WO2022014331A1 - Turbine pour production d'énergie cryogénique - Google Patents

Turbine pour production d'énergie cryogénique Download PDF

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Publication number
WO2022014331A1
WO2022014331A1 PCT/JP2021/024732 JP2021024732W WO2022014331A1 WO 2022014331 A1 WO2022014331 A1 WO 2022014331A1 JP 2021024732 W JP2021024732 W JP 2021024732W WO 2022014331 A1 WO2022014331 A1 WO 2022014331A1
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WIPO (PCT)
Prior art keywords
heat medium
turbine
blade
power generation
line
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Ceased
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PCT/JP2021/024732
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English (en)
Japanese (ja)
Inventor
亮 ▲高▼田
晃 川波
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Mitsubishi Heavy Industries Marine Machinery and Equipment Co Ltd
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Mitsubishi Heavy Industries Marine Machinery and Equipment Co Ltd
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Publication of WO2022014331A1 publication Critical patent/WO2022014331A1/fr
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Ceased legal-status Critical Current

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    • 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
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether

Definitions

  • the present disclosure relates to a turbine for cryogenic power generation provided in a heat medium circulation line configured to circulate a heat medium for heating a liquefied gas.
  • Liquefied gas for example, liquefied natural gas
  • a supply destination such as city gas or thermal power plant
  • a heat medium such as seawater.
  • cryogenic power generation may be performed in which cold energy is recovered as electric power instead of being discarded in seawater (for example, Patent Document 1).
  • a secondary medium Rankine cycle method or the like As a cryogenic power generation cycle of liquefied natural gas, a secondary medium Rankine cycle method or the like is known (for example, Patent Document 1).
  • a secondary medium Rankine cycle method a secondary medium circulating in a closed loop is heated by an evaporator using seawater as a heat source to evaporate, and this steam is introduced into a turbine for cryogenic power generation to obtain power.
  • It is a method of cooling and condensing with liquefied natural gas.
  • Turbines for cryogenic power generation include the temperature of seawater, which is the heat source for heating the secondary medium, and the flow rate of the liquefied gas (the amount of liquefied gas introduced into the heat exchanger that exchanges heat between the liquefied gas and the secondary medium). It may be a partial load operation depending on the situation. For example, in hot (low latitude) sea areas and summer, the seawater temperature is about 25 ° C, whereas in high latitude sea areas and winter, compared to low latitude sea areas and summer. As a result, the temperature of seawater drops. When the temperature of seawater, which is a heat source, is low, the temperature of the secondary medium supplied to the turbine is also low.
  • the supply amount of the secondary medium to the turbine is limited to a small amount, and the output of the turbine may decrease. Even if the circulation amount of the secondary medium in the closed loop is increased, the supply amount of the secondary medium to the turbine is limited according to the inlet temperature of the turbine, so that the secondary medium is used as a bypass line that bypasses the turbine. There is a risk that the output of the cryogenic power generation cycle will decrease because a large amount of water will flow.
  • an object of at least one embodiment of the present disclosure is to provide a turbine for cryogenic power generation capable of improving the output of the turbine during partial load operation.
  • the turbine for cryogenic power generation is A turbine for cryogenic power generation provided in a heat medium circulation line configured to circulate a heat medium for heating a liquefied gas.
  • the casing that houses the rotor shaft and A plurality of rotor blades provided around the rotor shaft, including a first rotor blade and a second rotor blade provided downstream of the first rotor blade.
  • a plurality of stationary blades supported inside the casing the first stationary blade provided on the upstream side of the first moving blade, the downstream side of the first moving blade, and the first one.
  • a plurality of stationary blades including a second stationary blade provided on the upstream side of the second moving blade, and A heat medium introduction line for introducing the heat medium into the first stationary blade, and An intermediate confluence line for introducing the heat medium into the second stationary blade by branching from the heat medium introduction line and bypassing the first stationary blade and the first moving blade.
  • a turbine for cryogenic power generation capable of improving the output of the turbine during partial load operation.
  • FIG. 2 is a schematic cross-sectional view schematically showing a cross section along an axis of a turbine for thermal power generation shown in FIG. 2, and is a schematic cross-sectional view showing a state in which an on-off valve is open.
  • FIG. 4 is a schematic cross-sectional view schematically showing a cross section along an axis of a turbine for thermal power generation shown in FIG. 4, and is a schematic cross-sectional view showing a state in which an on-off valve is open. It is a schematic cross-sectional view schematically showing the cross section along the axis of the turbine for cryogenic power generation which concerns on one Embodiment of this disclosure.
  • expressions such as “same”, “equal”, and “homogeneous” that indicate that things are in the same state not only represent exactly the same state, but also have tolerances or differences to the extent that the same function can be obtained. It shall also represent the existing state.
  • an expression representing a shape such as a quadrangular shape or a cylindrical shape not only represents a shape such as a quadrangular shape or a cylindrical shape in a geometrically strict sense, but also an uneven portion or a chamfer within the range where the same effect can be obtained. It shall also represent the shape including the part and the like.
  • the expression “includes”, “includes”, or “has” one component is not an exclusive expression that excludes the existence of another component.
  • the same reference numerals may be given to the same configurations, and the description thereof may be omitted.
  • FIG. 1 is a schematic configuration diagram schematically showing a configuration of a cryogenic power generation system including a turbine for cryogenic power generation according to an embodiment of the present disclosure.
  • the cryogenic power generation system 1 includes a turbine 2 for cold power generation (hereinafter referred to as a turbine 2), a liquefied gas supply line 3, a heat medium circulation line 4, and a heated water supply line 5.
  • a turbine 2 for cold power generation hereinafter referred to as a turbine 2
  • a liquefied gas supply line 3 a heat medium circulation line 4
  • a heated water supply line 5 a heated water supply line 5.
  • a generator 11, a first heat exchanger 12, and a second heat exchanger 13 Each of the liquefied gas supply line 3, the heat medium circulation line 4, and the heated water supply line 5 includes a flow path through which a fluid flows, such as a pipeline.
  • the liquefied gas supply line 3 is configured to send liquefied gas from the liquefied gas storage device 31.
  • the liquefied gas storage device for example, a liquefied gas tank
  • the liquefied gas storage device 31 is configured to store liquefied gas.
  • the heat medium circulation line 4 is configured to circulate a heat medium having a freezing point lower than that of water.
  • liquefied natural gas LNG
  • propane will be described as a specific example of the heat medium flowing through the heat medium circulation line 4.
  • liquefied gas other than liquefied natural gas It can also be applied to (liquid hydrogen, etc.), and can also be applied when a heat medium other than propane is used as a heat medium flowing through the heat medium circulation line 4.
  • the cryogenic power generation system 1 further includes a liquefied gas pump 32 provided in the liquefied gas supply line 3 and a heat medium circulation pump 41 provided in the heat medium circulation line 4. ..
  • One end side 33 of the liquefied gas supply line 3 is connected to the liquefied gas storage device 31, and the other end side 34 is connected to the liquefied gas device 35 provided outside the cryogenic power generation system 1.
  • the device 35 for liquefied gas include a gas holder provided on land and a gas pipe connected to the gas holder.
  • the liquefied gas stored in the liquefied gas storage device 31 is sent to the liquefied gas supply line 3 and flows through the liquefied gas supply line 3 from the upstream side to the downstream side. , Is sent to the device 35 for liquefied gas.
  • the turbine 2 By driving the circulation pump 41 for the heat medium, the heat medium circulates in the heat medium circulation line 4.
  • the turbine 2 is provided in a heat medium circulation line 4 configured to circulate a heat medium for heating the liquefied gas.
  • the turbine 2 includes a rotor shaft 21 and is configured to be driven by a heat medium (rotating the rotor shaft 21) flowing through the heat medium circulation line 4.
  • the generator 11 is connected to the rotor shaft 21 and is configured to generate electricity using the driving force of the turbine 2 (rotating force of the rotor shaft 21) as a driving source.
  • the heated water supply line 5 is configured to send heated water introduced from the outside of the cryogenic power generation system 1.
  • the "heated water” may be water that heats the heat exchange target as a heat medium in the heat exchanger, and may be water at room temperature.
  • the cryogenic power generation system 1 is mounted on a hull 10 or a floating body floating on water, the heated water is water that is easily available on the ship or the floating body (for example, outboard water such as seawater or cooling the engine of the ship). Cooling water, etc.) is preferable.
  • the cryogenic power generation system 1 and the turbine 2 for cryogenic power generation are mounted on a hull 10 or a floating body 10A as shown in FIG. In some other embodiment, the cryogenic power generation system 1 and the turbine 2 for cold power generation are installed on land.
  • the cryogenic power generation system 1 has an intermediate heat medium circulation line 6 configured to circulate an intermediate heat medium having a freezing point lower than that of water, and an intermediate heat medium provided in the intermediate heat medium circulation line 6.
  • a circulation pump 61 for heating water, a heating water pump 51 provided in the heating water supply line 5, and a third heat exchanger 14 are further provided.
  • the intermediate heat medium circulates in the intermediate heat medium circulation line 6 by driving the circulation pump 61 for the intermediate heat medium.
  • One end side 52 of the heated water supply line 5 is connected to a heated water supply source 15 provided outside the cryogenic power generation system 1, and the other end side 53 is a hot water discharge destination provided outside the cryogenic power generation system 1. Connected to 16.
  • the heating water pump 51 By driving the heating water pump 51, the heating water is sent from the heating water supply source 15 to the heating water supply line 5, flows through the heating water supply line 5 from the upstream side to the downstream side, and then heated. It is sent to the water discharge destination 16.
  • the heating water supply source 15 is, for example, an intake port 15A for introducing the outboard water provided on the hull 10. Can be mentioned.
  • the heated water discharge destination 16 includes, for example, a discharge port 16A provided on the hull 10 for discharging water to the outside of the ship. Can be mentioned.
  • the intermediate heat medium may be the same type of heat medium as the heat medium flowing through the heat medium circulation line 4, or may be a different type of heat medium.
  • the intermediate heat medium is made of propane and the heated water is made of seawater obtained from the outside of the ship.
  • the first heat exchanger 12 is configured to exchange heat between the liquefied gas flowing through the liquefied gas supply line 3 and the heat medium flowing through the heat medium circulation line 4.
  • the liquefied gas flow path 121 provided in the liquefied gas supply line 3 through which the liquefied gas flows and the heat medium provided in the heat medium circulation line 4 are provided.
  • the second heat exchanger 13 is configured to exchange heat between the heat medium flowing through the heat medium circulation line 4 and the intermediate heat medium flowing through the intermediate heat medium circulation line 6.
  • the second heat exchanger 13 is provided in the heat medium flow path 131 through which the heat medium flows, which is provided in the heat medium circulation line 4, and the intermediate heat provided in the intermediate heat medium circulation line 6.
  • the second heat exchanger 13 exchanges heat between the heat medium flowing through the heat medium circulation line 4 and the heated water flowing through the heated water supply line 5. It may be configured in.
  • the second heat exchanger 13 is a heated water flow path in which the heated water provided in the heated water supply line 5 flows, and is a heated water flow for exchanging heat with the heat medium flow path 132. It may include a road. In this case, since the cryogenic power generation system 1 does not need to include the intermediate heat medium circulation line 6 and the third heat exchanger 14, its structure can be suppressed from becoming large and complicated.
  • the third heat exchanger 14 is configured to exchange heat between the intermediate heat medium flowing through the intermediate heat medium circulation line 6 and the heated water flowing through the heated water supply line 5.
  • the third heat exchanger 14 is provided in the intermediate heat medium flow path 141 provided in the intermediate heat medium circulation line 6 through which the intermediate heat medium flows, and in the heated water supply line 5. Includes a heated water flow path 142 through which heated water flows. Heat exchange is performed between the intermediate heat medium in the intermediate heat medium flow path 141 and the heated water in the heated water flow path 142.
  • the first heat exchanger 12 (specifically, the liquefied gas flow path 121) is provided on the downstream side of the liquefied gas pump 32 of the liquefied gas supply line 3 and on the upstream side of the liquefied gas device 35. ..
  • the liquefied gas pump 32 is provided on the downstream side of the liquefied gas storage device 31 of the liquefied gas supply line 3.
  • the first heat exchanger 12 (specifically, the heat medium flow path 122) is provided on the downstream side of the turbine 2 of the heat medium circulation line 4 and on the upstream side of the circulation pump 41 for the heat medium. ..
  • the second heat exchanger 13 (specifically, the heat medium flow path 131) is provided on the downstream side of the heat medium circulation pump 41 of the heat medium circulation line 4 and on the upstream side of the turbine 2. Further, the second heat exchanger 13 (specifically, the intermediate heat medium flow path 132) is from the third heat exchanger 14 (specifically, the intermediate heat medium flow path 141) of the intermediate heat medium circulation line 6. Is provided on the downstream side and on the upstream side of the circulation pump 61 for the intermediate heat medium.
  • the third heat exchanger 14 (specifically, the heated water flow path 142) is provided on the downstream side of the heated water pump 51 of the heated water supply line 5 and on the upstream side of the heated water discharge destination 16.
  • the heating water pump 51 is provided on the downstream side of the heating water supply source 15 of the heating water supply line 5.
  • the liquefied gas boosted by the liquefied gas pump 32 is sent to the liquefied gas flow path 121 of the first heat exchanger 12.
  • the heat exchange in the first heat exchanger 12 heats the liquefied gas flowing through the liquefied gas flow path 121 and cools the heat medium flowing through the heat medium flow path 122. That is, the cold energy of the liquefied gas flowing through the liquefied gas flow path 121 is recovered by the heat medium flowing through the heat medium flow path 122. Due to the heat exchange in the first heat exchanger 12, the temperature of the heat medium flowing through the heat medium flow path 122 becomes lower than the freezing point of water (heated water).
  • the intermediate heat medium boosted by the circulation pump 61 for the intermediate heat medium is sent to the intermediate heat medium flow path 141 of the third heat exchanger 14. Further, the heated water boosted by the heated water pump 51 is sent to the heated water flow path 142. The heat exchange in the third heat exchanger 14 heats the intermediate heat medium flowing through the intermediate heat medium flow path 141.
  • a heat medium that has been cooled by the first heat exchanger 12 and then boosted by the circulation pump 41 for the heat medium is sent to the heat medium flow path 131 of the second heat exchanger 13. Further, the intermediate heat medium heated by the third heat exchanger 14 is sent to the intermediate heat medium flow path 132. The heat exchange in the second heat exchanger 13 heats the heat medium flowing through the heat medium flow path 131 and cools the intermediate heat medium flow path 132.
  • the cryogenic power generation system 1 branches from the downstream side of the second heat exchanger 13 in the heat medium circulation line 4 and bypasses the turbine 2 to bypass the first heat exchanger 12.
  • a bypass line 17 connected to the upstream side of the heat medium flow path 122 is further provided.
  • the main flow path 42 is a flow path (a flow path passing through the turbine 2) between the branch portion 171 where the bypass line 17 branches in the above-mentioned heat medium circulation line 4 and the confluence portion 172 where the bypass line 17 joins.
  • the cryogenic power generation system 1 further includes an on-off valve 43 provided on the upstream side of the turbine 2 of the main flow path 42, and an on-off valve 173 provided on the bypass line 17.
  • an on-off valve 43 provided on the upstream side of the turbine 2 of the main flow path 42
  • an on-off valve 173 provided on the bypass line 17.
  • the on-off valve 43 is closed and the on-off valve 173 is opened to allow the heat medium to bypass the turbine 2.
  • the on-off valve 43 is opened, the on-off valve 173 is closed, and the turbine 2 is passed through the heat medium.
  • the upstream side in the flow direction of the heat medium in the turbine 2 may be simply referred to as the upstream side
  • the downstream side in the flow direction of the heat medium in the turbine 2 may be simply referred to as the downstream side.
  • the turbine 2 for thermal power generation includes a rotor shaft 21, a casing 7 accommodating the rotor shaft 21, and a plurality of moving blades provided around the rotor shaft 21.
  • a blade 22 and a plurality of stationary blades 23 supported inside the casing 7 are provided.
  • the plurality of rotor blades 22 include a first rotor blade 22A and a second rotor blade 22B provided on the downstream side of the first rotor blade 22A.
  • the plurality of stationary blades 23 are a first stationary blade 23A provided on the upstream side of the first moving blade 22A, a downstream side of the first moving blade 22A, and an upstream side of the second moving blade 22B.
  • the second stationary blade 23B provided in the above is included.
  • the heat medium flowing through the main flow path 42 and introduced into the casing 7 passed through the first stationary blade 23A, the first moving blade 22A, the second stationary blade 23B, and the second moving blade 22B in this order. Later, it is discharged to the outside of the casing 7.
  • the turbine 2 has a heat medium introduction line 81 for introducing a heat medium into the first stationary blade 23A, and the first stationary blade 23A and the first stationary blade 23A branching from the heat medium introduction line 81. Further, an intermediate merging line 82 for introducing a heat medium into the second stationary blade 23B by bypassing the moving blade 22A of the first is provided.
  • the heat medium introduction line 81 includes a part of the main flow path 42 described above, and the intermediate merging line 82 branches from the main flow path 42 at the branch portion 44 and the first rotor blade 22A.
  • a sub-flow path 45 that joins the main flow path 42 between the blade and the second stationary blade 23B is included.
  • the turbine 2 may further include an on-off valve 46 provided in the auxiliary flow path 45.
  • the turbine 2 may be partially loaded according to the temperature of the heated water that is the heat source for heating the heat medium circulation line 4 and the flow rate of the liquefied gas (the amount of the liquefied gas introduced into the first heat exchanger 12).
  • the seawater temperature (heated water temperature) is about 25 ° C., so that the heat medium is sufficiently heated by heat exchange in the second heat exchanger 13. Is sent to the turbine 2.
  • the temperature of seawater is lower than that of low latitude sea areas or summer.
  • the heating of the intermediate heat medium in the third heat exchanger 14 and the heating of the heat medium in the second heat exchanger 13 become insufficient and are supplied to the turbine 2.
  • the temperature of the heat medium to be heated may be low. Further, if the amount of the liquefied gas introduced into the first heat exchanger 12 is large, the heat medium in the first heat exchanger 12 is excessively cooled, and the temperature of the heat medium supplied to the turbine 2 becomes low. Sometimes. As the temperature of the heat medium supplied to the turbine 2 decreases, it is necessary to decrease the saturation pressure of the turbine 2. Therefore, when the temperature of seawater, which is a heat source, is low, the amount of heat medium supplied to the turbine 2 is limited to a small amount, and the output of the turbine 2 may decrease.
  • the turbine 2 for cryogenic power generation is branched from the heat medium introduction line 81 for introducing the heat medium into the first stationary blade 23A and the heat medium introduction line 81, and the first stationary blade. It is provided with an intermediate merging line 82 for introducing a heat medium into the second stationary wing 23B by bypassing the 23A and the first moving wing 22A.
  • the turbine 2 may be in partial load operation.
  • the second stationary blade 23B Since a heat medium having a temperature lowered by working on the first rotor blade 22A is introduced into the second stationary blade 23B, the second stationary blade 23B is compared with the first stationary blade 23A.
  • the temperature of the heat medium that can be introduced is low. Therefore, by introducing a heat medium into the second stationary blade 23B through the merging line 82 that bypasses the first stationary blade 23A and the first moving blade 22A, the heat medium is located on the downstream side of the second stationary blade 23B.
  • the amount of heat medium introduced into the second rotor blade 22B can be increased. By increasing the amount of the heat medium introduced into the second rotor blade 22B, the output of the turbine 2 for cryogenic power generation can be improved.
  • the amount of the heat medium that can be supplied to the turbine 2 during the partial load operation can be increased by the intermediate merging line 82.
  • the amount of heat medium flowing through the bypass line 17 bypassing the turbine 2 can be reduced, so that the output of the cryogenic power generation system 1 can be improved.
  • FIG. 2 and 4 are schematic cross-sectional views schematically showing a cross section along the axis of the turbine for thermal power generation according to the embodiment of the present disclosure, and are schematic cross sections showing a state in which the on-off valve is closed. It is a figure.
  • FIG. 3 is a schematic cross-sectional view schematically showing a cross section along the axis of the turbine for thermal power generation shown in FIG. 2, and is a schematic cross-sectional view showing a state in which the on-off valve is open.
  • FIG. 5 is a schematic cross-sectional view schematically showing a cross section along the axis of the turbine for thermal power generation shown in FIG. 4, and is a schematic cross-sectional view showing a state in which the on-off valve is open.
  • the turbine 2 for thermal power generation includes the rotor shaft 21 described above, the casing 7 described above, the first rotor blade 22A, and the second moving blade 2.
  • the line 82 is provided. As shown in FIGS.
  • the above-mentioned heat medium introduction line 81 is provided on the outer peripheral side of the plurality of blades 22 (22A, 22B) and the plurality of stationary blades 23 (23A, 23B) inside the casing 7.
  • the formed first stationary blade 23A includes an intake chamber 81A for introducing a heat medium, and the above-mentioned intermediate confluence line 82 is formed on the inner peripheral side of the intake chamber 81A inside the casing 7. It includes a through hole 82A penetrating the partition wall portion 71 of the casing 7 that separates the inter-blade space 83 between the moving blade 22A of 1 and the moving blade 22B of 1 and the intake chamber 81A.
  • the turbine 2 (2A, 2B) for cryogenic power generation further includes an on-off valve 47A having a valve body 471 capable of closing the through hole 82A.
  • a plurality of through holes 82A may be formed by opening each other in the circumferential direction of the partition wall portion 71, and the turbine 2 can close at least one or a plurality of through holes 82A among the plurality of through holes 82A.
  • One on-off valve 47A may be provided.
  • the first rotor blade 22A is arranged on one side of the second rotor blade 22B in the axial direction of the turbine 2, that is, in the direction in which the axis CA of the turbine 2 extends.
  • the one side in the axial direction of the turbine 2 is defined as the front side, and the side opposite to the one side is defined as the rear side.
  • the radial direction of the turbine 2 may be simply referred to as a radial direction
  • the circumferential direction of the turbine 2 may be simply referred to as a circumferential direction.
  • the first rotor blade 22A is located on the front side of the second rotor blade 22B.
  • the first stationary blade 23A is arranged on the front side of the first moving blade 22A
  • the second stationary blade 23B is on the front side of the second moving blade 22B and more than the first moving blade 22A. It is located on the rear side.
  • the rotor shaft 21 includes a shaft portion 211 extending along the axis CA of the turbine 2, and a plurality of disc portions 213 protruding outward in a radial direction from the outer surface 212 of the shaft portion 211 in a disk shape.
  • the plurality of disc portions 213 are a front side disc portion 213A to which the first rotor blade 22A is attached to the outer periphery, and a rear side disc portion 213B located on the rear side of the front side disc portion 213A.
  • the rear side disk portion 213B to which the moving blade 22B is attached to the outer periphery is included.
  • the casing 7 supports the partition wall portion 71 described above, the first stationary blade support portion 72 that supports the outer peripheral portion (outer ring) of the first stationary blade 23A, and the outer peripheral portion (outer ring) of the second stationary blade 23B.
  • a second stationary blade support portion 73 and an outer casing 74 including an outer wall portion 741 for accommodating the partition wall portion 71 are included.
  • the partition wall 71 supports the first stationary blade support portion 72 on the front side of the through hole 82A in the axial direction and the second static portion 72 on the rear side of the through hole 82A in the axial direction. It supports the wing support portion 73.
  • the outer casing 74 includes the above-mentioned outer wall portion 741 and a rear side wall portion 742 that extends along the radial direction on the rear side of the through hole 82A in the axial direction and connects the partition wall portion 71 and the outer wall portion 741.
  • the front side wall portion 743 extending inward in the radial direction from the front end located on the front side of the partition wall portion 71 of the outer wall portion 741 and the front side wall portion 743 extending inward in the radial direction from the inner end of the front side wall portion 743.
  • the front side wall portion 743 extending inward in the radial direction from the front end located on the front side of the partition wall portion 71 of the outer wall portion 741 and the front side wall portion 743 extending inward in the radial direction from the inner end of the front side wall portion 743.
  • the front side wall portion 743 extending inward in the radial direction from the front end located on the front side of the partition wall portion 71 of the outer wall portion 741 and the front side wall portion 743 extending inward in the radial direction from the inner end of the front side wall portion 743.
  • the anterior inclined wall portion 744 that inclines rearward with respect to
  • an inner wall portion 745 that extends rearward from the inner end of the
  • the above-mentioned intake chamber 81A is formed between the partition wall portion 71 and the outer wall portion 741.
  • the heat medium introduced into the casing 7 flows inward in the radial direction along the inner surface of the front side wall portion 743, and then axially rearward along the inner surface of the front side inclined wall portion 744 and the inner wall portion 745. It flows to the side and is introduced into the first casing 23A.
  • the on-off valve 47A is in a closed state, and the valve body 471 comes into contact with the intake chamber side surface 711 of the partition wall portion 71, so that the through hole 82A is closed by the valve body 471.
  • the on-off valve 47A is a rotating portion 472 provided between the valve body 471 and the partition wall portion 71 and the valve body 471, and the valve body 471 is a partition wall portion.
  • the rotation mechanism portion 473 includes a cylinder in which a cylinder rod is attached to a valve body at 471. In response to an open or close instruction of the open / close control unit 474, the rotation mechanism unit 473 rotates the valve body 471 in the opening direction or the closing direction with the rotation unit 472 as the rotation center.
  • the on-off valve 47A comprises a slide valve 47B.
  • the slide valve 47B slides the valve body 471 and the valve body 471 described above in the open direction (rear side in the illustrated example) and the closed direction (front side in the illustrated example) with respect to the intake chamber side surface 711 of the partition wall portion 71.
  • the slide mechanism unit 475 and an open / close control unit 476 configured to instruct the slide mechanism unit 475 to open / close the valve body 471 are provided.
  • the slide mechanism portion 475 includes a cylinder in which a cylinder rod is attached to a valve body at 471.
  • the slide mechanism unit 475 slides the valve body 471 in the opening direction or the closing direction in response to the opening or closing instruction of the opening / closing control unit 476.
  • the on-off valve 47A is in an open state, and a heat medium can flow from the intake chamber 81A to the inter-blade space 83 through the through hole 82A.
  • the heat medium introduction line 81 includes the intake chamber 81A
  • the intermediate merging line 82 is a casing that separates the interwing space 83 formed on the inner peripheral side of the intake chamber 81A and the intake chamber 81A.
  • 7 includes a through hole 82A penetrating the partition wall portion 71.
  • the turbine 2 for cryogenic power generation includes an on-off valve 47A having a valve body 471 capable of closing the through hole 82A.
  • the through hole 82A as the intermediate merging line 82, the heat medium is introduced from the intake chamber 81A into the inter-blade space 83, so that the structure of the intermediate merging line 82 can be simplified.
  • the through hole 82A can be closed by the valve body 471, the opening / closing mechanism of the on-off valve 47A can be simplified. As a result, it is possible to suppress the increase in the price of the turbine 2 for cryogenic power generation. Further, since the through hole 82A can be used as an inspection hole when inspecting the inter-blade space 83, the inspection work of the inter-blade space 83 can be easily performed.
  • the on-off valve 47A described above comprises the slide valve 47B described above.
  • the on-off valve 47A is composed of the slide valve 47B, the opening / closing mechanism thereof can be simplified.
  • the two or more through holes 82A are closed by the valve body 471 of the slide valve 47B to open and close.
  • the number of valves 47A can be reduced. As a result, it is possible to suppress the increase in price of the turbine 2 for cryogenic power generation.
  • the turbine 2 for thermal power generation includes the rotor shaft 21 described above, the casing 7 described above, the first rotor blade 22A, and the second rotor blade 2.
  • the above-mentioned plurality of moving blades 22 including the blade 22B, the above-mentioned plurality of stationary blades 23 including the first stationary blade 23A and the second stationary blade 23B, the above-mentioned heat medium introduction line 81, and the above-mentioned intermediate merging.
  • the line 82 is provided. As shown in FIGS.
  • each of the first stationary blade 23A and the first moving blade 22A is provided on one side (left side in the figure) of the rotor shaft 21 in the axial direction, and the second stationary blade is provided.
  • Each of the blade 23B and the second rotor blade 22B is provided on the other side (right side in the figure) of the rotor shaft 21 in the axial direction.
  • the side on which the first rotor blade 22A is located with respect to the second rotor blade 22B in the axial direction of the rotor shaft 21, that is, the direction in which the axis CA of the turbine 2 extends is defined as the front side.
  • the side opposite to the side is defined as the rear side.
  • the radial direction of the turbine 2 may be simply referred to as a radial direction
  • the circumferential direction of the turbine 2 may be simply referred to as a circumferential direction.
  • the first blade 23A is arranged behind the first blade 22A and the second blade 23B is the second. It is located on the front side of the moving blade 22B.
  • the rotor shaft 21 has a shaft portion 211 extending along the axis CA of the turbine 2 and an outer side in the radial direction from the outer surface 212 of the shaft portion 211. Includes a plurality of disc portions 213 protruding in a disk shape.
  • the plurality of disk portions 213 are front side disk portions 213C provided on one side (front side) in the axial direction, and the front side disk portions 213C to which the first rotor blade 22A is attached to the outer periphery and the front disk portion 213C in the axial direction.
  • It is a rear side disk portion 213D provided on the other side (rear side), and includes a rear side disk portion 213D to which a second rotor blade 22B is attached to the outer periphery.
  • the casing 7 is arranged between the first moving blade 22A and the second moving blade 22B in the axial direction of the turbine 2 and is also arranged.
  • the partition wall 94 divided into a heat medium introduction path 93A, a rear side heat medium introduction path 93B provided on the other side (rear side) in the axial direction, and a rear side heat medium introduction path 93B.
  • the front side heat medium introduction path 93A is a flow path for introducing the heat medium flowing from the outside in the radial direction into the first rotor blade 22A from the rear side in the axial direction.
  • the rear side heat medium introduction path 93B is a flow path for introducing the heat medium flowing from the outside in the radial direction into the second rotor blade 22B from the front side in the axial direction.
  • the shaft accommodating portion 91 supports the inner peripheral portion (inner ring) of the first stationary blade 23A and the inner peripheral portion (inner ring) of the second stationary blade 23B. ..
  • a sealing member 101 is arranged between the front end 911 of the shaft accommodating portion 91 and the rotor shaft 21 to seal between them.
  • a sealing member 102 is arranged between the rear end 912 of the shaft accommodating portion 91 and the rotor shaft 21 to seal between them.
  • each of the front end 911 and the rear end 912 is a protrusion that protrudes inward in the radial direction, and the protrusions 101 and 102 are arranged between the front end 911 and the rotor shaft 21. Including the part.
  • the outer casing 92 supports the outer peripheral portion (outer ring) of the first stationary blade 23A and the outer peripheral portion (outer ring) of the second stationary blade 23B. Further, the outer casing 92 accommodates the first rotor blade 22A and the second rotor blade 22B.
  • the casing 7 has a first introduction port 951 for introducing the heat medium from the outside in the radial direction into the front side heat medium introduction path 93A.
  • a communication flow path forming portion 97 forming a communication flow path 970 for guiding the heat medium passing through the moving blade 22A to the second introduction port 961 and a heat medium passing through the second moving blade 22B in the axial direction.
  • the heat medium flowing through the main flow path 42 and introduced into the casing 7 passed through the first stationary blade 23A, the first moving blade 22A, the second stationary blade 23B, and the second moving blade 22B in this order. Later, it is discharged to the outside of the casing 7.
  • the heat medium introduced into the casing 7 through the first introduction port 951 flows forward along the front side heat medium introduction path 93A toward the front side, and the first stationary blade 23A. And pass through the first rotor blade 22A.
  • the heat medium that has passed through the first rotor blade 22A flows through the communication flow path 970 and the second introduction port 961 and is guided to the rear side heat medium introduction path 93B.
  • the heat medium guided to the rear side heat medium introduction path 93B flows toward the rear side along the rear side heat medium introduction path 93B in the axial direction and passes through the second stationary blade 23B and the second moving blade 22B. do.
  • the heat medium that has passed through the second rotor blade 22B flows rearward along the discharge flow path 980 along the axial direction, and then is discharged to the outside of the casing 7.
  • the heat medium passing through the first rotor blade 22A flows from the rear side to the front side in the axial direction, whereas the heat medium passing through the second rotor blade 22B flows from the front side to the rear side in the axial direction. It flows toward the side. That is, the heat medium passing through the second rotor blade 22B flows to the opposite side of the heat medium passing through the first rotor blade 22A in the axial direction.
  • the first thrust T1 toward the front side generated by receiving pressure from the heat medium by the first rotor blade 22A and the front disk portion 213C, and the second rotor blade 22B and the rear disk portion 213D from the heat medium. Since the second thrust T2 toward the rear side generated by receiving the pressure cancels out, the thrust of the rotor shaft 21 can be reduced.
  • the rotor blade 22A is provided on one side (front side) of the rotor shaft 21, and the second rotor blade 22B is provided on the other side (rear side) of the rotor shaft 21. Since the thrust of the shaft 21 can be reduced, the reliability of the turbine 2 for cryogenic power generation can be improved.
  • the turbine 2 described above is a connecting line 84 for supplying a heat medium that has passed through the first rotor blade 22A to the second stationary blade 23B, and is a connecting line to which the downstream end 822 of the intermediate confluence line 82 is connected. 84 is further provided.
  • the heat medium introduction line 81 includes a first introduction port 951 and a front heat medium introduction path 93A formed inside the casing 7. ..
  • the connecting line 84 includes a connecting flow path 970 formed inside the casing 7, a second introduction port 961, and a rear side heat medium introduction path 93B.
  • the intermediate merging line 82 has a connection pipe 82B in which the upstream end 821 is connected to the first heat medium introduction section 95 and the downstream end 822 is connected to the second heat medium introduction section 96. including.
  • connection pipe 82B communicates the first introduction port 951 and the second introduction port 961 so that the heat medium can be distributed, and the heat medium is connected from the first introduction port 951 to the second introduction port 961 through the connection pipe 82B. Is coming out.
  • the upstream end 821 is connected to the upstream side of the first heat medium introduction unit 95, and the downstream end 822 is connected to the second heat medium introduction unit 96.
  • the bypass pipe 82C includes the bypass pipe 82C.
  • the merging line 82 joins the connecting line 84, the heat medium that has passed through the first rotor blade 22A and the heat medium that has passed through the merging line 82 are second. It can be introduced to the stationary blade 23B. Thereby, with a simple structure, the amount of the heat medium introduced into the second rotor blade 22B can be increased, and the output of the turbine 2 for cryogenic power generation can be improved.
  • the shaft accommodating portion 91 described above accommodates the driven source 100 therein.
  • the driven source 100 is configured to be driven by transmitting the rotational force of the rotor shaft 21.
  • the driven source 100 includes at least one of a generator 11, a pump, and a compressor.
  • the driven source 100 includes the generator 11 described above.
  • the generator 11 includes a motor rotor 11A including a permanent magnet attached to the rotor shaft 21, and a motor stator 11B arranged radially outside the motor rotor 11A and supported by the shaft accommodating portion 91.
  • the shaft accommodating portion 91 described above faces the thrust collar 103 inside and the thrust collar 103 in front of the thrust collar 103. It houses the front thrust bearing 104 to be arranged and the rear thrust bearing 105 arranged to face the thrust collar 103 on the rear side of the thrust collar 103.
  • the thrust collar 103 is attached to the shaft portion 211 of the rotor shaft 21, and each of the front side thrust bearing 104 and the rear side thrust bearing 105 is supported by the shaft accommodating portion 91.
  • the thrust collar 103 and the thrust bearing front side thrust bearing 104, rear side thrust bearing 105 are accommodated inside the shaft accommodating portion 91, the thrust collar 103 and the thrust bearing are provided outside. Compared with the above, it is possible to suppress the increase in size of the turbine 2 for thermal power generation.
  • the above-mentioned intermediate merging line 82 branches from the heat medium introduction line 81 inside the casing 7 and is connected to the connecting line 84 inside the casing 7.
  • the heat medium introduction line 81 includes a first introduction port 951 and a front side heat medium introduction path 93A formed inside the casing 7.
  • the connecting line 84 includes a connecting flow path 970 formed inside the casing 7, a second introduction port 961, and a rear side heat medium introduction path 93B.
  • the intermediate merging line 82 has a connection pipe 82B in which the upstream end 821 is connected to the first heat medium introduction section 95 and the downstream end 822 is connected to the second heat medium introduction section 96. including.
  • connection pipe 82B has a flow path inside which connects the first introduction port 951 and the second introduction port 961 so that the heat medium can flow, and the first introduction port 951 to the second introduction port 951 to the second introduction port 951 through the connection pipe 82B.
  • the heat medium is designed to flow out to the mouth 961.
  • the structure of the merging line 82 (connecting pipe 82B) can be simplified, so that the cost of the turbine 2 for cryogenic power generation can be suppressed.
  • the above-mentioned intermediate merging line 82 branches from the heat medium introduction line 81 outside the casing 7 and is connected to the connecting line 84 inside the casing 7. ..
  • the heat medium introduction line 81 is formed on the outside of the casing 7 and is the above-mentioned main flow path 42 on the upstream side in the flow direction from the first introduction port 951. Including a part of.
  • the connecting line 84 includes a connecting flow path 970 formed inside the casing 7, a second introduction port 961, and a rear side heat medium introduction path 93B.
  • the upstream end 821 is connected to the above-mentioned main flow path 42 on the upstream side in the flow direction from the first introduction port 951, and the downstream end 822 is the second heat.
  • the bypass pipe 82C connected to the medium introduction unit 96 is included.
  • the degree of freedom in designing the branch position of the intermediate merging line 82 can be increased. Further, by branching from the heat medium introduction line 81 outside the casing 7, the complexity of the internal structure of the casing 7 can be suppressed, and the price increase of the turbine 2 for cryogenic power generation can be suppressed.
  • FIG. 8 is an explanatory diagram for explaining a turbine for cryogenic power generation according to an embodiment of the present disclosure.
  • the above-mentioned cryogenic energy storage turbine 2 has a heat medium flowing upstream of the connection portion 841 with the intermediate confluence line 82 in the above-mentioned connection line 84.
  • a heat exchanger 106 configured to exchange heat with a second heat medium having a temperature higher than that of this heat medium is further provided.
  • the heat exchanger 106 has a heat medium flow path 107 in which a heat medium is provided upstream of the connection portion 841 of the connection line 84 described above, and a second heat medium through which the second heat medium flows. Includes a heat medium flow path 108. Heat exchange is performed between the heat medium in the heat medium flow path 107 and the second heat medium in the second heat medium flow path 108 to heat the heat medium in the heat medium flow path 107.
  • the second heat medium may have a higher temperature than the heat medium introduced into the heat medium flow path 107.
  • the second heat medium may be the heated water flowing through the above-mentioned heated water supply line 5, or may be the intermediate heat medium flowing through the above-mentioned intermediate heat medium circulation line 6.
  • the heat exchanger 106 described above includes the second heat exchanger 13 described above. That is, in the above-mentioned heat exchanger 106, an intermediate between the heat medium flow path 131 in which the heat medium provided in the above-mentioned heat medium circulation line 4 flows and the intermediate heat medium provided in the above-mentioned intermediate heat medium circulation line 6 flows. It includes a heat medium flow path 132 and a heat medium flow path 107 through which a heat medium is provided upstream of the connection portion 841 of the connection line 84 described above. The heat medium in the heat medium flow path 132 and the heat medium in the heat medium flow path 107 are heated by the heat medium in the intermediate heat medium flow path 132.
  • the heat medium flowing upstream of the connecting portion 841 with the intermediate merging line 82 in the connecting line 84 passes through the first rotor blade 22A, and its temperature is lowered.
  • the thermal efficiency and output of the turbine 2 for cryogenic power generation can be improved.
  • the above-mentioned turbine 2 for cryogenic power generation has a pressure P1 of a heat medium introduced into the above-mentioned first stationary blade 23A at a design flow rate.
  • the pressure ratio P1 / P2 to the pressure P2 of the heat medium between the first moving blade 22A and the second stationary blade 23B is configured to be larger than the critical pressure ratio.
  • the pressure P2 of the heat medium between the first rotor blade 22A and the second stationary blade 23B is increased. growing.
  • the turbine 2 for cryogenic power generation is configured such that the pressure ratio P1 / P2 is larger than the critical pressure ratio at the design flow rate.
  • the choke is performed at the design flow rate, the flow velocity of the heat medium introduced into the first stationary blade 23A is not affected by the pressure P2, and the flow rate of the heat medium introduced into the first stationary blade 23A is not affected. Will depend on the pressure P1.
  • the turbine 2 is configured so that the pressure ratio P1 / P2 is smaller than the critical pressure ratio at the design flow rate, the heat to the second stationary blade 23B through the merging line 82 is generated.
  • the pressure P2 increases, and in response to this, the flow velocity of the heat medium introduced into the first stationary blade 23A decreases, and the heat medium introduced into the first stationary blade 23A decreases. There is a risk that the flow rate will be small.
  • the present disclosure is not limited to the above-mentioned embodiment, and includes a form in which the above-mentioned embodiment is modified and a form in which these forms are appropriately combined.
  • the turbine (2) for cryogenic power generation is A turbine (2) for cryogenic power generation provided in a heat medium circulation line (4) configured to circulate a heat medium for heating a liquefied gas.
  • Rotor shaft (21) and A casing (7) for accommodating the rotor shaft and A plurality of rotor blades (22) provided around the rotor shaft, the first rotor blade (22A) and the second rotor blade (22B) provided downstream of the first rotor blade.
  • a plurality of stationary blades (23) including a second stationary blade (23B) provided downstream of the blade (22A) and upstream of the second moving blade (22B).
  • the turbine for cryogenic power generation has a heat medium introduction line for introducing a heat medium into the first stationary blade, and a first stationary blade and a first vane branching from the heat medium introduction line. It is provided with an intermediate merging line for introducing a heat medium into the second stationary wing by bypassing the moving wing of 1.
  • the turbine may be in partial load operation. Since a heat medium having a temperature lowered by working on the first rotor blade is introduced into the second rotor blade, the heat that can be introduced into the second rotor blade is higher than that of the first rotor blade.
  • the temperature of the medium is low. Therefore, by introducing a heat medium into the second rotor blade through a confluence line that bypasses the first rotor blade and the first rotor blade, the second rotor blade is located downstream of the second rotor blade.
  • the amount of heat medium introduced into the blade can be increased.
  • the output of the turbine for cryogenic power generation can be improved.
  • the amount of heat medium that can be supplied to the turbine during partial load operation can be increased by the intermediate merging line.
  • the amount of heat medium flowing through the bypass line bypassing the turbine can be reduced, so that the output of the cryogenic power generation system can be improved.
  • the turbine (2) for cryogenic power generation according to 1) above.
  • the heat medium introduction line (81) is To introduce the heat medium into the first stationary blade (23A) formed on the outer peripheral side of the plurality of moving blades (22) and the plurality of stationary blades (23) inside the casing (7).
  • Including the intake chamber (81A) of The merging line (82) on the way is The interwing space (83) between the first rotor blade and the second stationary blade formed on the inner peripheral side of the intake chamber (81A) inside the casing (7), and the intake chamber. (81A) and a through hole (82A) penetrating the partition wall portion (71) of the casing separating the casing.
  • the turbine (2) for cryogenic power generation further includes an on-off valve (47A) having a valve body (471) capable of closing the through hole (82A).
  • the heat medium introduction line includes the intake chamber
  • the intermediate confluence line includes the partition wall portion of the casing that separates the inter-blade space formed on the inner peripheral side of the intake chamber and the intake chamber.
  • a turbine for cryogenic power generation includes an on-off valve having a valve body capable of closing a through hole.
  • the through hole can be closed by the valve body, the opening / closing mechanism of the on-off valve can be simplified. As a result, it is possible to suppress the increase in the price of the turbine for cryogenic power generation.
  • the through hole can be used as an inspection hole when inspecting the inter-blade space, the inspection work of the inter-blade space can be easily performed.
  • the turbine (2) for cryogenic power generation according to 2) above.
  • the on-off valve (47A) is composed of a slide valve (47B).
  • the on-off valve is composed of a slide valve, so that the on-off mechanism can be simplified. Further, when a plurality of through holes are formed at intervals in the circumferential direction of the partition wall, the number of on-off valves is reduced by closing two or more of the through holes with the valve body of the slide valve. can. As a result, it is possible to suppress the increase in the price of the turbine for cryogenic power generation.
  • the turbine (2) for cryogenic power generation according to 1) above.
  • Each of the first stationary blade (23A) and the first moving blade (22A) is provided on one side of the rotor shaft (21).
  • Each of the second stationary blade (23B) and the second moving blade (22B) is provided on the other side of the rotor shaft (21).
  • the turbine (2) for cryogenic power generation is a connecting line (84) for supplying the heat medium that has passed through the first rotor blade (22A) to the second stationary blade (23B).
  • a connecting line (84) to which the downstream end (822) of the intermediate merging line (82) is connected is further provided.
  • the thrust can be reduced by providing the first rotor blade on one side of the rotor shaft and the second rotor blade on the other side of the rotor shaft, so that the turbine for cryogenic power generation can be reduced. Can improve the reliability of the. Further, according to the configuration of 4) above, since the merging line joins the connecting line in the middle, the heat medium that has passed through the first rotor blade and the heat medium that has passed through the merging line in the middle are second. Can be introduced to the stationary blade. Thereby, with a simple structure, the amount of the heat medium introduced into the second rotor blade can be increased, and the output of the turbine for cryogenic power generation can be improved.
  • the turbine (2) for cryogenic power generation according to 4) above.
  • the intermediate merging line (82) branched from the heat medium introduction line (71) inside the casing (7) and was connected to the connecting line (84) inside the casing (7).
  • the structure of the confluence line can be simplified, so that the cost of the turbine for cryogenic power generation can be suppressed.
  • the turbine (2) for cryogenic power generation according to 4) above.
  • the intermediate merging line (82) branched from the heat medium introduction line (71) outside the casing (7) and was connected to the connecting line (84) inside the casing (7).
  • the turbine (2) for cryogenic power generation according to any one of 4) to 6) above.
  • a heat exchanger (106) configured to perform the exchange.
  • the heat medium flowing upstream of the connection portion with the intermediate confluence line in the connection line passes through the first rotor blade, and its temperature is lowered.
  • the thermal efficiency and output of the turbine for cryogenic power generation can be improved.
  • the turbine (2) for cryogenic power generation according to any one of 1) to 7) above.
  • the turbine for cryogenic power generation has the first moving blade (22A) and the second stationary blade (23B) at the pressure P1 of the heat medium introduced into the first stationary blade (23A) at the design flow rate.
  • the pressure ratio P1 / P2 to the pressure P2 of the heat medium is configured to be larger than the critical pressure ratio.
  • the turbine for cryogenic power generation is configured such that the pressure ratio P1 / P2 is larger than the critical pressure ratio at the design flow rate.
  • the choke since the choke is performed at the design flow rate, the flow velocity of the heat medium introduced into the first stationary blade is not affected by the pressure P2, and the flow rate of the heat medium introduced into the first stationary blade is described above. It becomes dependent on the pressure P1. Therefore, a fixed amount of heat medium can be introduced into the first stationary blade regardless of the amount of heat medium introduced through the confluence line on the way. As a result, the amount of the heat medium introduced into the second rotor blade can be increased as compared with the case where the choked flow does not occur, and the output of the cryogenic power generation system can be effectively improved.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne une turbine pour la production d'énergie cryogénique, ladite turbine comprenant : un arbre de rotor ; un carter qui loge l'arbre de rotor ; une pluralité de pales mobiles qui sont disposées autour de l'arbre de rotor et qui comprennent une première pale mobile et une seconde pale mobile qui est disposée en aval de la première pale mobile ; une pluralité de pales fixes qui sont supportées par le côté interne du boîtier, et comprenant une première pale fixe qui est disposée en amont de la première pale mobile et une seconde pale fixe qui est disposée en aval de la première pale mobile et en amont de la seconde pale mobile ; une ligne d'introduction de milieu de transfert de chaleur pour introduire un milieu de transfert de chaleur sur la première pale fixe ; et une ligne de jonction qui se ramifie à partir de la ligne d'introduction de milieu de transfert de chaleur, contourne la première pale fixe et la première pale mobile, et introduit le milieu de transfert de chaleur vers la seconde pale fixe.
PCT/JP2021/024732 2020-07-13 2021-06-30 Turbine pour production d'énergie cryogénique Ceased WO2022014331A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2020-119688 2020-07-13
JP2020119688A JP7382907B2 (ja) 2020-07-13 2020-07-13 冷熱発電用のタービン

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Publication Number Publication Date
WO2022014331A1 true WO2022014331A1 (fr) 2022-01-20

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Application Number Title Priority Date Filing Date
PCT/JP2021/024732 Ceased WO2022014331A1 (fr) 2020-07-13 2021-06-30 Turbine pour production d'énergie cryogénique

Country Status (2)

Country Link
JP (1) JP7382907B2 (fr)
WO (1) WO2022014331A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5865916A (ja) * 1981-10-14 1983-04-19 Toshiba Corp 冷熱発電プラント
JPH09209717A (ja) * 1996-01-29 1997-08-12 Ishikawajima Harima Heavy Ind Co Ltd 冷熱発電設備
JP2005291094A (ja) * 2004-03-31 2005-10-20 Osaka Gas Co Ltd 液化ガス気化装置利用発電設備

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5865916A (ja) * 1981-10-14 1983-04-19 Toshiba Corp 冷熱発電プラント
JPH09209717A (ja) * 1996-01-29 1997-08-12 Ishikawajima Harima Heavy Ind Co Ltd 冷熱発電設備
JP2005291094A (ja) * 2004-03-31 2005-10-20 Osaka Gas Co Ltd 液化ガス気化装置利用発電設備

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JP7382907B2 (ja) 2023-11-17

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