WO2012132514A1 - 排熱回収発電装置 - Google Patents

排熱回収発電装置 Download PDF

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Publication number
WO2012132514A1
WO2012132514A1 PCT/JP2012/051392 JP2012051392W WO2012132514A1 WO 2012132514 A1 WO2012132514 A1 WO 2012132514A1 JP 2012051392 W JP2012051392 W JP 2012051392W WO 2012132514 A1 WO2012132514 A1 WO 2012132514A1
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WO
WIPO (PCT)
Prior art keywords
heat recovery
exhaust
exhaust heat
main
inlet
Prior art date
Application number
PCT/JP2012/051392
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English (en)
French (fr)
Japanese (ja)
Inventor
雅幸 川見
芳弘 市来
福田　憲弘
篤 藤井
東森　弘高
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.)
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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 CN201280014789.5A priority Critical patent/CN103459816B/zh
Priority to KR1020137024932A priority patent/KR101521037B1/ko
Publication of WO2012132514A1 publication Critical patent/WO2012132514A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from combustion engines
    • 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
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/06—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially radially
    • F01D1/08—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially radially having inward flow
    • 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
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • 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
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • 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
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers

Definitions

  • the present invention relates to an exhaust heat recovery power generation apparatus.
  • the exhaust heat recovery power generation device generates power using heat energy recovered from exhaust gas discharged from various industrial plants, power sources for ships and vehicles, etc., hot drainage, etc. or geothermal / OTEC (patent) Reference 1 and Patent Reference 2).
  • a working medium heated and evaporated by heat from a heat source is introduced into a turbine, and turning energy of the working medium is converted into rotational power to generate power.
  • a radial turbine is widely used as the turbine.
  • the radial turbine is designed to have an optimum condition with respect to the pressure of the working medium, when a plurality of working media having different pressures are provided, for example, as shown in Patent Document 1, a plurality of turbines and generators, That is, one turbine and a generator are used for each working medium at one pressure. Alternatively, a structure in which one generator is connected to a plurality of turbines is also used. Although this uses the working medium of the same pressure, it is set as the structure shown by patent document 2, for example.
  • Patent Document 1 By the way, what uses a some turbine as shown by patent document 1 will enlarge an apparatus, and a manufacturing cost will increase in connection with it. In particular, the use is restricted in ships where installation space is limited. As shown in Patent Document 2, when a plurality of turbine wheels are provided on the same shaft, the number of turbine parts is large, the structure becomes complicated, and the manufacturing cost increases.
  • an object of the present invention is to provide an exhaust heat recovery power generator capable of recovering heat from a heat medium having a different temperature with a downsized and reduced device configuration.
  • one aspect of the present invention is configured by a plurality of evaporators that are installed in parallel in the circulation path of the working medium and that evaporate the working medium using a heat medium having different temperatures, and a single turbine wheel, and each has an axis.
  • a radial turbine that converts the rotational energy of each working medium from each evaporator introduced from different positions in the direction into rotational power, a generator that generates electric power using the rotational power of the radial turbine, and the radial turbine And a condenser for condensing the working medium.
  • a plurality of evaporators are installed in parallel in the circulation path of the working medium, and in each evaporator, the working medium is evaporated by a heat medium having a different temperature. Therefore, each evaporator has a different temperature and pressure. A gaseous working medium is produced.
  • These different working media are at different axial positions on the turbine wheel of the radial turbine, i.e., at a position where the pressure of the supplied working fluid coincides with the pressure that gradually decreases towards the outlet flowing through the turbine wheel. be introduced.
  • the working media introduced from different positions in the axial direction are sequentially mixed and flowed out of the turbine wheel while being sequentially reduced in pressure, thereby generating rotational power in the turbine wheel.
  • the generator generates power by the rotational power of the turbine wheel, in other words, the radial turbine.
  • the working medium that has passed through the radial turbine is condensed by a condenser and sent to each evaporator through a circulation path.
  • working media having different pressures can be generated by heat media having different temperatures, and these working media can be taken out as rotational power by a single turbine wheel, so that the entire apparatus can be downsized.
  • the manufacturing cost can be reduced and heat can be effectively recovered from the heat medium having different temperatures.
  • the turbine wheel has a main inlet at the outer peripheral end, and includes a main passage that gradually increases in blade height while curving from the radial direction to the axial direction, and at least one shroud surface of the main passage.
  • a shroud side entrance may be provided.
  • the main inlet is supplied with the highest pressure working medium.
  • the working medium introduced from the main inlet is discharged from the turbine wheel while being gradually reduced in pressure through a main passage that gradually increases in blade height while curving from the radial direction to the axial direction.
  • the working fluid supplied to the shroud side inlet provided in the shroud surface is introduced from the main inlet and mixed with the working medium passing through the main passage.
  • the working fluid supplied to the shroud side inlet is introduced from the main inlet, and the pressure is approximately equal to the pressure of the working fluid whose pressure is sequentially reduced through the main passage, that is, the operation supplied to the main inlet.
  • the pressure is lower than that of the medium.
  • the pressure decreases as the distance from the main inlet increases in the axial direction.
  • the installation position of the shroud side inlet is set according to the pressure of the working medium generated by the evaporator.
  • the turbine wheel has a main inlet at the outer peripheral end, and includes a main passage that is curved from the radial direction to the axial direction and gradually increases in blade height, and is branched from the hub surface of the main passage. You may make it provide the hub side inlet_port
  • the working medium introduced from the main inlet is discharged from the turbine wheel while being gradually reduced in pressure through a main passage that gradually increases in blade height while curving from the radial direction to the axial direction.
  • the working fluid supplied to the hub side inlet which is branched from the hub surface of the main passage and extends toward the back side of the main passage, is located at a radial position different from the main inlet at the outer peripheral end of the sub passage. It is introduced from the main inlet and mixed with the working medium passing through the main passage.
  • the working medium introduced from the hub side inlet has a pressure that is substantially equal to the pressure of the working fluid, in which the pressure in the mixing portion is introduced from the main inlet and gradually reduced through the main passage.
  • high pressure working fluid is supplied to the outer side.
  • engine cooling water that cools the internal combustion engine body and air cooling water that cools the compressed air discharged from the supercharger of the internal combustion engine may be used as the heat medium.
  • the engine cooling water for example, 80 to 90 ° C.
  • the air cooling water for example, 130 to 140 ° C.
  • engine cooling water that cools the internal combustion engine body as the heat medium steam that is heated by the exhaust gas of the internal combustion engine, air cooling water that cools the compressed air discharged from the supercharger of the internal combustion engine, May be used.
  • working media having different pressures can be generated by heat media having different temperatures, and these working media can be taken out as rotational power by a single turbine wheel, so that the entire apparatus can be miniaturized.
  • manufacturing cost can be reduced, and heat can be effectively recovered from heat media having different temperatures.
  • FIG. 1 is a block diagram schematically showing an exhaust heat recovery power generator according to a first embodiment of the present invention. It is sectional drawing which shows the power turbine concerning 1st embodiment of this invention. It is sectional drawing which shows another embodiment of the power turbine concerning 1st embodiment of this invention. It is sectional drawing which shows another aspect of the power turbine concerning 1st embodiment of this invention. It is a block diagram showing roughly an exhaust heat recovery power generator concerning a second embodiment of the present invention. It is a block diagram showing roughly an exhaust heat recovery power generator concerning a third embodiment of the present invention. It is sectional drawing which shows the power turbine concerning 3rd embodiment of this invention. It is sectional drawing which shows another embodiment of the power turbine concerning 3rd embodiment of this invention.
  • FIG. 1 is a block diagram schematically showing an exhaust heat recovery power generator 1 according to the present embodiment.
  • FIG. 2 is a cross-sectional view showing the power turbine 17 of the exhaust heat recovery power generator 1.
  • the exhaust heat recovery power generation apparatus 1 includes a first exhaust heat recovery unit (evaporator) that recovers heat from jacket cooling water (heat medium, engine cooling water) that flows in a cylinder jacket that cools a cylinder block or the like of the diesel engine 3. ) 5 and a second exhaust heat recovery device (evaporator) that recovers heat from the air cooling water (heat medium) that passes through the first air cooler 9 that cools the compressed air discharged from the supercharger 7 of the diesel engine 3.
  • a first exhaust heat recovery unit evaporator
  • jacket cooling water heat medium, engine cooling water
  • evaporator that recovers heat from the air cooling water (heat medium) that passes through the first air cooler 9 that cools the compressed air discharged from the supercharger 7 of the diesel engine 3.
  • a third exhaust heat recovery device (evaporator) 15 for recovering heat from the steam (heat medium) heated by the second exhaust gas economizer 13 through the air cooling water passing through the first air cooler 9, and the first exhaust heat A power turbine (radial turbine) 17 for converting the energy of the organic medium (working medium) recovered and evaporated by the recovery unit 5, the second exhaust heat recovery unit 11 and the third exhaust heat recovery unit 15; Power Turbi A generator 19 that generates electric power by the rotational power of 17, a condenser 21 that condenses an organic medium from the power turbine 17, an organic medium path (circulation path) 23 through which the organic medium circulates by connecting these devices, And an organic medium pump 24 for circulating the organic medium through the organic medium path 23.
  • the exhaust heat recovery power generator 1 constitutes an organic Rankin Cycle.
  • the organic medium path 23 includes a path through the first exhaust heat recovery unit 5, a path through the second exhaust heat recovery unit 11, and a third exhaust heat recovery unit 15 between the organic medium pump 24 and the power turbine 17. The route that passes is made parallel. In other words, a path passing through the first exhaust heat recovery unit 5 and a path passing through the second exhaust heat recovery unit 11 are branched from the path passing through the third exhaust heat recovery unit 15 and merged by the power turbine 17. .
  • the organic medium flowing through the organic medium path 23 for example, low molecular hydrocarbons such as isopentane, butane, propane, or the like, R134a, R245fa, or the like used as a refrigerant can be used.
  • the optimum organic medium is selected according to the temperature distribution of the plurality of heat media to be recovered.
  • the jacket cooling water flowing in the cylinder jacket is circulated in the jacket cooling water circulation passage 27 by the jacket cooling water pump 25.
  • the jacket cooling water circulation passage 27 is formed such that jacket cooling water flows in the order of the cylinder jacket, the temperature adjusting three-way valve 29, and the jacket cooling water pump 25.
  • the jacket cooling water coming out of the jacket has a water temperature of 80 to 90 ° C., for example.
  • the jacket cooling water circulation passage 27 is provided with a bypass passage 31 that passes through the first exhaust heat recovery device 5.
  • the flow rate flowing through the bypass flow path 31 is adjusted by a bypass flow rate adjustment valve 33. Thereby, the flow volume of the jacket cooling water which flows through the 1st waste heat recovery device 5 can be adjusted now.
  • the temperature adjusting three-way valve 29 operates so that the jacket cooling water flowing out from the cylinder jacket has a desired outlet temperature. Specifically, when the outlet temperature at which the jacket cooling water flows out of the cylinder jacket is higher than a set value, a large amount of fresh water of about 36 ° C. flowing from a central cooler (not shown) flows into the jacket cooling water circulation passage 27. To work.
  • the second air cooler 35 is installed on the downstream side of the first air cooler 9 with respect to the flow of compressed air discharged from the supercharger 7. Therefore, the first air cooler 9 is installed such that the temperature level is higher than that of the second air cooler 35. The fresh water that has cooled the compressed air by the second air cooler 35 is returned to the central cooler again.
  • the compressed air compressed by the supercharger 7 is, for example, 150 to 160 ° C., supplied to the diesel engine 3 through the first air cooler 9 and the second air cooler 35, and from a fuel supply system (not shown). It is mixed with the supplied fuel and burned.
  • the exhaust gas accompanying the combustion is used for the operation of the supercharger 7, and then discharged from the chimney 39 through the exhaust gas path 37.
  • the temperature of the exhaust gas leaving the supercharger 7 is about 220 ° C., for example.
  • a second exhaust gas economizer 13 and a first exhaust gas economizer 41 disposed on the upstream side of the second exhaust gas economizer 13 are installed in the exhaust gas path 37.
  • the exhaust gas path 37 is configured such that the exhaust gas can be selected from passing through the first exhaust gas economizer 41 and the second exhaust gas economizer 13, passing through either of them, or not passing through both. Yes.
  • a circulation path 45 is formed between the first exhaust gas economizer 41 and the steam drum 43.
  • Water in the steam drum 43 is sent to the first exhaust gas economizer 41 by the boiler drum water circulation pump 47, and steam is generated by heat recovery of the exhaust gas.
  • the generated steam is sent to an auxiliary device of the ship, and then returned to the atmospheric pressure drain tank 49 as water of about 70 ° C., for example.
  • the water in the atmospheric pressure drain tank 49 is supplied to the steam drum 43 by the water supply pump 51. At this time, the water level in the steam drum 43 is adjusted by the steam drum level control valve 53.
  • the water in the atmospheric pressure drain tank 49 is circulated by the water supply pump 55 through the water supply path 57, through the first air cooler 9 and the second exhaust heat recovery device 11, and then back to the atmospheric pressure drain tank 49.
  • the A branch path 59 branched at a branch point A located between the first air cooler 9 and the second exhaust heat recovery unit 11 is connected to the water supply path 57.
  • the branch path 59 is configured to return to the atmospheric pressure drain tank 49 through the second exhaust gas economizer 13 and the third exhaust heat recovery device 15.
  • the air cooling water that has passed through the first air cooler 9 is supplied to the second exhaust gas economizer 13 through the branch path 59, converted to high temperature / high pressure steam by the exhaust gas, and supplied to the third exhaust heat recovery unit 15. .
  • the power turbine 17 includes a casing 61, a rotating shaft 63 that is rotatably supported by the casing 61, and a radial turbine wheel (turbine wheel) 65 that is attached to the outer periphery of the rotating shaft 13.
  • a main inlet 67 substantially parallel to the rotation shaft 63 is formed at the outer peripheral end of the radial turbine wheel 65.
  • a main inflow passage 69 that is a scroll-like space is formed on the outer peripheral side of the main inlet 67.
  • a main introduction path 71 into which an organic medium supplied from the third exhaust heat recovery device 15 is introduced is connected to the main inflow path 69.
  • the main inflow path 69 and the main inlet 67 are connected by a connection path provided with a nozzle 73 composed of a plurality of blades arranged at intervals in the circumferential direction.
  • the radial turbine wheel 65 is formed with a main passage 77 that is curved from the radial direction to the axial direction so that the flow flows out from the main inlet 67 toward the turbine wheel outlet 75 and the blade height sequentially increases.
  • a shroud-side sub-entrance (a shroud-side inlet) 79 is formed at a position separated from the main inlet 67 in the radial direction and the axial direction.
  • a shroud-side secondary inflow passage 81 that is a scroll-like space is formed.
  • the shroud side secondary inlet path 81 is connected to a shroud side secondary inlet path 83 into which the organic medium supplied from the second exhaust heat recovery unit 11 is introduced.
  • the shroud side secondary inlet 81 and the shroud side secondary inlet 79 are connected by a connection path provided with a nozzle 85 composed of a plurality of blades arranged at intervals in the circumferential direction.
  • the hub surface of the main passage 77 is provided with a secondary passage 87 extending toward the back side.
  • the main passage 77 and the sub passage 87 are configured such that the flow joins at a joining portion that is a virtual line on the hub surface of the main passage 77 indicated by a dotted line.
  • the secondary passage 87 is formed to branch from the main passage 77 and extend toward the back side of the main passage 77.
  • a hub side secondary inlet (hub side inlet) 89 is formed at the outer peripheral end on the back side of the secondary passage 87 at a radial position different from the main inlet 27 over the entire circumference.
  • a hub side secondary inflow passage 91 On the outer peripheral side of the hub side secondary inlet 89, a hub side secondary inflow passage 91 that is a space having a uniform cross-sectional shape is formed.
  • a hub side secondary introduction path 93 into which an organic medium supplied from the first exhaust heat recovery device 5 is introduced is connected to the hub side secondary inflow path 91.
  • the hub side secondary inlet 91 and the hub side secondary inlet 89 are connected by a connection path provided with a nozzle 95 composed of a plurality of blades arranged at intervals in the circumferential direction.
  • the radial positions of the main inlet 67, the shroud side inlet 79, and the hub side inlet 89 are such that the main inlet 67 is located on the outermost side and the hub side secondary inlet 89 is located on the innermost side.
  • the radial position of the shroud side inlet 79 is such that the pressure of the organic medium introduced from the shroud side inlet 79 is introduced from the main inlet 67 and the pressure is reduced sequentially through the main passage 77.
  • the size is set to be approximately the same.
  • a plurality of shroud side inlets 79 may be provided in the axial direction if there is enough space.
  • the radial position of the hub side secondary inlet 89 is such that the pressure of the organic medium at the junction where the pressure of the organic medium introduced from the hub side secondary inlet 89 is sequentially reduced through the secondary passage 87 is introduced from the main inlet 67.
  • the pressure is set so as to substantially coincide with the pressure at the working fluid merging portion where the pressure is sequentially reduced through the main passage 77. Therefore, the radial position of the hub side secondary inlet 89 is positioned on the outer peripheral side of the radial direction position of the main inlet 67, and an organic medium having a higher pressure than the organic medium introduced into the main inlet 67 is supplied to the hub side secondary inlet 89. You may do it.
  • the organic medium pump 24 When the organic medium pump 24 is operated, the organic medium condensed by seawater in the condenser 21, for example, about 35 ° C. circulates in the organic medium path 23. At this time, a part of the organic medium passes through the first exhaust heat recovery unit 5 to the hub side secondary introduction path 93 of the power turbine 17, and another part passes through the second exhaust heat recovery unit 11 to the power turbine. 17 is supplied to the shroud side secondary introduction path 83, and the remainder is supplied to the main introduction path 71 of the power turbine 17 through the third exhaust heat recovery unit 15.
  • the jacket cooling water led to the cylinder jacket by the jacket cooling water pump 25 is heated to, for example, 80 to 90 ° C. by cooling the cylinder block or the like with the cylinder jacket. Since the jacket cooling water passes through the first exhaust heat recovery device 5 via the bypass flow path 31, heat exchange is performed between the jacket cooling water and the organic medium. The temperature is raised to about 64 ° C. and evaporated. In other words, the sensible heat of the jacket cooling water is recovered in the organic medium passing through the organic medium path 23.
  • the compressed air compressed by the supercharger 7 of the diesel engine 3 is supplied to the diesel engine 3 through the first air cooler 9 and the second air cooler 35.
  • the resulting compressed air is heat-exchanged with this water and cooled to about 80 ° C., for example.
  • the water passing through the water supply path 57 is heated by the compressed air, and is heated to about 140 ° C., for example. In other words, the sensible heat of the compressed air is recovered into the water passing through the water supply path 57.
  • the water passing through the water supply path 57 is heated by the first air cooler 9 and then passes through the second exhaust heat recovery unit 11, heat exchange is performed with the organic medium passing through the organic medium path 23.
  • the organic medium is heated to about 100 ° C. and evaporated. Therefore, the sensible heat of the compressed air is recovered by the organic medium in the organic medium path 23 through the water passing through the water supply path 57.
  • Part of the hot water that passes through the water supply path 57 that has been heated by the first air cooler 9 is branched at the branch point A, passes through the branch path 59, and passes through the second exhaust gas economizer 13.
  • exhaust gas having a temperature of about 210 ° C. recovered by the first exhaust gas economizer 41 is introduced, so that the hot water passing through the branch path 59 is heat-exchanged with the exhaust gas, for example, 190 The temperature is raised to ⁇ 200 ° C. to be steam.
  • the sensible heat of the exhaust gas is recovered in the hot water that passes through the branch path 59.
  • this hot water passes through the third exhaust heat recovery device 15 via the branch path 59, heat exchange is performed with the organic medium passing through the organic medium path 23, and the organic medium is, for example, 120 to 130 ° C. It is heated to a certain degree and evaporated. Therefore, the sensible heat of the compressed air and the exhaust gas is recovered by the organic medium in the organic medium path 23 through the hot water passing through the branch path 59.
  • the organic medium passing through the organic medium path 23 is independently evaporated by the first exhaust heat recovery device 5, the second exhaust heat recovery device 11, and the third exhaust heat recovery device 15.
  • the pressure of the organic medium is the highest generated by the third exhaust heat recovery unit 15, and decreases in the order of the second exhaust heat recovery unit 11 and the first exhaust heat recovery unit 5.
  • the relatively high pressure organic medium evaporated by the third exhaust heat recovery device 15 flows into the main inflow passage 69 through the main introduction passage 71.
  • the flow rate and flow velocity of the organic medium flowing into the main inflow path 69 are adjusted by the main inflow path 69 and the nozzle 73, and are supplied from the main inlet 67 to the main passage 77.
  • the organic medium passing through the main passage 77 flows while the pressure continuously decreases to the outlet of the radial turbine wheel 65, and generates rotational power in the radial turbine wheel 65 and the rotating shaft 63.
  • the relatively medium pressure organic medium evaporated by the second exhaust heat recovery unit 11 flows into the shroud-side sub-inflow path 81 through the shroud-side sub-introduction path 83.
  • the flow rate and flow velocity of the organic medium flowing into the shroud side secondary inflow path 81 are adjusted by the shroud side secondary inflow path 81 and the nozzle 85, supplied from the shroud side secondary inlet 79 to the radial turbine wheel 65, and supplied from the main inlet 67. Mixed with organic medium.
  • the pressure of the organic medium supplied from the shroud side inlet 79 into the radial turbine wheel 65 is sequentially reduced toward the outlet flowing through the main passage 77, in other words, continuously reduced. It is made to correspond to the pressure in position.
  • the relatively low-pressure organic medium evaporated by the first exhaust heat recovery device 5 flows into the hub side secondary inflow path 91 through the hub side secondary introduction path 93.
  • the flow rate and flow velocity of the organic medium that has flowed into the hub-side secondary inflow passage 91 are adjusted by the nozzle 95, and are supplied from the hub-side secondary inlet 89 to the secondary passage 87 of the radial turbine wheel 65.
  • the organic medium is depressurized as it passes through the secondary passage 87, and is joined with the organic medium flowing through the main passage 77 at the junction.
  • the pressure of the organic medium supplied to the hub side secondary inlet 89 is set to substantially coincide with the pressure of the organic medium flowing through the main passage 77 at the junction.
  • the organic media having different pressures from the first exhaust heat recovery unit 5, the second exhaust heat recovery unit 11 and the third exhaust heat recovery unit 15 are respectively transferred to the main inlet 67 and the shroud side secondary inlet of the radial turbine wheel 65. 79 and the hub side secondary inlet 89 can be taken out as rotational power by a single radial turbine wheel 65.
  • the power turbine 17 concerning this embodiment can reduce a number of parts compared with the turbine provided with a some turbine or a some radial turbine wheel, and can reduce manufacturing cost. For this reason, the exhaust heat recovery apparatus 1 can be reduced in size, and the manufacturing cost can be reduced.
  • the organic medium recovers heat from the jacket cooling water, the compressed air compressed by the supercharger 7 and the combustion exhaust gas. Therefore, the exhaust heat of the diesel engine 3 can be recovered effectively.
  • the organic medium that has finished its work in the power turbine 17 is guided to the condenser 21 and is condensed and liquefied by being cooled by cooling water such as seawater.
  • cooling water such as seawater.
  • Each temperature described above is an example, and varies according to various conditions such as the flow rate of each fluid and the operating condition of the diesel engine 3.
  • the shroud side secondary inflow passage 81 has a scroll shape, but may be a collector which is a space having a uniform sectional shape as shown in FIG.
  • the attachment positions of the main introduction path 71, the shroud side secondary introduction path 83, and the hub side secondary introduction path 93 may be set according to the installation position of the power turbine 17. For example, as shown in FIG. 4, the shroud side secondary introduction path 83 may be set to be positioned at the lower part.
  • FIG. 5 is a block diagram schematically showing the exhaust heat recovery power generator 1 according to the present embodiment.
  • the second exhaust gas economizer 13 is not installed.
  • the water supply path 57 is configured such that the water in the atmospheric pressure drain tank 49 is supplied to the second exhaust heat recovery device 11 through the second air cooler 35 and then returns to the atmospheric pressure drain tank 49.
  • a branch path 97 branched at a branch point B located between the second air cooler 35 and the second exhaust heat recovery unit 11 is connected to the water supply path 57.
  • the branch path 97 is configured to return to the atmospheric pressure drain tank 49 through the first air cooler 9 and the third exhaust heat recovery unit 15.
  • the exhaust heat recovery apparatus 1 Since the exhaust heat recovery apparatus 1 according to the present embodiment configured as described above operates in the same manner as in the first embodiment except for the exhaust heat recovery, description of overlapping parts is omitted.
  • the water in the atmospheric pressure drain tank 49 passes through the water supply path 57 to the second air cooler 35 by the water supply pump 55, the compressed air is heat-exchanged with this water and cooled. .
  • the water passing through the water supply path 57 is heated by the compressed air and heated.
  • the sensible heat of the compressed air is recovered into the water passing through the water supply path 57. Since the water passing through the water supply path 57 is heated by the second air cooler 35 and then passes through the second exhaust heat recovery unit 11, heat exchange is performed with the organic medium passing through the organic medium path 23. The organic medium is warmed and evaporated. Therefore, the sensible heat of the compressed air is recovered by the organic medium in the organic medium path 23 through the water passing through the water supply path 57.
  • Part of the hot water that passes through the water supply path 57 that has been heated by the second air cooler 35 is branched at the branch point B and passes through the first air cooler 9 through the branch path 97. Since the compressed air having a higher temperature than that of the second air cooler 35 is introduced into the first air cooler 9, the hot water passing through the branch path 97 is heat-exchanged with the compressed air having a high temperature and is heated. The In other words, the sensible heat of the compressed air is recovered in the hot water that passes through the branch path 97.
  • the branch path 97 passes through the third exhaust heat recovery device 15, heat exchange is performed with the organic medium passing through the organic medium path 23, and the organic medium is heated and evaporated. Therefore, the compressed air is recovered by the organic medium in the organic medium path 23 through the hot water passing through the branch path 97.
  • FIG. 6 is a block diagram schematically showing the exhaust heat recovery power generator 1 according to the present embodiment.
  • FIG. 7 is a cross-sectional view showing the power turbine 17 of the exhaust heat recovery power generator 1.
  • the exhaust heat recovery power generator 1 can be further downsized by the amount that the second exhaust heat recovery device 11 and related members can be omitted. it can.
  • the power turbine 17 has a shroud-side secondary inlet 79, a shroud-side secondary inlet 81, a shroud-side secondary inlet 83, and a nozzle 85 that handle the working fluid from the second exhaust heat recovery unit 11. The configuration is omitted. Therefore, the structure of the power turbine 17 can be simplified, the size can be reduced, and the manufacturing cost can be reduced.
  • the power turbine 17 used in the exhaust heat recovery power generator 1 is not limited to the structure shown in FIG.
  • the main inflow passage 69 and the main introduction passage 71, the shroud side sub inflow passage 91 and the shroud side sub introduction passage 93 are integrally formed over the entire circumference and the main inflow passage 69.
  • the shroud side secondary inflow passage 91 are configured to communicate with each other.
  • the main inflow passage 69 and the shroud side sub inflow passage 91 are partitioned by the partition plate 100.
  • the rotating shaft 63 can be shortened in length and shaft vibration can be reduced.
  • the shroud-side sub-inflow passage 91 and the shroud-side sub-introduction passage 93 that form the scroll may be flattened in the axial direction. In this way, when the casing 61 is opened, the casing 61 can be prevented from interfering with the shroud side secondary inlet passage 91 and the shroud side secondary inlet passage 93. Thereby, the casing 61 can be easily disassembled.
  • another independent additional power turbine 18 may be provided at the end of the rotating shaft 63 opposite to the mounting position of the power turbine 17.
  • the additional power turbine 18 can be driven by a medium different from that of the power turbine 17 or can be driven by the same medium because the flow path through which the medium flows is independent from the power turbine 17.
  • the steam from the second exhaust gas economizer 13 having a pressure higher than that of the organic medium supplied to the power turbine 17 can be directly introduced into the additional power turbine 18. Thereby, the exhaust heat of the diesel engine 3 can be recovered more effectively.
  • the exhaust of the power turbine 18 can be introduced into a low-pressure power turbine provided separately.
  • the power turbine 17 has the structure shown in FIG. 8, but is not limited to this, and the additional power turbine 18 has an appropriate structure including the power turbine 17 described in the present embodiment.
  • the power turbine 17 can be combined.
  • the power turbine 17 shown in FIG. 11 is configured such that the rotating shaft 63 is supported by magnetic bearings 110 and 111. Thus, when the rotating shaft 63 is supported by the magnetic bearings 110 and 111, it is not necessary to supply the lubricating oil, so that the lubricating oil can be prevented from scattering in the organic medium.
  • the power turbine 17 includes a shroud-side secondary inlet 79, a shroud-side secondary inlet passage 81, a shroud-side secondary inlet passage 83, and a nozzle 85, and a hub-side secondary inlet 89, a shroud-side secondary inlet passage 91.
  • the shroud side secondary introduction passage 93 and the nozzle 95 may be omitted, and the organic medium from the first exhaust heat recovery device 5 may be introduced from the shroud side secondary inlet 79.
  • the secondary passage 87 does not need to be provided, so that the power turbine 17 can be further downsized.
  • the water supply path 57 is configured such that the water in the atmospheric pressure drain tank 49 passes through the first air cooler 9 and then returns to the atmospheric pressure drain tank 49 through the second exhaust gas economizer 13 and the third exhaust heat recovery unit 15. Has been.
  • the exhaust heat recovery apparatus 1 configured as described above operates in the same manner as in the first embodiment except that the second exhaust heat recovery device 11 is not provided and the exhaust heat recovery associated therewith, and therefore overlapping portions. Description of is omitted.
  • the water passing through the water supply path 57 is heated by the compressed air when passing through the first air cooler 9, and then heated by the exhaust gas when passing through the second exhaust gas economizer 13. To be supplied.
  • the organic medium is heated by the heat medium passing through the water supply path 57 and heated. Therefore, the sensible heat of the compressed air and the exhaust gas is recovered in the organic medium of the organic medium path 23 through the water passing through the water supply path 57.
  • the present invention is not limited to the embodiments described above, and various modifications may be made without departing from the spirit of the present invention.
  • the exhaust heat recovery power generation apparatus 1 of each embodiment described above has been described as applied to a ship as an example, it can also be applied to a land-use internal combustion engine used for power generation or the like, and can be used for various industrial plants. It can also be applied to power generation using exhaust heat, geothermal heat, OTEC, or the like.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Supercharger (AREA)
PCT/JP2012/051392 2011-03-31 2012-01-24 排熱回収発電装置 WO2012132514A1 (ja)

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CN201280014789.5A CN103459816B (zh) 2011-03-31 2012-01-24 排热回收发电装置
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CN110307044A (zh) * 2019-07-09 2019-10-08 长兴永能动力科技有限公司 一种蒸汽涡轮增压器
WO2023106159A1 (ja) * 2021-12-10 2023-06-15 三菱重工マリンマシナリ株式会社 排熱回収システム

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JP2014114939A (ja) * 2012-12-12 2014-06-26 Mitsubishi Heavy Ind Ltd 磁気カップリング
KR102011859B1 (ko) * 2012-12-27 2019-08-19 대우조선해양 주식회사 선박의 폐열을 이용한 에너지 절감시스템
JP6214252B2 (ja) * 2013-07-12 2017-10-18 日立造船株式会社 ボイラシステム
JP6195299B2 (ja) * 2013-10-23 2017-09-13 三菱重工業株式会社 排熱回収システム、船舶及び排熱回収方法
JP6125415B2 (ja) * 2013-11-27 2017-05-10 三菱重工業株式会社 廃熱回収システム、舶用推進システム、船舶及び廃熱回収方法
JP5951593B2 (ja) * 2013-12-27 2016-07-13 三菱重工業株式会社 排熱回収装置、排熱回収型船舶推進装置および排熱回収方法
JP6489856B2 (ja) * 2015-02-04 2019-03-27 三菱重工業株式会社 排熱回収装置、排熱回収型船舶推進装置および排熱回収方法
JP6382127B2 (ja) * 2015-02-13 2018-08-29 株式会社神戸製鋼所 熱交換器、エネルギー回収装置、および船舶
KR102536261B1 (ko) 2015-12-18 2023-05-25 삼성전자주식회사 3차원 반도체 장치
JP7014518B2 (ja) * 2017-03-03 2022-02-01 三菱重工業株式会社 舶用ディーゼルエンジン
JP6781673B2 (ja) * 2017-06-22 2020-11-04 株式会社神戸製鋼所 熱エネルギー回収装置
JP7150630B2 (ja) 2019-02-07 2022-10-11 三菱重工マリンマシナリ株式会社 排熱回収装置およびその制御方法

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CN110307044A (zh) * 2019-07-09 2019-10-08 长兴永能动力科技有限公司 一种蒸汽涡轮增压器
WO2023106159A1 (ja) * 2021-12-10 2023-06-15 三菱重工マリンマシナリ株式会社 排熱回収システム

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JP5683359B2 (ja) 2015-03-11
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CN103459816A (zh) 2013-12-18
JP2012215124A (ja) 2012-11-08
KR20130117885A (ko) 2013-10-28

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