[go: up one dir, main page]

US20180292085A1 - Combustion gas supply system - Google Patents

Combustion gas supply system Download PDF

Info

Publication number
US20180292085A1
US20180292085A1 US16/006,961 US201816006961A US2018292085A1 US 20180292085 A1 US20180292085 A1 US 20180292085A1 US 201816006961 A US201816006961 A US 201816006961A US 2018292085 A1 US2018292085 A1 US 2018292085A1
Authority
US
United States
Prior art keywords
gas
combustion gas
compressor
compressed air
fuel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US16/006,961
Other languages
English (en)
Inventor
Hideshi SHIBUYA
Akihisa YANO
Tatsuya Oka
Takahito AKITA
Taiga YAMAMOTO
Yushi KAMEOKA
Yusuke Takeuchi
Koki YASUI
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IHI Corp
Original Assignee
IHI Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by IHI Corp filed Critical IHI Corp
Assigned to IHI CORPORATION reassignment IHI CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AKITA, TAKAHITO, KAMEOKA, YUSHI, OKA, TATSUYA, SHIBUYA, HIDESHI, TAKEUCHI, YUSUKE, YAMAMOTO, TAIGA, YANO, Akihisa, YASUI, KOKI
Publication of US20180292085A1 publication Critical patent/US20180292085A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C9/00—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber
    • F23C9/06—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber for completing combustion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C7/00—Combustion apparatus characterised by arrangements for air supply
    • F23C7/008—Flow control devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J15/00—Arrangements of devices for treating smoke or fumes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23K—FEEDING FUEL TO COMBUSTION APPARATUS
    • F23K5/00—Feeding or distributing other fuel to combustion apparatus
    • F23K5/002—Gaseous fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L7/00—Supplying non-combustible liquids or gases, other than air, to the fire, e.g. oxygen, steam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C2202/00—Fluegas recirculation
    • F23C2202/30—Premixing fluegas with combustion air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C2202/00—Fluegas recirculation
    • F23C2202/50—Control of recirculation rate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J15/00—Arrangements of devices for treating smoke or fumes
    • F23J15/06—Arrangements of devices for treating smoke or fumes of coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L15/00—Heating of air supplied for combustion
    • F23L15/04—Arrangements of recuperators
    • 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
    • Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery

Definitions

  • the present disclosure relates to a combustion gas supply system that supplies, as a heat source, a combustion gas generated by combusting a fuel.
  • Combustion gases generated by combusting fuels have been utilized by various kinds of instruments and equipment as energy sources that supply thermal energy or power energy.
  • a combustion gas is utilized as a power source, and the flow pressure of the combustion gas is converted into drive power or electric power.
  • a combustion gas is used as a heat source, and the thermal energy of the combustion gas is transferred via heat exchange to a target substance to thereby heat the target substance, cause a change in its state (such as vaporization), cause a chemical reaction to progress, and so on.
  • a combustor which generates a combustion gas adds a fuel to air to be used as an oxygen source and combusts them.
  • the combustion efficiency is enhanced by compressing air, supplying it to the combustor, and combusting the fuel in the compressed air, and then a high-temperature pressurized combustion gas is generated.
  • Publication Document 1 Japanese Utility Model Registration No. 3179432
  • the amount of heat that the combustion gas can supply is dependent on the conditions of the combustion in the combustor, the combustion conditions of the combustor can be adjusted so as to supply a desired amount of heat from the combustion gas by adjusting the amount of compressed air to be supplied to the combustor.
  • the power consumption of an air compressor is large. In other words, reducing the power consumption associated with air compressors is an important issue for energy saving. In view of this, a technical improvement is needed which can freely adjust the amount of compressed air to be supplied to adjust the combustion conditions of the combustor, while also suppressing increase in power consumption.
  • the present disclosure solves such a problem, and an object thereof is to provide a combustion gas supply system capable of increasing the amount of compressed air to be supplied as necessary to supply a combustion gas in a preferable manner, while also suppressing increase in power consumption.
  • the present inventors have conducted an earnest research on addition of a compressor and power use, and discovered a simple configuration capable of suppressing increase in energy consumption by utilizing a used gas after being used as a heat source. As a result, the present inventors have reached the technique of the present disclosure.
  • a combustion gas supply system is summarized as including: an air compressor that supplies compressed air; a fuel supply device that supplies a fuel; a combustor that generates a pressurized combustion gas by combusting the fuel supplied by the fuel supply device and the compressed air supplied by the air compressor; a gas supply and recovery section that supplies the pressurized combustion gas generated by the combustor to a heat consumption apparatus and recovers, as a used gas, the pressurized combustion gas whose heat has been consumed; and a re-pressurizing compressor that supplementarily compresses a part of the used gas recovered by the gas supply and recovery section and supplies the part of the used gas to the compressed air supplied by the air compressor.
  • the re-pressurizing compressor may supplementarily compress the part of the used gas so as to pressurize the part of the used gas to a same pressure as a pressure of the compressed air, and a remaining part of the used gas may be discharged to an outside.
  • the combustion gas supply system may further include a cooler that cools the part of the used gas, and a condensation separator that separates moisture condensed by the cooling, from the part of the used gas, wherein the re-pressurizing compressor may supplementarily compress the part of the used gas from which moisture has been removed by the condensation separator. This is suitable in view of reusing in combustion.
  • combustion gas supply system may further include a heat exchanger that causes the part of the used gas, before being cooled by the cooler, to exchange heat with the part of the used gas supplementarily compressed by the re-pressurizing compressor. This is suitable in view of thermal efficiency.
  • the combustion gas supply system may be configured such that it further includes a flow rate adjustment valve that adjusts a flow rate of the compressed air supplied by the air compressor, and a proportion of the compressed air supplied by the air compressor and the part of the used gas supplied by the re-pressurizing compressor may be adjusted by using the flow rate adjustment valve. In this way, the combustion conditions can be adjusted in a preferable manner.
  • the combustion gas supply system may be configured such that it further includes an oxygen concentration meter that detects an oxygen concentration of the compressed air to which the part of the used gas has been supplied by the re-pressurizing compressor, wherein the flow rate adjustment valve is controlled based on a detection value of the oxygen concentration meter.
  • the fuel supply device may include a fuel compressor and supply a compressed fuel pressurized to a same pressure as a pressure of the compressed air.
  • reusing the used gas after the heat is consumed makes it possible to reduce the mechanical power of the compressor for the system as a whole, by effectively utilizing the residual pressure. It is therefore possible to provide a combustion gas supply system capable of adjusting the combustion conditions in a preferable manner and saving energy.
  • FIG. 1 is a schematic diagram illustrating the configuration of a combustion gas supply system according to one embodiment of the present disclosure.
  • the compression ratio (pressure ratio) of a compressor can be set to a low ratio, it is possible to reduce the power consumption of the compressor. In other words, if the pressure of the air introduced to the compressor is high, it is possible to obtain compressed air at the target pressure while also reducing the power consumption.
  • a used gas that is a combustion gas after being used as a heat source is suitable to be re-pressurized by a low-compression ratio compressor and used if it is collected as is without releasing its pressure.
  • a combustion gas as a heat source as in a boiler, a reactor, or the like
  • decrease in pressure of the supplied combustion gas causes lowering its temperature, which is not preferable as a heat source.
  • an apparatus that consumes the heat hereinafter, referred to as heat consumption apparatus is configured such that the pressure of a combustion gas therein is maintained while heat is supplied from the combustion gas.
  • the pressure of a high-temperature pressurized combustion gas generated using compressed air in order to enhance the combustion efficiency is maintained inside the heat consumption apparatus, and the used gas discharged is a waste gas in a pressurized state such that the pressure of the unused combustion gas is substantially maintained excluding the pressure drop due to the resistance to flow and the like. Then, re-pressurizing and using this as a component of compressed air is very effective in reducing the power consumption of the compressor for the system as a whole. Also, although the oxygen content of the combustion gas decreases as a result of the consumption of oxygen in the combustion, the oxygen concentration is only about a half of that of air. Hence, by being mixed with normal air, the used gas can be utilized as compressed air to a satisfactory extent.
  • a used gas after being used as a heat source is recovered with its pressure maintained, compressed by a re-pressurizing compressor so as to regain a pressure equivalent to the pressure of the compressed air, and supplied to a combustor as supplementary compressed air.
  • the electric power consumed by the re-pressurizing compressor is such electric power that is required to compensate for the pressure of the combustion gas lost in the course of supplying the heat therein as a heat source.
  • the present disclosure can provide a combustion gas supply system capable of suppressing increase in cost due to increased supply of compressed air by efficiently recovering energy from the used gas being a combustion gas after being used as a heat source, and also of freely adjusting the combustion conditions via supply of compressed air so that a combustion gas suitable for the intended use can be supplied.
  • FIG. 1 illustrates a combustion gas supply system according to one embodiment of the present disclosure.
  • a combustion gas supply system 1 is a system that supplies a pressurized combustion gas generated by combusting compressed air containing a fuel, to a heat consumption apparatus C 1 .
  • the heat consumption apparatus C 1 is an apparatus having a heat exchange function that utilizes the combustion gas as a heat source and transfer the heat in the combustion gas to a target substance, and it consumes the heat in the supplied pressurized combustion gas and discharges, as a used gas, the pressurized combustion gas after the heat therein is consumed.
  • Examples of the heat consumption apparatus C 1 include apparatuses that heat a target substance or cause a change in its state (such as vaporization) by heating, such as a steam generator, a hot water generator, a thermic fluid heater, an air heater, and a hot gas generator, as well as reactors that heat a target substance to cause a chemical reaction therein to progress.
  • the heat consumption apparatus C 1 may also be a reactor using a catalyst containing an active metal such as Ni, Co, Fe, Pt, Ru, Rh, or Pd as its component.
  • the kind of target substance to be heated and the purpose of the heating vary depending on the intended use of the heat consumption apparatus C 1 , and the temperature of the combustion gas and the flow rate at which it is supplied are appropriately adjusted in accordance with them.
  • the combustion gas supply system 1 has an air compressor 3 , a fuel supply device 5 , a combustor 7 , a gas supply and recovery section 9 , and a re-pressurizing compressor 11 .
  • the air compressor 3 compresses air and supplies the compressed air to the combustor 7 through a flow channel L 1 .
  • the fuel supply device 5 supplies a fuel into the compressed air through a flow channel L 2 .
  • the combustor 7 receives the fuel and the compressed air supplied by the air compressor 3 and the fuel supply device 5 and combusts them to thereby generate a pressurized combustion gas.
  • the fuel supply device 5 includes a fuel source 5 a and a fuel compressor 5 b.
  • a gaseous fuel supplied from the fuel source 5 a is pressurized and compressed by the fuel compressor 5 b, supplied at substantially the same pressure as the compressed air from the flow channel L 2 , and added to and mixed with the compressed air in the flow channel L 1 .
  • the fuel source 5 a may be the fuel contained in a fuel container or may be such that supplies the fuel through a connection line by using an external fuel supply system as a supply source.
  • the fuel compressor 5 b can be omitted in a case where the fuel source is a fuel contained in a container such as a pressurized cylinder or the like having a pressure adjuster that can adjust the extraction pressure of the fuel such as a pressure adjustment valve.
  • the pressurized combustion gas in the combustor 7 is supplied to the heat consumption apparatus C 1 from a flow channel L 3 through the gas supply and recovery section 9 , and the pressurized combustion gas that the heat therein has been consumed is recovered as a used gas from the heat consumption apparatus C 1 .
  • the gas supply and recovery section 9 includes a supply connection member 9 a at an end of the flow channel L 3 and a recovery connection member 9 b at an end of a flow channel L 4 . They can connect the flow channels L 3 , L 4 and the heat consumption apparatus C 1 in a detachable manner and thereby allow the combustion gas supply system 1 and the heat consumption apparatus C 1 to communicate with each other without a pressure loss.
  • the pressurized combustion gas generated by the combustor 7 is supplied to the heat consumption apparatus C 1 from the flow channel L 3 through the gas supply and recovery section 9 while maintaining its pressure, and the pressurized combustion gas after the heat therein is consumed (used gas) is caused to flow back from the heat consumption apparatus C 1 into the flow channel L 4 while maintaining substantially its pressure excluding the pressure loss due to the flow resistance therein.
  • the used gas (waste gas in a pressurized state) collected by the gas supply and recovery section 9 is discharged to the outside from the flow channel L 4 through a flow channel L 5 .
  • a pressure meter 13 is provided on the flow channel L 4 , and a pressure adjustment valve 15 on the flow channel L 5 is controlled based on its detection value, and the discharge of the used gas to the outside is controlled so as to maintain the pressure inside the combustion gas supply system 1 at a predetermined pressure.
  • the pressure meter 13 of the flow channel L 4 detects the pressure of the used gas, which is lower than the pressure of the pressurized combustion gas by the pressure loss. Hence, a pressure taking the pressure loss into account is set as the predetermined pressure.
  • the pressure meter 13 may be provided to the flow channel L 3 and the predetermined pressure in that case is set to the pressure of the pressurized combustion gas.
  • Air contains oxygen by about 20 vol %.
  • compressed air with an oxygen concentration lower than this can still be used for combustion, and therefore a mixture of compressed air and the used gas can be combusted.
  • flow channels L 6 to L 9 are provided as a route branching from the flow channel L 4 and joining to the flow channel L 1 , and a part of the used gas recovered by the gas supply and recovery section 9 is supplied from the flow channel L 9 into the flow channel L 1 and reused for combustion, whereas the remaining part is discharge to the outside. It is note that the pressure of the used gas recovered from the heat consumption apparatus C 1 drops due to the resistance to flow.
  • the lost pressure of the used gas recovered from the flow channel L 4 is compensated for by the re-pressurizing compressor 11 , so that the used gas with its pressure raised to be equivalent to that of the compressed air is supplied to and mixed with the compressed air.
  • the used gas with a compensated pressure is supplied to the combustor 7 together with the compressed air as a mixture gas. Since the oxygen concentration of the compressed air to be supplied to the combustor 7 has a suitable range in view of combustion efficiency, the mixing ratio of the compressed air and the used gas has an appropriate range.
  • the flow channel L 1 there are installed an oxygen concentration meter 17 that detects the oxygen concentration of the mixture gas to be supplied to the combustor 7 , and a flowmeter 3 a and a flow rate adjustment valve 3 b which are electrically connected thereto in order to adjust the mixing ratio.
  • the flow rate adjustment valve 3 b is a valve controlled in accordance with the detection value of the flowmeter 3 a.
  • the flow rate of the compressed air in the flow channel L 1 is adjusted by controlling the flow rate adjustment valve 3 b based on the value of the oxygen concentration of the mixture gas detected by the oxygen concentration meter 17 such that the used gas and the compressed air are mixed in a ratio that provides an appropriate oxygen concentration.
  • the fuel supply device 5 includes a flowmeter 5 c and a flow rate adjustment valve 5 d on the flow channel L 2 .
  • the flowmeter 5 c and the flow rate adjustment valve 5 d are electrically connected to a temperature meter 19 which is installed on the flow channel L 3 to detect the temperature of the combustion gas.
  • the flow rate adjustment valve 5 d is controlled based on the temperature detected by the temperature meter 19 , and the flow rate of the compressed fuel is adjusted by the flow rate adjustment valve 5 d.
  • the temperature of the combustion gas is adjusted to the desired temperature.
  • a gas supply and recovery section 21 similar to the gas supply and recovery section 9 including a supply connection member 21 a and a recovery connection member 21 b, is provided on the flow channel L 6 and configured such that a different heat consumption apparatus C 2 that utilizes a heat source of lower temperature than the heat consumption apparatus C 1 can be connected.
  • the gas supply and recovery section 21 is optional, and it may be omitted or provided in series downstream of the gas supply and recovery section 9 on the flow channel L 4 .
  • the gas supply and recovery section 21 may be configured to be able to switch the connection between a state where the supply connection member 21 a and the recovery connection member 21 b are directly connected to each other and a state where they are connected to the heat consumption apparatus C 2 so that it is possible to arbitrarily select connection to the heat consumption apparatus C 2 or disconnection therefrom.
  • the combustion gas supply system 1 includes a heat exchanger 23 , a cooler 25 , and a condensation separator 27 , and moisture is removed from the used gas by gas-liquid separation utilizing cold condensation of water vapor.
  • the part of the recovered used gas is supplied from the flow channel L 6 to the cooler 25 on the flow channel L 7 and cooled down to such a temperature that the part of the collected used gas can be supplied to the re-pressurizing compressor 11 .
  • the part of the collected used gas is then supplied to the condensation separator 27 .
  • the moisture condensed from the water vapor by the cooling of the used gas is separated from the used gas at the condensation separator 27 and removed to the outside.
  • the used gas after removal of water vapor therefrom is introduced to the re-pressurizing compressor 11 from the condensation separator 27 through the flow channel L 8 to be supplementarily compressed, so that the lost pressure due to the resistance to flow is compensated for and the used gas is therefore pressurized to the same pressure as the pressure of the compressed air.
  • the heat exchanger 23 is provided upstream of the cooler 25 .
  • the used gas in the flow channel L 6 to be reused exchanges heat with the used gas in the flow channel L 8 supplementarily compressed by the re-pressurizing compressor 11 , at the heat exchanger 23 before being cooled by the cooler 25 .
  • the compressed used gas in the flow channel L 8 is lower in temperature than the used gas in the flow channel L 6 , and is heated at the heat exchanger 23 by receiving the residual heat of the used gas in the flow channel L 6 and its temperature therefore gets close to the temperature of the used gas in the flow channel L 6 . Consequently, the used gas dried and pressurized to the same pressure as the pressure of the compressed air flows through the flow channel L 9 at a temperature close to that at the time of the recovering from the heat consumption apparatus and joins to the compressed air in the flow channel L 1 . In other words, the residual heat of the used gas in the flow channel L 6 is effectively utilized as it is transferred to the supplementarily compressed used gas at the heat exchanger 23 .
  • An appropriate oxygen concentration of the compressed air to be supplied to the combustor 7 is preferably about 13 to 14 vol % in view of energy saving. Since the oxygen concentration of air is about 20 vol %, the used gas to be reused is preferably mixed so that its ratio (volume ratio) to the compressed air is about 1.5 to 1.8. Here, the proportion in volume of the compressed air in the mixture gas to be supplied to the combustor 7 is about 35 to 40% while the proportion in volume of the used gas is about 60 to 65%. Thus, in a state where the combustion gas supply system 1 of the present disclosure is in steady operation, about 60 to 65% of the used gas collected from the heat consumption apparatus C 1 is reused, and the remaining part, which is about 35 to 40%, is discharged from the flow channel L 5 .
  • combustion gas supply system 1 in FIG. 1 may be configured such that an expander is provided on the flow channel L 5 to recover and reuse energy of the used gas discharged from the flow channel L 5 as mechanical power. This further improves the energy efficiency.
  • the combustor 7 is a pressurized combustor with pressure resistance capable of combusting a fuel in compressed air.
  • the combustor 7 may be of any combustion type among an ignition type and a catalytic combustion type as long as it generates a combustion air by utilizing a combustion reaction.
  • a catalytic combustion-type combustor is preferable in view of the stability of the combustion reaction and the like, and examples of the catalyst for the combustion include platinum-based catalysts and palladium-based catalysts.
  • the required temperature of the combustion gas and the required amount of the combustion gas to be supplied vary depending on the intended use and usage conditions of the combustion gas at the heat consumption apparatus C 1 , and a combustor having a supply capability and thermal resistance suitable for the intended use and usage conditions may be selected as appropriate and used.
  • the fuel used for the combustion is a flammable gas, i.e. a gas containing a flammable component such as carbon monoxide, hydrogen, or a hydrocarbon compound (such as methane).
  • the flammable component of the fuel may be either a single component or a mixture composition.
  • Gaseous fuels typically used for gas turbines and the like are preferably usable, and examples include fuels such as natural gases, coal gasification fuels, and biogases.
  • the heating value of the fuel per unit volume varies depending on the content of its flammable component, and the appropriate amount of compressed air to be supplied varies as well.
  • the air compressor 3 maybe any compressor that can be generally used for supplying combustion gas, and examples include a centrifugal compressor, an axial flow compressor, a reciprocating compressor, a diaphragm compressor, a twin-screw compressor, a single-screw compressor, a scroll compressor, and the like.
  • a compressor capable of compressing air in a compression ratio (pressure ratio) of about 2.9 to 20.7 is preferably usable as the air compressor 3 .
  • the fuel compressor 5 b may be any compressor that is capable of compressing the fuel gas to a pressure equivalent to the pressure of the compressed air, and one with a capacity corresponding to the flow rate at which the fuel is supplied is used.
  • the fuel compressor 5 b can be omitted in the case where the fuel is contained in a tank or the like including a pressure adjustment valve or the like.
  • the re-pressurizing compressor 11 performs the supplementary pressurization in order to compensate for the lost pressure and therefore its pressure ratio required is lower than that of the air compressor 3 .
  • the pressure loss caused by the flow resistance varies depending on the flow conditions in the heat consumption apparatuses C 1 , C 2 , but the pressure loss per apparatus can usually be predicted to be within the range of about 1.5 to 15% of the pressure at which the combustion gas is supplied (gauge pressure).
  • a compressor capable of compressing air in a pressure ratio of about 1.8 to 19.6 is preferably usable as the re-pressurizing compressor 11 .
  • a heat exchanger can be selected as appropriate from among typically used gas-gas heat exchangers and used as the heat exchanger 23 . Examples include a stationary heat exchanger, a rotary regenerative heat exchanger, and a periodic-flow regenerative heat exchanger, and the heat exchanger 23 may be any of these types.
  • the cooler 25 is actually a heat exchanger, and neither its cooling method nor type of coolant is limited.
  • the cooler 25 may be any one capable of lowering the temperature of the used gas to such a temperature that the used gas can be supplied to the re-pressurizing compressor 11 , and having durability against the pressure of the used gas.
  • a gas-liquid heat exchanger is preferable in view of the cooling efficiency and the like, and a typically used water-cooling cooler is preferably usable.
  • the condensation separator 27 can also be selected as appropriate from among typically used gas-liquid separators, and one having durability against the pressure of the used gas is used.
  • the combustion gas supply system 1 has been described above as a system capable of selecting and replacing the heat consumption apparatus as necessary. In a case where changing the heat consumption apparatus is not necessary, this embodiment can be understood as a combustion gas supply system in which supply and consumption of the heat in a combustion gas are performed integrally.
  • the combustion gas supply system 1 is understood as including the air compressor 3 , which supplies compressed air, the fuel supply device 5 , which supplies a fuel, the combustor 7 , which generates a pressurized combustion gas by combusting the fuel supplied by the fuel supply device and the compressed air supplied by the air compressor, the heat consumption apparatus C 1 , which consumes the heat in the pressurized combustion gas and discharges, as a used gas, the pressurized combustion gas after the heat therein is consumed, and the re-pressurizing compressor 11 , which supplementarily pressurizes a part of the used gas discharged from the heat consumption apparatus and supplies it into the compressed air supplied by the air compressor.
  • the air compressor 3 which supplies compressed air
  • the fuel supply device 5 which supplies a fuel
  • the combustor 7 which generates a pressurized combustion gas by combusting the fuel supplied by the fuel supply device and the compressed air supplied by the air compressor
  • the heat consumption apparatus C 1 which consumes the heat in the pressurized combustion gas and discharges, as
  • the gas supply and recovery section 9 which enables attachment and detachment of the heat consumption apparatus, can be omitted, and the heat consumption apparatus C 1 may be directly connected to the flow channels L 3 , L 4 .
  • the heat consumption apparatus C 2 and the gas supply and recovery section 21 can be directly connected to the flow channels L 3 , L 4 .
  • a steady state in which the operation is stabilized by adjusting the mixture ratio of the used gas and the compressed air and the amount of the fuel to be supplied is as follows, for example.
  • the flow rate of the fuel is adjusted such that a combustion gas at a temperature of about 800 to 900° C., a pressure of about 1.7 to 2.0 MPaG, and an oxygen concentration of about 8 to 10 vol % is supplied from the combustor 7 to the heat consumption apparatus C 1 .
  • the pressure of the used gas recovered from the heat consumption apparatus C 1 usually drops to about 1.6 to 1.9 MPaG and its temperature is about 500 to 600° C.
  • a part of the used gas is subjected to the secondary use at the heat consumption apparatus C 2 and the heat therein is consumed, so that the temperature drops to about 450 to 550° C. and the pressure drops to about 1.5 to 1.8 MPaG.
  • This used gas can be cooled to about 120 to 145° C. at the heat exchanger 23 via heat exchange with the used gas from which moisture has been removed.
  • the used gas is further cooled to about 70 to 90° C. at the cooler 25 , so that condensate water is separated from the used gas.
  • the used gas dried by the gas-liquid separation at the condensation separator 27 is compressed to a pressure of about 1.8 to 2.1 MPaG by the re-pressurizing compressor 11 , and its temperature rises to about 90 to 110° C.
  • This compressed used gas is heated at the heat exchanger 23 , so that its temperature gets close to the temperature of the used gas having passed through the heat consumption apparatus C 2 .
  • a dried and compressed used gas at a temperature of about 480 to 580° C., a pressure of about 1.8 to 2.1 MPaG, and an oxygen concentration of about 8 to 10 vol % is obtained.
  • This used gas is mixed with compressed air at a temperature of about 150 to 170° C., a pressure of about 1.8 to 2.1 MPaG, and an oxygen concentration of 17 to 19 vol % supplied from the air compressor 3 and the fuel (used gas: 60 to 65 vol %, compressed air: 35 to 40 vol %).
  • a mixture gas at a pressure of about 1.8 to 2.1 MPaG and an oxygen concentration of about 11 to 15 vol % is prepared at a temperature of about 140 to 180° C.
  • This is supplied to the combustor 7 to generate a combustion gas similar to the above.
  • the amount of the remaining part of the used gas, which is discharged to the outside from the flow channel L 4 through the flow channel L 5 without being reused, corresponds to the amount of compressed air supplied by the air compressor 3 .
  • combustion gas supply system 1 in FIG. 1 One embodiment of operation of the combustion gas supply system 1 in FIG. 1 will be described below via a simulation based on an exemplary case where a combustion gas is utilized to cause a chemical reaction to progress in a reaction apparatus by heating at a temperature of about 800° C.
  • the reaction apparatus is connected to the gas supply and recovery section 9 as the heat consumption apparatus C 1
  • a relatively small steam generator for secondary use of the residual heat therein is connected to the gas supply and recovery section 21 as the heat consumption apparatus C 2 .
  • a compressed fuel is added from the fuel supply device 5 to a compressed air supplied from the air compressor 3 at a pressure of 1.95 MPaG and a temperature of 161° C. (oxygen concentration: 17.9 vol %) and supplied to and combusted in the combustor 7 , while the amount of the fuel to be supplied is adjusted such that the temperature of the combustion gas to be discharged from the combustor 7 will be 800° C. or higher.
  • a combustion gas at a temperature of 875° C., a pressure of 1.82 MPaG, and an oxygen concentration of 9.52 vol % is supplied to the heat consumption apparatus C 1 , and a used gas at a temperature of 576° C., a pressure of 1.74 MPaG, and an oxygen concentration of 9.52 vol %, is recovered from the heat consumption apparatus C 1 .
  • the used gas at a temperature of 556° C., a pressure of 1.71 MPaG, and an oxygen concentration of 9.52 vol % is cooled to 136° C. at the heat exchanger 23 and further cooled to 80° C. by the cooler 25 .
  • Condensate water is removed from this used gas by the condensation separator 27 , so that it has a temperature of 80° C., a pressure of 1.65 MPaG, and an oxygen concentration of 9.93 vol %.
  • This used gas is compressed in a pressure ratio of 1.2 by the re-pressurizing compressor 11 , so that a dried and compressed used gas at a temperature of 103° C. and a pressure of 1.98 MPaG is supplied to the heat exchanger 23 .
  • the dried and compressed used gas flowing out from the heat exchanger 23 is at a temperature of 546° C., a pressure of 1.95 MPaG, and an oxygen concentration of 9.93 vol %, and is mixed with the compressed air supplied from the air compressor 3 and the fuel.
  • the control on the flow rate adjustment valve 3 b based on the oxygen concentration meter 17 is initiated, thereby adjusting the flow rate of the compressed air such that the oxygen concentration of the mixture gas will be 13 vol %.
  • the proportions of the used gas and the compressed air occupying the mixture gas will be 61.5% and 38.5%, respectively.
  • the flow rate of the compressed air supplied from the air compressor 3 decreases and then becomes constant.
  • the used gas starts being discharged to the outside from the flow channel L 5 , and its proportion comes to 38.5%.
  • the combustion gas supply system of the present disclosure is a system capable of supplying a combustion gas while appropriately adjusting its temperature and supply amount, and is therefore capable of stably supplying a high-temperature combustion gas as a heat source.
  • the combustion gas supply system of the present disclosure is therefore particularly useful in cases where the heat consumption apparatuses are reaction apparatuses that perform chemical syntheses with various thermal reactions (endothermic reactions) or processing apparatuses that perform processes in which it is important to suppress alteration by means of temperature control when melting or fusion of a substance is caused to progress.
  • the reaction apparatuses include reactors that perform syntheses utilizing various thermal decomposition reactions such as steam reforming reaction of methane, dry reforming reaction of methane, and reforming reaction of methanol.
  • the heat consumption apparatuses are preferably apparatuses that utilize the supplied combustion gas only as a heat source and do not directly utilize the combustion gas as a mechanical power source. It is of course not problematic if mechanical power, electric power, or the like is indirectly generated from the heat obtained from the heat source.
  • the technique of the present disclosure by applying it to a system that supplies a combustion gas, can contribute to reduction of the amount of used gas discharged and reduction of power consumption. Through various chemical reactions and processes using the combustion gas as a heat source, the technique of the present disclosure can also contribute to stable supply of target reaction products and processed products and reduction of the production costs.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Air Supply (AREA)
  • Chimneys And Flues (AREA)
US16/006,961 2016-01-25 2018-06-13 Combustion gas supply system Abandoned US20180292085A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2016-011368 2016-01-25
JP2016011368A JP6657996B2 (ja) 2016-01-25 2016-01-25 燃焼ガス供給システム
PCT/JP2017/001153 WO2017130758A1 (ja) 2016-01-25 2017-01-16 燃焼ガス供給システム

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2017/001153 Continuation WO2017130758A1 (ja) 2016-01-25 2017-01-16 燃焼ガス供給システム

Publications (1)

Publication Number Publication Date
US20180292085A1 true US20180292085A1 (en) 2018-10-11

Family

ID=59398713

Family Applications (1)

Application Number Title Priority Date Filing Date
US16/006,961 Abandoned US20180292085A1 (en) 2016-01-25 2018-06-13 Combustion gas supply system

Country Status (8)

Country Link
US (1) US20180292085A1 (zh)
EP (1) EP3410013B1 (zh)
JP (1) JP6657996B2 (zh)
CN (1) CN108474555B (zh)
CA (1) CA3010257C (zh)
DK (1) DK3410013T3 (zh)
TW (1) TWI629411B (zh)
WO (1) WO2017130758A1 (zh)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6483909B1 (ja) * 2018-08-29 2019-03-13 ユニ・チャーム株式会社 吸収性物品

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4030874A (en) * 1975-12-15 1977-06-21 Battelle Memorial Institute Method of and apparatus for controlling combustion
US4854381A (en) * 1988-04-11 1989-08-08 Paul Mikula Heat exchanger device
US5051040A (en) * 1987-09-07 1991-09-24 L. & C. Steinmuller Gmbh Fluidized bed combustion system that is controllable under pressure
US5297729A (en) * 1992-08-28 1994-03-29 Combustion Concepts, Inc. Furnace apparatus
US6237339B1 (en) * 1997-06-06 2001-05-29 Norsk Hydro Asa Process for generating power and/or heat comprising a mixed conducting membrane reactor
US20030172656A1 (en) * 2002-03-12 2003-09-18 Jacques Labasque Method of operating a heat recovery boiler
US20140069307A1 (en) * 2011-07-13 2014-03-13 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Method for operating pulverized-coal-fired boiler facility

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3089151B2 (ja) * 1993-11-25 2000-09-18 三菱重工業株式会社 高圧噴霧燃焼装置
NO308400B1 (no) * 1997-06-06 2000-09-11 Norsk Hydro As Kraftgenereringsprosess omfattende en forbrenningsprosess
JP4629950B2 (ja) * 2002-08-05 2011-02-09 財団法人電力中央研究所 溶融炭酸塩形燃料電池発電システム及びこの発電システムにおける発電方法
EP1592867B1 (en) * 2003-02-11 2016-11-23 Statoil ASA Efficient combined cycle power plant with co2 capture and a combustor arrangement with separate flows
DE10325111A1 (de) * 2003-06-02 2005-01-05 Alstom Technology Ltd Verfahren zur Erzeugung von Energie in einer eine Gasturbine umfassende Energieerzeugungsanlage sowie Energieerzeugungsanlage zur Durchführung des Verfahrens
US7726114B2 (en) * 2005-12-07 2010-06-01 General Electric Company Integrated combustor-heat exchanger and systems for power generation using the same
US9297306B2 (en) * 2008-09-11 2016-03-29 General Electric Company Exhaust gas recirculation system, turbomachine system having the exhaust gas recirculation system and exhaust gas recirculation control method
US20110223501A1 (en) * 2008-11-18 2011-09-15 Tokyo Gas Co., Ltd. Hydrogen-recycling mcfc power-generating system
JP5517508B2 (ja) * 2009-07-06 2014-06-11 三菱重工業株式会社 燃料電池
JP2012007213A (ja) * 2010-06-25 2012-01-12 Mitsubishi Heavy Ind Ltd 直接還元製鉄法およびそのための還元ガス製造装置
PL2588727T3 (pl) * 2010-07-02 2019-05-31 Exxonmobil Upstream Res Co Spalanie stechiometryczne z recyrkulacją gazów spalinowych i chłodnicą bezpośredniego kontaktu
TWI593872B (zh) * 2011-03-22 2017-08-01 艾克頌美孚上游研究公司 整合系統及產生動力之方法
TWI563164B (en) * 2011-03-22 2016-12-21 Exxonmobil Upstream Res Co Integrated systems incorporating inlet compressor oxidant control apparatus and related methods of generating power
CN104428490B (zh) * 2011-12-20 2018-06-05 埃克森美孚上游研究公司 提高的煤层甲烷生产
US20130269310A1 (en) * 2012-04-12 2013-10-17 General Electric Company Systems and apparatus relating to reheat combustion turbine engines with exhaust gas recirculation
TWM448642U (zh) * 2012-06-22 2013-03-11 Sheng Zhun Entpr Co Ltd 燃燒裝置廢氣回流再使用控制系統
JP5936995B2 (ja) * 2012-11-26 2016-06-22 一般財団法人電力中央研究所 Ｃｏ２回収型ガス化ガス発電プラント

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4030874A (en) * 1975-12-15 1977-06-21 Battelle Memorial Institute Method of and apparatus for controlling combustion
US5051040A (en) * 1987-09-07 1991-09-24 L. & C. Steinmuller Gmbh Fluidized bed combustion system that is controllable under pressure
US4854381A (en) * 1988-04-11 1989-08-08 Paul Mikula Heat exchanger device
US5297729A (en) * 1992-08-28 1994-03-29 Combustion Concepts, Inc. Furnace apparatus
US6237339B1 (en) * 1997-06-06 2001-05-29 Norsk Hydro Asa Process for generating power and/or heat comprising a mixed conducting membrane reactor
US20030172656A1 (en) * 2002-03-12 2003-09-18 Jacques Labasque Method of operating a heat recovery boiler
US20140069307A1 (en) * 2011-07-13 2014-03-13 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Method for operating pulverized-coal-fired boiler facility

Also Published As

Publication number Publication date
EP3410013B1 (en) 2021-06-02
EP3410013A4 (en) 2019-07-17
CN108474555A (zh) 2018-08-31
JP2017133701A (ja) 2017-08-03
DK3410013T3 (da) 2021-07-26
TW201730428A (zh) 2017-09-01
WO2017130758A1 (ja) 2017-08-03
TWI629411B (zh) 2018-07-11
EP3410013A1 (en) 2018-12-05
CA3010257C (en) 2020-06-16
CA3010257A1 (en) 2017-08-03
CN108474555B (zh) 2021-04-06
JP6657996B2 (ja) 2020-03-04

Similar Documents

Publication Publication Date Title
US8110310B2 (en) Power generating plant
AU2002249811B2 (en) Multi-function energy system operable as a fuel cell, reformer, or thermal plant
EP3449523B1 (en) Methanation of anode exhaust gas to enhance carbon dioxide capture
US6926979B2 (en) Waste heat recovery means for fuel cell power system
JP7713864B2 (ja) ガスタービンシステム
JP2001155751A (ja) 燃料電池とガス供給装置を有する配列およびその配列の作動方法
RU2443040C2 (ru) Система топливных элементов
JP5602698B2 (ja) 動力変換システム
US20180292085A1 (en) Combustion gas supply system
JP2004018343A (ja) 炭化水素燃料からの電力と水素の併産方法とそのプラント及びその排熱回収型改質器
CN117550554B (zh) 一种包含多级热交换的甲醇重整制氢纯化系统及其控制方法
US20230228487A1 (en) System and method for drying using hydrogen combustion exhaust
JP2001085036A (ja) 燃料電池装置及びタービン設備
CN111453697B (zh) 用于sofc的多燃料通用型重整制氢系统及方法
US20220045344A1 (en) Solid oxide fuel cell with water recycle
KR102903915B1 (ko) 애노드 배기 가스로부터 수소 가스를 분리하는 연료 전지 시스템, 그 작동 방법 및 그 용도
KR102903917B1 (ko) 개질기 가열용 히트 펌프를 구비한 고온 pem 연료 전지 시스템, 그 작동 방법 및 그 용도
CN116314925A (zh) 一种天然气煤油双燃料固体氧化物燃料电池发电系统

Legal Events

Date Code Title Description
AS Assignment

Owner name: IHI CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SHIBUYA, HIDESHI;YANO, AKIHISA;OKA, TATSUYA;AND OTHERS;REEL/FRAME:046069/0911

Effective date: 20180419

STPP Information on status: patent application and granting procedure in general

Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION

STPP Information on status: patent application and granting procedure in general

Free format text: NON FINAL ACTION MAILED

STPP Information on status: patent application and granting procedure in general

Free format text: RESPONSE TO NON-FINAL OFFICE ACTION ENTERED AND FORWARDED TO EXAMINER

STPP Information on status: patent application and granting procedure in general

Free format text: FINAL REJECTION MAILED

STPP Information on status: patent application and granting procedure in general

Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION

STPP Information on status: patent application and granting procedure in general

Free format text: NON FINAL ACTION MAILED

STPP Information on status: patent application and granting procedure in general

Free format text: RESPONSE TO NON-FINAL OFFICE ACTION ENTERED AND FORWARDED TO EXAMINER

STPP Information on status: patent application and granting procedure in general

Free format text: FINAL REJECTION MAILED

STPP Information on status: patent application and granting procedure in general

Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION

STPP Information on status: patent application and granting procedure in general

Free format text: NON FINAL ACTION MAILED

STPP Information on status: patent application and granting procedure in general

Free format text: RESPONSE TO NON-FINAL OFFICE ACTION ENTERED AND FORWARDED TO EXAMINER

STPP Information on status: patent application and granting procedure in general

Free format text: FINAL REJECTION MAILED

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION