WO2024080158A1 - Appareil et système de production d'énergie cryogénique - Google Patents

Appareil et système de production d'énergie cryogénique Download PDF

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Publication number
WO2024080158A1
WO2024080158A1 PCT/JP2023/035595 JP2023035595W WO2024080158A1 WO 2024080158 A1 WO2024080158 A1 WO 2024080158A1 JP 2023035595 W JP2023035595 W JP 2023035595W WO 2024080158 A1 WO2024080158 A1 WO 2024080158A1
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Prior art keywords
inner casing
power generation
heat medium
cold energy
energy power
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PCT/JP2023/035595
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English (en)
Japanese (ja)
Inventor
晃 川波
亮 ▲高▼田
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三菱重工業株式会社
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Publication of WO2024080158A1 publication Critical patent/WO2024080158A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • 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 cold energy power generation device and a cold energy power generation system.
  • This application claims priority based on Japanese Patent Application No. 2022-164632, filed with the Japan Patent Office on October 13, 2022, the contents of which are incorporated herein by reference.
  • Liquefied gas for example, liquefied natural gas
  • liquefied natural gas is liquefied for the purpose of transportation and storage, and when it is supplied to destinations such as city gas and thermal power plants, it is heated and vaporized using a heat medium such as seawater.
  • a heat medium such as seawater.
  • the ORC Organic Rankine Cycle
  • the ORC is known as a cold energy power generation cycle that uses liquefied natural gas.
  • a low-temperature working fluid with a boiling point lower than that of water circulating in a closed loop is cooled and condensed with liquefied natural gas in a condenser, then pressurized by a pump, heated and evaporated in an evaporator using seawater or other heat sources, and this steam is introduced into a cold energy power generation turbine to generate power.
  • Patent Document 1 discloses a cold energy power generation device in which a turbine and a generator are arranged coaxially within the same casing in order to reduce the size of the device.
  • the generator is arranged in the center of the shaft, and the turbine and thrust bearing are arranged on one side of the generator.
  • This disclosure was made in consideration of the above-mentioned problems, and aims to provide a cold energy power generation device that can suppress a decline in generator performance by reducing windage loss (loss) in the thrust bearing.
  • the cold energy power generation device is a cold energy power generation device provided in a heat medium circulation line configured to circulate a heat medium for heating liquefied gas, and includes a generator including a rotor shaft, a motor rotor supported on the outer peripheral surface of the rotor shaft, and a motor stator arranged opposite the motor rotor, an inner casing that houses the generator, an outer casing that is arranged on the outer peripheral side of the inner casing and defines a heat medium flow path between the inner casing and the outer casing, a first stage turbine device that is arranged in the heat medium flow path and is arranged on one side of the rotor shaft in the axial direction relative to the generator, a second stage turbine device that is arranged in the heat medium flow path and is arranged on the other side of the rotor shaft in the axial direction relative to the generator, and on the inner peripheral side of the inner casing,
  • the second stage turbine device includes a journal bearing device arranged on the other side of the generator
  • the cold energy power generation device disclosed herein can reduce the pressure inside the inner casing at the position where the thrust bearing device is located, and by reducing the windage loss caused by the thrust bearing device, it is possible to suppress a decrease in generator performance.
  • FIG. 1 is a schematic diagram illustrating an overall configuration of a cold energy power generation system including a cold energy power generation device according to an embodiment of the present disclosure.
  • 1 is a schematic cross-sectional view of a cold energy generating device according to an embodiment of the present disclosure.
  • 2 is an enlarged cross-sectional view of the second stage turbine and its surroundings of a cold energy power generation device according to an embodiment of the present disclosure.
  • FIG. 3 is a schematic diagram of the AA cross section of the cold energy power generation device shown in FIG. 2.
  • 3 is a schematic diagram of the cross section BB of the cold energy power generation device shown in FIG. 2.
  • expressions indicating that things are in an equal state such as “identical,””equal,” and “homogeneous,” not only indicate a state of strict equality, but also indicate a state in which there is a tolerance or a difference to the extent that the same function is obtained.
  • expressions describing shapes such as a rectangular shape or a cylindrical shape do not only represent rectangular shapes or cylindrical shapes in the strict geometric sense, but also represent shapes that include uneven portions, chamfered portions, etc., to the extent that the same effect can be obtained.
  • the expressions “comprise”, “include”, or “have” a certain element are not exclusive expressions excluding the presence of other elements.
  • the same components are denoted by the same reference numerals and the description thereof may be omitted.
  • FIG. 1 is a schematic diagram illustrating an overall configuration of a cold energy power generation system including a cold energy power generation device according to an embodiment of the present disclosure.
  • the cold energy power generation system 100 is a cold energy power generation system 100 for recovering cold energy contained in a liquefied gas as electric power via a heat medium for heating the liquefied gas.
  • the cold energy power generation system 100 is installed, for example, on a water-borne floating structure 10A or a land-based liquefied gas base 10B, although there is no particular limitation thereto.
  • the water floating structure 10A is a structure that can float on the water.
  • the water floating structure 10A has a propulsion device configured to drive a thruster such as a propeller, and includes ships that can move on their own by driving the propulsion device, and floats that do not have a propulsion device.
  • the water floating structure 10A stores liquid liquefied gas, which is heated and vaporized by seawater or the like, and is then flowed into an engine (not shown) to obtain propulsion force. When the liquefied gas is vaporized, the cold energy is not dumped into the seawater by the cold energy power generation system 100, but is instead recovered as electricity by the cold energy power generation device 1 described below.
  • the land-based liquefied gas base 10B receives and stores the liquefied gas transported by the LNG carrier. Then, when it is to be supplied to a liquefied gas supply destination such as a city gas or thermal power plant, the liquefied gas is heated using seawater or the like to return it to gas. When the liquefied gas is vaporized, the cold energy generated by the cold energy power generation system 100 is not dumped into seawater, but is instead recovered as electricity by the cold energy power generation device 1, which will be described later.
  • the cold energy power generation system 100 of the present disclosure will be described as being installed on a ship 10 that uses liquefied gas as fuel, one of the above-mentioned floating structures 10A.
  • the cold energy power generation system 100 includes a cold energy power generation device 1, a liquefied gas supply line 2, a condenser 3, a heating fluid supply line 4, a cold energy pump 5, an evaporator 7, and a heat medium circulation line 9.
  • the cold energy power generation device 1, the condenser 3, the cold energy pump 5, and the evaporator 7 are each connected by the heat medium circulation line 9.
  • the liquefied gas supply line 2 is connected to the condenser 3.
  • the heating fluid supply line 4 is connected to the evaporator 7.
  • the heat medium circulation line 9, the liquefied gas supply line 2, and the heating fluid supply line 4 each include a flow path, such as a pipe, through which a fluid flows.
  • the cold energy power generation system 100 is configured to be driven by the heat medium circulating through the heat medium circulation line 9 while changing its state to liquid or gas.
  • the heat medium circulation line 9 is configured to circulate a heat medium with a lower freezing point than water.
  • liquefied natural gas LNG
  • propane is used as a specific example of a heat medium flowing through the heat medium circulation line 9.
  • the present disclosure is also applicable to liquefied gases other than liquefied natural gas (such as liquefied hydrogen), and is also applicable to cases where a heat medium other than propane, such as R1234yf or R1234ze, is used as the heat medium flowing through the heat medium circulation line 9.
  • the condenser 3 is configured to condense the working fluid (heat medium) by heat exchange between the heat medium and the liquefied gas.
  • a heating side pipe connected to the heat medium circulation line 9 and into which the heat medium circulating through the heat medium circulation line 9 flows, and a heated side pipe connected to the liquefied gas supply line 2 and into which the liquefied gas flowing through the liquefied gas supply line 2 flows.
  • the heat medium flowing through the heating side pipe and the liquefied gas flowing through the heated side pipe are configured to exchange heat.
  • the heat medium is cooled and condensed by heat exchange, and the liquefied gas is heated.
  • the liquefied gas supply line 2 upstream of the condenser 3 is connected to a liquefied gas pump 22 , and the further upstream side of the liquefied gas pump 22 is connected to a liquefied gas storage device 21 .
  • the liquefied gas in liquid form stored in the liquefied gas storage device 21 is sent to the liquefied gas supply line 2, flows through the liquefied gas supply line 2 from the upstream side to the downstream side, and is supplied to the condenser 3.
  • the liquefied gas vaporized by heat exchange inside the condenser 3 flows through the heated side pipe, and then flows through the liquefied gas supply line 2 again, and is supplied as fuel to the engine (not shown) of the ship 10 installed downstream of the condenser 3.
  • the cold heat pump 5 is configured to boost the pressure of the heat medium supplied from the condenser 3.
  • the heat medium circulates through the heat medium circulation line 9.
  • the heat medium flows from the condenser 3 to the cold heat pump 5, from the cold heat pump 5 to the evaporator 7, from the evaporator 7 to the cold energy power generation device 1, and from the cold energy power generation device 1 to the condenser 3.
  • the cold/heat pump 5 may be of any type as long as it can boost the pressure of the heat medium.
  • a turbo pump centrifugal pump, mixed flow pump, axial flow pump, etc.
  • a positive displacement pump reciprocating pump, rotary pump
  • a special pump submersible motor pump
  • the evaporator 7 is configured to evaporate the heat medium by heat exchange between the heat medium pressurized by the cold heat pump 5 and the heating fluid introduced from outside the cold heat power generation system 100.
  • the heat medium flowing through the heat medium heated side pipe and the heating fluid flowing through the heat medium heating side pipe are configured to exchange heat.
  • the heat medium is heated and evaporated by heat exchange, and the heating fluid is cooled.
  • the heating fluid supply line 4 upstream of the evaporator 7 is connected to a heating fluid pump 42.
  • the heating fluid supply line 4 further upstream of the heating fluid pump 42 is connected to a heating fluid supply source so that heating fluid is introduced from outside the cold energy power generation system 100.
  • the heating fluid is sent from the heating fluid supply source to the heating fluid supply line 4, flows through the heating fluid supply line 4 from the upstream side to the downstream side, and is supplied to the evaporator 7.
  • the heating fluid cooled by heat exchange inside the evaporator 7 flows through the heat medium heating side pipe, and then flows through the heating fluid supply line 4 again, and is discharged to the outside of the cold energy power generation system 100.
  • heating fluid may be any fluid that heats the heat medium circulating through the heat medium circulation line 9 as a heat medium in the evaporator 7, and may be steam, hot water, seawater, engine cooling water, or water at room temperature.
  • the heating fluid can preferably be water that is easily available on the ship 10 (e.g., outside ship water such as seawater, or engine cooling water that cools the engine of the ship 10).
  • the cold energy power generation device 1 is configured to be driven by a gaseous heat medium generated in an evaporator 7 .
  • the cold energy power generation device 1 also has a generator 8.
  • the generator 8 is driven by a rotor shaft 11 of the cold energy power generation device 1, which will be described later, being rotated by the gaseous heat medium generated in the evaporator 7.
  • the gaseous heat medium that has driven the cold energy power generation device 1 flows through a heat medium circulation line 9 toward the above-mentioned condenser 3, which is installed downstream of the cold energy power generation device 1.
  • FIG. 2 is a schematic cross-sectional view of the cold energy power generation device 1 according to an embodiment of the present disclosure.
  • Fig. 3 is an enlarged cross-sectional view of the second stage turbine device 24 and its surroundings of the cold energy power generation device 1 according to an embodiment of the present disclosure.
  • Fig. 4 is a schematic view of the A-A cross section of the cold energy power generation device shown in Fig. 2.
  • the upstream side in the flow direction of the heat medium in the cold energy power generation device 1 may be simply referred to as the upstream side
  • the downstream side in the flow direction of the heat medium in the cold energy power generation device 1 may be simply referred to as the downstream side.
  • the radial direction of the cold energy power generation device 1 may simply be referred to as the radial direction
  • the circumferential direction of the cold energy power generation device 1 may simply be referred to as the circumferential direction
  • the direction along the axis CA of the cold energy generating device 1 may be simply referred to as the axial direction.
  • the cold energy power generation device 1 in some embodiments includes a rotor shaft 11, a generator 8, a casing 6, a first stage turbine device 23, a second stage turbine device 24, a first journal bearing device 103, a second journal bearing device 104, and a thrust bearing device 102.
  • the rotor shaft 11 includes a shaft portion 111 having a longitudinal direction along the axis CA of the cold energy power generation device 1, a one-side disk portion 113A extending along the radial direction of the rotor shaft 11 on one side (upstream side) of the shaft portion 111 and supporting a first stage rotor blade 23B described later, and a other-side disk portion 113B extending along the radial direction of the rotor shaft 11 on the other side (downstream side) of the shaft portion 111 and supporting a second stage rotor blade 24B described later.
  • the axis of the rotor shaft 11 coincides with the axis CA of the cold energy power generation device 1 and the axis of the casing 6.
  • the axis of the rotor shaft 11 coincides with the horizontal direction, and the center of one end of the shaft portion 111 and the center of the other end of the shaft portion 111 are located at the same height level in the vertical direction.
  • the one-side disk portion 113A and the other-side disk portion 113B are fixed to the shaft portion 111 with nuts, and protrude radially outward from the outer surface of the shaft portion 111 in a circular plate shape.
  • the portion of the shaft portion 111 to which the one-side disk portion 113A and the other-side disk portion 113B are attached is formed with a smaller diameter than the other portions.
  • the generator 8 is configured to include a motor rotor 81 supported on the outer circumferential surface of the rotor shaft 11 , and a motor stator 82 disposed opposite the motor rotor 81 .
  • the motor rotor 81 is integrally formed on the outer circumferential surface of the rotor shaft 11, and the two have an integral structure.
  • the motor rotor 81 and the rotor shaft 11 may be formed separately, and the motor rotor 81 may be supported on the outer circumferential surface of the rotor shaft.
  • the motor stator 82 is supported on an inner circumferential surface 611 of the inner casing 61 described later, and is disposed radially outward of the motor rotor 81.
  • the casing 6 is composed of an inner casing 61 that houses the rotor shaft 11 and an outer casing 62 that is arranged on the outer periphery of the inner casing 61 and houses the inner casing 61 .
  • the inner casing 61 has a longitudinal direction along the axial direction of the cold energy power generation device 1, and is disposed between the first stage rotor blades 23B and the second stage rotor blades 24B in the axial direction of the cold energy power generation device 1.
  • a space 610 is formed inside the inner casing 61, and houses the shaft portion 111 and the generator 8 (in the illustrated example, the motor rotor 81 and the motor stator 82).
  • a heat medium flow path 63 is defined between the inner casing 61 and the outer casing 62.
  • the heat medium flow path 63 is defined between an outer peripheral surface 612 of the inner casing 61 and an inner peripheral surface 621 of the outer casing 62, and is configured to extend along the axial direction of the rotor shaft 11 from the upstream of the first stage stator vanes 23A to the downstream of the second stage rotor blades 24B.
  • the heat medium flow path 63 has a longitudinal direction along the axial direction of the cold-heat power generation device 1 and has an annular cross section surrounding the periphery of the inner casing 61.
  • the heat medium flow path 63 is configured to guide the heat medium from one side to the other side between the outer casing 62 and the inner casing 61.
  • a one-side cover 66A is disposed on one side (upstream side) of the inner casing 61, and a other-side cover 66B is disposed on the other side (downstream side).
  • the one-side cover 66A is disposed on one side of the inner casing body 61A so as to cover one end of the shaft portion 111 on one side in the axial direction of the first stage rotor blades 23B.
  • the other-side cover 66B is disposed on the other side of the inner casing body 61A so as to cover the other end of the shaft portion 111 on the other side in the axial direction of the second stage rotor blades 24B.
  • the heat medium flow path 63 extends to one side of the inner casing 61 by a space defined between the one-side cover 66A and the outer casing 62. Similarly, the heat medium flow path 63 extends to the other side of the inner casing 61 by a space defined between the other-side cover 66B and the outer casing 62.
  • a one-side inlet passage 64A for introducing the heat medium from one side along the axial direction into the heat medium passage 63 is formed on one side of the heat medium passage 63.
  • the one-side inlet passage 64A is defined by an inner surface of an inlet casing 65A connected to one side of the outer casing 62 on one axial side of the inner casing 61.
  • a second discharge passage 64B is formed on the other side of the heat medium passage 63 for discharging the heat medium from the heat medium passage 63 to the other side in the axial direction.
  • the second discharge passage 64B is defined by an inner surface of an outlet casing 65B connected to the other side of the outer casing 62 on the other axial side of the inner casing 61.
  • the heat medium introduced into the heat medium passage 63 from the one-side inlet passage 64A passes through the first-stage stator vanes 23A, and then acts on the first-stage rotor blades 23B to impart a rotational force to the rotor shaft 11, thereby driving the first-stage turbine device 23.
  • the heat medium passes through the first-stage rotor blades 23B, it exchanges heat with the heat generated in the generator 8 (motor rotor 81, motor stator 82) housed in the space 610 formed inside the inner casing 61 while flowing through the heat medium passage 63.
  • the heat generated in the generator 8 is absorbed by the heat medium flowing through the heat medium passage 63.
  • the generator 8 is cooled, and the heat medium flowing through the heat medium passage 63 is heated.
  • the heated heat medium acts on the second stage rotor blades 24B to impart a rotational force to the rotor shaft 11, thereby driving the second stage turbine device 24.
  • the heat medium heated by heat exchange with the generator 8 in the heat medium flow path 63 flows into the second stage turbine device 24, and this heated heat medium drives the second stage turbine device 24.
  • the heat medium that has flowed through the second stage turbine device 24 is discharged from the heat medium flow path 63 to the other side discharge path 64B and flows out to the outside of the cold energy power generation device 1.
  • the first stage turbine device 23 is disposed in the heat medium flow path 63.
  • the first stage turbine device 23 is configured to include a first stage rotor blade 23B provided on one side of the rotor shaft 11 relative to the motor rotor 81, and a first stage stator blade 23A supported by an inner circumferential surface 621 of the outer casing 62 or the inner casing 61 on one side of the rotor shaft 11 relative to the first stage rotor blade 23B.
  • the first stage rotor blades 23B are attached to the outer circumferential surface of the one-side disk portion 113A described above with a gap therebetween in the circumferential direction.
  • the first stage stator vanes 23A are supported by the inner circumferential surface 621 of the outer casing 62 and are provided on the inner circumferential surface 621 with a gap therebetween in the circumferential direction. In other embodiments, the first stage stator vanes 23A may be supported by the inner casing 61 and provided with a gap therebetween in the circumferential direction, or may be supported by both the inner circumferential surface 621 of the outer casing 62 and the inner casing 61.
  • the second stage turbine device 24 is disposed in the heat medium flow path 63.
  • the second stage turbine device 24 is configured to include second stage stator vanes 24A supported on the inner circumferential surface 621 of the outer casing 62 or the outer circumferential surface 612 of the inner casing 61 on the other side of the rotor shaft 11 from the motor rotor 81, and second stage rotor blades 24B provided on the other side of the rotor shaft 11 from the second stage stator vanes 24A.
  • the second stage rotor blades 24B are attached to the outer peripheral surface of the above-mentioned other-side disk portion 113B with a gap therebetween in the circumferential direction.
  • the second stage stator vanes 24A are supported by the inner peripheral surface 621 of the outer casing 62 and are provided on the inner peripheral surface 621 with a gap therebetween in the circumferential direction.
  • the second stage stator vanes 24A may be supported by the outer peripheral surface 612 of the inner casing 61 and provided on the outer peripheral surface 612 with a gap therebetween in the circumferential direction, or may be supported by both the inner peripheral surface 621 of the outer casing 62 and the outer peripheral surface 612 of the inner casing 61.
  • the first journal bearing device 103 is disposed inside the inner casing 61 on the other side of the generator 8, and includes a main bearing 103A and an auxiliary bearing 103B.
  • a main bearing 103A and an auxiliary bearing 103B that rotatably support the rotor shaft 11 are housed in a space 610 formed inside the inner casing 61.
  • the main bearing 103A is disposed on the other side of the motor rotor 81.
  • the auxiliary bearing 103B is disposed further on the other side of the main bearing 103A.
  • the first journal bearing device 103 may include only the main bearing 103A.
  • the second journal bearing device 104 is disposed inside the inner casing 61 on one side of the generator 8, and includes a main bearing 104A and an auxiliary bearing 104B.
  • a main bearing 104A and an auxiliary bearing 104B that rotatably support the rotor shaft 11 are housed in a space 610 formed inside the inner casing 61.
  • the main bearing 104A is disposed on one side of the motor rotor 81.
  • the auxiliary bearing 104B is disposed further on one side of the main bearing 104A.
  • the second journal bearing device 104 may include only the main bearing 104A.
  • the second journal bearing device 104 may not be provided.
  • the main bearings 103A, 104A may be magnetic bearings
  • the auxiliary bearings 103B, 104B may be ball bearings.
  • these auxiliary bearings 103B, 104B support the rotor shaft 11, preventing contact between the main bearings 103A, 104A and the rotor shaft 11.
  • the thrust bearing device 102 is disposed on one side of the first journal bearing device 103 inside the inner casing 61.
  • the thrust bearing device 102 is configured to include a one-side thrust bearing 102A and an other-side thrust bearing 102B disposed in a space 610 formed inside the inner casing 61, and receives the axial load (thrust force) of the rotor shaft 11. 2 and 3 , in the illustrated embodiment, the rotor shaft 11 further includes a thrust collar 112 extending radially inside the inner casing 61 on one side of the first journal bearing device 103 and on the other side of the generator 8.
  • the one-side thrust bearing 102A abuts against one side surface 112A, which is a side surface on one side of the thrust collar 112 provided on the rotor shaft 11.
  • the other-side thrust bearing 102B abuts against another side surface 112B, which is a side surface on the other side of the thrust collar 112.
  • the thrust bearing device 102 and the thrust collar 112 may be disposed inside the inner casing 61 on one side of the generator 8 .
  • the thrust bearing device 102 (the one-side thrust bearing 102A and the other-side thrust bearing 102B) may be configured by a magnetic bearing.
  • a radial gap 241 connected to the heat medium flow path 63 downstream of the second stage stator vane 24A is defined between the other-side end face 613, which is the other-side end face of the inner casing 61, and the other-side disk portion 113B.
  • the radial gap 241 is connected between the second stage stator vane 24A and the second stage rotor blade 24B in the heat medium flow passage 63, and has an annular cross section surrounding the rotor shaft 11.
  • the radial gap 241 has a uniform width in the axial direction, and extends along the radial direction.
  • the inner casing 61 is formed with at least one pressure equalizing passage 40 for communicating between a first space 614 on one side of the first journal bearing device 103 inside the inner casing 61 and the radial gap 241.
  • the pressure equalizing passage 40 includes a first space side opening 40A opening into the first space 614, a radial gap side opening 40B opening into the other side end face 613, a radial passage 401 extending along the radial direction from the first space side opening 40A, an axial passage 402 connecting to the radial passage 401 and extending in the axial direction of the rotor shaft 11, and a other side passage 403 connecting the axial passage 402 and the radial gap side opening 40B.
  • the other side passage 403 extends such that the distance from the axis of the rotor shaft 11 increases as it moves from the radial gap side opening 40B toward one side.
  • the first space side opening 40A is located radially outward from the radially inner end 102B1 of the other thrust bearing 102B, which is a stationary member. Therefore, the heat medium that flows from the upstream to the downstream of the thrust bearing device 102 can be introduced into the first space side opening 40A without being affected by the rotation of the rotor shaft 11.
  • the radial flow passages 401, the axial flow passages 402, and the other-side flow passages 403 each have a circular cross-sectional shape, and extend so that the flow passage areas are constant.
  • the radial flow passages 401, the axial flow passages 402, and the other-side flow passages 403 are also formed to have the same flow passage areas.
  • the heat medium introduced into the heat medium flow passage 63 from the one-side inlet passage 64A passes through the first-stage stator vanes 23A and the first-stage rotor blades 23B of the first-stage turbine device 23 and is introduced into the second-stage turbine device 24.
  • the heat medium introduced into the second-stage turbine device 24 passes through the second-stage stator vanes 24A and the second-stage rotor blades 24B of the second-stage turbine device and is discharged from the other-side discharge passage 64B. Further, a part of the heat medium leaks and flows into the inside of the inner casing 61, not into the heat medium flow passage 63.
  • the heat medium that has flowed into the inner casing 61 flows through the first space 614 and the pressure equalizing flow passage 40 in this order inside the inner casing 61, and flows into the radial gap 241 from the radial gap side opening 40B.
  • the pressure in the heat medium flow passage 63 downstream of the second stage stator vane 24A is lower than the inlet of the heat medium flow passage 63 because the heat medium passes through the first stage stator vane 23A, the first stage moving blade 23B, and the second stage stator vane 24A in that order.
  • the pressure in the heat medium flow passage 63 downstream of the second stage stator vane 24A is also lower than the pressure in the radial gap 241 of the heat medium that has passed through the inside of the inner casing 61.
  • the heat medium that has passed through the inner casing 61 and flowed into the radial gap 241 flows from the radial inside to the radial outside of the radial gap 241 and flows out into the heat medium flow passage 63 downstream of the second stage stator vane 24A. Then, the pressure inside the inner casing 61 decreases, and the pressure around the thrust bearing device 102 also decreases, reducing windage loss (loss) due to the thrust bearing device 102 and suppressing a decrease in generator performance.
  • the pressure inside the inner casing 61 is lower downstream due to pressure losses caused by the second journal bearing device 104, motor rotor 81, motor stator 82, etc.
  • the thrust bearing device 102 is disposed on the other side (downstream) of the generator 8, so the pressure around the thrust bearing device 102 is lowered, further reducing windage loss caused by the thrust bearing device 102 and suppressing deterioration of generator performance.
  • the first space 614 may also be formed on the other side of the thrust bearing device 102.
  • the pressure equalizing passage 40 communicates between the first space 614 and the radial gap 241 without passing through the radial outside of the thrust bearing device 102, which has a larger diameter. Therefore, the outer diameter of the inner casing 61 can be made smaller than when the pressure equalizing passage 40 passes through the radial outside of the thrust bearing device 102, and the entire cold energy power generation device 1 can be simplified.
  • multiple pressure equalizing channels 40 may be formed at intervals in the circumferential direction.
  • the multiple pressure equalizing channels 40 may be arranged at equal intervals in the circumferential direction.
  • the cross-sectional shape of the pressure equalizing channel 40 is circular, but it may be non-circular, such as elliptical or rectangular.
  • FIG. 5 is a schematic diagram of the cross section of the cold energy power generation device 1 shown in FIG. 2 taken along the line BB.
  • the other-side disk portion 113B has a through hole 50 that communicates the radial gap 241 and a space 615 on the other side of the second stage rotor blade 24B.
  • the pressure downstream of the second stage rotor blade 24B is lower than the pressure in the radial gap 241 defined upstream of the second stage rotor blade 24B. Therefore, by the through hole 50 connecting the radial gap 241 to the space downstream of the second stage rotor blade 24B, the heat medium in the radial gap 241 can flow out to the space 615, lowering the pressure inside the inner casing 61 in which the thrust bearing device 102 is disposed. This reduces the windage loss caused by the thrust bearing device 102.
  • the through hole 50 is also formed opposite the radial gap opening 40B. Therefore, the heat medium flowing out from the radial gap opening 40B of the pressure equalizing passage 40 can flow through the through hole 50 of the other side disk portion 113B into the space 615, thereby reducing the pressure inside the inner casing 61.
  • a plurality of through holes 50 may be formed at intervals in the circumferential direction.
  • the plurality of through holes 50 may be arranged at equal intervals in the circumferential direction.
  • the cross-sectional shape of the through hole 50 is circular, but it may be non-circular, for example, elliptical or rectangular.
  • the first space side opening 40A and the radial gap side opening 40B for the same pressure equalizing passage 40 are located on the same axial cross section including the axis of the rotor shaft 11.
  • the pressure equalizing passage 40 is formed without rotating around the axis CA of the cold energy power generation device 1. With this configuration, the pressure equalizing passage 40 can be easily formed in the inner casing 61.
  • the cold energy power generation device 1 further includes a seal portion 26 that seals between the rotor shaft 11 and the inner casing 61 on the other side of the first stage turbine device 23 and on one side of the generator 8.
  • the seal portion 26 seals the gap between the inner peripheral surface 611 of the inner casing 61 and the outer peripheral surface of the shaft portion 111 of the rotor shaft 11 on the other side of the first stage turbine device 23 and on one side of the generator 8.
  • the seal portion 26 may include a mechanical seal, or may include a labyrinth seal that is provided by machining the shaft portion 111 or the inner casing 61 to have projections and recesses.
  • the cold energy power generation device 1 described above does not include a member for sealing between the rotor shaft 11 and the inner casing 61 on the other side of the generator 8 inside the inner casing 61, as shown in Figures 2 and 3.
  • a sealing member such as a mechanical seal or labyrinth seal like the above-mentioned seal portion 26 is not provided on the other side of the generator 8 inside the inner casing 61.
  • a cold energy power generation device (1) includes: A cold energy power generation device (1) provided in a heat medium circulation line configured to circulate a heat medium for heating a liquefied gas, A rotor shaft (11); a generator (8) including a motor rotor (81) supported on an outer circumferential surface of the rotor shaft (11) and a motor stator (82) arranged opposite the motor rotor (81); an inner casing (61) that houses the generator (8); an outer casing (62) disposed on an outer circumferential side of the inner casing (61) and defining a heat medium flow path (63) between the outer casing (62) and the inner casing (61); a first stage turbine device (23) disposed in the heat medium flow path (63) and disposed on one side of the generator (8) in the axial direction of the rotor shaft (11); a second stage turbine device (24) disposed in the heat medium flow path (63) and disposed on the other side of the generator (8) in the axial direction of the rotor shaft (11); a journal
  • a radial gap is defined that is connected to the downstream side of the second stage stator vane in the heat medium flow passage, and at least one pressure equalizing passage is formed in the inner casing for communicating the radial gap with a first space on one side of the journal bearing device inside the inner casing.
  • the heat medium passes through the pressure equalizing passage from the first space, flows from the inside to the outside in the radial gap in the radial direction, and flows out into the heat medium flow passage.
  • the heat transfer medium flows through a heat transfer medium flow passage defined between the inner casing and the outer casing in the order of the first stage turbine device and the second stage turbine device.
  • the pressure in the radial gap defined downstream of the second stage stator vane is lower than the pressure upstream of the second stage stator vane. Therefore, by connecting the first space and the radial gap through the pressure equalizing passage, the pressure inside the inner casing in which the thrust bearing device is disposed can be reduced, thereby reducing windage loss of the thrust bearing device and suppressing deterioration of generator performance.
  • a cold energy power generation device (1) is the cold energy power generation device according to (1),
  • the thrust bearing device (102) is disposed on the other side of the generator (8).
  • the pressure on the other side of the generator is lower than the pressure on one side of the generator.
  • the thrust bearing device is positioned on the other side of the generator, which reduces the pressure in the area where the thrust bearing device is positioned, and reduces windage loss caused by the thrust bearing device.
  • a cold energy power generation device (1) according to yet another aspect is the cold energy power generation device according to (2),
  • the first space (614) is defined on the other side of the thrust bearing device (102).
  • the pressure equalizing passage communicates with the first space and the radial gap without passing through the radial outside of the thrust bearing device, which has a larger diameter. Therefore, the outer diameter of the inner casing body can be made smaller than when the pressure equalizing passage passes through the radial outside of the thrust bearing device, and the entire cold energy power generation device can be simplified.
  • a cold energy power generation device (1) is the cold energy power generation device according to (3),
  • the journal bearing device (103) includes a main bearing (103A) and an auxiliary bearing (103B).
  • a cold energy power generation device (1) is the cold energy power generation device according to any one of (1) to (4),
  • the disk portion (113B) has at least one through hole (50) penetrating in the axial direction of the rotor shaft (11).
  • the pressure downstream of the second stage rotor blades is lower than the pressure in the radial gap defined upstream of the second stage rotor blades. Therefore, with this configuration, the through holes connect the radial gap to the space downstream of the second stage rotor blades, allowing the heat medium in the radial gap to flow out into the space, thereby lowering the pressure inside the inner casing in which the thrust bearing device is located. This makes it possible to reduce windage loss caused by the thrust bearing device 102.
  • a cold energy power generation device (1) is the cold energy power generation device according to any one of (1) to (5),
  • the turbine further includes a seal portion (26) for sealing between the rotor shaft (11) and the inner casing (61) on the other side of the first stage turbine device (23) and on the one side of the generator (8).
  • the heat medium leaking from the high pressure region of the first stage turbine device into the inner casing can be sealed off, so the pressure inside the inner casing can be kept lower than when no seal member is provided, thereby reducing the thrust force acting on the rotor shaft and the windage loss (loss) caused by the thrust bearing device inside the inner casing.
  • the heat medium that has passed through the first stage rotor blades since it is possible to prevent the heat medium that has passed through the first stage rotor blades from leaking into the inside of the inner casing body, it is possible to prevent a decrease in the heat medium flowing through the heat medium flow passage compared to a case in which a sealing member is not provided, and it is possible to improve the efficiency of the second stage turbine device.
  • a cold energy power generation device (1) according to yet another aspect is the cold energy power generation device according to (6), On the other side of the generator (8) inside the inner casing (61), no sealing member is provided between the rotor shaft (11) and the inner casing (61).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)

Abstract

L'invention concerne un appareil de production d'énergie cryogénique doté d'un dispositif de palier de butée placé d'un côté dans le sens axial d'un arbre de rotor par rapport à un premier dispositif de palier lisse dans le côté circonférentiel interne d'un boîtier interne, un espace dans le sens radial relié à un canal de fluide thermique étant formé entre un disque et l'autre surface d'extrémité qui est la surface d'extrémité à l'autre extrémité du boîtier interne, et au moins un canal de pression uniforme reliant l'espace dans le sens radial et un premier espace situé d'un côté par rapport au premier palier à l'intérieur du boîtier interne étant formé dans ce dernier.
PCT/JP2023/035595 2022-10-13 2023-09-29 Appareil et système de production d'énergie cryogénique WO2024080158A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2022-164632 2022-10-13
JP2022164632A JP2024057758A (ja) 2022-10-13 2022-10-13 冷熱発電装置、及び冷熱発電システム

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WO2024080158A1 true WO2024080158A1 (fr) 2024-04-18

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Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58143101A (ja) * 1982-02-22 1983-08-25 Toshiba Corp 蒸気タ−ビン
JPS58156101U (ja) * 1982-04-14 1983-10-18 株式会社日立製作所 気体軸受式膨張タ−ビン
JP2006230145A (ja) * 2005-02-18 2006-08-31 Ebara Corp サブマージドタービン発電機
JP2010001894A (ja) * 2008-06-17 2010-01-07 Snecma 永続ピストン保持システムを備えたターボマシン
JP2012241604A (ja) * 2011-05-19 2012-12-10 Chiyoda Kako Kensetsu Kk 複合発電システム
JP2017194042A (ja) * 2016-04-22 2017-10-26 三菱重工サーマルシステムズ株式会社 ターボ圧縮機、これを備えたターボ冷凍装置
US20200059179A1 (en) * 2017-04-27 2020-02-20 Anax Holdings, Llc System and method for electricity production from pressure reduction of natural gas
CN210660229U (zh) * 2019-11-13 2020-06-02 重庆江增船舶重工有限公司 一种膨胀发电一体式高速膨胀机
CN112431640A (zh) * 2020-11-11 2021-03-02 中国船舶重工集团公司第七一一研究所 一种管道式工艺气压力能回收发电装置及工艺气减压管路
WO2021229897A1 (fr) * 2020-05-11 2021-11-18 日揮グローバル株式会社 Système et procédé de réglage de température
CN114867931A (zh) * 2021-11-09 2022-08-05 三菱重工船用机械株式会社 冷能发电用涡轮和具备冷能发电用涡轮的冷能发电动系统

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58143101A (ja) * 1982-02-22 1983-08-25 Toshiba Corp 蒸気タ−ビン
JPS58156101U (ja) * 1982-04-14 1983-10-18 株式会社日立製作所 気体軸受式膨張タ−ビン
JP2006230145A (ja) * 2005-02-18 2006-08-31 Ebara Corp サブマージドタービン発電機
JP2010001894A (ja) * 2008-06-17 2010-01-07 Snecma 永続ピストン保持システムを備えたターボマシン
JP2012241604A (ja) * 2011-05-19 2012-12-10 Chiyoda Kako Kensetsu Kk 複合発電システム
JP2017194042A (ja) * 2016-04-22 2017-10-26 三菱重工サーマルシステムズ株式会社 ターボ圧縮機、これを備えたターボ冷凍装置
US20200059179A1 (en) * 2017-04-27 2020-02-20 Anax Holdings, Llc System and method for electricity production from pressure reduction of natural gas
CN210660229U (zh) * 2019-11-13 2020-06-02 重庆江增船舶重工有限公司 一种膨胀发电一体式高速膨胀机
WO2021229897A1 (fr) * 2020-05-11 2021-11-18 日揮グローバル株式会社 Système et procédé de réglage de température
CN112431640A (zh) * 2020-11-11 2021-03-02 中国船舶重工集团公司第七一一研究所 一种管道式工艺气压力能回收发电装置及工艺气减压管路
CN114867931A (zh) * 2021-11-09 2022-08-05 三菱重工船用机械株式会社 冷能发电用涡轮和具备冷能发电用涡轮的冷能发电动系统

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