 7. Consequently, the output power of the ahead high-pressure turbine 7, and the output power of the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13 can be independently controlled.
  • the independent control of the two shafts can be achieved with a simple configuration in which the steam dump pipe 33, the pressure reducing valve 35, and the control section that controls the pressure reducing valve are added as described above.
  • the low-pressure drive steam is supplied from the low-pressure drive steam pipe 37 as a separate superheated steam supply system from the first supply pipe 29 and the second supply pipe 31 in which the exhaust steam from the ahead high-pressure turbine 7 is guided.
  • the output power of the ahead first low-pressure turbine 11 can be thereby increased independently from a main steam system guided to the ahead high-pressure turbine 7. Accordingly, the port engine 5 driven by the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13 can be stably controlled.
  • the low pressure-side turbine is divided into the two low-pressure turbines (the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13), and the steam is supplied only to the ahead first low-pressure turbine 11 from the low-pressure drive steam pipe 37. Accordingly, the controllability of the low pressure-side turbine (the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13) is improved.
  • FIG. 2 a second embodiment of the present invention will be described based on Fig. 2 .
  • the present embodiment is achieved by further improving the configuration of the first embodiment. Therefore, the same components as those in the configuration of the first embodiment are assigned the same reference numerals, and the description thereof is omitted.
  • An ahead medium-pressure turbine 40 mounted onto the same first drive shaft 4 as that of the ahead high-pressure turbine 7 is provided in the starboard engine 3 of a steam turbine driver 1B in the present embodiment.
  • the ahead high-pressure turbine 7 and the ahead medium-pressure turbine 40 constitute the high pressure-side turbine.
  • the ahead medium-pressure turbine 40 is driven by superheated steam obtained by reheating the exhaust steam from the ahead high-pressure turbine 7 by a reheater 42.
  • a bypass pipe 44 is branched from the exhaust steam pipe 27 on the exhaust side of the high-pressure turbine 7.
  • the exhaust steam is partially guided to the reheater 42 through the bypass pipe 44 and reheated therein.
  • the reheated steam is guided to the ahead medium-pressure turbine 40 through a reheated steam supply pipe 46.
  • the flow rate of the steam bypassed to the reheater 42 is determined by adjusting the opening degree of a bypass valve 49 that is provided in the exhaust steam pipe 27 of the ahead high-pressure turbine 7.
  • the opening degree of the bypass valve 49 is controlled based on a predetermined function given to a first control section 52.
  • the opening degree of the bypass valve 49 is increased to reduce the flow rate of the steam bypassed to the reheater 42.
  • the opening degree of the bypass valve 49 is decreased to increase the flow rate of the steam bypassed to the reheater 42.
  • the reheater 42 is generally configured as a portion of the unillustrated marine boiler.
  • the first control section 52 also controls the main steam valve 10.
  • the main steam valve 10 is controlled such that the opening degree is increased along with an increase in the ahead rotational speed (RPM (AHEAD)), that is, a throttle is applied as shown by a pattern indicated by reference numeral 22.
  • RPM ahead rotational speed
  • the superheated steam discharged from the ahead medium-pressure turbine 40 passes through an exhaust steam pipe 48, and joins the exhaust steam guided from the ahead high-pressure turbine 7 at a junction 50.
  • the steam is branched into the steam dump pipe 33 from a junction exhaust steam pipe 54 provided after the junction, and, similarly to the first embodiment, further branched into the first supply pipe 29 and the second supply pipe 31 connected in parallel with each other.
  • a pressure sensor 56 that measures the pressure of the steam reduced by the pressure reducing valve 35 provided in the steam dump pipe 33 is provided in the junction exhaust steam pipe 54.
  • the pressure sensor 56 also partially constitutes the pressure control means of the present invention.
  • a measurement pressure value PV measured by the pressure sensor 56 is fed to a second control section 58.
  • the second control section 58 compares a set pressure value SV given from outside and the measurement pressure value PV, and outputs an instruction value OP obtained by, for example, PID control to the pressure reducing valve 35 so as to obtain the set pressure value SV.
  • the opening degree of the pressure reducing valve 35 is controlled based on the instruction value OP.
  • the dump steam, the pressure of which is reduced through the pressure reducing valve 35, is guided to a condenser 60.
  • the superheated steam is guided to the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13 through the first supply pipe 29 and the second supply pipe 31, respectively.
  • a check valve 62 is provided in the first supply pipe 29.
  • the check valve 62 prevents the steam from flowing reversely from the ahead first low-pressure turbine 11 toward the high pressure-side turbine (the ahead high-pressure turbine 7 and the ahead medium-pressure turbine 40).
  • the steam obtained after passing through the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13 is guided to the condenser 60.
  • a pressure reducing valve 64 that controls the pressure of the utility steam to a constant value is provided in the low-pressure drive steam pipe 37.
  • the low-pressure drive steam passing through the pressure reducing valve 64 is branched at a branch point 66, and thereafter guided to the low-pressure drive steam valve 38.
  • the opening degree of the low-pressure drive steam valve 38 is controlled by a third control section 68.
  • the low-pressure drive steam valve 38 is controlled such that the opening degree is increased along with an increase in the ahead rotational speed (RPM (AHEAD)). Accordingly, a deficiency in the output power of the low pressure-side turbine (the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13) is compensated for independently from the main steam. While the opening degree of the low-pressure drive steam valve 38 is controlled as described above in the ahead motion, the low-pressure drive steam valve 38 is fully closed in the astern motion.
  • a high-pressure astern turbine 70 on the starboard side, and a low-pressure astern turbine 72 driven by exhaust steam from the high-pressure astern turbine 70 are employed instead of the astern turbines 9 and 15 both driven by the main steam in the first embodiment.
  • the high-pressure astern turbine 70 is rotationally driven by the main steam guided from an astern main steam pipe 74 that is branched from the main steam pipe 8.
  • a main steam valve 76 is provided in the astern main steam pipe 74.
  • the opening degree of the main steam valve 76 is controlled by a fourth control section 78.
  • the opening degree of the main steam valve 76 is controlled in the astern motion, and the main steam valve 76 is fully closed in the ahead motion.
  • the superheated steam discharged from the high-pressure astern turbine 70 passes through an astern exhaust steam pipe 78, and is then branched into a steam dump pipe 80.
  • a pressure reducing valve 82 is provided in the steam dump pipe 80.
  • a pressure sensor 84 that measures the pressure of the steam reduced by the pressure reducing valve 82 is provided in the astern exhaust steam pipe 78.
  • a measurement pressure value PV measured by the pressure sensor 84 is fed to a fifth control section 86.
  • the fifth control section 86 compares a set pressure value SV given from outside and the measurement pressure value PV, and outputs an instruction value OP obtained by, for example, PID control to the pressure reducing valve 82 so as to obtain the set pressure value SV.
  • the opening degree of the pressure reducing valve 82 is controlled based on the instruction value OP.
  • the steam dump pipe 80, the pressure reducing valve 82, the pressure sensor 84, and the fifth control section 86 for the astern motion constitute the pressure control means of the present invention.
  • the dump steam, the pressure of which is reduced through the pressure reducing valve 82, is guided to the condenser 60.
  • the superheated steam flowing through the astern exhaust steam pipe 78 without being branched into the steam dump pipe 80 is guided to the low-pressure astern turbine 72 through a supply pipe 88.
  • a low-pressure steam valve 90 is provided in the exhaust steam pipe 78.
  • the opening degree of the low-pressure steam valve 90 is controlled by a sixth control section 92.
  • the low-pressure steam valve 90 is controlled such that the opening degree is increased along with an increase in an astern rotational speed (RPM (ASTERN)), that is, a throttle is applied as shown by a pattern indicated by reference numeral 92.
  • An astern low-pressure drive steam pipe 96 that is branched from the branch point 66 of the low-pressure drive steam pipe 37 and joins the astern supply pipe 88 at a junction 94 is provided.
  • An astern low-pressure drive steam valve 98 is provided in the low-pressure drive steam pipe 96.
  • the opening degree of the low-pressure drive steam valve 98 is controlled by the sixth control section 92. For example, as shown by a pattern indicated by reference numeral 92, when the astern rotational speed (RPM (ASTERN)) is low, the low-pressure drive steam valve 98 is fully closed. When the astern rotational speed (RPM (ASTERN)) exceeds a predetermined value, the opening degree is gradually increased so as to increase the output power.
  • the low-pressure steam valve 90 and the low-pressure drive steam valve 98 for the astern motion are fully closed in the ahead motion.
  • the steam turbine driver 1B having the above configuration operates as described below.
  • the main steam valve 76, the low-pressure steam valve 90, and the low-pressure drive steam valve 98 for the astern motion are fully closed.
  • the main drive steam as high-pressure superheated steam is supplied to the ahead high-pressure turbine 7 from the marine boiler to rotationally drive the ahead high-pressure turbine 7.
  • the propeller shaft 24 is driven via the first drive shaft 4 and the speed reducer 20, and the starboard-side propeller is rotated. An ahead thrust is thereby generated.
  • the output power of the starboard-side propeller is adjusted by the opening degree of the main steam valve 10 controlled by the first control section 52.
  • the superheated steam discharged from the ahead high-pressure turbine 7 flows through the exhaust steam pipe 27.
  • a portion of the superheated steam is branched into the bypass pipe 44 according to the opening degree of the bypass valve 49 controlled by the first control section 52, and a remaining portion thereof flows to the downstream side of the exhaust steam pipe 27.
  • the superheated steam flowing through the bypass pipe 44 is reheated in the reheater 42 to become the reheated steam, which is guided to the ahead medium-pressure turbine 40 through the reheated steam supply pipe 46.
  • the superheated steam obtained after rotationally driving the ahead medium-pressure turbine 40 passes through the exhaust steam pipe 48, and joins the exhaust steam guided from the ahead high-pressure turbine 7 at the junction 50.
  • the superheated steam then flows through the first supply pipe 29 and the second supply pipe 31 provided in parallel with each other.
  • the superheated steam flowing through the first supply pipe 29 and the check valve 29 is guided to the ahead first low-pressure turbine 11 to rotationally drive the ahead first low-pressure turbine 11.
  • the superheated steam flowing through the second supply pipe 31 is guided to the ahead second low-pressure turbine 13 to rotationally drive the ahead second low-pressure turbine 13.
  • the pressure of the superheated steam supplied to the respective low-pressure turbines 11 and 13 as described above is adjusted by the pressure reducing valve 35 provided in the steam dump pipe 33. That is, the opening degree of the pressure reducing valve 35 is adjusted so as to obtain the set pressure value SV by the second control section 58 that controls the opening degree based on the measurement pressure value PV of the pressure sensor 56. To be more specific, the amount of steam guided to the condenser 60 through the steam dump pipe 33 is increased by increasing the opening degree of the pressure reducing valve 35, so that the pressure of the superheated steam guided to the respective low-pressure turbines 11 and 13 is lowered.
  • the amount of steam guided to the condenser through the steam dump pipe 33 is reduced by decreasing the opening degree of the pressure reducing valve 35, so that the pressure of the superheated steam guided to the respective low-pressure turbines 11 and 13 is raised.
  • the set pressure value SV given to the second control section 58 may be set to a variable value so as not to unnecessarily dump the steam.
  • the propeller shaft 25 is driven via the second drive shaft 14 and the speed reducer 21, and the port-side propeller is rotated. An ahead thrust is thereby generated.
  • the output power of the port-side propeller is adjusted by the opening degree of the pressure reducing valve 35 as described above.
  • the low-pressure drive steam guided from the low-pressure drive steam pipe 37 is supplied to the ahead first low-pressure turbine 11.
  • the pressure of the supplied low-pressure drive steam is adjusted by the low-pressure drive steam valve 38 controlled by the third control section 68.
  • the steam obtained after rotationally driving the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13 is guided to the condenser 60 as exhaust steam.
  • the main steam valve 10 and the low-pressure drive steam valve 38 for the ahead motion are fully closed. Since the same operation as that in the ahead motion is performed in the astern motion, the description thereof is omitted. That is, the operation is similar to that in the ahead motion in that the high-pressure astern turbine 70 is driven by the main drive steam and the low-pressure astern turbine 72 is driven by the exhaust steam from the high-pressure astern turbine 70, in that the pressure control is performed by the steam dump pipe 80, the pressure reducing valve 83, the pressure sensor 84, and the fifth control section 86, and in that the low-pressure astern turbine 72 is assist-driven by the low-pressure drive steam adjusted by the low-pressure drive steam valve 98.
  • a configuration in which two shafts using a single steam flow are provided is enabled by employing the first drive shaft 4 driven by the ahead high-pressure turbine 7 and the ahead medium-pressure turbine 40, and the second drive shaft 14 driven by the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13 that are driven by supply of the steam discharged from the high-pressure turbine 7. Accordingly, the configuration with two shafts can be achieved without causing an increase in installation space.
  • the steam dump pipe 33 and the pressure reducing valve 35 are provided so as to control the pressure of the steam discharged from the ahead high-pressure turbine 7 and the ahead medium-pressure turbine 40 and supplied to the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13. Accordingly, the pressure of the steam flowing into the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13 can be set without being affected by operating conditions of the ahead high-pressure turbine 7. Consequently, the output power of the ahead high-pressure turbine 7, and the output power of the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13 can be independently controlled.
  • the independent control of the two shafts can be achieved with a simple configuration in which the steam dump pipe 33, the pressure reducing valve 35, and the control section that controls the pressure reducing valve are added as described above.
  • the steam dump pipe 80 and the pressure reducing valve 82 are provided so as to control the pressure of the steam supplied to the low-pressure astern turbine 72 in a similar manner to the ahead turbines. The same effects as those of the ahead turbines are thereby obtained.
  • the low-pressure drive steam is supplied from the low-pressure drive steam pipe 37 as a separate superheated steam supply system from the first supply pipe 29 and the second supply pipe 31 in which the exhaust steam from the ahead high-pressure turbine 7 and the ahead medium-pressure turbine 40 is guided.
  • the output power of the ahead first low-pressure turbine 11 can be thereby increased independently from a main steam system guided to the ahead high-pressure turbine 7 and the ahead medium-pressure turbine 40. Accordingly, the port engine 5 driven by the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13 can be stably controlled.
  • the low pressure-side turbine is divided into the two low-pressure turbines (the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13), and the steam is supplied only to the ahead first low-pressure turbine 11 from the low-pressure drive steam pipe 37. Accordingly, the controllability of the low pressure-side turbine (the ahead first low-pressure turbine 11 and the ahead second low-pressure turbine 13) is improved.
  • the pressure of the low-pressure drive steam supplied to the first low-pressure turbine 11 may become relatively higher than the pressure of the superheated steam discharged from the high pressure-side turbines 7 and 40 depending on pressure conditions of the superheated steam (that is, depending on the set pressure value SV of the second control section 58), thereby possibly causing the steam to flow reversely from the first low-pressure turbine 11 toward the high pressure-side turbines 7 and 40.
  • the check valve 62 is provided in the first supply pipe 29. Accordingly, stable operation is achieved.
  • a third embodiment of the present invention will be described based on Fig. 3 .
  • the gas liquefaction apparatus 100 cools and liquefies natural gas (NG) as a raw material of liquefied gas such as LNG (liquefied natural gas).
  • NG natural gas
  • LNG liquefied natural gas
  • the gas liquefaction apparatus 100 uses the aforementioned steam turbine drivers 1A and 1B as a drive source of a compressor that constitutes a refrigeration cycle.
  • a high pressure-side turbine 102 a low pressure-side turbine 103, a pressure control means (not shown), an assist drive (not shown) using low-pressure drive steam, a first drive shaft 105, and a second drive shaft 107 have the same configurations as those of the first embodiment and the second embodiment.
  • the gas liquefaction apparatus 100 includes a first compressor 109 that is rotationally driven by the first drive shaft 105, and a second compressor 111 that is rotationally driven by the second drive shaft 107.
  • Each of the compressors 109 and 111 includes a coaxial two-stage compression section rotationally driven by each of the drive shafts 105 and 107.
  • a compressed refrigerant e.g., nitrogen
  • a first cold energy output section that obtains cold energy by expanding the refrigerant compressed by the first compressor 109, and a second cold energy output section that obtains cold energy by expanding the refrigerant compressed by the second compressor 111 are provided (a so-called double expansion cycle).
  • the first cold energy output section and the second cold energy output section cool and liquefy natural gas as a raw material of LNG.
  • the steam turbine drivers 1A and 1B capable of independently controlling the two shafts so as to achieve a refrigeration cycle having two expansion sections as in the present embodiment, a gas liquefaction apparatus having excellent installability and cost advantages can be provided. Also, since the respective drive shafts can be independently controlled, one of the compressors can be used as a high-pressure compressor, and another of the compressors can be used as a low-pressure compressor. Accordingly, highly efficient liquefaction can be achieved.
  • a fourth embodiment of the present invention will be described based on Fig. 4 .
  • the steam turbine drivers 1A and 1B are applied to the twin-screw marine vessel.
  • an example in which the steam turbine driver used as a marine vessel propulsion unit is converted into a power-generating driver is described as another application of the steam turbine driver.
  • an output mechanism section 201 composed of a speed reducer, a propeller shaft or the like is provided at an output destination of a steam turbine driver, that is, on the output sides of respective drive shafts 205 and 207.
  • a steam turbine driver that is, on the output sides of respective drive shafts 205 and 207.
  • the output mechanism section 201 becomes unnecessary.
  • the output mechanism section 201 is removed, and the steam turbine driver is converted into the steam turbine drivers 1A and 1B similar to the first embodiment and the second embodiment.
  • a pressure control means such as the steam dump pipe 33 and the pressure reducing valve 35, and an assist-drive system such as the low-pressure drive steam pipe 37 and the low-pressure drive steam valve 38 for guiding low-pressure drive steam such as utility steam are added between an existing high pressure-side turbine 202 and an existing low pressure-side turbine 203.
  • the first drive shaft 205 and the second drive shaft 207 are also respectively connected with a first power generator 209 and a second power generator 211 driven by the rotation thereof.
  • the existing propulsion unit can be converted so as to drive the power generator. Also, since the respective drive shafts 205 and 207 can be independently controlled, the steam turbine drivers 1A and 1B can freely adjust the electric power generations of the respective power generators 209 and 211, and can thereby flexibly respond to a demand for electric power.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Thermal Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Control Of Turbines (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP12749246.0A 2011-02-25 2012-02-09 Machine d'entraînement à turbine à vapeur, et navire et appareil de liquéfaction de gaz équipés chacun d'une machine d'entraînement à turbine à vapeur Active EP2679483B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011040717A JP5818459B2 (ja) 2011-02-25 2011-02-25 蒸気タービン駆動機、並びに、蒸気タービン駆動機を備えた船舶及びガス液化装置
PCT/JP2012/053017 WO2012114892A1 (fr) 2011-02-25 2012-02-09 Machine d'entraînement à turbine à vapeur, et navire et appareil de liquéfaction de gaz équipés chacun d'une machine d'entraînement à turbine à vapeur

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EP2679483A1 true EP2679483A1 (fr) 2014-01-01
EP2679483A4 EP2679483A4 (fr) 2017-05-17
EP2679483B1 EP2679483B1 (fr) 2019-04-10

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EP (1) EP2679483B1 (fr)
JP (1) JP5818459B2 (fr)
KR (1) KR101624017B1 (fr)
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WO (1) WO2012114892A1 (fr)

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JP6415997B2 (ja) * 2015-01-23 2018-10-31 三菱重工業株式会社 船舶の統合制御装置、それを備えた船舶、及び統合制御方法並びにプログラム
KR200488336Y1 (ko) 2017-01-04 2019-01-15 한전케이피에스 주식회사 저압터빈의 구동기 커플링용 분해 조립 작업대
JP7316068B2 (ja) * 2019-03-15 2023-07-27 三菱重工マリンマシナリ株式会社 浮体式設備及び浮体式設備の製造方法
CN113006885A (zh) * 2021-03-23 2021-06-22 攀钢集团西昌钢钒有限公司 一种汽轮发电机组定压运行控制方法
CN114993067B (zh) * 2022-07-28 2022-10-14 中国船舶重工集团公司第七一九研究所 一种船用防摇摆水箱及其参数设计方法

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JPS59192806A (ja) * 1983-04-15 1984-11-01 Hitachi Ltd ２軸蒸気タ−ビンのストレツチアウトラン運転方法およびその装置
DE69001679T2 (de) * 1989-01-26 1993-11-11 Gen Electric Überdrehzahlsicherung für ein Kombikraftwerk mit Gas/Dampf-Turbinen.
JPH0446892A (ja) * 1990-06-12 1992-02-17 Mitsubishi Heavy Ind Ltd Ｌｎｇ運搬船の推進装置
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JP4801465B2 (ja) * 2006-02-21 2011-10-26 三菱重工業株式会社 舶用推進プラントおよびこれを備えた船舶ならびに舶用推進プラントの制御方法
DE102006040857B4 (de) * 2006-08-31 2008-11-20 Siemens Ag Verfahren zum Betrieb eines Schiffes sowie Schiff mit einem Antriebssystem mit Abwärmerückgewinnung
JP5030710B2 (ja) * 2007-08-30 2012-09-19 三菱重工業株式会社 蒸気タービン船
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Also Published As

Publication number Publication date
WO2012114892A1 (fr) 2012-08-30
JP2012176691A (ja) 2012-09-13
EP2679483A4 (fr) 2017-05-17
EP2679483B1 (fr) 2019-04-10
CN103380056B (zh) 2016-05-11
KR20130106889A (ko) 2013-09-30
KR101624017B1 (ko) 2016-05-24
JP5818459B2 (ja) 2015-11-18
CN103380056A (zh) 2013-10-30

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