WO2011102408A1 - Exhaust heat recovery system, energy supply system, and exhaust heat recovery method - Google Patents
Exhaust heat recovery system, energy supply system, and exhaust heat recovery method Download PDFInfo
- Publication number
- WO2011102408A1 WO2011102408A1 PCT/JP2011/053352 JP2011053352W WO2011102408A1 WO 2011102408 A1 WO2011102408 A1 WO 2011102408A1 JP 2011053352 W JP2011053352 W JP 2011053352W WO 2011102408 A1 WO2011102408 A1 WO 2011102408A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat
- boiling point
- water
- heat medium
- steam
- Prior art date
Links
- 238000011084 recovery Methods 0.000 title claims abstract description 97
- 238000000034 method Methods 0.000 title claims abstract description 21
- 238000009835 boiling Methods 0.000 claims abstract description 185
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Chemical compound O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 180
- 238000001704 evaporation Methods 0.000 claims abstract description 11
- 230000008020 evaporation Effects 0.000 claims abstract description 10
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical group OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 claims description 54
- MTHSVFCYNBDYFN-UHFFFAOYSA-N diethylene glycol Chemical compound OCCOCCO MTHSVFCYNBDYFN-UHFFFAOYSA-N 0.000 claims description 54
- 238000010248 power generation Methods 0.000 claims description 22
- 230000008016 vaporization Effects 0.000 claims description 17
- 238000011144 upstream manufacturing Methods 0.000 claims description 10
- DNIAPMSPPWPWGF-UHFFFAOYSA-N Propylene glycol Chemical compound CC(O)CO DNIAPMSPPWPWGF-UHFFFAOYSA-N 0.000 claims description 9
- 239000012530 fluid Substances 0.000 claims description 9
- ZHNUHDYFZUAESO-UHFFFAOYSA-N Formamide Chemical compound NC=O ZHNUHDYFZUAESO-UHFFFAOYSA-N 0.000 claims description 6
- 238000009834 vaporization Methods 0.000 claims description 5
- PZBXEEXMBBGCML-UHFFFAOYSA-N ethane-1,2-diol;prop-1-ene Chemical compound CC=C.OCCO PZBXEEXMBBGCML-UHFFFAOYSA-N 0.000 claims description 3
- 239000007789 gas Substances 0.000 description 82
- 238000010438 heat treatment Methods 0.000 description 53
- 239000007788 liquid Substances 0.000 description 15
- 239000000498 cooling water Substances 0.000 description 8
- 230000009467 reduction Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 7
- 230000008859 change Effects 0.000 description 4
- KYKAJFCTULSVSH-UHFFFAOYSA-N chloro(fluoro)methane Chemical compound F[C]Cl KYKAJFCTULSVSH-UHFFFAOYSA-N 0.000 description 4
- 239000002918 waste heat Substances 0.000 description 4
- 229920006395 saturated elastomer Polymers 0.000 description 3
- OHMHBGPWCHTMQE-UHFFFAOYSA-N 2,2-dichloro-1,1,1-trifluoroethane Chemical compound FC(F)(F)C(Cl)Cl OHMHBGPWCHTMQE-UHFFFAOYSA-N 0.000 description 2
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- 235000011114 ammonium hydroxide Nutrition 0.000 description 2
- 239000000470 constituent Substances 0.000 description 2
- 230000005611 electricity Effects 0.000 description 2
- VHUUQVKOLVNVRT-UHFFFAOYSA-N Ammonium hydroxide Chemical compound [NH4+].[OH-] VHUUQVKOLVNVRT-UHFFFAOYSA-N 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 229910021529 ammonia Inorganic materials 0.000 description 1
- 239000000969 carrier Substances 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- -1 hydrofluorocarbon Chemical compound 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- RUOJZAUFBMNUDX-UHFFFAOYSA-N propylene carbonate Chemical compound CC1COC(=O)O1 RUOJZAUFBMNUDX-UHFFFAOYSA-N 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 239000008400 supply water Substances 0.000 description 1
- ZIBGPFATKBEMQZ-UHFFFAOYSA-N triethylene glycol Chemical compound OCCOCCOCCO ZIBGPFATKBEMQZ-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
- F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
-
- 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
- F01K23/04—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 condensation 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
- F01K23/10—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
- 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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/14—Combined heat and power generation [CHP]
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P80/00—Climate change mitigation technologies for sector-wide applications
- Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
- Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention relates to an exhaust heat recovery system, an energy supply system, and an exhaust heat recovery method.
- the present invention claims priority based on Japanese Patent Application No. 2010-034776 filed in Japan on February 19, 2010, the contents of which are incorporated herein by reference.
- Patent Document 1 discloses an example of a cogeneration facility (system) using an exhaust heat recovery boiler
- Patent Document 2 discloses an example of a multi-pressure vertical natural circulation exhaust heat recovery boiler
- Patent Document 3 discloses an example of a combined cycle power plant that combines exhaust heat recovery boilers
- Patent Document 4 discloses an example of a double pressure exhaust heat recovery boiler.
- a cogeneration system is known as an energy supply system that uses exhaust heat generated during power generation to extract thermal energy used for air conditioning and hot water supply.
- exhaust heat recovery by steam generation using an exhaust heat recovery boiler is generally performed.
- Patent Document 5 discloses a waste heat recovery device that recovers waste heat (exhaust heat) from a relatively low-temperature heat source of about 200 ° C. using first and second working fluids having different boiling points. Yes.
- This waste heat recovery apparatus uses water as the first working fluid, and as the second working fluid, chlorofluorocarbon, hydrochlorofluorocarbon, hydrofluorocarbon, chlorofluorocarbon, hydrochlorofluorocarbon, hydrofluorocarbon, Ammonia or ammonia water is used, and more heat is recovered from a relatively low temperature heat source to improve power generation efficiency.
- the conventional exhaust heat recovery method by generating water vapor from the water described above does not necessarily have an effective energy recovery efficiency that can be recovered from the energy of the exhaust gas (exhaust heat). Further improvement is expected.
- exhaust heat recovery from a relatively high temperature exhaust heat that greatly exceeds the evaporation temperature of water for example, high temperature exhaust heat exceeding 300 ° C.
- there is a limit to the evaporation temperature when water is vaporized in exhaust heat recovery from a relatively high temperature exhaust heat that greatly exceeds the evaporation temperature of water, for example, high temperature exhaust heat exceeding 300 ° C.
- the conventional exhaust heat recovery method does not have a sufficient effective energy recovery efficiency, and a large amount of effective energy is inevitably lost.
- the available energy is a thermodynamic concept also called exergy, and is generally known as energy that can be extracted as dynamic work from a certain system.
- the effective energy in the present invention means energy (work amount) that can be recovered as dynamic work (power such as electricity) in the total energy of the exhaust gas.
- the conventional exhaust heat recovery method using water (first working fluid) and the second working fluid having a boiling point lower than that of the water is intended for heat recovery from a relatively low-temperature heat source of about 200 ° C.
- the temperature of the vapor obtained by vaporizing the second working fluid is lower than the temperature of the vapor obtained by vaporizing the first working fluid. Energy recovery is almost impossible.
- the present invention relates to an exhaust heat recovery method for acquiring effective energy by vaporizing water, and more effective energy recovery than an exhaust heat recovery method for acquiring effective energy by vaporizing water and a liquid having a lower boiling point than the water.
- the objective is to improve efficiency.
- Another object of the present invention is to provide an energy supply system that has higher efficiency, energy saving rate, and CO2 reduction rate than conventional ones.
- a heat conduction path through which exhaust heat is conducted and a high boiling point heat medium having a higher evaporation temperature than water are conducted through the heat conduction path.
- a high-boiling-point heat medium steam generator that generates high-boiling-point heat medium steam by exchanging heat with exhaust heat is employed.
- the evaporation temperature is higher than water (vapor pressure is lower than water). Since the high-boiling point heat medium is evaporated to generate the high-boiling point heat medium vapor, it is possible to improve the recovery efficiency of the effective energy as compared with the conventional exhaust heat recovery method in which water is evaporated to generate water vapor.
- 2nd Embodiment of this invention it is a characteristic view which shows the energy-saving rate in the case where ethylene glycol is employ
- the energy supply system P ⁇ b> 1 includes an exhaust gas pipe 1, a high boiling point heat medium steam generator 2, a steam generator 3, a high boiling point heat medium preheater 4, and a water preheater 5.
- the steam turbine generator 13, the steam condenser 14, the condensate tank 15, and the cooling water supply device 16 are configured.
- reference numeral G denotes a high temperature exhaust gas
- R1 denotes a high boiling point heating medium
- R2 denotes a high boiling point heating medium vapor
- R3 denotes water
- R4 denotes water vapor.
- the exhaust gas pipe 1, the high boiling point heat medium steam generator 2, the steam generator 3, the high boiling point heat medium preheater 4, the water preheater 5, the high boiling point heat medium steam superheater 6, and the steam superheater. 7 constitutes an exhaust heat recovery section K1 for recovering exhaust heat from the high temperature exhaust gas G.
- the exhaust heat recovery unit K1 corresponds to the exhaust heat recovery system according to the present invention.
- the steam condenser 14, the condensate tank 15 and the cooling water supply device 16 constitute an electric power generation unit W.
- the power generation unit W supplies the high-boiling point heat medium R1 and water R3, which are liquid heat media, to the exhaust heat recovery unit K1, and the high-boiling point heat medium vapor R2 and water vapor that are vaporized by the above-described exhaust heat.
- the energy supply system P1 composed of the exhaust heat recovery unit K1 and the power generation unit W (power generation unit) is a high-boiling-point heat transfer steam generated by recovering exhaust heat from the high-temperature exhaust gas G in the exhaust heat recovery unit K1.
- the exhaust gas pipe 1 is a heat conduction path through which the high-temperature exhaust gas G supplied from the outside flows.
- the high-temperature exhaust gas G is, for example, high-temperature exhaust gas discharged from the combustor (that is, gas having exhaust heat), and a temperature that is significantly higher than the temperature required for vaporizing the water R3, for example, a temperature of 300 ° C. or higher.
- Such high-temperature exhaust gas G flows from the left side (upstream side) to the right side (downstream side) of the exhaust gas pipe 1 as shown in FIG.
- the high-boiling-point heat medium steam generator 2 is provided in the middle of the exhaust gas pipe 1, and by exchanging heat between the high-boiling point heat medium R1 and the high-temperature exhaust gas G, This is a device for generating the medium vapor R2.
- the steam generator 3 is provided in the exhaust gas pipe 1 on the downstream side of the high-boiling-point heat medium steam generator 2, and the water R3 is exchanged with the high-temperature exhaust gas G for high pressure. Is an apparatus (boiler) for generating water vapor R4.
- the high boiling point heating medium R1 is a liquid of a compound that has a higher evaporation temperature than water R3 (that is, a vapor pressure lower than that of water R3) and is chemically stable in heat exchange with the high-temperature exhaust gas G.
- ethylene glycol molecular formula: C 2 H 6 O 2
- diethylene glycol molecular formula: C 2 H 10 O 3
- propylene glycol C 3 H 8 O 2
- triethylene glycol molecular formula: C 6 H 14 O 4
- propylene carbonate molecular formula: C 4 H 5 O 3
- propylene ethylene glycol molecular formula: C 3 H 8 O 2
- formamide molecular formula: CH 3 NO
- the high boiling point heat medium preheater 4 is provided between the high boiling point heat medium steam generator 2 and the steam generator 3 in the exhaust gas pipe 1.
- This high boiling point heat medium preheater 4 is a kind of heat exchange that preheats to a temperature just before boiling, for example, by exchanging the high boiling point heat medium R1 supplied from the high boiling point heat medium supply pump 8 with the high temperature exhaust gas G.
- the high-boiling point heating medium R1 preheated is discharged to the high-boiling point heating medium steam generator 2.
- the water preheater 5 is provided on the downstream side of the steam generator 3 in the exhaust gas pipe 1.
- This water preheater 5 is a kind of heat exchanger that preheats the water R3 supplied from the feed water pump 9 to the temperature just before boiling, for example, by exchanging heat with the high-temperature exhaust gas G. It discharges to the generator 3 and the high-boiling-point heat medium steam condenser 11.
- the high boiling point heat medium steam superheater 6 is provided upstream of the high boiling point heat medium steam generator 2 in the exhaust gas pipe 1.
- the high boiling point heat medium steam superheater 6 is a kind of heat exchanger that superheats by exchanging heat between the high boiling point heat medium steam R2 supplied from the high boiling point heat medium steam generator 2 and the high temperature exhaust gas G.
- the high boiling point heat medium steam R2 is discharged to the high boiling point heat medium steam turbine generator 10.
- the steam superheater 7 is provided upstream of the high-boiling-point heat medium steam superheater 6 in the exhaust gas pipe 1.
- the steam superheater 7 is a kind of heat exchanger that superheats the steam R4 supplied from the steam generator 3 and the high-boiling-point heat medium steam condenser 11 by exchanging heat with the high-temperature exhaust gas G. Is discharged to the steam turbine generator 13.
- the high boiling point heating medium supply pump 8 is a pump that pumps out the high boiling point heating medium R 1 from the condensate tank 12 and supplies it to the high boiling point heating medium preheater 4.
- the water supply pump 9 is a pump that pumps water R3 from the condensate tank 15 and supplies it to the water preheater 5.
- the high boiling point heat medium steam turbine generator 10 rotates the turbine using the high pressure high boiling point heat medium steam R2 supplied from the high boiling point heat medium steam generator 2 via the high boiling point heat medium steam superheater 6.
- a turbine generator that generates electric power by driving a generator axially coupled to the turbine.
- the high-boiling point heat medium steam condenser 11 exchanges heat with the water R3 supplied from the water preheater 5 for the high-boiling point heat medium steam R2 after power recovery discharged from the turbine of the high-boiling point heat medium steam turbine generator 10.
- This is a kind of heat exchanger that condenses (liquefies) the high-boiling-point heat transfer medium vapor R2 to restore the high-boiling-point heat transfer medium R1, and vaporizes the water R3 to form the high-pressure steam R4.
- the high boiling point heat medium steam condenser 11 discharges the restored high boiling point heat medium R1 to the condensate tank 12, while the steam R4 generated by heat exchange with the high boiling point heat medium steam R2 is supplied to the steam superheater 7. Discharge.
- the condensate tank 12 is a storage tank that temporarily stores the high boiling point heat medium R1 supplied from the high boiling point heat medium vapor condenser 11.
- the steam turbine generator 13 is axially coupled to the turbine by rotating the turbine using the high-pressure steam R 4 supplied from the steam generator 3 and the high-boiling-point heat medium steam condenser 11 via the steam superheater 7. This is a turbine generator that generates electricity by driving a generator.
- the steam condenser 14 condenses (liquefies) water R3 by exchanging heat from the steam R4 after power recovery discharged from the turbine of the steam turbine generator 13 with the cooling water supplied from the cooling water supply device 16. It is a kind of heat exchanger that is restored to Such a steam condenser 14 discharges the restored water R3 to the condensate tank 15.
- the condensate tank 15 is a storage tank that temporarily stores the water R3 supplied from the steam condenser 14.
- the cooling water supply device 16 is a device that circulates and supplies the cooling water to the steam condenser 14.
- a plurality of heat exchangers that exchange heat with the high-temperature exhaust gas G are arranged from the upstream side to the downstream side of the exhaust gas pipe 1, that is, in the axial direction of the exhaust gas pipe 1. . That is, among the heat exchangers, the steam superheater 7 is located in the uppermost stream of the exhaust gas pipe 1, and the high boiling point heat medium steam superheater 6 ⁇ the high boiling point heat medium steam generator 2 is disposed downstream of the steam superheater 7. ⁇ The high boiling point heating medium preheater 4 ⁇ the steam generator 3 ⁇ the water preheater 5 are arranged in this order.
- the high-temperature exhaust gas G flowing through the region (heat exchange region) of the exhaust gas pipe 1 in which these heat exchangers are disposed deprives each heat exchanger of heat by passing through the heat exchange region from the upstream side to the downstream side. Therefore, the temperature is higher at the upstream side of the heat exchange region (the temperature is lower at the downstream side).
- the high boiling point heat medium steam generator 2 is located upstream of the steam generator 3 in the heat exchange region.
- the high boiling point heating medium R1 in the generator 2 exchanges heat with the high-temperature exhaust gas G that is higher in temperature than the water R3 in the steam generator 3.
- FIG. 2 shows the heat exchange state of each heat medium (that is, the high temperature exhaust gas G, the high boiling point heat medium R1, the high boiling point heat medium steam R2, the water R3, and the water vapor R4) in the heat exchange region and the heat exchange amount (horizontal axis) and the temperature. It is a characteristic view shown by the relationship with (vertical axis).
- a solid line Lg indicates a change in the state of the high-temperature exhaust gas G
- a broken line Ls indicated by a one-dot chain line indicates a change in the state of water R3 or water vapor R4
- a broken line Lk indicated by a dotted line indicates the high boiling point heating medium R1.
- steam R2 is shown.
- the exchange heat amount point A1 corresponds to the most downstream point in the heat exchange region
- the exchange heat amount point C3 corresponds to the most upstream point in the heat exchange region.
- Each heat exchanger is located between the exchange heat amount point A1 (the most downstream point) and the exchange heat amount point C3 (the most upstream point) in heat exchange characteristics, and performs heat exchange using the high-temperature exhaust gas G as a heat source.
- the water R3 is preheated by the water preheater 5. It is distributed and supplied to the steam generator 3 and the high boiling point heat medium steam condenser 11. Some of the water R3 is converted into water vapor R4 by heat exchange with the high-temperature exhaust gas G in the water vapor generator 3, and the remaining water R3 is exchanged with high boiling point heat medium steam R2 in the high boiling point heat medium steam condenser 11. It becomes water vapor R4.
- the region of the exchange heat points A1 to A2 in the broken line Ls corresponds to the temperature rise (pressurization) up to the temperature just before the boiling point of the water R3 by the water preheater 5, and the region of the exchange heat points A2 to B1 in the broken line Ls is also the same. This corresponds to the vaporization of a part of water R3 (steam R4) by the steam generator 3. Further, the region of the exchange heat amount points B1 to D in the polygonal line Ls corresponds to the vaporization (water vapor R4) of the remaining water R3 by the high boiling point heat medium steam condenser 11. That is, the water R3 preheated to a temperature just before the boiling point by the water preheater 5 becomes steam R4 due to the exchange heat quantity over the exchange heat quantity points A2 to D.
- the water vapor R 4 discharged from the water vapor generator 3 and the water vapor R 4 discharged from the high-boiling-point heat medium vapor condenser 11 join together and are supplied to the water vapor superheater 7. That is, the water vapor R4 generated in the water vapor generator 3 and the high-boiling-point heat medium vapor condenser 11 becomes water vapor R4 (superheated water vapor) superheated to the boiling point by heat exchange with the high-temperature exhaust gas G in the water vapor superheater 7. .
- the region of the exchange heat points C2 to C3 in the polygonal line Ls is a superheated region of the steam R4 by the steam superheater 7. Note that the temperature of the exchange heat amount point C2 corresponding to the overheating start point of the water vapor R4 is equal to the temperature of the exchange heat amount point D (vaporization end point) of the water vapor R4 as shown in the figure.
- the high boiling point heating medium R1 is preheated to a temperature just before the boiling point by heat exchange with the high temperature exhaust gas G in the high boiling point heating medium preheater 4, and then the high boiling point heating medium vapor is heated. It is supplied to the generator 2 to become a high boiling point heating medium vapor R2.
- the region of the exchange heat points B1 to B2 in the polygonal line Lk corresponds to the temperature rise (pressurization) up to the temperature just before the boiling point of the high boiling point heating medium R1 by the high boiling point heating medium preheater 4, and the exchange heat point in the polygonal line Lk as well.
- the region of B2 to C1 corresponds to the vaporization of the high boiling point heat medium R1 by the high boiling point heat medium steam generator 2 (high boiling point heat medium steam R2 conversion).
- the high-boiling-point heat transfer steam R2 discharged from the high-boiling-point heat transfer steam generator 2 is superheated above the boiling point by heat exchange with the high-temperature exhaust gas G in the high-boiling-point heat transfer steam superheater 6.
- R2 (superheated high boiling point heating medium vapor).
- the region of the exchange heat quantity points C1 to C2 in the polygonal line Lk is a superheated region of the high boiling point heat medium steam R2 by the high boiling point heat medium steam superheater 6.
- the high boiling point heating medium R 1 supplied to the high boiling point heating medium preheater 4 by the high boiling point heating medium supply pump 8 is discharged from the high boiling point heating medium steam turbine generator 10 in the high boiling point heating medium steam condenser 11.
- the high boiling point heating medium vapor R2 is liquefied by heat exchange with the water R3 discharged from the water preheater 5.
- the heat exchange in the high-boiling-point heat medium vapor condenser 11 corresponds to a region of exchange heat quantity points D to B1 on the polygonal line Lk.
- the heat of the heat exchange initially acts as sensible heat on the high-boiling-point heat transfer steam R2, thereby gradually lowering the temperature of the high-boiling-point heat transfer steam R2. Thereafter, the heat acts as latent heat on the high-boiling-point heat medium steam R2, so that a constant amount of the high-boiling-point heat medium steam R2 is condensed while maintaining a constant value.
- Such a state change of the high boiling point heating medium vapor R2 relates to the case where the high boiling point heating medium R1 is ethylene glycol (molecular formula: C 2 H 6 O 2 ), and varies depending on the type of the high boiling point heating medium R1.
- the water R3 in the state Ys corresponding to the exchange heat quantity point A1 is heated with the high-temperature exhaust gas G having a relatively low temperature in the water preheater 5 and the steam generator 3.
- the high-boiling-point heat medium steam R2 high-boiling-point heat medium steam
- the broken line Ls The steam R4 in the state Xs is heated to a temperature corresponding to the exchange heat quantity point C3.
- the steam R4 in the state Xs is supplied to the steam turbine generator 13 as a power source to release energy, and then cooled, condensed and condensed, and returns to the water R3 in the state Ys corresponding to the exchange heat point A1. .
- the high boiling point heat medium R1 in the state Yk corresponding to the exchange heat quantity point D is the high boiling point heat medium preheater 4, the high boiling point heat medium steam generator 2, and the high boiling point heat medium steam superheated.
- the high-boiling-point heat transfer steam R2 in the state Xk is heated to a temperature corresponding to the exchange heat point C2 of the broken line Lk.
- the high-boiling-point heat medium steam R2 in the state Xk is supplied to the high-boiling-point heat medium steam turbine generator 10 as a power source and released, thereby releasing the high-boiling point heat medium in the state YL corresponding to the exchange heat point D. Return to R1.
- the evaporation temperature is higher than that of water R3 by heat exchange with the high temperature exhaust gas G.
- the high-boiling point heat medium R1 is vaporized to a high-boiling point heat medium steam R2 by vaporizing the high boiling point heat medium R1 (which has a lower vapor pressure than the water R3), so that the effective energy recovery efficiency is improved over conventional exhaust heat recovery methods. It is possible to make it.
- a Rankine cycle in which power is extracted by an enthalpy difference between the state Xk (gas phase) and the state YL (gas phase or gas-liquid mixed phase) can be constructed, but the boiling point is higher than that of the water R3.
- a low boiling point heating medium conventional chlorofluorocarbon or alternative chlorofluorocarbon
- the high temperature range exceeds the critical point, and power cannot be taken out by Rankine cycle. That is, according to the exhaust heat recovery unit K1, by using the high boiling point heating medium R1, it is possible to efficiently extract effective energy in a high temperature range that is impossible with a low boiling point heating medium.
- the high boiling point heat medium steam R2 is superheated using the high boiling point heat medium steam superheater 6 and the steam R4 is superheated using the steam superheater 7, so that heat recovery is possible.
- the efficiency can be further improved as compared with the conventional exhaust heat recovery method.
- FIG. 3 the same components as those of the energy supply system P1 according to the first embodiment shown in FIG.
- the energy supply system P2 includes an exhaust heat recovery unit K2 and a power generation / steam output unit W2, and as shown in FIG. 3, the energy supply system according to the first embodiment described above.
- the steam superheater 7, steam turbine generator 13, steam condenser 14, condensate tank 15, and cooling water supply device 16 are deleted from P1. That is, in this energy supply system P2, the water vapor R4 discharged from the water vapor generator 3 and the water vapor R4 discharged from the high-boiling-point heat medium vapor condenser 11 are merged and supplied to the external water vapor load.
- the condensate recovered from is input to the feed pump 9.
- the exhaust heat recovery unit K2 includes the exhaust gas pipe 1, the high-boiling-point heat medium steam generator 2, the steam generator 3, It consists of a boiling point heat medium preheater 4, a water preheater 5, and a high boiling point heat medium steam superheater 6.
- the power generation / steam output section W2 is composed of a high boiling point heat medium supply pump 8, a feed water pump 9, a high boiling point heat medium steam turbine generator 10, a high boiling point heat medium steam condenser 11 and a condensate tank 12. Yes.
- each heat medium high temperature exhaust gas G, high boiling point heat medium R1, high boiling point heat medium steam R2, water R3 and water vapor R4 in the heat exchange region of such exhaust heat recovery section K2 is shown in FIG. It becomes. That is, when the heat exchange between the water R3 and the water vapor R4 and the high temperature exhaust gas G, that is, the heat exchange in the water preheater 5 and the water vapor generator 3, the water R3 in the state Ys1 corresponding to the exchange heat quantity point Aa is broken.
- heat exchange with the high temperature exhaust gas G at a relatively low temperature in the water preheater 5 preheats to the exchange heat point Ab, which is a temperature just before the boiling point, and further the high temperature in the steam generator 3
- the heat exchange with the exhaust gas G and the heat exchange with the high boiling point heat medium vapor R2 (high boiling point heat medium vapor) in the high boiling point heat medium vapor condenser 11 result in the water vapor R4 in the state Xs1 corresponding to the exchange heat quantity point Da.
- the water vapor R4 in the state Xs1 is supplied as a heat source to the external heat load, and returns to the water R3 in the state Ys1 corresponding to the exchange heat amount point Aa by releasing energy by the external heat load.
- the high boiling point heating medium R1 in the state Yk1 corresponding to the exchange heat point B1 is exchanged with the high temperature exhaust gas G having a relatively high temperature in the high boiling point heating medium preheater 4 and the high boiling point heating medium steam generator 2,
- the high boiling point heat medium steam R2 is in a state corresponding to the exchange heat point C1 of the polygonal line Lk1, and the high boiling point heat medium steam R2 is superheated above the boiling point by heat exchange with the high temperature exhaust gas G in the high boiling point heat medium steam superheater 6. It becomes the high boiling point heating medium vapor R2 (superheated high boiling point heating medium vapor) of the state Xk1.
- the high boiling point heating medium steam R2 (superheated high boiling point heating medium steam) in the state Xk1 is supplied to the high boiling point heating medium steam turbine generator 10 as drive power and discharged, thereby corresponding to the exchange heat point Da. It returns to the high boiling point heating medium R1 in the state YL1.
- this energy supply system P2 is a cogeneration system that supplies electric energy to the outside and supplies heat energy from water vapor to the outside.
- the water R3 is exchanged by heat exchange with the high temperature exhaust gas G in the same manner as the exhaust heat recovery unit K1 of the energy supply system P1 according to the first embodiment described above.
- high-boiling point heat medium R1 has a higher evaporation temperature than water R3 (has a lower vapor pressure than water R3) due to heat exchange with high-temperature exhaust gas G. Therefore, the effective energy recovery efficiency can be improved as compared with the conventional exhaust heat recovery method.
- the overall efficiency is slightly higher than when diethylene glycol is used, but the power generation efficiency is higher when diethylene glycol is used than when ethylene glycol is used.
- Such a difference in power generation efficiency is attributed to the pressure difference between the gas and liquid of both heat carriers. Under the same temperature condition, for example, when the gas pressure of both heating media is 1.5 MPa, the liquid pressure of ethylene glycol is 0.109 MPa, whereas the liquid pressure of diethylene glycol is 0.027 MPa. That is, since diethylene glycol has a lower liquid pressure than ethylene glycol, diethylene glycol has a greater gas-liquid pressure difference than ethylene glycol. This difference in gas-liquid pressure difference is the cause of power generation efficiency.
- FIG. 5 shows energy saving rates when ethylene glycol is used as the high boiling point heating medium R1 and when diethylene glycol is used.
- FIG. 5 is a characteristic diagram in which the horizontal axis is the power generation end thermal efficiency ⁇ E based on the low calorific value (LHV) and the vertical axis is the exhaust heat recovery efficiency ⁇ H , and the energy saving efficiency ⁇ S1 when ethylene glycol is used and The energy saving efficiency ⁇ S2 when diethylene glycol is used is shown.
- the energy saving efficiency ⁇ S1 is 23.5%
- the energy saving efficiency ⁇ S2 is 25.1%.
- ethylene glycol is used. A slightly higher value.
- FIG. 6 shows the CO 2 reduction rate when ethylene glycol is used as the high boiling point heating medium R1 and when diethylene glycol is used.
- FIG. 6 is a characteristic diagram with the heat generation end thermal efficiency ⁇ E based on the low calorific value (LHV) as the horizontal axis and the exhaust heat recovery efficiency ⁇ H as the vertical axis, and the CO 2 reduction rate S 1 when ethylene glycol is used and This shows the CO 2 reduction rate S2 when diethylene glycol is used.
- the CO 2 reduction rate S 1 is 38.4%
- the CO 2 reduction rate S 2 is 40.4%
- diethylene glycol is used in the same manner as the energy saving rate described above. When this is done, the value is slightly higher than when ethylene glycol is used.
- the energy supply system P2 is a cogeneration system that supplies electric energy to the outside and supplies heat energy from water vapor to the outside.
- the energy supply system P2 collects exhaust heat from the exhaust gas like the energy supply system P1 of the first embodiment.
- the energy supply device that converts the available energy obtained from the above into electric energy and supplies it as power, or the energy that is converted into only heat energy and supplied to the outside as steam, such as a well-known exhaust heat recovery boiler Different from the feeding device. In these energy supply devices, available energy is converted into a single energy such as electric energy or heat energy, so that a high energy saving rate and CO 2 reduction rate cannot be achieved as in the case of the energy supply system P2.
- FIG. 7 the same components as those of the energy supply system P2 according to the second embodiment shown in FIG.
- the energy supply system P3 according to the third embodiment is mainly characterized in that the steam generator 3 is replaced with a flash tank 17 in the energy supply system P2 according to the second embodiment.
- the energy supply system P3 further includes a pressurizing pump 18 as a component accompanying the flash tank 17.
- the exhaust heat recovery unit K3 in the energy supply system P2 includes an exhaust gas pipe 1, a high boiling point heat medium steam generator 2, a high boiling point heat medium preheater 4, a water preheater 5, a high boiling point heat medium steam superheater 6, and It is composed of a flash tank 17.
- the power generation / steam output unit W3 includes a high boiling point heat medium supply pump 8, a feed water pump 9, a high boiling point heat medium steam turbine generator 10, a high boiling point heat medium steam condenser 11, a condensate tank 12, and a pressure pump. It is comprised from 18.
- the flash tank 17 is a flash-type steam generator that steams water (high-temperature high-pressure water) supplied from the water preheater 5 by a flash phenomenon.
- This flash tank 17 is a kind of container in which the internal pressure is adjusted so that the water (high-temperature high-pressure water) supplied from the water preheater 5 is vaporized by the flash phenomenon, and the steam R4 (flash steam) and the saturated water R5. And generate
- the flash phenomenon is known as a phenomenon in which a part of the high-temperature high-pressure water is vaporized as saturated water vapor when the pressure is released by releasing the high-temperature high-pressure water into a low-pressure atmosphere.
- the pressurizing pump 18 is a pump that pressurizes water recovered from an external heat load.
- the water discharged from the pressurizing pump 18 is distributed and supplied to the feed water pump 9 and the high boiling point heat medium steam condenser 11. Further, the water vapor R4 generated in the flash tank 17 is supplied to an external heat load, and the saturated water R5 similarly generated in the flash tank 17 is a water supply pump discharged from a pressurizing pump 18 as shown in the figure, for example.
- 9 is distributed to the feed water pump 9 and the high-boiling-point heat medium steam condenser 11 by being supplied to the branch point j between the high-boiling-point heat medium steam condenser 11.
- this energy supply system P3 has a pressure (reduced pressure) instead of the steam generator 3 of the second embodiment that generates the steam R4 by the action of heat obtained by heat exchange between the water R3 and the high temperature exhaust gas G. ) Is provided with a flash tank 17 that generates water vapor R4.
- the pressure pump 18 is not an essential component of the third embodiment, but is preferably provided.
- FIG. 8 shows the heat exchange state of each heat medium (high-temperature exhaust gas G, high-boiling-point heat medium R1, high-boiling-point heat medium steam R2, water R3, and water vapor R4) in the exhaust heat recovery unit K3 of the energy supply system P3.
- the water R3 can be preheated in a region extending from the exchange heat amount points Aa to B1, that is, a region wider than a region extending from the exchange heat amount points Aa to Ab of the second embodiment.
- the heat exchange between the water R3 and the high-temperature exhaust gas G in the region extending over the exchange heat quantity points Aa to B1 is more effective energy as can be seen from comparison with FIG. 4 showing the heat exchange state of the second embodiment. Can be obtained from the high temperature exhaust gas G. Therefore, according to the third embodiment, since a larger amount of water R3 can be preheated, it is possible to generate a larger amount of water vapor R4 than in the second embodiment. Further, according to the third embodiment, since the flash tank 17 is used in place of the steam generator 3, the cost of the system can be reduced.
- the high-boiling point heat medium R1 having a vapor pressure lower than that of the water R3 is used to recover heat from the high-temperature exhaust gas G
- the exhaust heat of the high temperature exhaust gas G may be recovered by using only the high boiling point heating medium R1 or using three or more kinds of liquids having different vapor pressures.
- the high-boiling-point heat medium preheater 4 and the water preheater 5 are constituent elements. However, although the heat recovery efficiency is reduced, the high-boiling point heat medium preheater is used as necessary. 4 and the water preheater 5 may be omitted.
- the heat source (exhaust heat) used as the object of heat recovery is not limited to the high temperature exhaust gas G (gas).
- the heat conduction path in the present invention is not limited to the exhaust gas pipe 1 through which the high-temperature exhaust gas G (gas) flows.
- the high-boiling-point heat medium steam turbine generator 10 and the steam turbine generator 13 are used as constituent elements to generate electric power that is one form of power.
- a compressor, a blower, a pump, a propeller, or the like various forms of power may be taken out.
- the water vapor generator 3 in the second embodiment is replaced with the flash tank 17, but the water vapor generator 3 in the first embodiment may be replaced with the flash tank 17. .
- one flash tank 17 is provided. However, a plurality of flash tanks 17 are provided in parallel, and water R3 output from the water preheater 5 is provided in parallel by the plurality of flash tanks 17. May be steamed.
- the exhaust heat recovery method for acquiring effective energy by vaporizing water and the effective energy than the exhaust heat recovery method for acquiring effective energy by vaporizing water and a liquid having a lower boiling point than the water. It is possible to provide an exhaust heat recovery system and an exhaust heat recovery method with high recovery efficiency. Further, according to the present invention, as described above, since the effective energy recovery efficiency in the exhaust heat recovery is high, it is possible to provide an energy supply system that is higher in energy efficiency than in the past.
- cooling water supply device 17 ... flash tank, 18 ... pressure pump, G ... high temperature exhaust gas, R1 ... high boiling point heat Medium, R2 ... high boiling point heat medium vapor, R3 ... water, R4 ... water vapor, P1-P3 ... energy supply system, K1-K3 ... exhaust heat recovery unit (exhaust heat recovery system), W1 ... electric power generation unit, W2, W3 ... Power generation / steam output section
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
Description
また、本発明は、2010年2月19日に日本国に出願された特願2010-034776号に基づき優先権を主張し、その内容をここに援用する。 The present invention relates to an exhaust heat recovery system, an energy supply system, and an exhaust heat recovery method.
The present invention claims priority based on Japanese Patent Application No. 2010-034776 filed in Japan on February 19, 2010, the contents of which are incorporated herein by reference.
また、水(第1の作動流体)と当該水よりも沸点が低い第2の作動流体とを用いる従来の排熱回収方法は、200℃程度の比較的低温の熱源からの熱回収を念頭に置いたものであり、第2の作動流体を気化させて得られる蒸気の温度は、第1の作動流体を気化させて得られる蒸気の温度よりさらに低いため、比較的高温の排熱からの有効エネルギの回収は殆ど不可能である。 However, the conventional exhaust heat recovery method by generating water vapor from the water described above does not necessarily have an effective energy recovery efficiency that can be recovered from the energy of the exhaust gas (exhaust heat). Further improvement is expected. In particular, in exhaust heat recovery from a relatively high temperature exhaust heat that greatly exceeds the evaporation temperature of water, for example, high temperature exhaust heat exceeding 300 ° C., there is a limit to the evaporation temperature when water is vaporized. However, the conventional exhaust heat recovery method does not have a sufficient effective energy recovery efficiency, and a large amount of effective energy is inevitably lost. The available energy is a thermodynamic concept also called exergy, and is generally known as energy that can be extracted as dynamic work from a certain system. The effective energy in the present invention means energy (work amount) that can be recovered as dynamic work (power such as electricity) in the total energy of the exhaust gas.
In addition, the conventional exhaust heat recovery method using water (first working fluid) and the second working fluid having a boiling point lower than that of the water is intended for heat recovery from a relatively low-temperature heat source of about 200 ° C. The temperature of the vapor obtained by vaporizing the second working fluid is lower than the temperature of the vapor obtained by vaporizing the first working fluid. Energy recovery is almost impossible.
また、本発明は、効率、また省エネ率やCO2削減率が従来よりも高いエネルギ供給システムを提供することを目的とする。 The present invention relates to an exhaust heat recovery method for acquiring effective energy by vaporizing water, and more effective energy recovery than an exhaust heat recovery method for acquiring effective energy by vaporizing water and a liquid having a lower boiling point than the water. The objective is to improve efficiency.
Another object of the present invention is to provide an energy supply system that has higher efficiency, energy saving rate, and CO2 reduction rate than conventional ones.
〔第1実施形態〕
最初に、本発明の第1実施形態について図1及び図2を参照して説明する。
本第1実施形態に係るエネルギ供給システムP1は、図1に示すように、排ガス管1、高沸点熱媒蒸気発生器2、水蒸気発生器3、高沸点熱媒予熱器4、水予熱器5、高沸点熱媒蒸気過熱器6、水蒸気過熱器7、高沸点熱媒供給ポンプ8、給水ポンプ9、高沸点熱媒蒸気タービン発電機10、高沸点熱媒蒸気凝縮器11、復液タンク12、水蒸気タービン発電機13、水蒸気凝縮器14、復水タンク15及び冷却水供給装置16によって構成されている。なお、この図1において、符合Gは高温排ガス、R1は高沸点熱媒、R2は高沸点熱媒蒸気、R3は水、またR4は水蒸気を示している。 Embodiments of the present invention will be described below with reference to the drawings.
[First Embodiment]
First, a first embodiment of the present invention will be described with reference to FIG. 1 and FIG.
As shown in FIG. 1, the energy supply system P <b> 1 according to the first embodiment includes an
次に、本発明の第2実施形態について図3及び図4を参照して説明する。
なお、図3では、図1に示した第1実施形態に係るエネルギ供給システムP1の構成要素と同一の構成要素には同一符合を付している。 [Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIGS.
In FIG. 3, the same components as those of the energy supply system P1 according to the first embodiment shown in FIG.
次に、本発明の第3実施形態について図7及び図8を参照して説明する。なお、図7では、図3に示した第2実施形態に係るエネルギ供給システムP2の構成要素と同一の構成要素には同一符合を付している。 [Third Embodiment]
Next, a third embodiment of the present invention will be described with reference to FIGS. In FIG. 7, the same components as those of the energy supply system P2 according to the second embodiment shown in FIG.
(1)上記各実施形態では、蒸気圧が異なる2種類の液体、つまり水R3に加え、当該水R3よりも蒸気圧が低い高沸点熱媒R1を用いて高温排ガスGの排熱を熱回収するが、これに代えて、高沸点熱媒R1のみを用いて、あるいは蒸気圧が異なる3種類以上の液体を用いて高温排ガスGの排熱を熱回収するようにしても良い。 In addition, this invention is not limited to said each embodiment, For example, the following modifications can be considered.
(1) In each of the above embodiments, in addition to two types of liquids having different vapor pressures, that is, water R3, the high-boiling point heat medium R1 having a vapor pressure lower than that of the water R3 is used to recover heat from the high-temperature exhaust gas G However, instead of this, the exhaust heat of the high temperature exhaust gas G may be recovered by using only the high boiling point heating medium R1 or using three or more kinds of liquids having different vapor pressures.
また、本発明によれば、上述したように排熱回収における有効エネルギの回収効率が高いので、従来よりもエネルギ効率が高いエネルギ供給システムを提供することができる。 According to the present invention, the exhaust heat recovery method for acquiring effective energy by vaporizing water, and the effective energy than the exhaust heat recovery method for acquiring effective energy by vaporizing water and a liquid having a lower boiling point than the water. It is possible to provide an exhaust heat recovery system and an exhaust heat recovery method with high recovery efficiency.
Further, according to the present invention, as described above, since the effective energy recovery efficiency in the exhaust heat recovery is high, it is possible to provide an energy supply system that is higher in energy efficiency than in the past.
Claims (14)
- 排熱が伝導する熱伝導路と、
水よりも蒸発温度が高い高沸点熱媒を熱伝導路を伝導する排熱と熱交換させることにより高沸点熱媒蒸気を発生させる高沸点熱媒蒸気発生器と
を具備する排熱回収システム。 A heat conduction path through which exhaust heat is conducted; and
An exhaust heat recovery system comprising a high boiling point heat medium steam generator that generates high boiling point heat medium steam by exchanging heat between a high boiling point heat medium having a higher evaporation temperature than water and exhaust heat conducted through a heat conduction path. - 熱伝導路において高沸点熱媒蒸気発生器の下流側に設けられ、水を排熱と熱交換させることにより水蒸気を発生させる水蒸気発生器をさらに備える請求項1記載の排熱回収システム。 The exhaust heat recovery system according to claim 1, further comprising a steam generator provided on the downstream side of the high-boiling-point heat medium steam generator in the heat conduction path and generating water vapor by exchanging heat with the exhaust heat.
- 熱伝導路において高沸点熱媒蒸気発生器の上流側に、排熱との熱交換により高沸点熱媒蒸気を過熱する高沸点熱媒蒸気過熱器あるいは排熱との熱交換により水蒸気を過熱する水蒸気過熱器の何れか一方あるいは両方を備える請求項1または2記載の排熱回収システム。 In the heat conduction path, on the upstream side of the high-boiling-point heat medium steam generator, the high-boiling-point heat medium steam superheater that superheats the high-boiling point heat medium steam by heat exchange with exhaust heat or superheats the steam by heat exchange with exhaust heat. The exhaust heat recovery system according to claim 1 or 2, comprising either or both of a steam superheater.
- 高沸点熱媒を予熱する高沸点熱媒予熱器あるいは/及び水を予熱する水予熱器をさらに備える請求項1~3のいずれか一項に記載の排熱回収システム。 The exhaust heat recovery system according to any one of claims 1 to 3, further comprising a high boiling point heat medium preheater for preheating the high boiling point heat medium and / or a water preheater for preheating water.
- 熱伝導路は、排熱を帯びた排ガスが流通する排ガス管である請求項1~4のいずれか一項に記載の排熱回収システム。 The exhaust heat recovery system according to any one of claims 1 to 4, wherein the heat conduction path is an exhaust gas pipe through which exhaust gas with exhaust heat flows.
- 高沸点熱媒は、エチレングリコール、ジエチレングリコール、プロピレングリコール、プロピレンエチレングリコールあるいはホルムアミドである請求項1~5のいずれか一項に記載の排熱回収システム。 The exhaust heat recovery system according to any one of claims 1 to 5, wherein the high boiling point heat medium is ethylene glycol, diethylene glycol, propylene glycol, propylene ethylene glycol, or formamide.
- 水蒸気発生器に代えて、水予熱器で予熱された水をフラッシュ現象によって水蒸気化させるフラッシュ式水蒸気発生器を備える請求項4~6のいずれか一項に記載の排熱回収システム。 The exhaust heat recovery system according to any one of claims 4 to 6, further comprising a flash-type steam generator that vaporizes water preheated by the water preheater by a flash phenomenon, instead of the steam generator.
- 請求項1~7のいずれか一項に記載の排熱回収システムと、
該排熱回収システムに高沸点熱媒あるいは/及び水を供給すると共に、高沸点熱媒蒸気あるいは/及び水蒸気を排熱回収システムから回収し、高沸点熱媒蒸気あるいは/及び水蒸気を作動流体として動力を発生する動力発生部と
を具備するエネルギ供給システム。 An exhaust heat recovery system according to any one of claims 1 to 7,
While supplying the high boiling point heat medium or / and water to the exhaust heat recovery system, the high boiling point heat medium vapor or / and water vapor is recovered from the exhaust heat recovery system, and the high boiling point heat medium vapor or / and water vapor is used as the working fluid. An energy supply system comprising a power generation unit that generates power. - 動力発生部は、動力の発生に供された後の高沸点熱媒蒸気と水とを熱交換して高沸点熱媒蒸気を凝縮液化すると共に水蒸気を発生させる熱交換器を備える請求項8記載のエネルギ供給システム。 The power generation unit includes a heat exchanger that heat-exchanges the high-boiling-point heat medium vapor and water after being used for generating power to condense and liquefy the high-boiling-point heat medium steam and generate water vapor. Energy supply system.
- 水よりも蒸発温度が高い高沸点熱媒を排熱によって気化させて熱回収する排熱回収方法。 An exhaust heat recovery method for recovering heat by evaporating a high boiling point heat medium having a higher evaporation temperature than water by exhaust heat.
- 高沸点熱媒による熱回収後の排熱により水を気化させて熱回収する請求項10記載の排熱回収方法。 The exhaust heat recovery method according to claim 10, wherein water is vaporized by exhaust heat after heat recovery by a high boiling point heat medium to recover heat.
- 排熱との熱交換により高沸点熱媒蒸気あるいは/及び水蒸気を過熱する請求項10または11記載の排熱回収方法。 The exhaust heat recovery method according to claim 10 or 11, wherein the high boiling point heat medium steam and / or steam is superheated by heat exchange with the exhaust heat.
- 高沸点熱媒は、エチレングリコール、ジエチレングリコール、プロピレングリコール、プロピレンエチレングリコールあるいはホルムアミドである請求項10~12のいずれか一項に記載の排熱回収方法。 The exhaust heat recovery method according to any one of claims 10 to 12, wherein the high boiling point heat medium is ethylene glycol, diethylene glycol, propylene glycol, propylene ethylene glycol or formamide.
- 高沸点熱媒による熱回収後の排熱により水を気化させて熱回収することに代えて、高沸点熱媒による熱回収後の排熱により水を予熱し、当該予熱された水をフラッシュ現象によって気化させて熱回収する請求項11~13のいずれか一項に記載の排熱回収方法。 Instead of vaporizing water by exhaust heat after heat recovery with a high boiling point heat medium and recovering heat, water is preheated with exhaust heat after heat recovery with a high boiling point heat medium, and the preheated water is flushed The exhaust heat recovery method according to any one of claims 11 to 13, wherein the heat recovery is carried out by vaporization by the method.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/576,273 US20120297774A1 (en) | 2010-02-19 | 2011-02-17 | Exhaust heat recovery system, energy supply system, and exhaust heat recovery method |
DE112011100603T DE112011100603T5 (en) | 2010-02-19 | 2011-02-17 | Exhaust heat recovery system, energy supply system and exhaust heat recovery process |
JP2012500639A JP5062380B2 (en) | 2010-02-19 | 2011-02-17 | Waste heat recovery system and energy supply system |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010034776 | 2010-02-19 | ||
JP2010-034776 | 2010-02-19 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011102408A1 true WO2011102408A1 (en) | 2011-08-25 |
Family
ID=44482994
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2011/053352 WO2011102408A1 (en) | 2010-02-19 | 2011-02-17 | Exhaust heat recovery system, energy supply system, and exhaust heat recovery method |
Country Status (4)
Country | Link |
---|---|
US (1) | US20120297774A1 (en) |
JP (2) | JP5062380B2 (en) |
DE (1) | DE112011100603T5 (en) |
WO (1) | WO2011102408A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9604864B2 (en) | 2013-03-12 | 2017-03-28 | Ingenica Ingenierie Industrielle | Steam generation method and method for recovering crude oil by steam-assisted gravity drainage (SAGD) including said steam generation method |
US10054308B2 (en) | 2014-09-11 | 2018-08-21 | Ingenica Ingenierie Industrielle | Method for generating steam from raw water, in particular from blow down water coming from a steam generator |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2199547A1 (en) * | 2008-12-19 | 2010-06-23 | Siemens Aktiengesellschaft | Heat steam producer and method for improved operation of same |
KR20150086246A (en) | 2012-11-22 | 2015-07-27 | 시게카즈 우지 | Device for recovering volatile organic compound |
US9587520B2 (en) | 2013-05-30 | 2017-03-07 | General Electric Company | System and method of waste heat recovery |
US9145795B2 (en) * | 2013-05-30 | 2015-09-29 | General Electric Company | System and method of waste heat recovery |
US9593597B2 (en) | 2013-05-30 | 2017-03-14 | General Electric Company | System and method of waste heat recovery |
DE102013012179A1 (en) * | 2013-07-22 | 2015-01-22 | Rmb/Energie Gmbh | Device for utilizing combustion heat |
JP2015025422A (en) | 2013-07-26 | 2015-02-05 | 株式会社Ihi | Feed water for boiler preheating system and feed water for boiler preheating method |
DE102015208360A1 (en) * | 2015-05-06 | 2016-11-10 | Bayerische Motoren Werke Aktiengesellschaft | motor vehicle |
US20170314422A1 (en) * | 2016-04-27 | 2017-11-02 | Tao Song | Engine Exhaust and Cooling System for Power Production |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01150763A (en) * | 1987-12-08 | 1989-06-13 | Babcock Hitachi Kk | Waste heat recovery chilling unit |
JPH06146815A (en) * | 1992-11-09 | 1994-05-27 | Mitsubishi Heavy Ind Ltd | Gas turbine composite power generator |
JPH0893414A (en) * | 1994-09-27 | 1996-04-09 | 忠幸 ▲吉▼田 | Mercury utilizing generator |
JPH09303111A (en) * | 1996-05-17 | 1997-11-25 | Hiroyuki Dan | Warm drain water generating system |
JP2002161716A (en) * | 2000-11-29 | 2002-06-07 | Yanmar Diesel Engine Co Ltd | Heat recovery rankine cycle system and heat recovery method |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3817038A (en) * | 1972-09-01 | 1974-06-18 | Texaco Development Corp | Method for heating a fluid |
US4070862A (en) * | 1976-09-24 | 1978-01-31 | E. I. Du Pont De Nemours And Company | Cascaded two-fluid rotary closed Rankine cycle engine |
JPS5968504A (en) * | 1982-10-13 | 1984-04-18 | Hitachi Ltd | Heat recovery system of gas turbine cooling medium |
JP4459325B2 (en) | 1999-06-04 | 2010-04-28 | バブコック日立株式会社 | Double pressure vertical natural circulation exhaust heat recovery boiler |
JP2001027131A (en) * | 1999-07-16 | 2001-01-30 | Ishikawajima Harima Heavy Ind Co Ltd | Multiple pressure steam injection type partial regenerative cycle gas turbine |
JP2002021583A (en) | 2000-06-30 | 2002-01-23 | Toshiba Corp | Combined cycle power generating plant |
JP2003021302A (en) | 2001-07-09 | 2003-01-24 | Ishikawajima Harima Heavy Ind Co Ltd | Bypass damper for exhaust heat recovery boiler employed in cogeneration facility |
JP4666641B2 (en) * | 2006-06-16 | 2011-04-06 | 株式会社日立製作所 | Energy supply system, energy supply method, and energy supply system remodeling method |
JP2008267341A (en) | 2007-04-24 | 2008-11-06 | Toshiba Corp | Exhaust heat recovering device |
JP5168011B2 (en) | 2008-07-28 | 2013-03-21 | 株式会社村田製作所 | Non-reciprocal circuit element |
-
2011
- 2011-02-17 JP JP2012500639A patent/JP5062380B2/en active Active
- 2011-02-17 US US13/576,273 patent/US20120297774A1/en not_active Abandoned
- 2011-02-17 WO PCT/JP2011/053352 patent/WO2011102408A1/en active Application Filing
- 2011-02-17 DE DE112011100603T patent/DE112011100603T5/en not_active Ceased
-
2012
- 2012-06-07 JP JP2012129895A patent/JP5459353B2/en active Active
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01150763A (en) * | 1987-12-08 | 1989-06-13 | Babcock Hitachi Kk | Waste heat recovery chilling unit |
JPH06146815A (en) * | 1992-11-09 | 1994-05-27 | Mitsubishi Heavy Ind Ltd | Gas turbine composite power generator |
JPH0893414A (en) * | 1994-09-27 | 1996-04-09 | 忠幸 ▲吉▼田 | Mercury utilizing generator |
JPH09303111A (en) * | 1996-05-17 | 1997-11-25 | Hiroyuki Dan | Warm drain water generating system |
JP2002161716A (en) * | 2000-11-29 | 2002-06-07 | Yanmar Diesel Engine Co Ltd | Heat recovery rankine cycle system and heat recovery method |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9604864B2 (en) | 2013-03-12 | 2017-03-28 | Ingenica Ingenierie Industrielle | Steam generation method and method for recovering crude oil by steam-assisted gravity drainage (SAGD) including said steam generation method |
US10054308B2 (en) | 2014-09-11 | 2018-08-21 | Ingenica Ingenierie Industrielle | Method for generating steam from raw water, in particular from blow down water coming from a steam generator |
Also Published As
Publication number | Publication date |
---|---|
JPWO2011102408A1 (en) | 2013-06-17 |
US20120297774A1 (en) | 2012-11-29 |
JP2012198018A (en) | 2012-10-18 |
DE112011100603T5 (en) | 2013-01-31 |
JP5062380B2 (en) | 2012-10-31 |
JP5459353B2 (en) | 2014-04-02 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5062380B2 (en) | Waste heat recovery system and energy supply system | |
JP7173245B2 (en) | power generation system | |
TW449642B (en) | Method of heating gas turbine fuel in a combined cycle power plant using multi-component flow mixtures | |
JP4838318B2 (en) | Power generation method and power plant | |
US8181463B2 (en) | Direct heating organic Rankine cycle | |
US9410535B2 (en) | Binary power generation system | |
US20060260314A1 (en) | Method and system integrating combined cycle power plant with a solar rankine power plant | |
US6216436B1 (en) | Integrated gasification combined cycle power plant with kalina bottoming cycle | |
JP5674922B2 (en) | Energy recovery and steam supply for increased power output in combined cycle power systems | |
US9341086B2 (en) | Cascaded power plant using low and medium temperature source fluid | |
US9784248B2 (en) | Cascaded power plant using low and medium temperature source fluid | |
US5007240A (en) | Hybrid Rankine cycle system | |
JP2000257407A (en) | Improved bottoming cycle for cooling air around inlet of gas-turbine combined cycle plant | |
JP2009221961A (en) | Binary power generating system | |
JP2008101521A (en) | Power generation system by exhaust heat | |
JP2010230001A (en) | Split flow regenerative power cycle | |
EP3458688B1 (en) | Cogenerative organic rankine cycle system | |
WO2018143171A1 (en) | Heat cycle facility | |
JP2010038160A (en) | System and method for use in combined or rankine cycle power plant | |
JP2001248409A (en) | Exhaust heat recovery system | |
JP4509453B2 (en) | Integrated gasification combined cycle power plant with carina bottoming cycle | |
JP3059124B2 (en) | Hydrogen combustion turbine plant | |
EP3757359A1 (en) | Parallel regenerative cycle in organic rankine cycle with convective heat source | |
JP2004060507A (en) | Combined power generating plant | |
CA3226671A1 (en) | Heat recovery in a lng plant |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 11744694 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2012500639 Country of ref document: JP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 13576273 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 112011100603 Country of ref document: DE Ref document number: 1120111006039 Country of ref document: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 11744694 Country of ref document: EP Kind code of ref document: A1 |