CN112160808B - Waste heat recovery power-cooling combined supply system of ship gas turbine - Google Patents
Waste heat recovery power-cooling combined supply system of ship gas turbine Download PDFInfo
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- CN112160808B CN112160808B CN202011010898.2A CN202011010898A CN112160808B CN 112160808 B CN112160808 B CN 112160808B CN 202011010898 A CN202011010898 A CN 202011010898A CN 112160808 B CN112160808 B CN 112160808B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
- F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
- F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
- F01K25/106—Ammonia
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0014—Recuperative heat exchangers the heat being recuperated from waste air or from vapors
Abstract
The invention relates to a waste heat recovery power-cooling combined supply system of a ship gas turbine, belonging to the technical field of ships and energy conservation. This naval vessel gas turbine waste heat recovery merit cold antithetical couplet supplies system, including ORC liquid feed pump, ORC steam generator, ORC over heater, ORC turbine, sprayer, refrigeration evaporimeter, condenser, low pressure liquid feed pump, low pressure pre-heater, low pressure steam generator, low pressure over heater, steam pocket, blender, governing valve, stop valve and choke valve. The system fully utilizes the characteristics of variable temperature and phase change of the non-azeotropic mixed working medium and the characteristic of larger difference of thermal properties of vapor and liquid phases when the system is in balance to realize the temperature matching of the heat exchange fluid and the self-adaptation of the high-temperature and low-temperature two-stage circulating working medium, thereby reducing the total irreversible loss of the system and improving the total efficiency of the compound circulation.
Description
Technical Field
The invention relates to a waste heat recovery power-cooling combined supply system of a ship gas turbine, belonging to the technical field of ships and energy conservation.
Background
Because gas turbines have the advantages of compact structure, light weight, high power density, high flexibility, fast response to power demand, short start-up time, low manpower demand, low emissions, and low noise, naval vessels are increasingly moving toward using gas turbines as prime movers rather than diesel engines. However, despite the advances in turbomachinery, blade materials and processes, and the significant advantages of using gas turbine technology, certain disadvantages remain. Gas turbines typically have higher exhaust temperatures (about 500 ℃) compared to diesel engines, resulting in lower gas turbine thermal efficiency and exergy efficiency, higher fuel consumption and higher operating costs. For naval ships, the improvement of the utilization efficiency of fuel has important significance for improving the cruising ability.
The integrated high-efficiency energy-saving waste heat recovery circulation is the most effective and sustainable technology for improving the energy efficiency of ships. There are currently many conventional power cycles that can be used in conjunction with gas turbine power cycles to recover high temperature exhaust gas waste heat, such as Steam Rankine Cycle (SRC), supercritical rankine cycle (SCRC), Kalina Cycle (KC). However, the conventional power cycle operation is long in starting time and inflexible, needs to remove hardness and salt of water, needs to be provided with a vacuum maintaining system, occupies large space and is low in power density, and is not suitable for use scenes of ships with strict control requirements on space and weight. Due to supercritical CO2Power cycle (S-CO)2) Has the advantage of good temperature difference matching with a heat source, is suitable for waste heat recovery, and has a compact structure compared with the traditional power cycle[8]The use of S-CO has been proposed by some scholars2The power circulation system recovers the residual heat of the ship gas turbine, but the single S-CO2Circulation in order to obtain higher circulation efficiency, heat recovery is usually adopted, so that the temperature of a waste heat outlet is overhigh, and in order to reduce the temperature of waste heat emission, transcritical CO is usually combined2Circulation (T-CO)2) Or Organic Rankine Cycle (ORC) as a bottoming cycle, increases system complexity, and S-CO2The system has the defect of overhigh pressure, and the circulating high pressure is generally as high as more than 20 MPa. For the present time, S-CO2The circulation technique is still in theoryIn the research and research stage, the method is quite immature, the supercritical heat transfer deterioration mechanism is not clear, a relatively reasonable turbulence model and a general heat transfer coefficient correlation are lacked, the axial thrust is large, and the bearing, sealing and rotor dynamics problems are serious.
With S-CO2Power cycle vs. Organic Rankine Cycle (ORC) as a kind of medium and low temperature waste heat: (<350 deg.C) have been commercially implemented using relatively well-established technologies in the field. In recent years, some researchers have also made some studies on the utilization of high-temperature heat of ORC, and some practical engineering applications have been made. Fahad et al use a biomass combustion furnace as a driving heat source, ORC as power cycle to construct a combined cooling heating and power system, and use organic media with higher boiling points such as n-octane, n-octadecane and the like as ORC cycle working media. ORC has also been proposed as a bottoming cycle for gas turbine waste heat utilization, and since gas turbine exhaust waste heat temperatures are typically above 450 ℃, finding a suitable method and gas turbine match is critical to the application. The ORC has the characteristics of simple structural form, stable and reliable operation and low operation and maintenance cost, and researches show that the combined cycle of the gas turbine and the ORC has better thermodynamic performance compared with the combined cycle consisting of the gas turbine and the SRC. In the existing gas turbine, a regenerator is generally used to heat compressed air by using gas turbine exhaust gas so as to reduce the exhaust gas temperature, and a thermal oil is often used as an intermediate heat transfer fluid for driving an ORC cycle. In view of the high temperature of the waste heat source, in terms of structural form, regenerative ORC, dual-pressure evaporation ORC and transcritical ORC are mostly adopted.
Although there are international studies on recovery of exhaust waste heat of a gas turbine by using ORC, there are few cases in which the ORC technology is actually applied to recovery of waste heat of a ship gas turbine.
Disclosure of Invention
In order to solve the problems and the defects of the prior art, the invention provides a combined power and cooling system (fig. 1) for recovering the waste heat of a ship gas turbine in a cascade manner by adopting a composite cycle consisting of a non-azeotropic mixed working medium Organic Rankine Cycle (ORC) and an injection refrigeration cycle (ERC) in order to effectively utilize the waste heat of the gas turbine to improve the power of the ship or the cruising capacity of the ship as much as possible. The system fully utilizes the characteristics of variable temperature and phase change of the non-azeotropic mixed working medium and the characteristic of larger difference of thermal properties of vapor and liquid phases when the system is in balance to realize the temperature matching of the heat exchange fluid and the self-adaptation of the high-temperature and low-temperature two-stage circulating working medium, thereby reducing the total irreversible loss of the system and improving the total efficiency of the compound circulation. The system can recover the exhaust waste heat of the gas turbine in a stepped manner to the maximum extent, can provide power by the ORC turbine when needed, can efficiently convert available energy into power for driving a ship, can use the recovered exhaust low-temperature section part of the waste heat for cooling at ordinary times, and improves the comfort of ship-borne personnel. The invention is realized by the following technical scheme.
A ship gas turbine waste heat recovery power-cooling combined supply system comprises an ORC liquid supply pump 1, an ORC steam generator 2, an ORC superheater 3, an ORC turbine 4, an ejector 5, a refrigeration evaporator 6, a condenser 7, a low-pressure liquid supply pump 8, a low-pressure preheater 9, a low-pressure steam generator 10, a low-pressure superheater 11, a steam drum 12, a mixer 13, a regulating valve, a stop valve and a throttle valve 18; the flue gas of the ship gas turbine sequentially passes through the ORC superheater 3, the ORC steam generator 2, the low-pressure superheater 11, the low-pressure steam generator 10 and the low-pressure preheater 9 to emit heat, and then is discharged from a flue gas outlet of the low-pressure preheater 9; a steam working medium outlet at the top of the low-pressure steam generator 10 is connected with an inlet of a low-pressure superheater 11, a superheated steam working medium outlet of the low-pressure superheater 11 is divided into two paths, one path of the superheated steam working medium outlet enters a middle air supply inlet of an ORC turbine 4 through a regulating valve I14, the other path of the superheated steam working medium outlet enters a working fluid inlet of an ejector 5 through a regulating valve II 15, and an outlet of a refrigeration evaporator 6 is connected with an injection fluid inlet of the ejector 5; an organic liquid working medium outlet of the low-pressure steam generator 10 is pumped into a steam drum 12 through an ORC liquid supply pump 1, steam working medium at an outlet at the top of the steam drum 12 enters an ORC turbine 4 to be expanded and do work after being overheated through an ORC superheater 3, a lower end outlet of the steam drum 12 is connected with a working medium end inlet of an ORC steam generator 2, and a working medium end outlet of the ORC steam generator 2 is connected with a lower end inlet of the steam drum 12; waste steam at the outlet of the ORC turbine 4 enters the low-pressure preheater 9 for heat release and then enters the mixer 13, a gas-liquid mixture at the outlet of the ejector 5 enters the mixer 13, a mixed liquid working medium outlet of the mixer 13 enters the condenser 7 for condensation to form saturated working medium liquid, part of the saturated working medium liquid enters the refrigeration evaporator 6 for cold energy supply after throttling and pressure reduction through the stop valve II 17 and the throttle valve 18, the rest of the saturated working medium liquid is pumped into the low-pressure preheater 9 for preheating through the stop valve I16 and the low-pressure liquid supply pump 8, the preheated saturated working medium liquid enters the low-pressure evaporator 10, and a cycle is completed.
The low-pressure preheater 9 adopts a three-fluid shell-and-tube preheater to simultaneously recover the heat of flue gas of the ship gas turbine and waste steam of the ORC turbine 4, the ORC steam generator 2 adopts a plate-fin heat exchanger, and the low-pressure steam generator 10 adopts an in-tube falling film type efficient compact heat exchanger.
The saturated working medium liquid adopts a non-azeotropic mixed working medium which is formed by combining alkane, aromatic hydrocarbon or linear siloxane with higher critical temperature and boiling point and a low boiling point refrigerant.
The non-azeotropic mixed working medium is CO 2/acetone, NH3/H2O, NH3/LiNO3, NH3/NaSCN, propane/n-hexane or H2O/LiBr.
The working principle of the waste heat recovery power-cooling combined supply system of the ship gas turbine is as follows:
flue gas of the ship gas turbine as a waste heat source sequentially enters the ORC superheater 3, the ORC steam generator 2, the low-pressure superheater 11, the low-pressure steam generator 10 and the low-pressure preheater 9 to release heat. The steam working medium at the top outlet of the low-pressure steam generator 10 enters the low-pressure superheater 11 to be superheated, the superheated steam working medium after being superheated is divided into two paths, one path enters the middle of the ORC turbine 4 through a regulating valve I14 to supply air and do work, the other path enters a working fluid inlet of the ejector 5 through a regulating valve II 15 to serve as working fluid, meanwhile, the steam at the outlet of the refrigeration evaporator 6 serves as injection fluid and enters an injection fluid inlet of the ejector 5, and the working fluid and the injection fluid are subjected to momentum, heat and mass exchange in the ejector 5. The residual organic liquid working medium of the low-pressure steam generator 10 is pumped into a steam drum 12 through an ORC liquid supply pump 1, the steam working medium at the top outlet of the steam drum 12 enters an ORC turbine 4 for expansion work after being overheated through an ORC superheater 3, the exhaust steam at the outlet of the ORC turbine 4 enters a low-pressure preheater 9 for heat exchange, the gas-liquid mixture at the outlet of the low-pressure preheater 9 and the gas-liquid mixture at the outlet of an ejector 5 are uniformly mixed in a mixer 13 and then enter a condenser 7 for condensation into saturated working medium liquid, part of the saturated working medium liquid enters a refrigeration evaporator 6 for providing cold energy after being throttled and depressurized through a stop valve II 17 and a throttle valve 18, the residual saturated liquid is pumped into the low-pressure preheater 9 through a stop valve I16 and the low-pressure liquid supply pump 8 for preheating, and the preheated liquid enters the low-pressure evaporator 10 to complete a cycle.
The working fluid of the ORC steam generator 2 is a conventional ORC steam generator working fluid.
The invention has the beneficial effects that:
(1) the method has the advantages that a composite cycle for efficiently recycling the flue gas waste heat of the ship gas turbine is constructed on the basis of the ORC power cycle and the ERC refrigeration cycle of the non-azeotropic mixed working medium, the cycle fully utilizes the temperature change and phase change characteristics of the non-azeotropic mixed working medium and the characteristic that the thermal property difference of a gas-liquid two-phase fluid is large when the non-azeotropic mixed working medium is in balance, so that the temperature matching of a heat exchange fluid and the self-adaptation of a high-temperature and low-temperature two-stage cycle working medium are realized, the total irreversible loss of a system is reduced, and the total efficiency of the composite cycle is improved;
(2) the system can recover the waste heat of the gas turbine exhaust to the maximum extent, can efficiently convert the available energy of the waste heat into power for driving a ship when needed, and can use the recovered waste heat of the low-temperature section of the exhaust for cooling at ordinary times, thereby improving the comfort of ship-borne personnel;
(3) on the basis of researching the heat transfer process in the composite cycle, the method firstly proposes that a three-fluid shell-and-tube preheater is adopted in the low-temperature section of the composite cycle to simultaneously recover the waste heat of the low-temperature section of the exhaust gas and the heat of the exhaust steam of the composite cycle high-temperature ORC turbine, and simultaneously adopts a plate-fin steam generator and a high-efficiency compact heat exchanger of the in-tube falling film steam generator as a high-low temperature steam generating device. The novel efficient compact heat exchange technology can strengthen the heat transfer of a high-temperature and low-temperature two-phase region, enhance the heat exchange efficiency, reduce the equipment volume and improve the power density of a system.
Drawings
FIG. 1 is a schematic diagram of a waste heat recovery power-cooling combined supply system of a ship gas turbine according to the present invention;
in the figure: the system comprises a 1-ORC liquid supply pump, a 2-ORC steam generator, a 3-ORC superheater, a 4-ORC turbine, a 5-ejector, a 6-refrigeration evaporator, a 7-condenser, an 8-low-pressure liquid supply pump, a 9-low-pressure preheater, a 10-low-pressure steam generator, an 11-low-pressure superheater, a 12-steam drum, a 13-mixer, a 14-regulating valve I, a 15-regulating valve II, a 16-stop valve I, a 17-stop valve II and an 18-throttling valve.
Detailed Description
The invention is further described with reference to the following drawings and detailed description.
Example 1
As shown in fig. 1, the ship gas turbine waste heat recovery power-cooling combined supply system includes an ORC liquid feed pump 1, an ORC steam generator 2, an ORC superheater 3, an ORC turbine 4, an ejector 5, a refrigeration evaporator 6, a condenser 7, a low-pressure liquid feed pump 8, a low-pressure preheater 9, a low-pressure steam generator 10, a low-pressure superheater 11, a steam drum 12, a mixer 13, a regulating valve, a stop valve, and a throttle valve 18; the flue gas of the ship gas turbine sequentially passes through the ORC superheater 3, the ORC steam generator 2, the low-pressure superheater 11, the low-pressure steam generator 10 and the low-pressure preheater 9 to emit heat, and then is discharged from a flue gas outlet of the low-pressure preheater 9; a steam working medium outlet at the top of the low-pressure steam generator 10 is connected with an inlet of a low-pressure superheater 11, a superheated steam working medium outlet of the low-pressure superheater 11 is divided into two paths, one path of the superheated steam working medium outlet enters a middle air supply inlet of an ORC turbine 4 through a regulating valve I14, the other path of the superheated steam working medium outlet enters a working fluid inlet of an ejector 5 through a regulating valve II 15, and an outlet of a refrigeration evaporator 6 is connected with an injection fluid inlet of the ejector 5; an organic liquid working medium outlet of the low-pressure steam generator 10 is pumped into a steam drum 12 through an ORC liquid supply pump 1, steam working medium at an outlet at the top of the steam drum 12 enters an ORC turbine 4 to be expanded and do work after being overheated through an ORC superheater 3, a lower end outlet of the steam drum 12 is connected with a working medium end inlet of an ORC steam generator 2, and a working medium end outlet of the ORC steam generator 2 is connected with a lower end inlet of the steam drum 12; waste steam at the outlet of the ORC turbine 4 enters the low-pressure preheater 9 for heat release and then enters the mixer 13, a gas-liquid mixture at the outlet of the ejector 5 enters the mixer 13, a mixed liquid working medium outlet of the mixer 13 enters the condenser 7 for condensation to form saturated working medium liquid, part of the saturated working medium liquid enters the refrigeration evaporator 6 for cold energy supply after throttling and pressure reduction through the stop valve II 17 and the throttle valve 18, the rest of the saturated working medium liquid is pumped into the low-pressure preheater 9 for preheating through the stop valve I16 and the low-pressure liquid supply pump 8, the preheated saturated working medium liquid enters the low-pressure evaporator 10, and a cycle is completed.
The low-pressure preheater 9 adopts a three-fluid shell-and-tube preheater to simultaneously recover the heat of flue gas of the ship gas turbine and waste steam of the ORC turbine 4, the ORC steam generator 2 adopts a plate-fin heat exchanger, and the low-pressure steam generator 10 adopts an in-tube falling film type efficient compact heat exchanger; the waste heat flue gas inlet temperature of the ORC superheater 3 is 500 ℃, the flue gas flow rate is 1kg/s, the non-azeotropic mixed working medium adopts a CO 2/acetone binary working medium pair, the mass fraction is 0.6:0.4, and the mass flow rate is 0.5 kg/s. Under the condition that ORC full load operation and fuel consumption are the same, the output power of ships is increased by 5-8%, the thermal efficiency of the combined cycle is more than or equal to 10%, and the final emission temperature of the flue gas is controlled within 100 ℃.
Example 2
As shown in fig. 1, the ship gas turbine waste heat recovery power-cooling combined supply system includes an ORC liquid feed pump 1, an ORC steam generator 2, an ORC superheater 3, an ORC turbine 4, an ejector 5, a refrigeration evaporator 6, a condenser 7, a low-pressure liquid feed pump 8, a low-pressure preheater 9, a low-pressure steam generator 10, a low-pressure superheater 11, a steam drum 12, a mixer 13, a regulating valve, a stop valve, and a throttle valve 18; the flue gas of the ship gas turbine sequentially passes through the ORC superheater 3, the ORC steam generator 2, the low-pressure superheater 11, the low-pressure steam generator 10 and the low-pressure preheater 9 to emit heat, and then is discharged from a flue gas outlet of the low-pressure preheater 9; a steam working medium outlet at the top of the low-pressure steam generator 10 is connected with an inlet of a low-pressure superheater 11, a superheated steam working medium outlet of the low-pressure superheater 11 is divided into two paths, one path of the superheated steam working medium outlet enters a middle air supply inlet of an ORC turbine 4 through a regulating valve I14, the other path of the superheated steam working medium outlet enters a working fluid inlet of an ejector 5 through a regulating valve II 15, and an outlet of a refrigeration evaporator 6 is connected with an injection fluid inlet of the ejector 5; an organic liquid working medium outlet of the low-pressure steam generator 10 is pumped into a steam drum 12 through an ORC liquid supply pump 1, steam working medium at an outlet at the top of the steam drum 12 enters an ORC turbine 4 to be expanded and do work after being overheated through an ORC superheater 3, a lower end outlet of the steam drum 12 is connected with a working medium end inlet of an ORC steam generator 2, and a working medium end outlet of the ORC steam generator 2 is connected with a lower end inlet of the steam drum 12; waste steam at the outlet of the ORC turbine 4 enters the low-pressure preheater 9 for heat release and then enters the mixer 13, a gas-liquid mixture at the outlet of the ejector 5 enters the mixer 13, a mixed liquid working medium outlet of the mixer 13 enters the condenser 7 for condensation to form saturated working medium liquid, part of the saturated working medium liquid enters the refrigeration evaporator 6 for cold energy supply after throttling and pressure reduction through the stop valve II 17 and the throttle valve 18, the rest of the saturated working medium liquid is pumped into the low-pressure preheater 9 for preheating through the stop valve I16 and the low-pressure liquid supply pump 8, the preheated saturated working medium liquid enters the low-pressure evaporator 10, and a cycle is completed.
The low-pressure preheater 9 adopts a three-fluid shell-and-tube preheater to simultaneously recover the heat of flue gas of the ship gas turbine and waste steam of the ORC turbine 4, the ORC steam generator 2 adopts a plate-fin heat exchanger, and the low-pressure steam generator 10 adopts an in-tube falling film type efficient compact heat exchanger; the non-azeotropic mixed working medium is NH 3/H2O.
Example 3
As shown in fig. 1, the ship gas turbine waste heat recovery power-cooling combined supply system includes an ORC liquid feed pump 1, an ORC steam generator 2, an ORC superheater 3, an ORC turbine 4, an ejector 5, a refrigeration evaporator 6, a condenser 7, a low-pressure liquid feed pump 8, a low-pressure preheater 9, a low-pressure steam generator 10, a low-pressure superheater 11, a steam drum 12, a mixer 13, a regulating valve, a stop valve, and a throttle valve 18; the flue gas of the ship gas turbine sequentially passes through the ORC superheater 3, the ORC steam generator 2, the low-pressure superheater 11, the low-pressure steam generator 10 and the low-pressure preheater 9 to emit heat, and then is discharged from a flue gas outlet of the low-pressure preheater 9; a steam working medium outlet at the top of the low-pressure steam generator 10 is connected with an inlet of a low-pressure superheater 11, a superheated steam working medium outlet of the low-pressure superheater 11 is divided into two paths, one path of the superheated steam working medium outlet enters a middle air supply inlet of an ORC turbine 4 through a regulating valve I14, the other path of the superheated steam working medium outlet enters a working fluid inlet of an ejector 5 through a regulating valve II 15, and an outlet of a refrigeration evaporator 6 is connected with an injection fluid inlet of the ejector 5; an organic liquid working medium outlet of the low-pressure steam generator 10 is pumped into a steam drum 12 through an ORC liquid supply pump 1, steam working medium at an outlet at the top of the steam drum 12 enters an ORC turbine 4 to be expanded and do work after being overheated through an ORC superheater 3, a lower end outlet of the steam drum 12 is connected with a working medium end inlet of an ORC steam generator 2, and a working medium end outlet of the ORC steam generator 2 is connected with a lower end inlet of the steam drum 12; waste steam at the outlet of the ORC turbine 4 enters the low-pressure preheater 9 for heat release and then enters the mixer 13, a gas-liquid mixture at the outlet of the ejector 5 enters the mixer 13, a mixed liquid working medium outlet of the mixer 13 enters the condenser 7 for condensation to form saturated working medium liquid, part of the saturated working medium liquid enters the refrigeration evaporator 6 for cold energy supply after throttling and pressure reduction through the stop valve II 17 and the throttle valve 18, the rest of the saturated working medium liquid is pumped into the low-pressure preheater 9 for preheating through the stop valve I16 and the low-pressure liquid supply pump 8, the preheated saturated working medium liquid enters the low-pressure evaporator 10, and a cycle is completed.
The low-pressure preheater 9 adopts a three-fluid shell-and-tube preheater to simultaneously recover the heat of flue gas of the ship gas turbine and waste steam of the ORC turbine 4, the ORC steam generator 2 adopts a plate-fin heat exchanger, and the low-pressure steam generator 10 adopts an in-tube falling film type efficient compact heat exchanger; the non-azeotropic mixed working medium is NH3/LiNO 3.
While the present invention has been described in detail with reference to the embodiments shown in the drawings, the present invention is not limited to the embodiments, and various changes can be made without departing from the spirit and scope of the present invention.
Claims (1)
1. The utility model provides a naval vessel gas turbine waste heat recovery merit cold antithetical couplet supplies system which characterized in that: the system comprises an ORC liquid supply pump (1), an ORC steam generator (2), an ORC superheater (3), an ORC turbine (4), an ejector (5), a refrigeration evaporator (6), a condenser (7), a low-pressure liquid supply pump (8), a low-pressure preheater (9), a low-pressure steam generator (10), a low-pressure superheater (11), a steam drum (12), a mixer (13), a regulating valve, a stop valve and a throttle valve (18); the flue gas of the ship gas turbine sequentially passes through the ORC superheater (3), the ORC steam generator (2), the low-pressure superheater (11), the low-pressure steam generator (10) and the low-pressure preheater (9) to emit heat, and then is discharged from a flue gas outlet of the low-pressure preheater (9); a steam working medium outlet at the top of the low-pressure steam generator (10) is connected with an inlet of a low-pressure superheater (11), the superheated steam working medium outlet of the low-pressure superheater (11) is divided into two paths, one path enters a middle air supply inlet of an ORC turbine (4) through a regulating valve I (14), the other path enters a working fluid inlet of an ejector (5) through a regulating valve II (15), and meanwhile, an outlet of a refrigeration evaporator (6) is connected with an injection fluid inlet of the ejector (5); an organic liquid working medium outlet of the low-pressure steam generator (10) is pumped into a steam drum (12) through an ORC liquid supply pump (1), steam working medium at an outlet at the top of the steam drum (12) enters an ORC turbine (4) to be expanded and do work after being overheated through an ORC superheater (3), a lower end outlet of the steam drum (12) is connected with a working medium end inlet of an ORC steam generator (2), and a working medium end outlet of the ORC steam generator (2) is connected with a lower end inlet of the steam drum (12); waste steam at the outlet of an ORC turbine (4) enters a low-pressure preheater (9) for heat release and then enters a mixer (13), a gas-liquid mixture at the outlet of an ejector (5) enters the mixer (13), a mixed liquid working medium outlet of the mixer (13) enters a condenser (7) for condensation to form saturated working medium liquid, part of the saturated working medium liquid enters a refrigeration evaporator (6) for providing cold energy after throttling and pressure reduction through a stop valve II (17) and a throttle valve (18), the rest of the saturated working medium liquid is pumped into the low-pressure preheater (9) for preheating through a stop valve I (16) and a low-pressure liquid supply pump (8), and the preheated saturated working medium liquid enters a low-pressure steam generator (10) to complete a cycle;
the low-pressure preheater (9) adopts a three-fluid shell-and-tube preheater to simultaneously recover the heat of flue gas of a ship gas turbine and exhaust steam of an ORC turbine (4), the ORC steam generator (2) adopts a plate-fin heat exchanger, and the low-pressure steam generator (10) adopts an in-tube falling-film efficient compact heat exchanger;
the saturated working medium liquid adopts a non-azeotropic mixed working medium which is formed by combining alkane, aromatic hydrocarbon or linear siloxane with higher critical temperature and boiling point and a low boiling point refrigerant;
the non-azeotropic mixed working medium is CO2Acetone, NH3/H2O、NH3/LiNO3NH3/NaSCN, propane/n-hexane or H2O/LiBr.
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| CN112160808B true CN112160808B (en) | 2021-12-21 |
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| CN113356952B (en) * | 2021-06-25 | 2022-12-09 | 西安交通大学 | Combined cooling and power system capable of pre-cooling air at inlet of gas turbine and operation method thereof |
| CN113803156A (en) * | 2021-09-14 | 2021-12-17 | 哈尔滨工程大学 | Combined cooling heating and power system of ORC-jet type refrigerating device |
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