KR101624017B1 - Steam turbine driving machine, and ship and gas liquefaction apparatus each equipped with steam turbine driving machine - Google Patents

Steam turbine driving machine, and ship and gas liquefaction apparatus each equipped with steam turbine driving machine Download PDF

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KR101624017B1
KR101624017B1 KR1020137021871A KR20137021871A KR101624017B1 KR 101624017 B1 KR101624017 B1 KR 101624017B1 KR 1020137021871 A KR1020137021871 A KR 1020137021871A KR 20137021871 A KR20137021871 A KR 20137021871A KR 101624017 B1 KR101624017 B1 KR 101624017B1
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pressure
steam
turbine
low
driven
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KR1020137021871A
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Korean (ko)
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KR20130106889A (en
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마사루 오카
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미츠비시 쥬고교 가부시키가이샤
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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

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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)

Abstract

Provided is a steam turbine driver capable of independently driving two output shafts by a simple configuration after bimaxing without causing an increase in installation space. A first driving shaft 4 driven by a forward high pressure turbine 7 and a steam exhausted from a forward high pressure turbine 7 are supplied and driven A second drive shaft 14 driven by a forward first low pressure turbine 11 and a forward second low pressure turbine 13 and a forward first low pressure turbine 11 and a forward second low pressure turbine 13, (1), which is exhausted from a forward high pressure turbine (7) and controls the pressure of the steam supplied to the first low pressure turbine (11) for advancing and the second low pressure turbine (13) for forwarding, A dump pipe 33 and a pressure reducing valve 35 are provided.

Figure R1020137021871

Description

TECHNICAL FIELD [0001] The present invention relates to a steam turbine actuator, a steam turbine drive device, and a steam turbine drive device, and a gas liquefaction device,

The present invention relates to a steam turbine driver having two drive shafts, and to a ship having a steam turbine driver and a gas liquefaction device.

A high pressure turbine in which superheated steam derived from a boiler is supplied and rotated as a steam turbine for rotating a propeller of a ship and a low pressure turbine in which superheated steam exhausted from a high pressure turbine is supplied and rotated is known 1). In this marine steam turbine, a high-pressure turbine and a low-pressure turbine are arranged side by side in the line width direction, and each rotary output obtained from these turbines is combined by a reduction gear to rotate one propeller.

In the case where the output shaft for rotating the propeller is required to be biaxially due to enlargement of the ship or the like, if a steam turbine described in Patent Document 1 is applied, a high-pressure turbine and a low-pressure turbine are required for each output shaft. However, in the engine room, there is a limitation in the installation space (especially in the line width direction), and it is difficult to install the engine space.

Therefore, when the ship is required to be biaxially drawn, a low-speed diesel direct-coupled system or an electric motor propulsion system is mainly employed.

In order to solve the problem of installation space of such a steam turbine, a steam turbine described in Patent Document 2 below has been proposed. This steam turbine arranges the high pressure turbine and the low pressure turbine in a line width direction, drives one of the output shafts by the high pressure turbine, and drives the other output shaft by the low pressure turbine, thereby avoiding an increase in installation space.

However, since a single flow type of superheated steam which drives the low pressure turbine by the superheated steam discharged from the high pressure turbine is employed, an imbalance of the high pressure turbine output and the low pressure turbine output inevitably occurs. In order to solve this problem, the steam turbine disclosed in this document has an axis generator and an electric motor formed on each output shaft and electrically connected to each other, thereby eliminating the unbalance of the respective outputs.

Japanese Laid-Open Patent Publication No. 2006-17007 ([0027], Fig. 1) Japanese Laid-Open Patent Publication No. 2009-56868

The steam turbine disclosed in Patent Document 2 is excellent in that output unbalance of each output shaft can be solved, but it is necessary to form an axial generator and an electric motor, which leads to an increase in facility complexity and cost.

SUMMARY OF THE INVENTION The present invention has been made in view of such circumstances, and it is an object of the present invention to provide a steam turbine driver capable of independently driving two output shafts by a simple configuration after bimaxing without causing an increase in installation space, It is an object of the present invention to provide a vessel equipped with a driving machine and a gas liquefaction apparatus.

Means for Solving the Problems In order to solve the above problems, a steam turbine driver of the present invention and a ship having a steam turbine driver and a gas liquefier employ the following means.

That is, a steam turbine driver according to a first aspect of the present invention includes: a high-pressure side turbine to which steam is supplied and driven; a first drive shaft driven by the high-pressure side turbine; Pressure side turbine and a second drive shaft driven by the low-pressure side turbine, wherein the steam turbine driver includes pressure control means for controlling the pressure of the steam exhausted from the high-pressure side turbine and supplied to the low-pressure side turbine .

The steam turbine driver employs a first drive shaft driven by a high pressure side turbine and a second drive shaft driven by a low pressure side turbine driven by supplying steam exhausted from a high pressure side turbine, The biaxialization can be realized without causing an increase in installation space.

Pressure turbine exhausted from the high-pressure turbine and controlling the pressure of the steam supplied to the low-pressure turbine, the pressure of the steam flowing into the low-pressure turbine is controlled by the pressure of the high- . Thus, the output of the high-pressure side turbine and the output of the low-pressure side turbine can be independently controlled. As described above, the biaxial independent control can be realized with a simple configuration in which the pressure control means is added.

The high-pressure side turbine includes a high-pressure turbine driven by a high-pressure superheated steam from the boiler. In addition to the high-pressure turbine, the superheated steam obtained by reheating the exhaust steam from the high- And an intermediate pressure turbine driven.

Further, the output of each drive shaft of the steam turbine driver may be used, for example, for driving a propeller of a ship, as a power source for a compressor for liquefying the gas, or for driving a generator.

Further, in the steam turbine driver according to the first aspect, the pressure control means includes a steam dump path for branching a part of the steam exhausted from the high-pressure turbine into a condenser, and a steam dump path for reducing steam flowing through the steam dump path And a control unit for controlling the pressure reducing valve so that steam flowing to the low pressure side turbine becomes a predetermined pressure.

A portion of the steam exhausted from the high-pressure side turbine is guided to the condenser through the steam dump path to reduce the pressure of the steam introduced into the low-pressure side turbine. At this time, the control unit controls the pressure reducing valve that reduces the pressure of the steam flowing in the steam dump path, and the pressure of the steam flowing to the low pressure side turbine is set to a predetermined value. Thus, the inlet vapor pressure of the low-pressure side turbine can be independently controlled regardless of the exhaust pressure of the high-pressure side turbine.

The steam turbine driver according to the first aspect may be configured such that steam derived from a separate system different from the exhaust system of the high-pressure turbine is supplied to the low-pressure turbine.

The superheated steam of the separate system is supplied to the low pressure side turbine to increase the output of the low pressure side turbine. As a result, the output can be increased or decreased independently of the high-pressure side turbine, so that the low-pressure side turbine can be stably controlled.

The steam derived from the separate system may be, for example, a utility steam derived from a boiler reheat steam line. Thereby, it can be independent from the main turbine system, and more stable operation can be expected.

In the above configuration, the low-pressure turbine is composed of two low-pressure turbines, a first low-pressure turbine and a second low-pressure turbine formed in parallel with the superheated steam supplied from the high-pressure turbine, The steam may be supplied from the separate system.

The low-pressure turbine is divided into two low-pressure turbines, and steam is supplied from a separate system to only one of the first low-pressure turbines. This improves the controllability of the low-pressure side turbine.

In the above arrangement, the steam supply path for connecting the inlet side of the first low-pressure turbine and the exhaust side of the high-pressure turbine is provided with a steam supply passage for preventing the backward flow of steam from the first low- A valve is formed.

The steam from the separate system is supplied to the first low-pressure turbine. Therefore, depending on the pressure condition of the superheated steam exhausted from the high-pressure turbine (that is, depending on the set pressure value of the pressure control means) The steam may flow backward from the first low-pressure turbine to the high-pressure-side turbine. In order to prevent this backflow, a check valve is formed to realize stable operation.

The ship according to the second aspect of the present invention is characterized in that it comprises a steam turbine actuator described in any of the above, a first propeller rotationally driven by the first drive shaft, and a second propeller rotationally driven by the second drive shaft Respectively.

Since the steam turbine driver described above can be used to realize a biaxial ship having two propellers using a steam turbine driver capable of independently driving two axes, Can be provided.

Further, the high-pressure side turbine and the low-pressure side turbine can be applied not only to the forward turbine but also to the reverse turbine.

According to a third aspect of the present invention, there is provided a gas liquefier comprising: the steam turbine actuator described in any of the above; a first compressor rotationally driven by the first drive shaft; a second compressor rotationally driven by the second drive shaft; A first cold / hot output section for expanding the refrigerant compressed by the first compressor to obtain cold heat, and a second cold / heat output section for expanding the refrigerant compressed by the second compressor to obtain cold heat, And the liquefied gas is cooled by the one cold / heat output section and the second cold / heat output section to liquefy.

By using a steam turbine actuator capable of independently driving two axes, two liquefied gases were liquefied by independently driving two compressors and obtaining two expansion cycles. Thereby, it is possible to provide a gas liquefier which is advantageous in terms of installation property and cost.

Pressure side turbine and the pressure control means for controlling the pressure of superheated steam exhausted from the high-pressure side turbine and supplied to the low-pressure side turbine. Therefore, the output of the high-pressure side turbine and the output of the low- have.

1 is a schematic configuration diagram showing a steam turbine driver according to a first embodiment of the present invention.
2 is a schematic structural view showing a steam turbine actuator according to a second embodiment of the present invention.
3 is a schematic structural view showing an example in which the steam turbine driver of the present invention is applied to a gas liquefier.
4 is a schematic diagram showing an example in which the steam turbine driver of the present invention is applied when the FSRU is converted from the existing one axis.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described with reference to the drawings.

[First Embodiment]

A first embodiment of the present invention will be described below with reference to Fig.

Fig. 1 shows a steam turbine actuator 1A used for a biaxial cable provided with two propellers. The steam turbine actuator 1A has a starboard machine 3 and a port machine 5.

The starboard machine (3) is provided with a forward high pressure turbine (high pressure side turbine) (7) and a reverse turbine (9).

In the high-pressure turbine 7 for advancement, a main drive steam made of a high-pressure superheated steam is led from a ship boiler (not shown) through the main steam pipe 8. The main steam pipe 8 is provided with a main steam valve 10 which performs opening control by a control unit (not shown), whereby the output of the high-pressure turbine 7 is controlled. The main steam valve 10 is subjected to opening adjustment at the time of forward movement and is fully closed at the time of backward movement.

In the backward turbine 9, the main drive steam made of high-pressure superheated steam is derived from a ship boiler (not shown) at the time of backward movement.

The forward high pressure turbine 7 and the reverse turbine 9 are mounted on the same first drive shaft 4 and the output thereof is decelerated through the speed reducer 20 and then transmitted to the thrust bearing 22 And is transmitted to the propeller shaft 24. A starboard-side propeller (not shown) is mounted on the tip of the propeller shaft 24 to impart propulsion to the ship.

The port assembly 5 is provided with a first low pressure turbine (low pressure side turbine) 11 for advancing, a second low pressure turbine (low pressure side turbine) 13 for advancing, and a reverse turbine 15. The forward first low pressure turbine 11, the forward second low pressure turbine 13 and the reverse turbine 15 are mounted on the same second drive shaft 14 and the output thereof is transmitted to the speed reducer 21 And is then transmitted to the propeller shaft 25 supported by the thrust bearing 23. At the tip of the propeller shaft 25, a not-shown port side propeller is mounted, giving a propulsion force to the ship.

The forward first low pressure turbine 11 and the second reverse low pressure turbine are disposed coaxially so as to face each other, and the expansion process is parallel.

An exhaust steam pipe 27 is connected to the exhaust side of the high pressure turbine 7 for forward use and a first supply pipe 29 connected to the steam inlet of the first low pressure turbine 11 for forward movement, A second supply pipe 31 connected to the inlet of the second low-pressure turbine 13, and a steam dump pipe (steam dump path) 33 connected to a condenser, not shown, are connected. The steam dump pipe (33) is provided with a pressure reducing valve (35) capable of opening adjustment in a range from full closing to full opening. The opening of the pressure reducing valve 35 is controlled by a control unit (not shown). Pressure control means for controlling the pressure of the superheated steam supplied to each of the low-pressure turbines 11 and 13 is constituted by a control section for controlling the steam dump pipe 33, the pressure reducing valve 35 and the pressure reducing valve 35 .

A low-pressure driving steam pipe 37 is connected to the steam inlet of the first low-pressure turbine 11 for forwarding, and a low-pressure driving steam made of utility steam derived from the boiler reheat steam line is supplied. The low-pressure-driving steam pipe 37 is provided with a low-pressure-drive steam valve 38 which performs opening adjustment by a control unit (not shown). Therefore, the forward first low-pressure turbine 11 is supplied with the low-pressure driving steam from the low-pressure driving steam pipe 37 in addition to the steam exhausted from the forwarding high-pressure turbine 7. [

The steam turbine actuator 1A configured as described above operates as follows.

From the ship boiler, the main drive steam made of high-pressure superheated steam is supplied to the forwarding high-pressure turbine 7 and the forwarding high-pressure turbine 7 is rotationally driven. As a result, the propeller shaft 24 is driven through the first drive shaft 4 and the speed reducer 20, and the starboard propeller rotates to generate the forward thrust force. The output of the starboard side propeller is adjusted by the opening degree of the main steam valve 10.

The superheated steam discharged from the forward 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 formed in parallel. The superheated steam flowing through the first supply pipe 29 is guided to the first low pressure turbine 11 for forward rotation and drives the first low pressure turbine 11 for forward rotation. Similarly, the superheated steam flowing through the second supply pipe 31 is guided to the second low pressure turbine 13 for forward rotation to drive the second low pressure turbine 13 for forward rotation.

The pressure of the super heated steam supplied to each of the low pressure turbines 11 and 13 is adjusted by the pressure reducing valve 35 formed in the steam dump pipe 33. In other words, by increasing the opening degree of the pressure reducing valve 35, the amount of steam that passes through the steam dump pipe 33 and is led to the condenser is increased, so that the pressure of the superheated steam led to each of the low pressure turbines 11, The amount of steam that passes through the steam dump pipe 33 and is led to the condenser is reduced by decreasing the opening degree of the pressure reducing valve 35. As a result, the amount of superheated steam introduced into each of the low pressure turbines 11, The pressure rises. The opening control of the pressure reducing valve 35 is performed by a control unit (not shown), and is adjusted in accordance with the thrust required for the port side propeller.

When the forward first low pressure turbine 11 and the forward second low pressure turbine 13 are rotationally driven, the propeller shaft 25 is driven through the second drive shaft 14 and the speed reducer 21, and the port side propeller And the forward thrust is generated. The output of the port side propeller is adjusted by the opening degree of the pressure reducing valve 35 as described above.

When the output of the port side propeller is insufficient, the low-pressure driving steam derived from the low-pressure-driving steam pipe 37 is supplied to the first low-pressure turbine 11 for forwarding. The pressure of the supplied low-pressure driving steam is controlled by the low-pressure driving steam valve 38.

The steam that has been rotated by driving the forward first low pressure turbine 11 and the forward second low pressure turbine 13 is led to the condenser as exhaust steam.

At the time of the backward movement, the main drive steam is supplied to each of the backward turbines 9 and 15, and the turbines 9 and 15 are rotationally driven. As a result, the starboard-side propeller and the port-side propeller rotate in the reverse direction to generate the backward thrust. The steam, which is rotated and driven by each of the reverse turbines 9 and 15, is guided to the condenser as exhaust steam.

As described above, according to the present embodiment, the following operational effects are exhibited.

A first drive shaft 4 driven by a forward high pressure turbine 7 and a forward first low pressure turbine 11 and a second forward low pressure turbine driven by the steam exhausted from the high pressure turbine 7 13, it is possible to realize biaxialization without causing an increase in the installation space by carrying out biaxialization by a single flow of the vapor.

In order to control the pressure of the steam exhausted from the forward high pressure turbine 7 and supplied to the forward first low pressure turbine 11 and the forward second low pressure turbine 13, the steam dump pipe 33 and the reduced pressure And a valve (35). Thereby, the pressure of the steam flowing into the first low pressure turbine 11 for advancing and the second low pressure turbine 13 for advancing can be set without being affected by the operating conditions of the forwarding high pressure turbine 7. [ Therefore, the output of the forward high-pressure turbine 7 and the output of the forward first low-pressure turbine 11 and the forward second low-pressure turbine 13 can be independently controlled. As described above, the two-axis independent control can be realized with a simple configuration in which the control unit for controlling the steam dump pipe 33, the pressure reducing valve 35, and the pressure reducing valve is added.

A superheated steam supply system as a separate system different from the first supply pipe 29 and the second supply pipe 31 from which the exhaust steam of the forwarding high pressure turbine 7 is guided is a low pressure steam pipe 37, Steam was supplied. Thus, the output of the first low-pressure turbine 11 for forwarding can be increased independently of the main steam system introduced into the forward high-pressure turbine 7. [ This makes it possible to stably control the port drive unit 5 driven by the first low pressure turbine 11 for forward movement and the second low pressure turbine 13 for forward movement.

The low-pressure turbine is divided into two low-pressure turbines (the first low-pressure turbine 11 for forward and the second low-pressure turbine 13 for forward), and only one of the first low- And the steam is supplied from the driving steam pipe (37). As a result, the controllability of the low-pressure turbine (the first low-pressure turbine 11 for advancing and the second low-pressure turbine 13 for advancing) is improved.

[Second Embodiment]

Next, a second embodiment of the present invention will be described with reference to Fig. The present embodiment further improves the configuration of the first embodiment. Therefore, the same components as those in the first embodiment are denoted by the same reference numerals, and a description thereof will be omitted.

A forward intermediate pressure turbine 40 mounted on the same first drive shaft 4 as the forward high pressure turbine 7 is formed in the starboard 3 of the steam turbine drive 1B of the present embodiment. The high pressure turbine 7 and the forward intermediate pressure turbine 40 constitute a high pressure side turbine. The forwarding intermediate pressure turbine 40 is driven by the superheated steam obtained by reheating the exhaust steam from the forwarding high pressure turbine 7 by the reheater 42. Specifically, the bypass piping 44 is branched from the exhaust steam pipe 27 on the exhaust side of the high-pressure turbine 7, and a portion of the exhaust steam is guided to the reheat 42 by the bypass piping 44 And the reheated steam is led to the forwarding intermediate pressure turbine 40 by the reheated steam supply pipe 46. The steam flow rate bypassed to the reheater 42 is determined by adjustment of the opening degree of the bypass valve 49 formed in the exhaust steam pipe 27 on the side of the forward high pressure turbine 7. [ The opening degree of the bypass valve 49 is controlled on the basis of a predetermined function given to the first control section 52. For example, when the forward rotation speed (RPM (AHEAD)) is low as shown in the figure represented by the numeral 52, the opening degree of the bypass valve 49 is increased to bypass the reheater 42 side The steam flow rate is decreased. When the forward rotation speed is high, the opening degree of the bypass valve 49 is reduced to increase the steam flow rate bypassed to the reheater 42 side. The reheater 42 is generally constructed as a part of a ship boiler (not shown).

The first control unit 52 also controls the main steam valve 10. For example, as shown in the figure at 52, throttle is provided so that the opening degree increases as the number of rotations of the forward rotation speed (RPM (AHEAD)) increases.

The superheated steam discharged from the forwarding intermediate pressure turbine 40 passes through the exhaust steam pipe 48 and merges with the exhaust steam derived from the forwarding high pressure turbine 7 at the confluence point 50. The branch from the merged exhaust steam pipe 54 after merging to the steam dump pipe 33 and branching to the first supply pipe 29 and the second supply pipe 31 connected in parallel is the same as the first embodiment .

A pressure sensor 56 for measuring the steam pressure reduced by the pressure reducing valve 35 formed in the steam dump pipe 33 is formed in the merged exhaust steam pipe 54. This pressure sensor 56 also constitutes a part of the pressure control means of the present invention. The measurement pressure value PV measured by the pressure sensor 56 is sent to the second control unit 58. [ The second control section 58 compares the externally applied set pressure value SV with the measured pressure value PV and determines whether or not the pressure reducing valve 35 is operated by the PID control, And outputs the command value OP. The opening degree of the pressure reducing valve 35 is controlled on the basis of this command value OP.

The dump steam after passing through the pressure reducing valve 35 and reduced in pressure is led to the condenser 60.

The superheated steam after the pressure control is supplied to the first low pressure turbine 11 and the second low pressure turbine 13 for forwarding via the first supply pipe 29 and the second supply pipe 31, . This point is the same as in the first embodiment. However, in this embodiment, the check valve 62 is formed in the first supply pipe 29. This check valve 62 prevents backward flow of the vapor from the first low pressure turbine 11 to the high pressure side turbine side (the forward high pressure turbine 7 and the forward intermediate pressure turbine 40).

The steam, which has been finished in the first low pressure turbine 11 for forward use and the second low pressure turbine 13 for forwarding, is led to the condenser 60.

The low-pressure-driving steam pipe 37 is provided with a pressure-reducing valve 64 for controlling the utility steam pressure to be constant. The low-pressure driving steam that has passed through the pressure reducing valve 64 is branched to the branch point 66 and then guided to the low-pressure driving steam valve 38. The opening degree of the low-pressure-driving steam valve 38 is controlled by the third control section 68. Specifically, as the forward rotation speed (RPM (AHEAD)) increases, the opening degree is increased. Thus, the lack of power of the low-pressure turbine (the first low-pressure turbine 11 for advancing and the second low-pressure turbine 13 for advancing) is supplemented independently of the main steam. The low-pressure-driving steam valve 38 is controlled in opening as described above at the time of advancing, but is closed at the time of retreating.

In the present embodiment, in the first embodiment, instead of the backward turbines 9 and 15 driven by the main steam, the high-pressure backward turbine 70 on the starboard side and the high- Pressure reverse turbine 72 driven by steam.

The high pressure backward turbine 70 is rotationally driven by the main steam derived from the backward main steam pipe 74 branching from the main steam pipe 8.

A main steam valve 76 is formed in the main steam pipe 74 for backward movement, and the opening of the main steam pipe 74 is controlled by the fourth control unit 79. The main steam valve 76 is subjected to opening control at the time of backward movement, and is closed at the time of forward movement.

The super heated steam exhausted from the high pressure backward turbine 70 passes through the backward exhaust steam pipe 78 and branches to the steam dump pipe 80. In the steam dump pipe 80, a pressure reducing valve 82 is formed.

A pressure sensor 84 for measuring the steam pressure reduced by the pressure reducing valve 82 is formed in the exhaust gas pipe 78 for backward movement. The measurement pressure value PV measured by the pressure sensor 84 is sent to the fifth control unit 86. [ The fifth control section 86 compares the externally applied set pressure value SV with the measured pressure value PV and outputs the set pressure value SV to the pressure reducing valve 82 by PID control, And outputs a command value OP. The opening degree of the pressure reducing valve 82 is controlled on the basis of this command value OP.

Thus, the backward steam dump pipe 80, the pressure reducing valve 82, the pressure sensor 84 and the fifth control unit 86 constitute the pressure control means of the present invention.

The dump steam after passing through the pressure reducing valve 82 and reduced in pressure is led to the condenser 60.

The superheated steam flowing through the backward exhaust steam pipe 78 without branching to the steam dump pipe 80 passes through the supply pipe 88 and is led to the low pressure backward turbine 72. A low-pressure steam valve (90) is formed in the exhaust steam pipe (78). The opening degree of the low-pressure steam valve (90) is controlled by the sixth control section (92). For example, as shown in the figure denoted by reference numeral 92, throttle is provided so that the opening degree increases as the number of revolutions of the reverse rotation speed (RPM (ASTERN)) increases.

Pressure drive steam pipe 96 branched from the branch point 66 of the low-pressure drive steam pipe 37 and joined to the supply pipe 88 for reverse at the confluence point 94 is formed. A low-pressure driving steam valve 98 is formed in the low-pressure driving steam pipe 96. The opening degree of the low-pressure-driving steam valve 98 is controlled by the sixth control section 92. For example, as shown in the figure denoted by reference numeral 92, when the number of revolutions of the reverse rotation speed (RPM (ASTERN)) is low, it is closed, and when the predetermined number of revolutions is exceeded, the output is increased The opening degree is gradually increased.

The low-pressure low-pressure steam valve 90 and low-pressure driving steam valve 98 are closed at the time of advancement.

The steam turbine driver 1B having the above-described configuration operates as follows.

The backward main steam valve 76, the low-pressure steam valve 90, and the low-pressure drive steam valve 98 are closed at the time of advancement.

Then, the main drive steam made of high-pressure superheated steam from the ship boiler is supplied to the forwarding high-pressure turbine 7, and the forwarding high-pressure turbine 7 is rotationally driven. As a result, the propeller shaft 24 is driven through the first drive shaft 4 and the speed reducer 20, and the starboard propeller rotates to generate the forward thrust force. The output 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 exhausted from the forward high pressure turbine 7 flows through the exhaust steam pipe 27 and partially flows into the bypass pipe 44 And the remainder flows to the downstream side of the exhaust steam pipe 27. The superheated steam flowing in the bypass piping 44 is reheated in the reheater 42 to become reheated steam and is led to the forwarding intermediate pressure turbine 40 through the reheated steam supply pipe 46. The superheated steam which has been rotated by driving the forward intermediate pressure turbine 40 passes through the exhaust steam pipe 48 and joins the exhaust steam derived from the forwarding high pressure turbine 7 at the confluence point 50. The superheated steam flows through the first supply pipe 29 and the second supply pipe 31 formed in parallel. The superheated steam flowing through the first supply pipe 29 and the check valve 62 is guided to the first low pressure turbine 11 for forward rotation to drive the first low pressure turbine 11 for forward rotation. Likewise, the superheated steam flowing through the second supply pipe 31 is guided to the second low pressure turbine 13 for forward rotation to drive the second low pressure turbine 13 for forward rotation.

The pressure of the super heated steam supplied to each of the low pressure turbines 11 and 13 is adjusted by the pressure reducing valve 35 formed in the steam dump pipe 33. That is, the opening degree of the pressure reducing valve 35 is adjusted by the second control section 58, which controls based on the measurement pressure value PV of the pressure sensor 56, to be the set pressure value SV. Specifically, by increasing the opening degree of the pressure reducing valve 35, the amount of steam that is introduced into the condenser 60 through the steam dump pipe 33 is increased. Therefore, the amount of superheated steam introduced into each of the low pressure turbines 11, As the pressure decreases and the opening degree of the pressure reducing valve 35 is reduced, the amount of steam that passes through the steam dump pipe 33 and is guided to the condenser is reduced. Therefore, the amount of steam introduced into each of the low pressure turbines 11, The pressure of superheated steam increases. Here, it is preferable to make the set pressure value SV given to the second control unit 58 variable so that the steam is not dumped inefficiently.

When the forward first low pressure turbine 11 and the forward second low pressure turbine 13 are rotationally driven, the propeller shaft 25 is driven through the second drive shaft 14 and the speed reducer 21, and the port side propeller And the forward thrust is generated. The output of the port side propeller is adjusted by the opening degree of the pressure reducing valve 35 as described above.

When the output of the port side propeller is insufficient, the low-pressure driving steam derived from the low-pressure-driving steam pipe 37 is supplied to the first low-pressure turbine 11 for forwarding. The pressure of the supplied low-pressure driving steam is adjusted by the low-pressure-driving steam valve 38 controlled by the third control unit 68. [

The steam that has been rotated by driving the forward first low pressure turbine 11 and the forward second low pressure turbine 13 is led to the condenser 60 as exhaust steam.

The forward main steam valve 10 and the low-pressure driving steam valve 38 are closed at the time of the backward movement.

In the reverse operation, the same operation as that in the forward operation is performed, so that the description thereof will be omitted. That is, the high-pressure backward turbine 70 is driven by the main drive steam, the low-pressure backward turbine 72 is driven by the exhaust steam of the high-pressure backward turbine 70, and the steam dump pipe 80, Pressure backward turbine 72 is driven by the low-pressure driving steam adjusted by the low-pressure driving steam valve 98, that is, the pressure is controlled by the pressure sensor 82, the pressure sensor 84 and the fifth control unit 86, It is the same as the case of forward movement.

As described above, according to the present embodiment, the following operational effects are exhibited.

A first drive shaft 4 driven by the forward high pressure turbine 7 and the forward intermediate pressure turbine 40 and a forward first low pressure turbine 11 driven by the steam exhausted from the high pressure turbine 7, And the second drive shaft 14 driven by the second low-pressure turbine 13 for forward use are employed. By biaxialization by a single flow of the steam, biaxialization can be realized without increasing installation space .

In order to control the pressure of the steam exhausted from the forward high pressure turbine 7 and the forward intermediate pressure turbine 40 and supplied to the forward first low pressure turbine 11 and the forward second low pressure turbine 13, A steam dump pipe 33 and a pressure reducing valve 35. [ Thereby, the pressure of the steam flowing into the first low pressure turbine 11 for advancing and the second low pressure turbine 13 for advancing can be set without being affected by the operating conditions of the forwarding high pressure turbine 7. [ Therefore, the output of the forward high-pressure turbine 7 and the output of the forward first low-pressure turbine 11 and the forward second low-pressure turbine 13 can be independently controlled. As described above, the two-axis independent control can be realized with a simple configuration in which the control unit for controlling the steam dump pipe 33, the pressure reducing valve 35, and the pressure reducing valve is added.

The backward turbines 70 and 72 are provided with the steam dump pipe 80 and the pressure reducing valve 82 in order to control the pressure of the steam supplied to the low pressure backward turbine 72, So that the same action effect as that for forward movement was obtained.

As a superheated steam supply system of a separate system which is different from the first supply pipe 29 and the second supply pipe 31 from which the exhaust vapors of the forward high pressure turbine 7 and the forward intermediate pressure turbine 40 are guided, And the low-pressure driving steam is supplied from the steam pipe (37). This makes it possible to increase the output of the first low-pressure turbine 11 for forwarding independently of the main steam system led to the forward high-pressure turbine 7 and the forward intermediate-pressure turbine 40. This makes it possible to stably control the port drive unit 5 driven by the first low pressure turbine 11 for forward movement and the second low pressure turbine 13 for forward movement.

The low-pressure turbine is divided into two low-pressure turbines (the first low-pressure turbine 11 for forward operation and the second low-pressure turbine 13 for forward operation) and only one of the first low- And the steam is supplied from the driving steam pipe (37). As a result, the controllability of the low-pressure turbine (the first low-pressure turbine 11 for advancing and the second low-pressure turbine 13 for advancing) is improved.

The low pressure driving steam supplied to the first low pressure turbine 11 is supplied to the high pressure side turbines 7 and 40 in accordance with the pressure condition of the superheated steam discharged from the high pressure side turbines 7 and 40 The pressure of the low-pressure driving steam becomes relatively large, and there is a possibility that steam flows backward from the first low-pressure turbine 11 to the high-pressure turbine 7, 40 side. Therefore, The valve 62 is formed. Thus, stable operation is realized.

[Third embodiment]

Next, a third embodiment of the present invention will be described with reference to Fig. In the first and second embodiments, it is assumed that the steam turbine drivers 1A and 1B are applied to the biaxial line. However, the present embodiment is applicable to the gas liquefier 100 as the other use of the steam turbine driver Respectively.

The gas liquefier 100 is for liquefying natural gas (NG), which is a raw material of a liquefied gas such as LNG (liquefied natural gas), by cooling it. In the gas liquefier 100, the above-described steam turbine drivers 1A and 1B are used as a drive source of a compressor constituting a refrigeration cycle. The steam turbine actuators 1A and 1B are schematically shown in the drawing. The steam turbine actuators 1A and 1B are schematically illustrated as a high pressure turbine 102, a low pressure turbine 103, a pressure control means (not shown) The drive (not shown), the first drive shaft 105, and the second drive shaft 107 have the same configurations as those of the first embodiment and the second embodiment.

The gas liquefier 100 includes a first compressor 109 rotationally driven by a first drive shaft 105 and a second compressor 111 rotationally driven by a second drive shaft 107. Each of the compressors 109 and 111 is provided with a two-stage compressing portion formed on a coaxial shaft rotatably driven by drive shafts 105 and 107. The compressed refrigerant (for example, nitrogen) do.

In a refrigeration cycle not shown, a first cold / heat output section for expanding the refrigerant compressed by the first compressor 109 to obtain cold heat, a second cold / heat output section for expanding the refrigerant compressed by the second compressor 111, A cold / hot output section is formed (a so-called double expansion cycle). The first cold / heat output section and the second cold / heat output section cools the natural gas or the like, which is a raw material of the LNG, to be liquefied.

By applying the steam turbine drivers 1A and 1B capable of independently controlling the two axes in order to realize the refrigeration cycle having the two expanders as in the present embodiment, a gas liquefier device having favorable installation property and cost is provided can do. In addition, since the drive shafts can be independently controlled, one compressor can be used for high pressure and the other compressor can be used for low pressure, and high-efficiency liquefaction can be realized.

[Fourth Embodiment]

Next, a fourth embodiment of the present invention will be described with reference to Fig. In the first and second embodiments, it is assumed that the steam turbine drivers 1A and 1B are applied to the biaxial line. However, the present embodiment is not limited to the steam used as the propulsion device of the ship And the turbine driver is converted into a power generator.

An output mechanism section 201 composed of a speed reducer, a propeller shaft, and the like is formed on the output side of the steam turbine drive machine, that is, the output side of each of the drive shafts 205 and 207, in the conventional single-shaft steam turbine line. When such a steam turbine line is changed to a floating body that does not require a propeller such as a floating storage and regasification unit (FSRU), the output mechanism unit 201 becomes unnecessary.

Thus, in this embodiment, the output mechanism unit 201 is detached and converted into the same steam turbine drivers 1A and 1B as those of the first and second embodiments. Specifically, pressure control means such as a steam dump pipe 33, a pressure reducing valve 35 and the like and a low pressure driving steam such as a utility steam are induced between the existing high-pressure side turbine 202 and the low- Pressure driving steam pipe 37 and the low-pressure driving steam valve 38 for reducing the pressure of the exhaust gas. The first generator 209 and the second generator 211 driven by the rotation of the first drive shaft 205 and the second drive shaft 207 are connected to each other.

As in the present embodiment, even when a conventional single-shaft steam turbine line is changed to a reactor such as an FSRU, the existing propulsion device can be modified and used for driving a generator. Since the steam turbine drivers 1A and 1B can independently control the drive shafts 205 and 207, the power generation amounts of the generators 209 and 211 can be arbitrarily adjusted, .

1A, 1B: Steam turbine actuator
4:
7: High pressure turbine for forward (high pressure side turbine)
11: First low pressure turbine for forward use (low pressure side turbine)
13: 2nd low pressure turbine for forward (low pressure side turbine)
14: second drive shaft
33, 80: Steam dump piping (pressure control means)
35, 82: Pressure reducing valve (pressure control means)
37: Low pressure driven steam piping
56, 84: Pressure sensor (pressure control means)
58: second control section (pressure control means)
62: Check valve
86: fifth control unit (pressure control means)

Claims (7)

A high pressure side turbine to which steam is supplied and driven,
A first drive shaft driven by the high-pressure side turbine,
A low pressure side turbine to which steam exhausted from the high pressure side turbine is supplied and driven;
And a second drive shaft driven by the low pressure side turbine,
And a pressure control means for controlling the pressure of the steam exhausted from the high-pressure-side turbine and supplied to the low-pressure-side turbine,
The steam on the low-pressure side turbine is further supplied from a separate system different from the exhaust system of the high-pressure side turbine,
The low-pressure side turbine comprises two low-pressure turbines, a first low-pressure turbine and a second low-pressure turbine formed in parallel with the superheated steam supplied from the high-pressure-side turbine,
And for the first low-pressure turbine only, steam is further supplied from the separate system. The method according to claim 1,
Wherein the pressure control means comprises:
A steam dump path for branching a part of the steam exhausted from the high-pressure side turbine and leading the steam to a condenser;
A pressure reducing valve for reducing the pressure of steam flowing through the steam dump passage,
And a control unit for controlling the pressure reducing valve so that steam flowing to the low-pressure turbine becomes a predetermined pressure. delete delete The method according to claim 1,
The steam supply path connecting the inlet side of the first low-pressure turbine and the exhaust side of the high-pressure turbine is provided with a check valve for preventing reverse flow of the vapor from the first low- Actuator. A steam turbine actuator according to any one of claims 1, 2, and 5;
A first propeller rotatably driven by the first drive shaft,
And a second propeller rotatably driven by the second drive shaft. A steam turbine actuator,
A first compressor rotationally driven by a first drive shaft,
A second compressor rotationally driven by a second drive shaft,
A first cool / heat output unit for expanding a refrigerant compressed by the first compressor to obtain cold heat,
And a second cold / heat output unit for expanding the refrigerant compressed by the second compressor to obtain cold heat,
And the gas is cooled by the first and second cold / heat output sections and the second cold /
Wherein the steam turbine driver comprises a high pressure side turbine to which steam is supplied and is driven, a first drive shaft driven by the high pressure side turbine, a low pressure side turbine driven by supplying steam exhausted from the high pressure side turbine, A second drive shaft driven by a low pressure side turbine and a pressure control means for controlling a pressure of steam exhausted from the high pressure side turbine and supplied to the low pressure side turbine.
KR1020137021871A 2011-02-25 2012-02-09 Steam turbine driving machine, and ship and gas liquefaction apparatus each equipped with steam turbine driving machine KR101624017B1 (en)

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PCT/JP2012/053017 WO2012114892A1 (en) 2011-02-25 2012-02-09 Steam turbine driving machine, and ship and gas liquefaction apparatus each equipped with steam turbine driving machine

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CN103380056A (en) 2013-10-30
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JP5818459B2 (en) 2015-11-18

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