WO2024253605A1 - Système de génération de vapeur de pression utilisable à l'aide de chaleur perdue à basse température provenant de moteurs à combustion interne - Google Patents

Système de génération de vapeur de pression utilisable à l'aide de chaleur perdue à basse température provenant de moteurs à combustion interne Download PDF

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WO2024253605A1
WO2024253605A1 PCT/TR2023/050528 TR2023050528W WO2024253605A1 WO 2024253605 A1 WO2024253605 A1 WO 2024253605A1 TR 2023050528 W TR2023050528 W TR 2023050528W WO 2024253605 A1 WO2024253605 A1 WO 2024253605A1
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pressure
compressor
low
expander
steam
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PCT/TR2023/050528
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English (en)
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Emir ÖNAL
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Priority to ES23761630T priority Critical patent/ES3049238T3/es
Priority to CN202380099124.7A priority patent/CN121263589A/zh
Priority to EP23761630.5A priority patent/EP4508314B1/fr
Priority to PCT/TR2023/050528 priority patent/WO2024253605A1/fr
Publication of WO2024253605A1 publication Critical patent/WO2024253605A1/fr
Anticipated expiration legal-status Critical
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Classifications

    • 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
    • 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
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • F01K17/005—Using steam or condensate extracted or exhausted from steam engine plant by means of a heat pump
    • 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
    • F01K19/00—Regenerating or otherwise treating steam exhausted from steam engine plant
    • F01K19/02—Regenerating by compression
    • 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
    • F01K23/106—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 with water evaporated or preheated at different pressures in exhaust boiler

Definitions

  • the invention relates to a system of generating steam at usable pressure level, in particular by compressing the low-pressure steam which is generated by recovering the low temperature waste heat rejected from an internal combustion engine, whereas the motive steam at high pressure required to compress the low- pressure steam is generated by the recovery of the high temperature exhaust waste heat of the same internal combustion engine.
  • the amount of low temperature reject heat from the internal combustion engine is of significance when compared with total heat input to the internal combustion engine, and comparable to the high temperature exhaust waste heat.
  • Internal combustion engines are widely used for generation of electric power & heat in mostly land based applications and rarely in marine applications. They use fuel and combustion air to generate power. These types of engines are used as prime movers to drive electric generators to generate electricity. Extensive use of internal combustion engines is employed in industries where both generated power and the waste heat from the internal combustion engine are utilized, and utilization of heat which is a byproduct makes the localized use of the internal combustion engines further economical. Less than half of the fuel input to the internal combustion engine is converted into electricity whereas the rest of the energy input is rejected in several waste heat streams.
  • Third heat rejection from the internal combustion engine is from the surface losses into the ambient, and in general not utilized for further use.
  • the steam requirement of heat consumers may exceed the amount of available steam from the heat recovery steam generator downstream of the exhaust stream of the internal combustion engine.
  • either steam generation of the heat recovery steam generator is increased by injecting supplementary fuel (and air as required) into the exhaust gas stream to cause supplementary combustion, or extra steam requirement is supplied by an auxiliary boiler where both systems consume fuel. Sometimes both systems are used as required. Combustion of extra fuel means increased amount fuel cost as well as increased amount of gaseous emissions.
  • Secondary heat rejection from internal combustion engine is for engine cooling purposes where the sources are mainly engine lube oil, engine block and combustion charge air. This heat is removed from the internal combustion engine by a cooling fluid stream which is in most cases an antifreeze & water solution, and mostly operating under 100 °C. Heated cooling fluid stream downstream of the internal combustion engine rejects the heat mainly into the atmosphere in air cooled radiators, and cooled fluid is circulated back into the internal combustion engine. The amount of heat in secondary heat rejection stream is significant and comparable with the usable amount of heat contained in high temperature exhaust gases in primary heat rejection of the internal combustion engine.
  • CN1 11441837B discloses a waste heat recovery device and a recovery method of an internal combustion engine, wherein the waste heat recovery device comprises: the waste heat recovery device of the internal combustion engine comprises an internal combustion engine cylinder body, a flue gas heat exchanger, an expander, a pressurized air preheater, a high-temperature heat regenerator, a low-temperature heat regenerator, a cooling unit, a pressurizing unit and a working medium tank, wherein the waste heat recovery device of the internal combustion engine uses supercritical/subcritical CO2 as a circulating working medium.
  • the invention utilizes supercritical/subcritical CO2, fully recovers the waste heat of various heat sources with different qualities in the internal combustion engine, such as flue gas, cylinder liner water and pressurized air.
  • CN107542556A relates to generating power by waste heat of tail gas of automobile field, more particularly to a kind of self-adjusting for afterheat of IC engine recovery electricity generation system and its fitness- for-service assessment method.
  • An object of the invention to provide a system with the apparatus of prior art devices which overcomes the above-mentioned disadvantages, which reduces the total amount of fuel used to generate steam by recovering the low temperature heat source from the secondary heat rejection circuit of the internal combustion engine, generating low-pressure steam from this source and further compressing it to usable pressure levels as required by the heat consumers.
  • Proposed systems for compressing low pressure steam are mechanical compression which uses expander compressor, and alternatively thermal compression which uses thermocompressor.
  • Internal combustion engine is a prior art used to generate power which consumes fuel and combustion air. Expanded combustion gases leaves the internal combustion engine at a fairly high temperature still containing high amount of energy and oxygen. Exhaust of internal combustion engine is connected to a waste heat boiler generating steam at a higher pressure and temperature level than as required by the heat consumers. The waste heat boiler is furnished with duct burner adding energy to the exhaust stream making it possible to generate higher amount of steam at higher temperatures and pressures as required.
  • an expander compressor machinery In mechanical compression, an expander compressor machinery is used to compress the low-pressure steam while expanding the high-pressure steam. Mechanical power input to the compressor causes compression of the low-pressure steam, therefore this system is specified as mechanical compression.
  • the generated high-pressure steam by the waste heat boiler after the internal combustion engine is forwarded into expander section of an expander compressor package and expansion of steam to the pressure level as required by heat consumers causes extraction of thermal energy and generation of work at rotating output shaft of the expander.
  • the expanded steam is supplied to heat consumer. This work generated is transmitted by transmission into the inlet rotating shaft of the compressor.
  • Compressor inlet low-pressure steam is generated in a low-pressure boiler generating steam at a fairly low pressure and temperature where the source to this boiler is the cooling fluid stream in which the secondary heat rejection of the internal combustion engine is made into, whereas this cooling fluid stream mostly operates under 100 °C.
  • This low- pressure steam is then compressed in the compressor section of the expander compressor consuming work whereas the necessary work is supplied by the expander through the transmission.
  • This compressed low-pressure steam is also supplied to heat consumer.
  • Required heat for the generation of low-pressure steam is supplied from a waste source and no fuel is consumed to generate it.
  • the suggested system for generating high pressure steam from the heat recovery steam generator and in addition low pressure steam from the low pressure boiler consumes less fuel in total when compared with generating the same amount steam with conventional systems using heat recovery steam generator or with an addition of an auxiliary boiler where both needs extra fuel combustion.
  • thermocompressor device In thermal compression, a thermocompressor device is used to compress the low-pressure steam while expanding the high-pressure steam.
  • thermocompressor conversion of high-pressure steam static pressure to dynamic pressure, heat transfer from high-pressure steam to low-pressure steam in direct contact and mixing, and conversion of dynamic pressure to static pressure of the mixture are thermal processes and therefore this system is specified as thermal compression.
  • the generated high-pressure steam by the waste heat boiler after the internal combustion engine is forwarded into thermocompressor nozzle section which increases the velocity of the high-pressure inlet steam while decreasing its static pressure creating a low-pressure environment in suction chamber section of the thermocompressor.
  • Low- pressure steam is generated in a low-pressure boiler generating steam at a fairly low pressure and temperature where the source to this boiler is the cooling fluid stream in which the secondary heat rejection of the internal combustion engine is made into, whereas this cooling fluid stream mostly operates under 100 °C.
  • This low-pressure steam is connected to the suction chamber of the thermocompressor, and the lower pressure of the suction chamber causes suction of low-pressure steam into the thermocompressor. Both streams flow into the mixing chamber while transferring energy from waste heat boiler generated high pressure steam to low pressure boiler generated low pressure steam in direct contact and mixing.
  • An expansion chamber with increased cross section follows the mixing chamber causing decrease in velocity and increase in static pressure of the mixture.
  • thermocompressor outlet stream is supplied to heat consumer and or process user.
  • Required heat for the generation of low-pressure steam is supplied from a waste source and no fuel is consumed to generate it.
  • the suggested system for generating high pressure steam from the heat recovery steam generator and in addition low pressure steam from the low pressure boiler consumes less fuel in total when compared with generating the same amount steam with conventional systems using heat recovery steam generator or with an addition of an auxiliary boiler where both needs extra fuel combustion.
  • Figure 1 A block diagram of the process arranged with apparatus in accordance with and embodying the present invention with mechanical compression.
  • Figure 2 A schematic illustration, in greater detail of the single stage pressure casing expander compressor package given in Figure 1 .
  • FIG. 3 A schematic illustration, in greater detail of the multi stage pressure casing expander compressor package with multi transmission given in Figure 1.
  • Figure 4 A schematic illustration, in greater detail of the common transmission multi stage pressure casing of expander compressor package given in Figure 1 .
  • FIG. 5 A block diagram of the process arranged with apparatus in accordance with and embodying the present invention with thermal compression.
  • Figure 6 A schematic illustration, in greater detail of a single stage thermocompressor given in Figure 5.
  • FIG. 7 A schematic illustration, in greater detail of a multiple stage thermocompressor given in Figure 5
  • Figure 8 A block diagram of a hybrid compressor package, a combination of mechanical compression and thermal compression.
  • thermocompressor package 64 multi-stage thermocompressor package
  • an internal combustion engine (1 ) uses combustion air (3) and fuel (4) to create combustion. Increasing pressure and temperature by combustion is transformed into kinetic energy by expansion of hot combustion gasses causing movement and/or rotating internal components which is used to propel an electric generator (2). After completion of expansion, hot combustion gases are moved away from the internal combustion engine (1 ) with exhaust gas stream (5).
  • the exhaust gas stream (5) comprises high levels of energy due to its high temperature.
  • a waste heat recovery boiler (25) is used to cool down the exhaust gas stream (5) while generating high-pressure steam (28) by heating up, evaporating and superheating high pressure condensate (32) with heating surfaces of economizer, evaporator and superheater.
  • the high-pressure condensate (32) fluid type used to generate high-pressure steam (28), is as per the requirement by heat consumer (20).
  • Supplementary fuel (26) is supplied to the waste heat recovery boiler (25) for supplementary combustion causing increased steam generation. Air also can be supplied along with supplementary fuel (26), if required.
  • a waste heat recovery boiler exhaust gas stream (27) is used to exhaust from the waste heat recovery boiler (25).
  • Engine cooling fluid stream (6) removes heat dissipated from several sources within the internal combustion engine (1 ) for cooling purposes.
  • Cold engine cooling fluid (8) is forwarded by circulation pump (9) into the internal combustion engine (1 ) and forces engine cooling fluid stream (6) to pass through the cooling circuits where heat rejection is made from heating surfaces.
  • Hot engine cooling fluid (7) flows into a low pressure boiler (15).
  • the low-pressure boiler (15) is an evaporator where the hot engine cooling fluid (7) flows within one side of heating surface while transferring its heat into the low-pressure condensate (16) which is within the other side of the heating surface, causing evaporation of the condensate and generating low-pressure steam (17).
  • the low-pressure condensate (16) fluid type used to generate the low-pressure steam (17) is as per the requirement of the heat consumer (20) and can be either the same type or other type of fluid than the high-pressure condensate (32).
  • Both the high-pressure steam (28) and the low-pressure steam (17) flows into expander compressor package (35) through separate streams.
  • the expander compressor package (35) comprises compressor (38), expander (36) and transmission (37).
  • the high pressure steam (28) flows into the expander (36) whereas the low-pressure steam (17) flows into the compressor (38) of the expander compressor package (35).
  • the expander (36) is a machine which extracts thermal energy from the high-pressure steam (28) by expansion of it and uses it to do mechanical work on a rotating output shaft connected to the transmission (37), while the expanded high-pressure steam (28) leaves the expander (36) from expander exhaust stream (30) with lower pressure and temperature and consequently lower thermal energy compared with the inlet.
  • the compressor (38) is a machine that increases the pressure and consequently the thermal energy of the low-pressure steam (17) by reducing its volume or increasing its velocity or a mix of both, while consuming the required mechanical work from a rotating input shaft connected to the transmission (37), while the compressed low-pressure steam (17) leaves the compressor (38) from compressor discharge stream (19) with higher pressure and temperature and consequently higher thermal energy compared with the inlet.
  • the transmission (37) mechanically or hydraulically connects rotating output shaft of the expander (36) to rotating input shaft of the compressor (38).
  • the energy extracted from the expander (36) by expansion of the high-pressure steam (28) is transmitted through the transmission (37) to the compressor (38) where the compression of the low-pressure steam (17) consumes the generated power by the expander (36).
  • the compressor discharge stream (19) and the expander exhaust stream (30) are supplied to the heat consumer (20).
  • the heat consumer (20) extracts internal energy of both the expander exhaust stream (30) and the compressor discharge stream (19) and causes condensation of them.
  • the heat consumer (20) delivers the high-pressure condensate (32) into the waste heat recovery boiler (25) and the low-pressure condensate (16) into the low-pressure boiler (15).
  • single stage pressure casing type of the expander compressor package (35) is illustrated in the Figure 1 and further details of single stage pressure casing the expander compressor package (35) are given in Figure 2.
  • the expander compressor package (35) can be of multi stage pressure casing type, and details of such configuration are given with Figure 3 and Figure 4.
  • the expander (36) can be of a single stage or multi stage axial type of turbine, single stage or multi stage radial type of turbine, multi stage a mix of axial and radial type of turbine or can be of single stage or multi-stage positive displacement type of expander.
  • the expander (36) is packed into an individual pressure casing.
  • the compressor (38) can be of a single stage or multi stage axial type of compressor, single stage or multi stage radial type of compressor, multi stage a mix of axial and radial type of compressor or can be of single stage or multi-stage positive displacement type of compressor.
  • the compressor (38) is packed into an individual pressure casing.
  • the transmission (37) can be mechanical shaft type, gearbox type, hydraulic type or continuous variable type.
  • a multi stage pressure casing of the expander compressor package (35) with multi transmission referred in the Figure 1 is explained.
  • function of each high-pressure expander (43) and low-pressure expander (44) given in the Figure 3 are the same with the function of the expander (36) given in the Figure 1 and the Figure 2.
  • Function of each low-pressure compressor (40) and high-pressure compressor (41 ) given in the Figure 3 are the same with the function of the compressor (36) in the Figure 1 and the Figure 2.
  • Function of each first transmission (45) and second transmission (46) given in the Figure 3 are the same in principle with the transmission (37) given in the Figure 1 and the Figure 2.
  • the high-pressure steam (28) is expanded within the high-pressure expander (43) to an intermediate pressure level and exits through high-pressure expander exhaust stream (29), flowing into the low-pressure expander (44) and further expanded within, and leaving through the expander exhaust stream (30) with a lower pressure. While the steam stream decreases in pressure, the temperature and the thermal energy decreases as well.
  • the total work by expanding the high-pressure steam (28) to the expander exhaust stream (30) is generated by two expanders connected in series on steam side where each high-pressure expander (43) and low- pressure expander (44) extracts some portion of the total extracted thermal energy and generates corresponding amount of work.
  • the low-pressure steam (17) is compressed within the low-pressure compressor (40) to an intermediate pressure level and exits through low-pressure compressor discharge stream (18), flowing into the high- pressure compressor (41 ) and further compressed within, and leaving through the compressor discharge stream (19) with a higher pressure. While the steam stream increases in pressure, the temperature and thermal energy increases as well.
  • the total work consumed by compressing the low-pressure steam (17) to the compressor discharge stream (19) is consumed by two compressors connected in series on steam side where each low-pressure compressor (40) and high-pressure compressor (41 ) transfers some portion of the energy to the steam stream and consumes corresponding amount of work.
  • the energy extracted from the high-pressure expander (43) by expansion of the high-pressure steam (28) to high-pressure expander exhaust stream (29) is transmitted through the first transmission (45) to the high- pressure compressor (41 ) where the compression of the low-pressure compressor discharge stream (18) to the compressor discharge stream (19) consumes the generated power by the expander high pressure (43).
  • the energy extracted from the low-pressure expander (44) by expansion of high-pressure expander exhaust stream (29) to the expander exhaust stream (30) is transmitted through the second transmission (46) to the low-pressure compressor (40) where the compression of low-pressure steam (17) to the low- pressure compressor discharge stream (18) consumes the generated power by the expander low pressure (44).
  • the high-pressure expander (43) and/or the low-pressure expander (44) can be of a single stage or multi stage axial type of turbine, single stage or multi stage radial type of turbine, multi stage a mix of axial and radial type of turbine or can be of single stage or multi stage positive displacement type of expander.
  • Each of the high-pressure expander (43) and the low-pressure expander (44) are packed into individual pressure casings.
  • the high-pressure compressor (41 ) and/or the low-pressure compressor (40) can be of a single stage or multi stage axial type of compressor, single stage or multi stage radial type of compressor, multi stage a mix of axial and radial type of compressor or can be of single stage or multi stage positive displacement type of compressor.
  • Each of the high-pressure compressor (41 ) and the low-pressure compressor (40) are packed into individual pressure casings.
  • the first transmission (45) and/or the second transmission (46) can be mechanical shaft type, gearbox type, hydraulic type, or continuous variable type.
  • pressure casings are calculated and optimized as per technical requirements, for the simplicity, only two pressure casings “high-pressure” and “low-pressure” are embodied in the Figure 3.
  • arrangement would comprise a high-pressure expander connected to a high-pressure compressor with transmission, an intermediate-pressure expander connected to an intermediate-pressure compressor with transmission, and a low-pressure expander connected to the low-pressure compressor with transmission, compressor pressure casings connected in series on the steam side and expander pressure casings connected in series on the steam side such as explained for the Figure 3 configuration above.
  • FIG. 4 a common transmission multi stage pressure casing type of the expander compressor package (35) given in the Figure 1 is explained. Descriptions for compressor and expander sections of the Figure 3 are valid for the Figure 4 while in the Figure 4, compressor input shafts and expander output shafts are connected to a common transmission (48). Rotating output shaft of the high-pressure expander (43), rotating output shaft of the low-pressure expander (44), rotating input shaft of the high-pressure compressor (41 ) and rotating input shaft of the low-pressure compressor (40) are all connected to the common transmission (48).
  • the common transmission (48) can be gearbox type, hydraulic type or continuous variable type or a mix of those for each connection.
  • the reason behind going from a multi-transmission multi stage pressure casing the expander compressor package (35) in the Figure 3 to common transmission multi stage pressure casing the expander compressor package (35) in the Figure 4 is to match total work generated by the expanders to total work consumed by the compressors while allowing each compressor pressure casing and expander pressure casing to operate at rotational speeds and duties not necessary to match each other.
  • thermocompressor package (50) comprises a single stage thermocompressor (55) or multiple of the thermocompressor (55) connected in series.
  • the single stage thermocompressor (55) is illustrated. Details and operation of the thermocompressor (55) is given in Figure 6 whereas the arrangement and further description of the multistage thermocompressor (55) is given in Figure 7.
  • thermocompressor (55) is a device using the high-pressure steam (28) to create a high velocity and decreased static pressure stream which causes suction of the low-pressure steam (17) and further mixing of both streams occurs in downstream section of the device while the outlet section of the thermocompressor (55) decrease the velocity of the mixture causing increase in static pressure, while thermocompressor exhaust stream (51 ) leaves the thermocompressor (55) at a pressure level between the high-pressure steam (28) and the low pressure steam (17).
  • the thermocompressor exhaust stream (51 ) is supplied to the heat consumer (20).
  • the heat consumer (20) extracts internal energy to the thermocompressor exhaust stream (51 ) and causes condensation of the stream.
  • the heat consumer (20) delivers the high-pressure condensate (32) into the waste heat recovery boiler (25) and the low-pressure condensate (16) into the low-pressure boiler (15), which both are the same fluid at different pressure levels.
  • thermocompressor (55) operation of the thermocompressor (55) is explained.
  • the high-pressure steam (28) flows into a nozzle (56).
  • the high-pressure steam (28) supplied to nozzle (56) is referred as motive steam (67).
  • the nozzle (56) causes velocity increase of the high-pressure steam (28) creating a jet flow while decreasing its static pressure to a point lower than the low-pressure steam (17).
  • Outlet steam velocity of the nozzle (56) can be subsonic or supersonic, higher the velocity, higher the compression ratio of the low-pressure steam (17) can be achieved.
  • Compression ratio is provided as thermocompressor exhaust stream (51 ) pressure divided by the low-pressure steam (17) pressure.
  • Outlet stream of the nozzle (56) flows into the mixing chamber (58) while creating a lower pressure environment in a suction chamber (57) causing flow of the low-pressure steam (17) into the suction chamber (57) and subsequent mixing of streams in a mixing chamber (58).
  • velocity of the mixture is decreased due to the increase in cross section, while increasing the static pressure of the mixture.
  • the thermocompressor exhaust stream (51 ) is at a pressure level between the high-pressure steam (28) and the low-pressure steam (17).
  • thermocompressor package (64) is explained.
  • only two stage thermocompressor (55) are embodied whereas number of the thermocompressor (55) connected in series can increase as required.
  • Compression ratio of the thermocompressor (55) is limited, therefore when higher compression ratio is required, multiple of the thermocompressor (55) are connected in series to achieve higher compression ratios.
  • Compression ratio is provided as the thermocompressor exhaust stream (51 ) pressure divided by the low-pressure steam (17) pressure.
  • Motive steam (67) which can be supplied either from the high-pressure steam (28) or the thermocompressor exhaust stream (51 ) is supplied to the nozzle section of a thermocompressor 1st stage (65).
  • thermocompressor 1st stage (65) compresses the low-pressure steam (17) to an interim pressure level below the thermocompressor exhaust stream (51 ) and above the low-pressure steam (17).
  • the high-pressure steam (28) is supplied to a thermocompressor 2nd stage (66) to compress the thermocompressor 1st stage outlet stream (68) and delivers the thermocompressor outlet stream (51 ) at a pressure point between the high-pressure steam (28) and a thermocompressor first stage outlet stream (68).
  • thermocompressor package (50) a hybrid compression system comprising the expander compressor package (35) and the thermocompressor package (50) is embodied.
  • the expander compressor package (35) and the thermocompressor package (50) can be connected in series as required or when required.
  • sequence, number of compression stages and compressor types can be arranged as required, for simplicity, the thermocompressor package (50) followed by the expander compressor package (35) is embodied.
  • the high-pressure steam (28) flows into the thermocompressor (55) and compresses the low- pressure steam (17), and delivers the thermocompressor exhaust stream (51 ) to the compressor (38) suction.
  • the compressor (38) compresses the inlet stream and delivers the compressor discharge stream (19).
  • Required power for the compressor (38) is supplied by the expander (36) through the transmission (37) and generated by the expander (36) by the expansion of the high-pressure steam (28).
  • the compressor discharge steam (19) and the expander exhaust stream (30) are supplied to the heat consumer (20), and the pressure level of these streams can be the same or different.

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

Abstract

L'invention se rapporte à un système de génération de vapeur à un niveau de pression utilisable, en particulier par compression de la vapeur à basse pression qui est générée par récupération de la chaleur perdue à basse température rejetée par un moteur à combustion interne, tandis que la vapeur motrice à haute pression requise pour comprimer la vapeur à basse pression est générée par récupération de la chaleur perdue d'échappement à haute température du même moteur à combustion interne. La quantité de chaleur de rejet à basse température provenant du moteur à combustion interne est importante par comparaison avec une entrée de chaleur totale dans le moteur à combustion interne, et comparable à la chaleur perdue d'échappement à haute température. Avec le système proposé, l'utilisation de la chaleur perdue à basse température et la génération de vapeur à un niveau de pression utilisable diminue la consommation totale de carburant par comparaison avec la génération de la même quantité de vapeur avec des systèmes classiques consommant du carburant.
PCT/TR2023/050528 2023-06-05 2023-06-05 Système de génération de vapeur de pression utilisable à l'aide de chaleur perdue à basse température provenant de moteurs à combustion interne Ceased WO2024253605A1 (fr)

Priority Applications (4)

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ES23761630T ES3049238T3 (en) 2023-06-05 2023-06-05 A system for generation of usable pressure steam using low temperature waste heat from internal combustion engines
CN202380099124.7A CN121263589A (zh) 2023-06-05 2023-06-05 一种利用内燃机低温废热产生可用压力蒸汽的系统
EP23761630.5A EP4508314B1 (fr) 2023-06-05 2023-06-05 Système de génération de vapeur de pression utilisable à l'aide de chaleur perdue à basse température provenant de moteurs à combustion interne
PCT/TR2023/050528 WO2024253605A1 (fr) 2023-06-05 2023-06-05 Système de génération de vapeur de pression utilisable à l'aide de chaleur perdue à basse température provenant de moteurs à combustion interne

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PCT/TR2023/050528 WO2024253605A1 (fr) 2023-06-05 2023-06-05 Système de génération de vapeur de pression utilisable à l'aide de chaleur perdue à basse température provenant de moteurs à combustion interne

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107542556A (zh) 2017-09-08 2018-01-05 天津大学 一种用于内燃机余热回收的自调整发电系统及其评价方法
CN110905619A (zh) * 2019-11-18 2020-03-24 天津大学 一种用于内燃机余热回收的混合工质朗肯循环系统
CN111441837A (zh) 2020-03-19 2020-07-24 天津大学 一种内燃机余热回收装置及其回收方法
US11143102B2 (en) * 2016-02-22 2021-10-12 Nuovo Pignone Tecnologie Srl Waste heat recovery cascade cycle and method

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11143102B2 (en) * 2016-02-22 2021-10-12 Nuovo Pignone Tecnologie Srl Waste heat recovery cascade cycle and method
CN107542556A (zh) 2017-09-08 2018-01-05 天津大学 一种用于内燃机余热回收的自调整发电系统及其评价方法
CN110905619A (zh) * 2019-11-18 2020-03-24 天津大学 一种用于内燃机余热回收的混合工质朗肯循环系统
CN111441837A (zh) 2020-03-19 2020-07-24 天津大学 一种内燃机余热回收装置及其回收方法

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CN121263589A (zh) 2026-01-02
EP4508314B1 (fr) 2025-10-01
ES3049238T3 (en) 2025-12-15
EP4508314A1 (fr) 2025-02-19

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