WO2018159245A1 - ボイラ及びボイラシステム並びにボイラの運転方法 - Google Patents

ボイラ及びボイラシステム並びにボイラの運転方法 Download PDF

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Publication number
WO2018159245A1
WO2018159245A1 PCT/JP2018/004249 JP2018004249W WO2018159245A1 WO 2018159245 A1 WO2018159245 A1 WO 2018159245A1 JP 2018004249 W JP2018004249 W JP 2018004249W WO 2018159245 A1 WO2018159245 A1 WO 2018159245A1
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WO
WIPO (PCT)
Prior art keywords
pressure
steam
gas
boiler
boil
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Application number
PCT/JP2018/004249
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English (en)
French (fr)
Japanese (ja)
Inventor
貴澄 寺原
健太 高本
英輝 天野
Original Assignee
三菱重工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Priority to KR1020197022958A priority Critical patent/KR102314907B1/ko
Priority to DK18761517.4T priority patent/DK3591293T3/da
Priority to EP18761517.4A priority patent/EP3591293B1/en
Priority to CN201880011465.3A priority patent/CN110325793B/zh
Publication of WO2018159245A1 publication Critical patent/WO2018159245A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/001—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space spraying nozzle combined with forced draft fan in one unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B35/00—Control systems for steam boilers
    • F22B35/06—Control systems for steam boilers for steam boilers of forced-flow type
    • F22B35/14—Control systems for steam boilers for steam boilers of forced-flow type during the starting-up periods, i.e. during the periods between the lighting of the furnaces and the attainment of the normal operating temperature of the steam boilers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D17/00—Burners for combustion conjointly or alternatively of gaseous or liquid or pulverulent fuel
    • F23D17/002—Burners for combustion conjointly or alternatively of gaseous or liquid or pulverulent fuel gaseous or liquid fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23Q—IGNITION; EXTINGUISHING-DEVICES
    • F23Q3/00—Igniters using electrically-produced sparks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2204/00—Burners adapted for simultaneous or alternative combustion having more than one fuel supply
    • F23D2204/10—Burners adapted for simultaneous or alternative combustion having more than one fuel supply gaseous and liquid fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2207/00—Ignition devices associated with burner
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23Q—IGNITION; EXTINGUISHING-DEVICES
    • F23Q3/00—Igniters using electrically-produced sparks
    • F23Q3/008—Structurally associated with fluid-fuel burners

Definitions

  • the present invention relates to a boiler, a boiler system, and a method of operating a boiler.
  • the LNG carrier carries and transports LNG (Liquefied Natural Gas) into an LNG tank. Since the LNG filled in the LNG tank has a low vaporization temperature, a large amount of vaporized gas (boil off gas) is generated in the LNG tank during the voyage of the LNG carrier under the influence of the outside air temperature and the like.
  • boil off gas When boil off gas is generated in the LNG tank, the pressure in the LNG tank rises, but the pressure in the LNG tank is maintained appropriately by mainly consuming the boil off gas with the main engine of the LNG carrier.
  • the boil-off gas is burned by a gas combustion unit (GCU) or the like to prevent an increase in pressure in the LNG tank.
  • GCU gas combustion unit
  • Patent Document 1 discloses an LNG carrier equipped with a gas burner downstream of an LNG storage tank.
  • the pressure of the LNG storage tank is set up by the evaporative gas (boil off gas) generated inside the LNG storage tank.
  • the evaporative gas (boil off gas) is sent to a gas burner (GCU) for burning and burning.
  • Patent Document 2 discloses a conventional boiler for burning a boil-off gas.
  • Patent No. 4563420 Unexamined-Japanese-Patent No. 4-46892
  • the present invention has been made in view of such circumstances, and provides a boiler, a boiler system, and a boiler operating method that can process boil-off gas and simultaneously utilize energy of the boil-off gas.
  • the purpose is to
  • a boiler according to an aspect of the present invention is a boiler to which a boil-off gas generated by a fuel tank storing fuel is supplied, comprising a burner for burning the boil-off gas, the burner comprising a first igniter, And a second igniter having a frequency of sparking at the time of ignition more than the first igniter.
  • the boil-off gas generated in the fuel tank is supplied to the boiler.
  • the boil-off gas generated in the fuel tank can be burned by the boiler. Therefore, the boil-off gas can be processed without providing a dedicated device (such as a GCU) for burning the boil-off gas, and at the same time, the energy of the boil-off gas can generate steam.
  • the burner includes the first igniter and the second igniter having a higher frequency of sparking at the time of ignition than the first igniter. Since the second igniter has a higher frequency of sparking at the time of ignition than the first igniter, the load at the time of ignition is large, and the second igniter is easily consumed more than the first igniter. That is, the first igniter is less likely to be consumed than the second igniter because the opposite is true and the frequency of sparks at the time of ignition is lower than that of the second igniter.
  • the burner is provided with an igniter having different characteristics. Therefore, it is possible to burn the boil-off gas appropriately and to generate steam by using different igniters having different characteristics according to the conditions in the boiler and the fuel tank, and prolong the product life of the igniters. Can.
  • the second igniter may be used when starting combustion by the boil-off gas in the burner.
  • Boil-off gas is generated in the fuel tank, and if the pressure in the fuel tank becomes high, the fuel tank may be damaged. For this reason, when the pressure in the fuel tank is lowered by burning the boil-off gas, if the pressure in the fuel tank becomes a threshold pressure which is smaller by a predetermined value than the pressure at which the fuel tank may be damaged It is necessary to burn off the boil off gas. Therefore, when burning the boil-off gas, it is preferable that the time to ignition of the burner be short.
  • the second igniter is used when burning the boil-off gas. The second igniter can perform ignition in a shorter time than the first igniter, so that the boil-off gas can be burned quickly. Therefore, in the boiler, the boil-off gas can be subjected to combustion processing to preferably maintain the pressure in the fuel tank at a predetermined value or less.
  • a boiler according to an aspect of the present invention includes a steam drum in which steam is contained, and the first igniter is used to start boosting the steam pressure in the steam drum by the combustion of the burner.
  • the boiler may be overloaded.
  • the amount of combustion treatment of the boil off gas in the boiler may be limited due to the overload of the boiler, and a desired amount of boil off gas may not be burnt. Therefore, when the boil off gas is burned in the boiler, if the steam pressure in the steam drum is not sufficient, it is necessary to increase the steam pressure in the steam drum.
  • the first igniter is used.
  • the second igniter which is more easily damaged than the first igniter, when boosting the steam pressure in the steam drum. Therefore, the frequency of use of the second igniter can be reduced, and the product life of the second igniter can be extended.
  • a boiler system is a boiler system including the above-described boiler, comprising: drum pressure detection means for detecting steam pressure in the steam drum; and tank pressure for detecting pressure in the fuel tank Based on the detecting means, the steam pressure in the steam drum detected by the drum pressure detecting means, and the target steam pressure in the steam drum, which is the steam pressure for burning the boil-off gas, the inside of the steam drum
  • a target pressure arrival time calculating unit that calculates a time until the steam pressure reaches the target steam pressure, the pressure in the fuel tank detected by the tank pressure detection unit, and the boil-off gas supplied to the fuel tank Calculating the time until the pressure in the fuel tank reaches the predetermined pressure, based on the predetermined pressure in the fuel tank, which is The pressure in the fuel tank is calculated based on the predetermined pressure arrival time calculation unit, the target pressure arrival time calculated by the target pressure arrival time calculation unit, and the predetermined pressure arrival time calculated by the predetermined pressure arrival time calculation unit.
  • An ignition timing calculation unit that calculates an ignition timing so that the steam pressure in the steam drum becomes the target steam pressure when the predetermined pressure is reached, and the ignition timing calculated by the ignition timing calculation unit Ignition control means for igniting the burner by the first igniter and starting pressure increase of the steam pressure in the steam drum.
  • the burner when the pressure in the fuel tank reaches a predetermined pressure for supplying the boil-off gas to the boiler, the burner is ignited so that the steam pressure in the steam drum becomes the target pressure. Therefore, when the boil-off gas is burned in the boiler, the steam pressure in the steam drum can be set to a steam pressure sufficient to burn the boil-off gas, and the boiler steam pressure has not reached the target steam pressure. It is possible to prevent the boiler from being overloaded and to burn the boil off gas suitably.
  • the amount of boil-off gas generated in the fuel tank that is, the tendency of the pressure increase in the fuel tank fluctuates depending on the conditions such as sea conditions, so the boiler pressure increase was started based only on the predetermined pressure in the fuel tank.
  • the combustion of the boil-off gas may not be ready.
  • the ignition timing is calculated such that the steam pressure in the steam drum becomes the target steam pressure when the pressure in the fuel tank reaches a predetermined pressure. ing. Therefore, when the pressure in the fuel tank reaches a predetermined pressure, the pressure in the steam drum in the steam drum is completed to the target pressure, so boil-off gas is promptly supplied to the boiler for combustion, and the inside of the fuel tank Pressure can be reduced.
  • the predetermined pressure is, for example, a threshold pressure smaller by a predetermined value than a pressure at which the fuel tank may be damaged.
  • the time taken for the pressure in the fuel tank to reach a predetermined pressure is calculated, and the burner in the steam drum is preliminarily made to match the time for the pressure in the fuel tank to reach a predetermined pressure.
  • the pressure in the steam drum is raised by ignition to the target pressure state.
  • the steam pressure in the steam drum is increased according to the pressure increase rate in the fuel tank, and the steam pressure in the steam drum is constantly maintained at a high pressure in order to burn the boil-off gas. There is no need.
  • the time during which the boiler operates at high pressure can be shortened compared to a boiler system that maintains a high pressure state so that the boil off gas can always be processed, and fuel in the boiler (MGO (Marine Gas Oil) etc.) Consumption can be reduced.
  • MGO Marine Gas Oil
  • the operating method of a boiler is an operating method of a boiler to which a boil-off gas generated in a fuel tank storing fuel is supplied, and a burner provided in the boiler is ignited by a first igniter. And the second igniter, wherein the second igniter has a higher frequency of sparks during ignition than the first igniter, after the step of pressurizing the vapor pressure in the steam drum by the combustion of the burner and the step of pressurizing the second igniter. And a combustion step of performing combustion by the boil-off gas in the burner.
  • a boiler can process boil-off gas, and at the same time, energy of the boil-off gas can be utilized.
  • the boiler system according to the present embodiment is applied to, for example, an LNG carrier 2 equipped with a gas-fired main engine 10.
  • the LNG carrier 2 recovers the heat of the LNG tank (fuel tank) 3 for storing LNG, the boiler 4 for burning the boil off gas generated in the LNG tank 3 to generate steam, and the exhaust gas generated by the main engine 10 And an economizer 5 for generating steam, and a control device 6 for controlling the boiler 4.
  • Boil-off gas generated in the LNG tank 3 is supplied by the first supply compressor 13 provided in the boil-off gas supply pipe 12 to the main engine 10, the mixed combustion engine (not shown) for power generation, the reliquefaction device 15 and the like. .
  • the main engine 10 and the mixed combustion engine for power generation burn the supplied boil-off gas to obtain driving force.
  • the boil off gas is reliquefied by compressing and cooling the boil off gas, and the reliquefied boil off gas is returned to the LNG tank 3 through the return pipe 16.
  • a part of the boil-off gas generated in the LNG tank 3 is supplied to the boiler 4 via the boil-off gas supply pipe 17 connecting the LNG tank 3 and the boiler 4.
  • the boil-off gas supply pipe 17 is provided with a second supply compressor 18 used to supply the boil-off gas to the boiler 4 and a vent pipe 19 discharging the boil-off gas to the atmosphere.
  • an in-tank pressure gauge (tank pressure detection means) 20 for detecting the pressure in the LNG tank 3 is provided in the LNG tank 3.
  • the in-tank pressure gauge 20 transmits the acquired pressure in the LNG tank 3 to the cargo tank control device 40.
  • the boiler 4 includes a furnace (not shown), a steam drum 21 disposed on the upper side, and a water drum 22 disposed on the lower side.
  • the furnace is provided with a burner 23 (see FIG. 2A) and performs combustion in the furnace.
  • the burner 23 is ignited in the furnace and the feed water is heated in the boiler 4, the water rises from the lower water drum 22 to the upper steam drum 21, and the gas and liquid are separated by the steam drum 21.
  • the steam drum 21 is provided with an in-drum pressure gauge (drum pressure detection means) 24 that measures the steam pressure in the steam drum 21.
  • the in-drum pressure gauge 24 transmits the acquired steam pressure in the steam drum 21 to the control device 6.
  • the steam drum 21 is connected to a boiler steam supply pipe 28 for supplying the steam separated by the steam drum 21 to a power generation turbine 26, a condenser 27, steam-using equipment and the like.
  • a generator 29 is connected to the rotation shaft of the power generation turbine 26, and the generator 29 generates electric power by the rotational force of the power generation turbine 26.
  • the steam discharged from the power generation turbine 26 is supplied to the condenser 27 via the steam discharge pipe 30.
  • Two economizers 5 are provided and respectively generate steam by heat exchange between the flue gas discharged from the main engine 10 and water.
  • the economizer 5 and the steam drum 21 are connected by an economizer steam supply pipe 32.
  • the economizer steam supply pipe 32 supplies the gas and liquid generated by the economizer 5 to the steam drum 21.
  • the separated steam is supplied to each device such as the power generation turbine 26 via the boiler steam supply pipe 28.
  • the water drum 22 and the economizer 5 are connected by a water supply pipe 33.
  • the water supply pipe 33 supplies the water in the water drum 22 to the economizer 5 by a pump 34 provided at an intermediate position.
  • the steam separator 35 may be separately provided to separate the gas and liquid produced by the economizer 5 in the steam separator 35.
  • the economizer 5 and the brackish water separator 35 are connected by the economizer steam supply pipe 36 and the water supply pipe 37.
  • the steam generated in the economizer 5 is supplied to the steam separator 35 by the economizer steam supply pipe 36.
  • the water supply pipe 37 supplies the water in the steam separator 35 to the economizer 5 by a pump 38 provided at an intermediate position.
  • the number of economizers 5 may be one, or three or more.
  • a boiler system is configured by the boiler 4, the control device 6, the in-tank pressure gauge 20, the in-drum pressure gauge 24, and the like.
  • the burner 23 provided in the furnace of the boiler 4 will be described in detail with reference to FIGS. 2A to 4.
  • the burner 23 includes a main burner 41 that forms a flame in the furnace, a pilot burner 42 that ignites the main burner 41, and an intermittent discharge igniter (second igniter) 43. And have.
  • the main burner 41 includes an oil supply unit that supplies oil, a gas supply unit that supplies boil-off gas, and an air passage that supplies combustion air.
  • the oil supply unit includes an oil supply pipe 47 for distributing oil supplied from an oil supply device (not shown) via the oil supply passage 11 (see FIG. 1).
  • the oil supply pipe 47 is formed of a cylindrical member extending in the vertical direction substantially at the center of the burner 23, and oil flows downward from the inside.
  • the oil supply pipe 47 is disposed such that the lower end portion thereof is located in the furnace.
  • a tip 48 is provided at the lower end of the oil supply pipe 47, and the oil passing through the tip 48 is sprayed into the furnace. Examples of the oil to be supplied include light oil and heavy oil.
  • the gas supply unit has a gas supply chamber 49 connected to a boil-off gas supply pipe 17 through which boil-off gas from the LNG tank 3 flows, and five gas distribution pipes 50 extending downward from the gas supply chamber 49.
  • the five gas distribution pipes 50 are arranged at equal intervals so as to surround the oil supply pipe 47, as shown in FIG. Moreover, as shown to FIG. 2A and FIG. 2B, the gas distribution piping 50 is arrange
  • a nozzle 51 is provided at the lower end of the gas distribution pipe 50, and the nozzle 51 ejects a boil-off gas into the furnace.
  • the air passage is provided to cover the oil supply pipe 47 and the gas distribution pipe 50.
  • the air passage includes a cylindrical air passage 52 extending vertically, a cylindrical burner tile 53 extending downward from the lower end of the air passage 52, and a plurality of swirlers 54 provided in the burner tile 53. ing.
  • the air passage 52 distributes the combustion air supplied from the air supply device (not shown) to the inside as shown by the arrows in FIGS. 2A and 2B.
  • a cylindrical burner tile 53 is attached to the lower portion of the air passage portion 52, the upper portion of the inner peripheral surface of the burner tile 53 extends in a substantially vertical direction, and the lower portion of the inner peripheral surface has a diameter toward the center of the furnace. Is formed to expand.
  • the lower part of the burner tile 53 is a truncated cone-shaped hollow part.
  • the plurality of swirl vanes 54 are interposed between the gas distribution pipe 50 and the outer peripheral surface of the oil supply pipe 47, and are arranged at equal intervals in the circumferential direction of the oil supply pipe 47.
  • the pilot burner 42 extends parallel to the oil supply pipe 47 of the main burner 41 near the main burner 41 as shown in FIGS. 2A and 2B, and the lower end is the lower end of the oil supply pipe 47 and the gas distribution pipe 50 It is arranged to be positioned above the other. Further, as shown in FIG. 4, the pilot burner 42 extends in the vertical direction and an oil supply pipe 55 through which oil flows, and a continuous discharge igniter (first ignition device) extending substantially in parallel with the oil supply pipe 55. And a pilot burner main body 57 provided so as to cover the oil supply pipe 55 and the continuous discharge igniter 56.
  • the oil supply pipe 55 internally distributes the oil supplied from an oil supply pump (not shown).
  • a tip 58 is provided at the lower end of the oil supply pipe 55, and the oil passing through the tip 58 is sprayed.
  • the continuous discharge igniter 56 is connected to the igniter cable 59 and is continuously discharged by the electricity from the igniter cable 59.
  • the lower end portion of the continuous discharge igniter 56 is bent so as to be disposed vertically below the lower end of the oil supply pipe 55. That is, the pilot burner 42 is ignited by discharging the oil sprayed from the oil supply pipe 55 from the lower end portion of the continuous discharge igniter 56.
  • a flame is formed from the pilot burner 42 downward.
  • the formed flame is formed such that the lower end of the flame is located below the lower ends of the oil supply pipe 47 and the gas distribution pipe 50. That is, the formed flame ignites the oil or gas discharged from the oil supply pipe 47 or the gas distribution pipe 50.
  • the intermittent discharge igniter 43 extends vertically in the vicinity of the main burner 41, and is inclined so that the lower portion approaches the main burner 41.
  • the lower end portion of the intermittent discharge igniter 43 is intermittently discharged by electricity.
  • the intermittent discharge igniter 43 is supported so as to be movable up and down by a predetermined distance.
  • the lower end portion of the intermittent discharge igniter 43 is disposed below the lower ends of the oil supply pipe 47 and the gas distribution pipe 50, as shown in FIG. 2A, when the ignition is performed.
  • the lower end portion of the intermittent discharge igniter 43 discharges the oil or gas sprayed from the oil supply pipe 47 or the gas distribution pipe 50 to perform ignition. After ignition, as shown in FIG.
  • the lower end is pulled upward so as to be positioned above the lower ends of the oil supply pipe 47 and the gas distribution pipe 50.
  • the lower end of the intermittent discharge igniter 43 is prevented from being damaged by the flame of the main burner 41.
  • the intermittent discharge igniter 43 has a higher frequency of sparking at the time of ignition than the continuous discharge igniter 56 that ignites the pilot burner 42.
  • the intermittent discharge igniter 43 discharges at a voltage of about 1500 V, intermittently performs sparking until the ignition of the main burner 41 is completed, and continuously performs 20 times of sparks for one second until the ignition is completed.
  • the continuous discharge igniter 56 discharges at a voltage of about 10000 V and maintains the ignition state until the ignition of the pilot burner 42 is completed. That is, the continuous discharge igniter 56 sparks only once.
  • Ignition to the main burner 41 by the intermittent discharge igniter 43 is performed by discharging the oil sprayed from the oil supply pipe 47 of the main burner 41 or the gas sprayed from the gas distribution pipe 50 from the intermittent discharge igniter 43 Directly by the sparks.
  • ignition to the main burner 41 by the pilot burner 42 is performed by the flame of the pilot burner 42 ignited by the discharge of the continuous discharge igniter 56. That is, the continuous discharge igniter 56 indirectly ignites the main burner 41 via the flame of the pilot burner 42.
  • the ignition to the main burner 41 by the continuous discharge igniter 56 drives the oil supply device for sending the oil to the oil supply pipe 55, and the oil is circulated in the oil supply pipe 55, and then the continuous discharge igniter A number of procedures are required such as ignition of the pilot burner 42 by 56 and confirmation of ignition of the pilot burner 42 and then ignition of the main burner 41. For this reason, indirect ignition to the main burner 41 by the continuous discharge igniter 56 takes longer time than direct ignition to the main burner 41 by the intermittent discharge igniter 43.
  • the control device 6 calculates a time required for the steam pressure in the steam drum 21 to reach the target steam pressure Pb2, and a time for the pressure in the LNG tank 3 to reach the predetermined pressure Pset. And the ignition timing for the main burner 41 so that the steam pressure in the steam drum 21 becomes the target steam pressure Pb2 when the pressure in the LNG tank 3 reaches the predetermined pressure Pset.
  • An ignition timing calculation unit that calculates Ts, and an ignition control unit that ignites the main burner 41 at the ignition timing Ts calculated by the ignition timing calculation unit and starts boosting the steam pressure in the steam drum 21.
  • control device 6 may be, for example, a CPU (Central Processing Unit), a RAM (Random Access) Memory), a ROM (Read Only Memory), a computer readable storage medium, and the like. Then, a series of processes for realizing various functions are stored in the form of a program, for example, in a storage medium or the like in the form of a program, and the CPU reads this program into a RAM or the like to execute information processing and arithmetic processing. Thus, various functions are realized.
  • the program may be installed in advance in a ROM or other storage medium, may be provided as stored in a computer-readable storage medium, or may be distributed via a wired or wireless communication means. Etc. may be applied.
  • the computer readable storage medium is a magnetic disk, a magneto-optical disk, a CD-ROM, a DVD-ROM, a semiconductor memory or the like.
  • the target pressure arrival time calculation unit calculates the steam pressure Pb1 in the steam drum 21 acquired by the pressure gauge in the drum 24 and the target steam in the steam drum 21 which is a steam pressure at which the boiler 4 can burn the boil-off gas. Based on the pressure Pb2, a target pressure arrival time Tr which is a time until the steam pressure Pb1 in the steam drum reaches the target steam pressure Pb2 is calculated. Specifically, first, a graph (see FIG. 5) indicating the time until the steam pressure in the steam drum 21 stored in the control device 6 reaches a predetermined steam pressure from the state of 0 bar is read.
  • the time Tb2 to reach the target steam pressure Pb2 and the time Tb1 to reach the steam pressure Pb1 in the steam drum 21 acquired by the in-drum pressure gauge 24 are obtained. Then, the time Tb1 until the steam pressure Pb1 in the steam drum 21 acquired by the in-drum pressure gauge 24 is subtracted from the time Tb2 until the target steam pressure Pb2 is reached, and the target pressure reaching time Tr is calculated.
  • the target steam pressure Pb2 is 16 bar. Therefore, time Tb2 until it becomes target vapor pressure Pb2 will be set to 2.5 h. At this time, when the steam pressure Pb1 in the steam drum 21 acquired by the in-drum pressure gauge 24 is 3 bar, the time Tb1 until the steam pressure Pb1 is reached is 1.8 h, so the target pressure reaching time Tr is Calculates 2.5 (Tb2) -1.8 (Tb1) and is calculated as 0.7 h.
  • the control is one example, and the method of calculating the target pressure arrival time Tr may be based on the vapor pressure Pb1 acquired by the pressure gauge in the drum 24 and the target vapor pressure Pb2, and this method may be used. It is not limited. For example, another graph may be used as the graph showing the time required for the steam pressure in the steam drum to reach a predetermined steam pressure from 0 bar.
  • the predetermined pressure arrival time calculation unit calculates the pressure in the LNG tank 3 detected by the in-tank pressure gauge 20 and the predetermined pressure in the LNG tank 3 which is a pressure for supplying boil-off gas to the LNG tank 3. Based on Pset, a predetermined pressure arrival time Tpset, which is a time until the pressure in the LNG tank 3 reaches the predetermined pressure Pset, is calculated.
  • the predetermined pressure Pset is, for example, a threshold pressure smaller by a predetermined value than the pressure at which the fuel tank may be damaged. In this embodiment, it is 10 kPa. Specifically, first, when the pressure in the LNG tank 3 starts to rise from the in-tank pressure gauge 20, the information is acquired.
  • the pressure P1 in the LNG tank 3 is obtained from the in-tank pressure gauge 20 again.
  • the pressure increase rate Pt in the LNG tank 3 per hour is defined as P1.
  • the predetermined pressure arrival time Tpset is calculated by dividing the predetermined pressure Pset by the pressure increase rate Pt.
  • the predetermined pressure Pset is divided by 0.5, and the predetermined pressure arrival time Tpset is It is calculated as 20h (T1 shown in FIG. 6).
  • the predetermined pressure Pset is divided by 0.75, and the predetermined pressure arrival time Tpset is 15 h (T2 shown in FIG. 6). Is calculated.
  • the control is one example, and the method of calculating the predetermined pressure arrival time Tpset may be based on the steam pressure Pb1 in the steam drum 21 and the target steam pressure Pb2 in the steam drum 21. It is not limited to the method.
  • the interval for acquiring the pressure in the LNG tank 3 may be shorter than one hour or longer than one hour.
  • the ignition timing calculation unit is based on the target pressure arrival time Tr in the steam drum 21 calculated by the target pressure arrival time calculation unit and the predetermined pressure arrival time Tpset in the LNG tank 3 calculated by the predetermined pressure arrival time calculation unit.
  • the ignition timing Ts is calculated so that the steam pressure in the steam drum 21 becomes the target steam pressure Pb2 when the pressure in the LNG tank 3 becomes the predetermined pressure Pset.
  • the ignition timing Ts is the time from the present time until pressure increase of the steam drum 21 of the boiler 4 is started. That is, it indicates that boosting is started after Tsh from the present time. Specifically, it is calculated by subtracting the target pressure arrival time Tr in the steam drum 21 from the predetermined pressure arrival time Tpset in the LNG tank 3. For example, when the predetermined pressure reaching time Tpset is 15 h and the target pressure reaching time Tr is 0.7 h, the ignition timing Ts is 14.3 h.
  • the ignition control means compares the time T from the present time to the predetermined pressure arrival time Tpset and the ignition timing Ts, and when Ts reaches T, sends a signal to the continuous discharge igniter 56 etc., and the pilot burner 42 Ignite 41 Then, the pressure increase of the steam pressure of the steam drum 21 is started.
  • the operation of this embodiment will be described with reference to FIGS. 1, 2A and 2B.
  • the boiler 4 When the boiler 4 is not generating steam, the steam is circulated through the heating coil 61 in the water drum 22 so as to maintain the pressure in the steam drum 21 at about 3 bar, thereby performing the warm-up operation.
  • the in-tank pressure gauge 20 detects an increase in pressure in the LNG tank, the in-tank pressure gauge 20 transmits a signal to the cargo tank control device 40.
  • the cargo tank control device 40 sends a signal to start the boil-off gas processing mode to the control device 6.
  • the control device 6 When receiving the signal from the cargo tank control device 40, the control device 6 starts the boil off gas processing mode. When the boil-off gas processing mode is started, the control device 6 performs the above-described control to calculate the ignition timing Ts. The time T from the present time to the predetermined pressure arrival time Tpset is compared with the ignition timing Ts, and the ignition control means sends a signal to the pilot burner 42 at the timing when Ts becomes larger than T.
  • the pilot burner 42 receiving the signal drives the oil supply device for supplying the oil to the oil supply pipe 55, spouts the oil from the oil supply pipe 55, drives the continuous discharge igniter 56, and starts the discharge.
  • the pilot burner 42 is ignited to form a flame.
  • the control unit confirms that a flame is formed by the pilot burner 42
  • the main burner 41 drives an oil supply device that supplies oil to the oil supply pipe 47, and ejects oil from the oil supply pipe 47.
  • the ejected oil is ignited by the flame of the pilot burner 42, whereby the main burner 41 forms a flame.
  • the oil supply to the pilot burner 42 is stopped, and the pilot burner 42 extinguishes.
  • boosting of the boiler 4 is started, and the pressure in the boiler 4 is boosted (boosting step).
  • oil but boil off gas can also be used as a fuel.
  • the boil-off gas is ejected from the gas distribution pipe 50, and ignition is performed by the flame of the pilot burner.
  • the intermittent discharge igniter 43 is moved so that the lower end is located below the lower end of the gas distribution pipe 50 (see FIG. 2A).
  • the intermittent discharge type igniter 43 discharges intermittently to ignite the boil-off gas ejected from the gas distribution pipe 50.
  • the main burner 41 forms a flame.
  • the intermittent discharge igniter 43 stops the discharge, and the lower end moves so as to be positioned above the lower end of the gas distribution pipe 50 (see FIG. 2B). Steam is generated by the combustion gas generated by the flame of the main burner 41.
  • the boiler 4 burns the boil-off gas and generates steam (combustion step).
  • the boil-off gas generated in the LNG tank 3 is supplied to the boiler 4.
  • the boil-off gas generated in the LNG tank 3 can be burned by the boiler 4. Therefore, the boil-off gas can be processed without providing a dedicated device (eg, GCU (Gas combustion unit) etc.) for burning the boil-off gas, and at the same time, the energy of the boil-off gas can be used to generate steam. it can.
  • the generated steam is used for power generation by the power generation turbine 26 and use in steam-using equipment and the like, so that the energy efficiency of the entire LNG carrier 2 can be improved.
  • the burner 23 includes a continuous discharge igniter 56 and an intermittent discharge igniter 43 having a higher frequency of sparking at the time of ignition than the continuous discharge igniter 56. Since the intermittent discharge igniter 43 directly ignites the main burner 41, it takes less time than the pilot burner 42 equipped with the continuous discharge igniter 56 indirectly ignites the main burner 41. Ignition can be performed. On the other hand, since the intermittent discharge igniter 43 has a higher spark frequency at the time of ignition than the continuous discharge igniter 56, the load at the time of ignition is large, and the damage is more likely to occur than the continuous discharge igniter 56.
  • the intermittent discharge igniter 43 since the intermittent discharge igniter 43 has a large number of sparks during one ignition, the intermittent discharge igniter 43 is more easily consumed than the continuous discharge igniter 56 that performs only one spark during one ignition. Further, since the frequency of sparks at the time of ignition is smaller than that of the intermittent discharge igniter 43, the continuous discharge igniter 56 is less damaged and consumed than the intermittent discharge igniter 43.
  • the ignition to the main burner 41 using the continuous discharge igniter 56 is an indirect one requiring many procedures such as igniting the pilot burner 42 by the continuous discharge igniter 56, the intermittent discharge igniter 43 It takes a longer time to ignition than direct ignition.
  • the burner 23 is provided with an igniter having different characteristics. Therefore, it is possible to burn the boil-off gas appropriately and to generate steam by using the igniter having different characteristics according to the conditions in the boiler 4 and the LNG tank 3, and the igniter has redundancy. Can extend the product life.
  • the LNG tank 3 may be damaged. Therefore, when the boil-off gas is burnt to reduce the pressure in the LNG tank 3, the pressure in the LNG tank 3 is lower than the pressure at which the LNG tank 3 may be damaged by a threshold value which is smaller by a predetermined value. When the pressure reaches a predetermined pressure Pset, it is necessary to burn the boil-off gas promptly. Therefore, when burning the boil-off gas, it is preferable that the time until ignition of the main burner 41 be short. In the present embodiment, the intermittent discharge igniter 43 is used when the boil off gas is burned.
  • the intermittent discharge igniter 43 can perform ignition in a shorter time than the pilot burner 42 using the continuous discharge igniter 56, the boil-off gas can be burned rapidly. Therefore, in the boiler 4, the boil-off gas can be burnt-processed, and the pressure in the LNG tank 3 can be suitably maintained below the predetermined pressure Pset.
  • the boiler 4 When boil off gas is burned by the boiler 4 in a state where the steam pressure in the steam drum 21 is low, the boiler 4 may be overloaded. In addition, due to the boiler 4 being overloaded, the amount of combustion processing of the boil off gas in the boiler 4 is limited, and there is a possibility that the desired amount of boil off gas can not be burned. Therefore, when the boil-off gas is burned in the boiler 4, if the steam pressure in the steam drum 21 is not sufficient, it is necessary to increase the steam pressure in the steam drum 21. In such a case, it is not necessary to igniter the main burner 41 particularly quickly. In the present embodiment, when the pressure in the steam drum 21 is increased, a pilot burner 42 using a continuous discharge igniter 56 is used.
  • the intermittent discharge igniter 43 which is more easily damaged than the continuous discharge igniter 56 when boosting the vapor pressure in the steam drum 21. Therefore, the frequency of use of the intermittent discharge igniter 43 can be reduced, and the product life of the intermittent discharge igniter 43 can be extended.
  • the pressure of the steam pressure in the steam drum 21 is increased, it is not particularly necessary to rapidly ignite the main burner 41. Even if ignition is performed by the pilot burner 42 using the long time continuous discharge igniter 56, there is no problem.
  • the main burner 41 is ignited so that the steam pressure in the steam drum 21 becomes the target steam pressure Pb2. doing. Therefore, when the boil-off gas is burned in the boiler 4, the steam pressure in the steam drum 21 can be set to a steam pressure sufficient to burn the boil-off gas, thereby preventing the boiler 4 from being overloaded. Preferably, the boil-off gas can be burned. Further, when the pressure in the LNG tank 3 reaches the predetermined pressure Pset, the steam pressure in the steam drum 21 is in the state of the target steam pressure Pb2, so boil-off gas is promptly supplied to the boiler 4 for combustion. Pressure in the LNG tank 3 can be reduced.
  • the steam pressure in the steam drum 21 is boosted to a target steam pressure Pb2 state, so that the steam drum 21 is burned to burn the boil-off gas. It is not necessary to maintain the internal steam pressure constantly at high pressure. Therefore, the energy consumption of the boiler 4 can be reduced.
  • the present invention is not limited to the invention according to the above-described embodiments, and appropriate modifications can be made without departing from the scope of the invention.
  • the ignition may be performed by the pilot burner 42 when the intermittent discharge igniter 43 breaks down.
  • the main burner may be ignited by the intermittent discharge igniter 43 to boost the pressure of the steam drum 21 of the boiler 4.
  • the ignition device of the main burner 41 can have redundancy.
  • the boiler 4 may be operated at a low load to compensate for the required steam of the LNG carrier 2.
  • the low-load auxiliary boiler such as a donkey boiler

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
PCT/JP2018/004249 2017-02-28 2018-02-07 ボイラ及びボイラシステム並びにボイラの運転方法 WO2018159245A1 (ja)

Priority Applications (4)

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KR1020197022958A KR102314907B1 (ko) 2017-02-28 2018-02-07 보일러 및 보일러 시스템 그리고 보일러의 운전 방법
DK18761517.4T DK3591293T3 (da) 2017-02-28 2018-02-07 Kedel, kedelsystem, og kedeldriftsfremgangsmåde
EP18761517.4A EP3591293B1 (en) 2017-02-28 2018-02-07 Boiler, boiler system, and boiler operation method
CN201880011465.3A CN110325793B (zh) 2017-02-28 2018-02-07 锅炉、锅炉系统以及锅炉的运转方法

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JP2017035869A JP6957165B2 (ja) 2017-02-28 2017-02-28 ボイラ及びボイラシステム並びにボイラの運転方法
JP2017-035869 2017-02-28

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JPS5261666U (ko) * 1975-10-31 1977-05-06
JPH0446892A (ja) 1990-06-12 1992-02-17 Mitsubishi Heavy Ind Ltd Ｌｎｇ運搬船の推進装置
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JP4563420B2 (ja) 2007-01-17 2010-10-13 デウ シップビルディング アンド マリーン エンジニアリング カンパニー リミテッド Ｌｎｇ運搬船の推進装置及び方法
JP2012117781A (ja) * 2010-12-02 2012-06-21 Mitsubishi Heavy Ind Ltd 舶用ボイラ、舶用ボイラの運転方法

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JPS51143844U (ko) * 1975-05-15 1976-11-19
JPS51140002A (en) * 1975-05-28 1976-12-02 Hitachi Ltd Controlling process of starting operation in drum boiler
JPS5261666U (ko) * 1975-10-31 1977-05-06
JPH0446892A (ja) 1990-06-12 1992-02-17 Mitsubishi Heavy Ind Ltd Ｌｎｇ運搬船の推進装置
WO2008030107A1 (en) * 2006-09-06 2008-03-13 Stephen Percy Kendall Ignition system
JP4563420B2 (ja) 2007-01-17 2010-10-13 デウ シップビルディング アンド マリーン エンジニアリング カンパニー リミテッド Ｌｎｇ運搬船の推進装置及び方法
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EP3591293A4 (en) 2020-06-10
CN110325793B (zh) 2021-03-23
CN110325793A (zh) 2019-10-11
KR20190104574A (ko) 2019-09-10
EP3591293B1 (en) 2021-10-20
JP2018141584A (ja) 2018-09-13
JP6957165B2 (ja) 2021-11-02
KR102314907B1 (ko) 2021-10-19
EP3591293A1 (en) 2020-01-08
DK3591293T3 (da) 2021-11-15

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