WO2017012129A1 - 对气体机余热能进行梯级回收的多能量形式输出的能源塔 - Google Patents
对气体机余热能进行梯级回收的多能量形式输出的能源塔 Download PDFInfo
- Publication number
- WO2017012129A1 WO2017012129A1 PCT/CN2015/085040 CN2015085040W WO2017012129A1 WO 2017012129 A1 WO2017012129 A1 WO 2017012129A1 CN 2015085040 W CN2015085040 W CN 2015085040W WO 2017012129 A1 WO2017012129 A1 WO 2017012129A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- water
- heat
- pipeline
- internal combustion
- combustion engine
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
- F01K27/02—Plants modified to use their waste heat, other than that of exhaust, e.g. engine-friction heat
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
- F02G5/02—Profiting from waste heat of exhaust gases
- F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from combustion engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/10—Adaptations for driving, or combinations with, electric generators
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/18—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids characterised by adaptation for specific use
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
- F01K25/14—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 using industrial or other waste gases
-
- 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
- F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
-
- 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
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
- F01K7/38—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating the engines being of turbine type
-
- 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
- F01N2240/00—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
- F01N2240/02—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being a heat exchanger
-
- 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
- F01N2240/00—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
- F01N2240/22—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being a condensation chamber
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G2260/00—Recuperating heat from exhaust gases of combustion engines and heat from cooling circuits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/60—Application making use of surplus or waste energy
- F05D2220/62—Application making use of surplus or waste energy with energy recovery turbines
-
- 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 invention relates to an energy tower for utilizing waste heat of an internal combustion engine.
- it relates to an energy tower for multi-energy output output for step recovery of gas residual heat energy.
- the most important residual heat source is engine exhaust, the temperature can reach up to 600 °C; the second is the residual heat of the liner water, but the temperature of the liner water is generally between about 75-85 ° C; if it is a pressurized gas machine, increase The pressurized gas also carries away a portion of the heat, which is typically around 120 ° C at the supercharger outlet.
- the main heat and heat quality of the main residual heat sources are very different, and the temperature after the waste heat recovery and utilization is greatly reduced, which belongs to the large temperature difference residual heat and the energy quality span is large.
- any waste heat recovery method can only efficiently recover the heat of a certain energy quality section, so a single waste heat recovery method cannot fully utilize the waste heat of the gas machine.
- the technical problem to be solved by the present invention is to provide a multi-energy output energy tower for step-by-step recovery of waste heat energy of a gas machine by using a combination of cold, heat and electricity combined with excess heat recovery.
- a multi-energy output energy tower for step recovery and utilization of gas waste heat energy comprising an internal combustion engine, further provided with heat exchange with a high temperature gas discharged from the internal combustion engine to expand the steam turbine
- the work water vapor Rankine cycle system exchanges heat with the high temperature gas, cylinder liner water, charge air and condensation heat in the water vapor Rankine cycle system of the internal combustion engine, respectively, so that the expander expands and works organically.
- a Rankine cycle system a bromine-cooling unit that exchanges part of the cylinder liner water discharged from the internal combustion engine as a heat source of an absorption refrigeration system, and a heat connected to the high-temperature gas terminal discharged from the internal combustion engine for heating domestic water Water heat exchanger.
- the cylinder liner of the internal combustion engine discharges three branches, and the first branch heat exchanges with the high temperature gas discharged from the internal combustion engine after heat exchange through the water vapor Rankine cycle system through a cylinder water heater, and then enters the bromine cold
- the generator in the unit is heat exchanged as a heat source of the absorption refrigeration system and flows into the internal combustion engine through the meeting point; the second branch is used for heat exchange with the organic Rankine cycle system, and then flows into the internal combustion engine through the meeting point;
- the third branch flows directly into the internal combustion engine through the meeting point.
- the water vapor Rankine cycle system includes: a high temperature gas that can be exhausted through the internal combustion engine, for a waste heat boiler that is heated by the internal water to be heated into a high-temperature and high-pressure gas, and is connected to a high-temperature and high-pressure gas flowing out of the waste heat boiler through a pipeline, and is used for a steam turbine that expands work, and is connected to a steam body that is discharged after the steam turbine is operated by a pipeline, and is used for giving
- the first condenser for cooling and condensing the vapor body is connected to the outlet of the first condenser condensed into liquid water through a pipeline for pumping the liquid water, and the pump is pressurized
- the liquid water enters the waste heat boiler through the pipeline and exchanges heat with the high temperature gas discharged from the internal combustion engine.
- the organic Rankine cycle system includes an expander that performs expansion work by flowing high-temperature gaseous working medium, and connects a low-temperature gaseous working fluid flowing out of the expander after work, and is heated with cooling water flowing through the inside.
- the exchanged second condenser, the low-temperature liquid working medium flowing out of the second condenser is divided into three paths through a pipeline and a working fluid pump disposed on the pipeline, wherein one of the low-temperature liquid working fluids is connected to the cylinder liner through the pipeline
- the pipeline is connected to a pressurized air preheater for heating the low temperature liquid working medium by the pressurized air of the internal combustion engine, and the liquid working medium flowing out from the pressurized air preheater is
- a first condenser that condenses heat to form a high-temperature gaseous working medium
- the high-temperature gaseous working medium flowing out from the first condenser is connected to the expander through a pipeline for work, and the working fluid discharged after the work is passed through the second condensation.
- the pump and the working fluid pump start the next cycle.
- the high-temperature gas terminal discharged from the internal combustion engine that has undergone heat exchange with the low-temperature liquid working medium through the exhaust gas preheater is connected to a hot water heat exchanger for heating domestic water through a pipeline.
- the bromine-cooling unit includes a generator for heating a dilute solution flowing through the inside through a liner water flowing in through the second branch b, and the liner water flowing out of the generator is connected to the meeting point through a pipeline and Flowing into the internal combustion engine; a portion of the dilute solution heated by the generator becomes a gaseous refrigerant connected to a third condenser for condensing the gaseous refrigerant through a pipeline, and the other portion becomes a high-temperature concentrated solution and sequentially passes through the solution heat exchange And the first expansion valve is connected to the absorber for absorbing the refrigerant; the refrigerant condensed into the liquid by the cooling water through the third condenser is sequentially connected to the brine for passing through the subcooler and the second expansion valve
- the heat exchange evaporator, the refrigerant after heat exchange through the evaporator is connected to the subcooler through a pipeline and exchanges heat with the liquid refrigerant flowing from the third condenser
- the multi-energy output energy tower for step recovery of gas waste heat energy of the invention is based on the principle of energy cascade utilization and combined with the different requirements of energy for building energy, and proposes a combination of excess heat recovery mode. , heat, electricity triple for waste heat recovery system.
- steam Rankine cycle the organic Rankine cycle, the bromine cooler, and several heat exchangers to use the waste heat of the gas machine according to its characteristics, in order to maximize the recovery of the residual heat energy of the gas machine, to provide different quality to the building and
- the energy of the function makes the waste heat of the gas machine fully utilized, and at the same time greatly improves the comprehensive energy utilization rate of the whole system and achieves the effect of energy saving and emission reduction.
- Figure 1 is a schematic view showing the entire structure of the present invention.
- the energy tower of the present invention for multi-energy output of step recovery of a gas engine includes a gas-fuel internal combustion engine 1, and is further provided with heat exchange with the high-temperature gas discharged from the internal combustion engine 1, thereby
- the water vapor Rankine cycle system 2 for steam turbine expansion work exchanges heat with the high temperature gas, the jacket water, the charge air, and the condensation heat in the water vapor Rankine cycle system 2 discharged from the internal combustion engine 1, respectively, thereby causing expansion
- the cylinder liner of the internal combustion engine 1 discharges three branches of water, and the first branch a passes through a cylinder water heater 6 and a high temperature gas of about 180 ° C discharged from the internal combustion engine 1 after heat exchange through the water vapor Rankine cycle system 2.
- the temperature of the cylinder liner water from the generator is lowered to a temperature slightly lower than that required to enter the internal combustion engine 1, through the meeting point d flows into the internal combustion engine 1;
- the second branch b is used for heat exchange with the organic Rankine cycle system 3 for preheating the organic working fluid in the organic Rankine cycle system 3, and preheating the cylinder after the working medium
- the temperature of the jacket water drops to a temperature slightly lower than that required to enter the internal combustion engine 1, and flows into the internal combustion engine 1 through the meeting point d;
- the third branch c directly flows into the meeting point d, and is used to adjust the cylinder liner water of the three branches after the final mixing.
- the temperature is such that it flows into the internal combustion engine 1 after satisfying the temperature required for the jacket water to enter the internal combustion engine 1.
- the design temperature of the cylinder water of the first branch a and the second branch b at the meeting point d is lower than the required temperature of the inlet to avoid the water temperature after the convergence of the three branches is higher than the required temperature of the inlet, and further Perform additional cooling.
- adjusting the flow rate of the third branch c can adjust the final inlet temperature of the liner water.
- the water vapor Rankine cycle system 2 includes a high temperature gas that can be exhausted through the internal combustion engine 1 and a waste heat boiler 21 for heating water flowing inside into a high temperature and high pressure gas, and is connected to the waste heat boiler 21 through a pipeline.
- the high-temperature and high-pressure gas flowing out is used for the steam turbine 22 for expanding the work, the steam body discharged after the work of the steam turbine 22 is connected through the pipeline, and the first condenser 23 for cooling and condensing the steam body is connected through the pipeline.
- the first condenser 23 is condensed into an outlet of liquid water, a pump 24 for pressurizing the liquid water, and the liquid water pressurized by the pump 24 enters the waste heat boiler 21 through a pipeline to be again
- the high temperature gas discharged from the internal combustion engine 1 is heat exchanged, and the steam turbine 22 is of a back pressure type.
- the steam turbine 22 is of a back pressure type, and its outlet pressure is slightly higher than atmospheric pressure, so the condensation temperature of the water in the condenser 24 is slightly larger than 100 °C. Since the condensation temperature is high, this part of the condensation heat continues as the evaporation heat source of the lower organic Rankine cycle system 3 cycle.
- the water condensed into a liquid is pumped by the pump to the waste heat boiler 21 to continue heating for the next cycle.
- the high temperature exhaust gas is reduced to about 180 ° C after a heat exchange in the waste heat boiler.
- the organic Rankine cycle system 3 includes an expander 31 for performing expansion work by flowing high-temperature gaseous working medium, and connecting the low-temperature gaseous working fluid flowing out of the expander 31 after work, and cooling with the internal flow.
- the second condenser 32 for heat exchange of water, the low-temperature liquid working medium flowing out of the second condenser 32 is divided into three paths through a pipeline and a working fluid pump 33 disposed on the pipeline, wherein one of the low-temperature liquid working fluid passes through
- the pipeline is connected to the exhaust preheater 34 for heating the low temperature liquid working fluid at the exhaust end of the jacket water heat exchanger 6, and the high temperature liquid working medium flowing out of the exhaust preheater 34 is connected to the working point of the working fluid through the pipeline.
- the second low-temperature liquid working medium is connected to the pressurized air preheater 35 heated by the pressurized air of the internal combustion engine 1 to the low-temperature liquid working medium, and flows out from the pressurized air preheater 35.
- the liquid working medium is connected to the working point convergence point e through a pipeline;
- the third low temperature liquid working medium is connected through a pipeline to the cylinder jacket water flowing out from the second branch b of the cylinder liner of the internal combustion engine to the low temperature liquid working a heated cylinder liner water preheater 36, preheating from the cylinder liner
- the liquid working fluid flowing out of the device 36 is connected to the working point convergence point e through a pipeline, and the three-way low-temperature liquid working fluid flowing to the working point confluence point e is connected to the water vapor Rankine cycle system 2 through the pipeline.
- the first condenser 23 (which functions as a lower organic Rankine cycle evaporator) for forming a high-temperature gaseous working medium by absorbing heat of condensation of the water vapor Rankine cycle system, and the high-temperature gaseous working medium flowing out from the first condenser 23 Then, the expander 31 is connected to the expander 31 for work.
- the working fluid discharged after the work is condensed into a liquid state by the second condenser 32, and the next cycle is started after the pressurization of the working fluid pump 33.
- the low temperature liquid working medium which is pressurized from the condenser 32 and passed through the working fluid pump is divided into three paths after the pump: Part of it is preheated by part of the liner water to near the jacket water outlet temperature; the other part is preheated by the charge air to a relatively high temperature level (close to the charge air temperature but less than or equal to the organic Rankine cycle system 3) Evaporation temperature), while the charge air is cooled to near the condenser outlet temperature in the organic Rankine cycle system 3, so that the charge air is substantially reduced to the temperature required for combustion into the cylinder, so the organic Rankine cycle system 3
- the pressurized air preheater also functions as an air intercooler; the last part of the working medium is preheated by the low temperature exhaust after the secondary heat exchange to a relatively high temperature (close to the exhaust heat in the cylinder jacket water) The temperature at the outlet of the vessel is less than or equal to the
- the working fluid has been preheated to a higher temperature level, and By a two-phase fluid.
- the organic working fluid absorbs the heat of condensation of the upper water in the first condenser of the water vapor Rankine cycle (corresponding to the evaporator of the organic Rankine cycle system 3) and all becomes a high temperature gaseous working medium.
- the high-temperature gaseous working fluid expands in the expander, it is condensed into a liquid through the second condenser, and then pumped to each heat exchanger by the pump to start the next cycle.
- the high-temperature gas terminal discharged from the internal combustion engine 1 through which the exhaust gas preheater 34 exchanges heat with the low-temperature liquid working medium is connected to a hot water heat exchanger 5 for heating domestic water.
- the bromine-cooling unit 4 includes a generator 41 for heating a dilute solution flowing through the inside through a liner water flowing in through the second branch b, and the cylinder water flowing out from the generator 41 is connected to the pipeline through a pipe Convergence point d flows into the internal combustion engine 1; a portion of the dilute solution heated by the generator 41 becomes a gaseous refrigerant connected to the third condenser 46 for condensing the gaseous refrigerant through a line, and the other portion becomes a high temperature
- the concentrated solution is sequentially connected to the absorber 44 for absorbing the refrigerant through the solution heat exchanger 42 and the first expansion valve 43, and the refrigerant condensed into the liquid by the cooling water through the third condenser 46 sequentially passes through the subcooler 47,
- the second expansion valve 48 is connected to an evaporator 49 for heat exchange of the brine, and the refrigerant exchanged by the evaporator 49 is connected to the subcooler 47 through the pipeline and
- the liquid refrigerant of the cooler 47 After the liquid refrigerant of the cooler 47 is subjected to heat exchange, it is connected to an absorber 44 for absorbing the refrigerant and performing heat exchange with the cooling water through a pipe, and the liquid refrigerant after the absorber 44 forms a dilute solution through the pipe and Solution set on the pipeline 45 is connected to the solution heat exchanger 42 and exchanges heat with the concentrated solution flowing from the generator 41 into the solution heat exchanger 42 to enter the generator 41, and again with the liner water flowing through the generator 41. Heat exchange.
- the multi-energy output energy tower for step recovery of gas waste heat energy of the invention has four heat exchanges: the first heat exchange heats the water into superheated steam, and the heat exchange temperature is about 180 ° C;
- the second heat exchange is used to heat the part of the liner water which is the heat source of the absorption refrigeration system, so as to increase the evaporation end temperature and the input heat in the generator, thereby increasing the cooling capacity, and the temperature after heat exchange is about 110 ° C;
- the third time The heat transfer is to transfer the remaining higher temperature heat to the organic Rankine cycle system 3, increase the output power of the organic Rankine cycle system 3, the temperature after heat exchange is about 60 ° C;
- the last heat transfer is heating life With low-temperature hot water (such as bath water), because the hydrogen content in the gaseous fuel is high, the water vapor content in the exhaust gas after combustion is relatively large, and this part of water vapor condenses into water at about 60 ° C, and emits more latent heat of condensation. Therefore, this part of the
- the water vapor Rankine cycle is the first stage for recycling waste heat, and the waste heat boiler, back pressure turbine, condenser, and water pump are connected in sequence to form a Rankine cycle.
- the exhaust gas after the turbocharger first enters the waste heat boiler, and heats the water to a superheated steam of high temperature and high pressure of 1.6 MPa.
- back pressure is 2bar
- the superheated steam comes out of the boiler and enters the steam turbine to expand work, pushing the steam turbine to rotate.
- the steam turbine is connected to a generator to drive the motor to Building power supply.
- the steam turbine is connected to the hot fluid side of the condenser, and the expanded vapor is condensed here to a saturated liquid water of 120 ° C under a condensing pressure of 2 bar, and then pressurized by the water pump to the evaporation pressure and sent to the waste heat boiler again, thereby completing the cycle. .
- the water vapor Rankine cycle can deliver approximately 90 kW of output work. After the flue gas has undergone a heat exchange in the waste heat boiler, the temperature is lowered to about 180 °C.
- the condenser of the Rankine cycle is also the evaporator of the lower ORC (Organic Rankine Cycle System), which is a connecting component of two cycles.
- the hot fluid in the heat exchanger is the working water of the Rankine cycle
- the cold fluid is the organic of the ORC.
- Working fluid, the organic working fluid in this embodiment is R123.
- the working medium R123 absorbs the heat of condensation of the upper water in the evaporator and all becomes saturated steam at 110 ° C under 0.97 MPa, and then enters the expander to expand work.
- the expander is also connected to a generator and drives the motor to power the building.
- the expanded organic working fluid is cooled by external cooling water to a saturated liquid working medium of about 38 °C.
- the working fluid after the condenser is divided into three branches: the first branch is connected to the cold fluid side of the liner water preheater, and then connected to the working point.
- the hot fluid in the preheater is a part of the cylinder liner water, which is at the inlet temperature of the heat exchanger of 85 ° C and the outlet temperature is about 70 ° C.
- the working fluid on the branch is heated to 80 in the cylinder jacket water preheater. °C; the second branch is connected to the cold fluid side of the charge air preheater, and then connected to the working point.
- the hot fluid in the preheater is the charge air.
- the temperature of the charge air at the inlet of the heat exchanger is about 130 °C. After the heat exchange with the low temperature working medium, the temperature drops to about 43 °C and flows into the gas machine, and the working medium is heated. It is about 110 °C; the third branch is connected to the cold fluid side of the exhaust preheater, and then connected to the working point.
- the hot fluid in the preheater is the low temperature exhaust after the cylinder water heater, and the inlet temperature is about 120 °C.
- the working fluid on this branch flows into the exhaust preheater and is heated to about 100 °C.
- the exhaust gas temperature is reduced to about 60 °C.
- the organic working fluids of the three branches are re-synthesized into a working fluid flow after coming out of the respective heat exchangers, and the temperature is about 100 °C.
- the ORC evaporator is connected after the meeting point, where the working fluid is all heated to saturated steam.
- the ORC output power is approximately 85 kW.
- the liner water is cooled in the gas machine and is taken out of the body after the temperature rises. After exiting the machine, it is divided into three branches: the first branch is connected to the cylinder water preheater. After the cylinder water is preheated here, the temperature is lowered to about 70 °C, and then connected to the meeting point; A strip heat exchanger is connected in turn to the exhaust heat exchanger, and the generator of the bromine cold unit is connected to the meeting point.
- the liner water on this branch is heated in the exhaust heat exchanger by a low-temperature exhaust (about 180 ° C) after heat exchange to nearly 90 ° C, and then enters the generator in the bromine cooling unit as absorption refrigeration.
- the heat source of the system after flowing out of the generator, drops to a temperature of about 70 ° C and then merges into the meeting point.
- the tail gas is reduced to about 120 °C by the secondary heat exchange temperature; the third branch directly flows into the meeting point, and the junction point is followed by the cylinder liner water inlet into the machine. After the three branches are merged, the temperature becomes 75 °C required by the inlet. Then flow into the gas engine block.
- the absorption refrigeration system produces approximately 200 kW of domestic refrigeration.
- the exhaust gas flow path is connected with a waste heat boiler, a cylinder water heater, an ORC preheater, a domestic water heater, a total of four heat exchangers, and finally discharged into the environment.
- the entire system can recover approximately 175 kW of electrical energy, 200 kW of domestic cold, and about 100 kW of low-temperature living heat.
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
参数 | 数值 |
气体机额定功率 | 1100kW |
尾气温度 | 540℃ |
进气体积流量(标准状况) | 1.16m3/s |
燃气体积流量(标准状况) | 0.0784m3/s |
缸套水流量 | 8.33kg/s |
缸套水出机温度 | 85℃ |
缸套水进机温度 | 75℃ |
增压空气增压器后温度 | 130℃ |
Claims (6)
- 一种对气体机余热能进行梯级回收利用的多能量形式输出的能源塔,包括内燃机(1),其特征在于,还设置有与所述内燃机(1)排出的高温气体进行热交换,使汽轮机膨胀作功的水蒸气朗肯循环系统(2),分别与所述内燃机(1)排出的高温气体、缸套水,增压空气以及水蒸气朗肯循环系统(2)中的冷凝热进行热交换,使膨胀机膨胀作功的有机朗肯循环系统(3),将所述内燃机(1)排出的部分缸套水作为吸收式制冷系统热源进行热交换的溴冷机组(4),以及与所述的内燃机(1)排出的高温气体终端相连用于给生活用水进行加热的热水换热器(5)。
- 根据权利要求1所述的对气体机余热能进行梯级回收利用的多能量形式输出的能源塔,其特征在于,所述的内燃机(1)排出的缸套水分三条支路,第一条支路(a)通过一个缸套水加热器(6)与经过水蒸气朗肯循环系统(2)热交换后的内燃机(1)排出的高温气体进行热交换,然后进入溴冷机组(4)中的发生器中作为吸收式制冷系统的热源进行热交换后经汇合点(d)流入内燃机(1);第二条支路(b)用于与所述的有机朗肯循环系统(3)进行热交换,然后经汇合点(d)流入内燃机(1);第三条支路(c)直接经汇合点(d)流入内燃机(1)。
- 根据权利要求1所述的对气体机余热能进行梯级回收利用的多能量形式输出的能源塔,其特征在于,所述的水蒸气朗肯循环系统(2)包括有:内部能够贯通所述内燃机(1)排出的高温气体,用于将流过内部的水加热成高温高压气体的余热锅炉(21),通过管路连接余热锅炉(21)流出的高温高压气体,用于膨胀做功的汽轮机(22),通过管路连接汽轮机(22)作功后排出的汽体,用于给所述的汽体降温冷凝的第一冷凝器(23),通过管路连接经第一冷凝器(23)的冷凝成液体水的出口,用于对所述液体水进行加压的泵(24),所述经泵(24)加压后的液体水通过管路进入所述的余热锅炉(21)再次与所述的内燃机(1)排出的高温气体进行热交换。
- 根据权利要求1所述的对气体机余热能进行梯级回收利用的多能量形式输出的能源塔,其特征在于,所述的有机朗肯循环系统(3)包括有通过流入的高温气态工质进行膨胀作功的膨胀机(31),通过管路连接膨胀机(31)做功后流出的低温气态工质,并与流经内部的冷却水进行热交换的第二冷凝器(32),流出第二冷凝器(32)的低温液态工质通过管路和设置在所述管路上的工质泵(33)分为三路,其中的一路低温液态工质通过管路连接到 缸套水换热器(6)排气端的用于加热低温液态工质的排气预热器(34),排气预热器(34)流出的高温液态工质通过管路连接至工质汇合点(e);第二路低温液态工质通过管路连接到用所述内燃机(1)的增压空气给低温液态工质加热的增压空气预热器(35),从所述增压空气预热器(35)流出的液态工质通过管路连接至工质汇合点(e);第三路低温液态工质通过管路连接到用所述内燃机(1)缸套水的第二条支路(b)流出的缸套水给低温液态工质加热的缸套水预热器(36),从所述缸套水预热器(36)流出的液态工质通过管路连接至工质汇合点(e),所述的流至工质汇合点(e)的三路低温液态工质共同通过管路连接水蒸气朗肯循环系统(2)中的用于通过吸收水蒸气朗肯循环系统(2)的冷凝热而形成高温气态工质的第一冷凝器(23),从第一冷凝器(23)流出的高温气态工质再通过管路连接到所述膨胀机(31)作功,作功后流出的工质再经由第二冷凝器(32)和工质泵(33)开始下次循环。
- 根据权利要求4所述的对气体机余热能进行梯级回收利用的多能量形式输出的能源塔,其特征在于,流经所述排气预热器(34)与所述的低温液态工质进行热交换后的内燃机(1)排出的高温气体终端通过管路连接用于给生活用水进行加热的热水换热器(5)。
- 根据权利要求1所述的对气体机余热能进行梯级回收利用的多能量形式输出的能源塔,其特征在于,所述的溴冷机组(4)包括有通过经第二支路b流入的缸套水对流经内部的稀溶液进行加热的发生器(41),从所述发生器(41)流出的缸套水通过管路连接到汇合点(d)并流入内燃机(1);经所述发生器(41)加热后的稀溶液一部分变为气态制冷剂通过管路连接到用于冷凝所述气态制冷剂的第三冷凝器(46),另一部分变为高温浓溶液依次通过溶液热交换器(42)和第一膨胀阀(43)连接到用于吸收制冷剂的吸收器(44);经第三冷凝器(46)被冷却水冷凝成液态的制冷剂依次通过过冷器(47)、第二膨胀阀(48)连接到用于对载冷剂进行热交换的蒸发器(49),经过蒸发器(49)热交换后的制冷剂通过管路连接过冷器(47)并与从所述第三冷凝器(46)流入过冷器(47)的液态制冷剂进行热交换后,通过管路连接到用于吸收制冷剂并与冷却水进行热交换的吸收器(44),经吸收器(44)后形成稀溶液通过管路和设置在管路上的溶液泵(45)连接至溶液热交换器(42),并与从所述发生器(41)流入溶液热交换器(42)中出的浓溶液进行热交换后进入发生器(41),与流经发生器(41)内的缸套水再次进行热交换。
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US15/739,761 US10247050B2 (en) | 2015-07-21 | 2015-07-24 | Energy tower of multi-energy-form output for stepwise recovering waste heat of a gas engine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201510431672.2A CN105003351B (zh) | 2015-07-21 | 2015-07-21 | 对气体机余热能进行梯级回收的多能量形式输出的能源塔 |
CN201510431672.2 | 2015-07-21 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2017012129A1 true WO2017012129A1 (zh) | 2017-01-26 |
Family
ID=54376169
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/CN2015/085040 WO2017012129A1 (zh) | 2015-07-21 | 2015-07-24 | 对气体机余热能进行梯级回收的多能量形式输出的能源塔 |
Country Status (3)
Country | Link |
---|---|
US (1) | US10247050B2 (zh) |
CN (1) | CN105003351B (zh) |
WO (1) | WO2017012129A1 (zh) |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107882605A (zh) * | 2017-12-11 | 2018-04-06 | 翁志远 | 热能回收动力系统及机动设备 |
CN108825320A (zh) * | 2018-09-11 | 2018-11-16 | 翁志远 | 一种低温工质发电系统及动力系统 |
CN110131912A (zh) * | 2019-05-25 | 2019-08-16 | 墙新奇 | 一种用气动压缩机的制冷发电装置 |
WO2019177464A1 (en) * | 2018-03-16 | 2019-09-19 | Cronus Technology As | A system for recovery of waste heat from an industrial plant |
CN113464227A (zh) * | 2021-07-14 | 2021-10-01 | 国能龙源蓝天节能技术有限公司 | 热电联供控制方法及热电联供系统 |
CN113654372A (zh) * | 2021-08-13 | 2021-11-16 | 浙江雅德居实业有限公司 | 一种定型机的余热回收系统及工艺 |
CN113686051A (zh) * | 2021-08-16 | 2021-11-23 | 山东大学 | 一种高温高湿气体中水热回收的开式压缩吸收式热泵系统 |
CN113686169A (zh) * | 2021-08-13 | 2021-11-23 | 浙江雅德居实业有限公司 | 一种定型机的余热回收系统及工艺 |
CN114198173A (zh) * | 2021-11-04 | 2022-03-18 | 合肥通用机械研究院有限公司 | 一种全回热布雷顿循环与吸收式制冷集成的电冷联供系统 |
Families Citing this family (32)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2544051B (en) * | 2015-11-03 | 2020-01-01 | Perkins Engines Co Ltd | An energy recovery system for an internal combustion engine |
CN105909329B (zh) * | 2016-03-24 | 2018-02-16 | 上海光热实业有限公司 | 大型内燃机冷热电三联供优化系统 |
CN107304754B (zh) * | 2016-04-24 | 2022-09-20 | 吕书龙 | 利用浮力采能的变形式朗肯循环低温差能开发系统 |
CN106089344B (zh) * | 2016-07-25 | 2017-12-22 | 华电电力科学研究院 | 一种余热多级利用的分布式能源发电系统及方法 |
CN106246407A (zh) * | 2016-08-25 | 2016-12-21 | 广西大学 | 一种优化发动机余热回收的系统 |
CN106246268B (zh) * | 2016-10-10 | 2018-05-01 | 哈尔滨工业大学(威海) | 一种发动机余热综合回收系统 |
CN106546033B (zh) * | 2016-11-03 | 2018-06-19 | 天津大学 | 气体机多余热源驱动增压三效复合制冷循环系统 |
CN107060927A (zh) * | 2017-06-09 | 2017-08-18 | 翁志远 | 余热回收利用系统及其方法和发电站 |
CN107060930A (zh) * | 2017-06-09 | 2017-08-18 | 翁志远 | 热能利用系统及发电站 |
CN107143435A (zh) * | 2017-06-22 | 2017-09-08 | 江苏科技大学海洋装备研究院 | 一种lng动力船的分布式能源系统及工作方法 |
CN107939548B (zh) * | 2017-10-17 | 2020-06-23 | 山东大学 | 新型内燃机余热利用冷热电联供系统及其工作方法 |
CN108534345A (zh) * | 2018-04-18 | 2018-09-14 | 苏州清荷坊环保科技有限公司 | 一种自动循环式水预热器 |
CN108868932B (zh) * | 2018-07-12 | 2024-04-09 | 苏州颜吉通新能源科技有限公司 | 低温余热发电装置 |
CN109736963B (zh) * | 2018-12-29 | 2021-01-19 | 西安交通大学 | 一种船舶发动机的余热利用系统及方法 |
CN109546179A (zh) * | 2019-01-07 | 2019-03-29 | 中氢新能技术有限公司 | 一种甲醇重整燃料电池电堆散热系统 |
CN109827352B (zh) * | 2019-01-24 | 2020-12-11 | 山东大学 | 一种冷热电和纯水四联供系统及联供方法 |
CN109707472B (zh) * | 2019-02-28 | 2021-10-22 | 东北大学 | 一种利用干熄焦余热的分布式能源系统 |
CN109879251B (zh) * | 2019-03-07 | 2024-05-03 | 南京工程学院 | 一种基于能量综合利用的氯化氢合成系统 |
CN111852600A (zh) * | 2019-04-30 | 2020-10-30 | 中国船舶重工集团公司第七一一研究所 | 一种复叠式柴油机余热回收热电联产系统 |
CN110173347B (zh) * | 2019-05-28 | 2020-02-28 | 浙江亿扬能源科技有限公司 | 一种煤矿在用设备的余热回收利用系统及运行方法 |
CN110388241B (zh) * | 2019-07-31 | 2021-07-20 | 东北师范大学 | 一种汽车发动机废热回收热力循环系统 |
UA141780U (uk) * | 2019-10-21 | 2020-04-27 | Іван Іванович Котурбач | Дизель-парова електростанція |
CN110905618A (zh) * | 2019-11-18 | 2020-03-24 | 天津大学 | 适用于分布式能源系统的内燃机热电联产余热回收系统 |
CN110821707A (zh) * | 2019-11-25 | 2020-02-21 | 天津大学 | 基于二氧化碳动力循环的柴油机余热利用梯级耦合系统 |
CN111594281A (zh) * | 2020-06-23 | 2020-08-28 | 南京天加热能技术有限公司 | 一种聚酯酯化蒸汽余热发电系统 |
CN112178971B (zh) * | 2020-09-30 | 2021-08-17 | 武汉理工大学 | 一种利用邮轮发动机余热及太阳能的冷梁空调装置 |
CN112282962B (zh) * | 2020-11-17 | 2023-11-21 | 天津大学合肥创新发展研究院 | 混合工质代替内燃机缸套水的余热回收有机朗肯循环系统 |
CN113074028B (zh) * | 2021-04-22 | 2023-05-12 | 中创清洁能源发展(沈阳)股份有限公司 | 一种利用发电机组的烟气低温余热发电系统 |
CN113374299B (zh) * | 2021-05-18 | 2022-05-13 | 青建集团股份公司 | 一种装配式建筑及其控制方法 |
CN114000926A (zh) * | 2021-11-01 | 2022-02-01 | 哈尔滨工程大学 | 一种低速柴油机排气分流两级余热利用系统 |
CN114087047B (zh) * | 2021-11-02 | 2023-09-19 | 鞍钢集团工程技术有限公司 | 一种ccpp电厂燃气回流能量回收系统及方法 |
CN116481210B (zh) * | 2023-05-23 | 2024-03-29 | 哈尔滨工程大学 | 低速柴油机排气能量分流的orc和溴化锂制冷双循环梯度余热利用系统、工作方法 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2004251263A (ja) * | 2003-02-21 | 2004-09-09 | Kh Kogyo:Kk | 内燃機関の冷却水廃熱・排気ガス熱及び不完全燃焼排気ガスの再燃焼熱を対向流式熱交換ボイラーで高効率熱回収を用いる動力発生装置及び熱利用装置及びこれらの併合装置 |
CN201321918Y (zh) * | 2008-12-25 | 2009-10-07 | 上海交通大学 | 大型船舶柴油机废热利用的热电冷联产装置 |
CN103161607A (zh) * | 2013-03-04 | 2013-06-19 | 西安交通大学 | 一种基于内燃机余热利用的联合发电系统 |
CN103352772A (zh) * | 2013-06-25 | 2013-10-16 | 天津大学 | 内燃机多品位余热利用的联合循环热电转换系统 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4576005A (en) * | 1985-01-07 | 1986-03-18 | Force Louis W | Wellhead gas treatment and co-generation method and system |
US6523357B1 (en) * | 2001-12-04 | 2003-02-25 | Takuma Co., Ltd. | Absorption refrigerator |
JP5281587B2 (ja) | 2008-02-14 | 2013-09-04 | サンデン株式会社 | 内燃機関の廃熱利用装置 |
US8776517B2 (en) * | 2008-03-31 | 2014-07-15 | Cummins Intellectual Properties, Inc. | Emissions-critical charge cooling using an organic rankine cycle |
GB2480988B (en) * | 2009-04-09 | 2013-11-06 | Ocean Synergy Ltd | Deep ocean energy system with full or partial sea water air conditioning and utility waste heat utilization |
US8850814B2 (en) * | 2009-06-11 | 2014-10-07 | Ormat Technologies, Inc. | Waste heat recovery system |
US8650879B2 (en) * | 2011-04-20 | 2014-02-18 | General Electric Company | Integration of waste heat from charge air cooling into a cascaded organic rankine cycle system |
CN103206317B (zh) | 2013-04-24 | 2014-11-05 | 哈尔滨广瀚新能动力有限公司 | 一种内燃发电机组余热梯级回收利用系统 |
CN103758658B (zh) | 2013-12-27 | 2015-06-24 | 天津大学 | 二级双回路内燃机余热梯级利用热回收系统 |
-
2015
- 2015-07-21 CN CN201510431672.2A patent/CN105003351B/zh active Active
- 2015-07-24 US US15/739,761 patent/US10247050B2/en active Active
- 2015-07-24 WO PCT/CN2015/085040 patent/WO2017012129A1/zh active Application Filing
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2004251263A (ja) * | 2003-02-21 | 2004-09-09 | Kh Kogyo:Kk | 内燃機関の冷却水廃熱・排気ガス熱及び不完全燃焼排気ガスの再燃焼熱を対向流式熱交換ボイラーで高効率熱回収を用いる動力発生装置及び熱利用装置及びこれらの併合装置 |
CN201321918Y (zh) * | 2008-12-25 | 2009-10-07 | 上海交通大学 | 大型船舶柴油机废热利用的热电冷联产装置 |
CN103161607A (zh) * | 2013-03-04 | 2013-06-19 | 西安交通大学 | 一种基于内燃机余热利用的联合发电系统 |
CN103352772A (zh) * | 2013-06-25 | 2013-10-16 | 天津大学 | 内燃机多品位余热利用的联合循环热电转换系统 |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107882605A (zh) * | 2017-12-11 | 2018-04-06 | 翁志远 | 热能回收动力系统及机动设备 |
WO2019177464A1 (en) * | 2018-03-16 | 2019-09-19 | Cronus Technology As | A system for recovery of waste heat from an industrial plant |
CN108825320A (zh) * | 2018-09-11 | 2018-11-16 | 翁志远 | 一种低温工质发电系统及动力系统 |
CN110131912A (zh) * | 2019-05-25 | 2019-08-16 | 墙新奇 | 一种用气动压缩机的制冷发电装置 |
CN110131912B (zh) * | 2019-05-25 | 2024-05-14 | 墙新奇 | 一种用气动压缩机的制冷发电装置 |
CN113464227A (zh) * | 2021-07-14 | 2021-10-01 | 国能龙源蓝天节能技术有限公司 | 热电联供控制方法及热电联供系统 |
CN113654372B (zh) * | 2021-08-13 | 2024-03-22 | 浙江尤佳节能科技有限公司 | 一种定型机的余热回收系统及工艺 |
CN113654372A (zh) * | 2021-08-13 | 2021-11-16 | 浙江雅德居实业有限公司 | 一种定型机的余热回收系统及工艺 |
CN113686169A (zh) * | 2021-08-13 | 2021-11-23 | 浙江雅德居实业有限公司 | 一种定型机的余热回收系统及工艺 |
CN113686169B (zh) * | 2021-08-13 | 2024-03-22 | 浙江尤佳节能科技有限公司 | 一种定型机的余热回收系统及工艺 |
CN113686051A (zh) * | 2021-08-16 | 2021-11-23 | 山东大学 | 一种高温高湿气体中水热回收的开式压缩吸收式热泵系统 |
CN114198173B (zh) * | 2021-11-04 | 2023-10-13 | 合肥通用机械研究院有限公司 | 一种全回热布雷顿循环与吸收式制冷集成的电冷联供系统 |
CN114198173A (zh) * | 2021-11-04 | 2022-03-18 | 合肥通用机械研究院有限公司 | 一种全回热布雷顿循环与吸收式制冷集成的电冷联供系统 |
Also Published As
Publication number | Publication date |
---|---|
CN105003351B (zh) | 2016-08-17 |
US10247050B2 (en) | 2019-04-02 |
US20180187575A1 (en) | 2018-07-05 |
CN105003351A (zh) | 2015-10-28 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2017012129A1 (zh) | 对气体机余热能进行梯级回收的多能量形式输出的能源塔 | |
CN111022138B (zh) | 一种基于吸收式热泵余热回收的超临界二氧化碳发电系统 | |
CN106762489B (zh) | 一种基于低温太阳能及液化天然气冷能的发电系统 | |
CN103161607A (zh) | 一种基于内燃机余热利用的联合发电系统 | |
CN107939548B (zh) | 新型内燃机余热利用冷热电联供系统及其工作方法 | |
CN104675521A (zh) | 一种新型燃气-蒸汽联合循环冷热电联供系统 | |
CN105423592A (zh) | 双工况直燃双效型溴化锂吸收式热泵机组 | |
CN206071658U (zh) | 一种lng冷能综合利用系统 | |
CN112554983A (zh) | 一种耦合卡琳娜循环的液态二氧化碳储能系统及方法 | |
CN108798898B (zh) | 质子交换膜燃料电池与燃气轮机联合供应蒸汽和热水的系统及方法 | |
CN104697239A (zh) | 一种生物质驱动的新型有机郎肯循环冷热电三联供系统 | |
CN110905618A (zh) | 适用于分布式能源系统的内燃机热电联产余热回收系统 | |
US10344626B2 (en) | Hybrid power generation system | |
CN113864017A (zh) | 一种利用lng冷能和地热能的卡琳娜/有机朗肯联合循环发电系统 | |
CN110925041B (zh) | 一种联合循环高效燃煤发电系统 | |
US20220220868A1 (en) | Combined cycle power device | |
WO2023226666A1 (zh) | 一种与煤电机组耦合的二氧化碳储能系统及方法 | |
CN210530935U (zh) | 一种多轴布置的双机回热系统 | |
CN110953069A (zh) | 一种燃机电站多能耦合发电系统 | |
CN109882292A (zh) | 一种lng燃气轮机耦合冷能发电系统及发电方法 | |
CN205330748U (zh) | 利用涡流管的高效热力循环系统 | |
CN208831058U (zh) | 天然气压差能发电装置 | |
CN108894836B (zh) | 基于天然气压力能回收的多能互补系统 | |
Fang et al. | Modeling and experimental investigation on a gas engine-driven heat pump for space-heating and sanitary hot water | |
TWI399512B (zh) | 利用低階熱能產生電力及冷凍之裝置與方法 |
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: 15898685 Country of ref document: EP Kind code of ref document: A1 |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 15898685 Country of ref document: EP Kind code of ref document: A1 |
|
32PN | Ep: public notification in the ep bulletin as address of the adressee cannot be established |
Free format text: NOTING OF LOSS OF RIGHTS PURSUANT TO RULE 112(1) EPC (EPO FORM 1205N DATED 02/08/2018) |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 15898685 Country of ref document: EP Kind code of ref document: A1 |