WO2010035927A1 - Système de récupération d'énergie thermique - Google Patents

Système de récupération d'énergie thermique Download PDF

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Publication number
WO2010035927A1
WO2010035927A1 PCT/KR2009/000292 KR2009000292W WO2010035927A1 WO 2010035927 A1 WO2010035927 A1 WO 2010035927A1 KR 2009000292 W KR2009000292 W KR 2009000292W WO 2010035927 A1 WO2010035927 A1 WO 2010035927A1
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WO
WIPO (PCT)
Prior art keywords
fluid
engine
accelerator
heat exchanger
input fluid
Prior art date
Application number
PCT/KR2009/000292
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English (en)
Korean (ko)
Inventor
김성완
Original Assignee
주식회사 자이벡
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Filing date
Publication date
Application filed by 주식회사 자이벡 filed Critical 주식회사 자이벡
Publication of WO2010035927A1 publication Critical patent/WO2010035927A1/fr

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Classifications

    • 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
    • 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
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M31/00—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture
    • F02M31/02—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating
    • F02M31/04—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating combustion-air or fuel-air mixture
    • F02M31/06—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating combustion-air or fuel-air mixture by hot gases, e.g. by mixing cold and hot air
    • F02M31/08—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating combustion-air or fuel-air mixture by hot gases, e.g. by mixing cold and hot air the gases being exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M31/00—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture
    • F02M31/02—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating
    • F02M31/04—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating combustion-air or fuel-air mixture
    • F02M31/10—Apparatus for thermally treating combustion-air, fuel, or fuel-air mixture for heating combustion-air or fuel-air mixture by hot liquids, e.g. lubricants or cooling water
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to a heat energy recovery system, and more particularly to an energy recovery system configured to recover and utilize the heat energy generated by the operation of the engine.
  • a compressor is a mechanical device that compresses gas and increases pressure, also called a compressor.
  • Compressors are basically the same as pumps in that they compress mechanical fluids and apply mechanical energy to fluids, but pumps pressurize liquids and compressors pressurize gases to increase pressure. The gas passed through such a compressor increases in pressure and temperature.
  • An internal combustion engine is an engine that generates a mechanical power by directly burning a fuel having chemical energy with oxygen in air and using thermal energy generated during combustion. At this time, the gas emitted after combustion contains a lot of heat, and this heat is generally not utilized and radiated to the outside.
  • a fuel cell is an apparatus that directly generates power without a mechanical driving unit by causing an electrochemical reaction between fuel (hydrogen, LNG, LPG, methanol, etc.) and oxygen in the air.
  • fuel hydrogen, LNG, LPG, methanol, etc.
  • oxygen in the air.
  • existing power generation technology fuel combustion steam generation turbine drive generator drive
  • a fuel cell generates a lot of heat in the process of producing power in the stack by injecting fuel and air, and the introduced air becomes a high temperature state and is discharged to the outside with steam.
  • the molten carbonate fuel cell (MCFC) used as a fuel cell for power generation has a high temperature of 650 degrees Celsius and a solid oxide fuel cell (SOFC) of 1,000 degrees Celsius. to be.
  • the engines that change the state of the supplied fluid to generate power (energy) or receive energy from the outside to change the state of the fluid are discharged from the fluid contains heat, and this thermal energy is not utilized. As it is not wasted and wasted, it is a cause of lowering the energy efficiency of the engine.
  • the present invention has been made on the basis of the technical background as described above, to provide a heat energy recovery system that can improve the energy efficiency of the engine by recovering and utilizing the heat energy discharged through any engine.
  • Heat energy recovery system i) having an inlet for the input fluid and an outlet for discharging the output fluid, and transfers energy to the input fluid to change the state of the input fluid or An engine for converting the energy of the input fluid into another type of energy; ii) an inlet pipe connected to the inlet of the engine and circulating the input fluid to the engine; and iii) connected to the inlet pipe.
  • An input fluid accelerator for increasing a conveying speed of the input fluid flowing into the engine and iv) an outlet pipe connected to an outlet of the engine and circulating an output fluid whose state is changed in the engine to the outside of the engine, v) A heat exchanger mounted to the outlet pipe and collecting heat energy from the output fluid while circulating a working fluid; vi) the heat exchanger and the Power Connect fluid accelerator, and includes a return line for the thermal energy is obtained from the output state is changed to the fluid supply the operation fluid to the fluid input accelerator.
  • the input fluid accelerator may be formed in a pipe shape, and may include an accelerator having a convex portion curved toward a center and a suction nozzle communicating with the recovery tube and the convex portion.
  • the heat exchanger has an inlet and an outlet, and the working fluid is introduced through the inlet of the heat exchanger, receives heat energy from the output fluid, and is discharged through the outlet in a vaporized (superheated gas) state.
  • the working fluid in the vaporized state can be supplied to the input fluid accelerator.
  • the output fluid accelerator may be formed in a tubular shape, and may include an accelerator having a convex portion curved toward the center and a suction nozzle communicating the recovery tube with the convex portion.
  • the outlet of the heat exchanger may be connected to the suction nozzle of the output fluid accelerator so that the working fluid vaporized may be supplied to the output fluid accelerator.
  • the engine includes a plurality of different inlets, and the inlet pipes are connected to the different inlets, respectively, to supply different types of input fluids.
  • Water may be used as the working fluid.
  • the engine may be a compressor that compresses the input fluid by receiving electrical or mechanical energy from the outside.
  • the engine may be an internal combustion engine generating fuel and air into the input fluid to explode inside the engine and generate power to the outside.
  • the engine may be a boiler in which fuel and air are introduced into the input fluid to generate heat energy while burning inside the engine to vaporize water circulating through the engine and discharge it in a vapor state.
  • the engine may be a gas turbine that generates mechanical power using thermal energy.
  • the engine may be a fuel cell in which air and fuel are introduced into the input fluid to generate electricity by causing an electrochemical action inside the engine.
  • a heat exchanger is provided on the outlet side of the engine, and the working fluid is circulated through the heat exchanger to absorb the heat energy of the exhaust gas so that the temperature and pressure on the engine outlet side can be lowered, thereby reducing the engine power required and improving efficiency. You can.
  • the working fluid absorbed thermal energy through the heat exchanger has the effect of reducing the power required of the engine by driving the fluid accelerator in the vaporized state to provide the power required for the inflow of fluid into the engine.
  • FIG. 1 is a schematic diagram showing a thermal energy recovery system according to an embodiment of the present invention.
  • FIG. 2 is an exploded perspective view illustrating a fluid accelerator installed in a heat energy recovery system according to an exemplary embodiment of the present invention.
  • FIG. 3 is a partially cutaway perspective view illustrating the fluid accelerator shown in FIG. 2 in combination.
  • FIG. 4 is an axial cross-sectional view of the fluid accelerator shown in FIG. 2 in combination.
  • FIG. 5 is a plan view illustrating a spacer applied to the fluid accelerator illustrated in FIG. 2.
  • FIG. 6 is a plan view illustrating a modification of the spacer member applied to the fluid accelerator illustrated in FIG. 2.
  • FIG. 7 is a schematic diagram showing a conventional compressor system.
  • FIG. 8 is a schematic diagram showing a heat energy recovery system according to a first embodiment of the present invention, wherein the compressor system includes a heat exchanger, a recovery pipe, and a fluid accelerator.
  • FIG. 9 is a schematic diagram showing a heat energy recovery system according to a second embodiment of the present invention, in which an internal combustion engine is provided with a heat exchanger, a recovery tube, and a fluid accelerator.
  • FIG. 10 is a schematic diagram showing a conventional boiler system.
  • FIG. 11 is a schematic diagram showing a heat energy recovery system according to a third embodiment of the present invention, wherein a boiler system includes a heat exchanger, a recovery pipe, and a fluid accelerator.
  • FIG. 12 is a schematic diagram showing a conventional direct combustion gas turbine system.
  • FIG. 13 is a schematic diagram showing a conventional indirect combustion gas turbine system.
  • FIG. 14 is a schematic diagram showing a heat energy recovery system according to a fourth embodiment of the present invention, in which a gas turbine system includes a heat exchanger, a recovery pipe, and a fluid accelerator.
  • 15 is a schematic diagram for explaining the operation of the fuel cell.
  • 16 is a schematic diagram showing a conventional fuel cell system.
  • FIG. 17 is a schematic diagram showing the application of a thermal energy recovery system according to a fifth embodiment of the present invention to a fuel cell.
  • FIG. 1 is a schematic diagram showing a thermal energy recovery system according to an embodiment of the present invention.
  • the engine that changes the state by introducing a fluid and then discharges the engine transfers energy to the input fluid according to the type of fluid flowing in and the function of the engine, thereby changing the state of the input fluid or the energy of the input fluid. To convert to other forms of energy.
  • the engine 10 has an inlet for inlet and an outlet for discharging the output fluid, and the inlet is connected with an inlet pipe to distribute the input fluid and the outlet is connected with an outlet pipe for output.
  • the fluid can be circulated.
  • the inlet and the inlet pipe may be formed in plural according to the characteristics of the engine 10, the first input fluid can be circulated through the first inlet tube-the first inlet port and the second inlet tube-the second inlet port
  • the second input fluid can be distributed.
  • the first input fluid and the second input fluid may be different types of input fluid.
  • the input fluid may be air
  • the output fluid may be high temperature and high pressure air.
  • electrical or mechanical energy is supplied from the outside to compress air as an input fluid.
  • the input fluid may be air and fuel
  • the output fluid may be hot exhaust gas.
  • the air and the fuel are mixed and burned in the internal combustion engine to transmit mechanical power to the outside.
  • the input fluid may be air (O 2 ) and fuel
  • the output fluid is high temperature exhaust gas.
  • the boiler sends heat to the outside as air (O 2 ) and fuel are mixed and combusted.
  • the input fluid is divided into air O 2 and fuel H 2 , and the output fluid is a high temperature exhaust gas.
  • the fuel cell generates electrical energy by chemical reaction between air (O 2 ) and fuel (H 2 ).
  • the input fluid may be air and fuel in the direct combustion method, or air in the indirect combustion method.
  • the output fluid becomes hot exhaust gas or air.
  • the gas turbine outputs mechanical power.
  • Table 1 summarizes the state of the input fluid and the output fluid according to the engine applied above.
  • the working fluid may be mainly used water, the operation of the working fluid will be described in detail below.
  • the output fluid discharged through the engine 10 includes heat not only when energy is supplied from the engine 10 (eg, a compressor) but also when energy is generated (eg, an internal combustion engine, a fuel cell, etc.). This heat is released to the outside becomes a part of the energy loss.
  • the heat exchanger 15 is attached to the outlet pipe adjacent to the outlet of the engine 10.
  • the heat exchanger 15 recovers thermal energy from the high temperature output fluid discharged through the outlet pipe while circulating the working fluid therein.
  • "high temperature” means the temperature of the output fluid increased compared to the temperature of the input fluid, and as shown in Table 1, the temperature of the output fluid is set variously for each engine.
  • the heat exchanger 15 may have an inlet and an outlet, and the working fluid is introduced through the inlet of the heat exchanger 15 to receive heat energy from the output fluid and convert it into a gas (superheated gas) state (vaporization). Can be discharged through the outlet.
  • the working fluid is a fluid that can easily vaporize by absorbing heat energy, and a material that does not react specifically with the input fluid even when supplied inside the engine may be suitably used, and water may be typically used.
  • An input fluid accelerator 20 is connected to the inlet pipe adjacent to the inlet of the engine 10.
  • the input fluid accelerator 20 may increase the feed rate of the input fluid flowing into the engine 10.
  • the fluid accelerator will be described in detail below with reference to the drawings.
  • the input fluid accelerator 20 is connected through the heat exchanger 15 and the recovery pipe 12 outside the engine 10.
  • the recovery pipe 12 may supply the operating fluid having a changed state to the input fluid accelerator 20 by obtaining thermal energy radiated from the high temperature output fluid circulated to the outlet pipe.
  • the speed of the input fluid passing through the input fluid accelerator 20 may be increased due to the working fluid containing the heat energy transferred through the recovery pipe 12, and the energy efficiency of the engine 10 may be improved.
  • the output fluid accelerator 23 is connected to the outlet pipe in the rear of the heat exchanger 15 can increase the transfer speed of the output fluid.
  • the outlet of the heat exchanger 15 may be connected to the side of the output fluid accelerator 23 so that the vaporized working fluid may be supplied to the output fluid accelerator 23.
  • This output fluid accelerator 23 may be selectively applied in this embodiment.
  • FIG. 2 is an exploded perspective view illustrating a fluid accelerator installed in a heat energy recovery system according to an exemplary embodiment of the present invention. This structure of the fluid accelerator is applied to the output fluid accelerator as well as the input fluid accelerator in the above embodiment.
  • the fluid accelerator 20 has an inflow guide 212 and an inflow guide 212 whose inner cross-sectional area decreases toward the traveling direction of the input fluid (or output fluid) (y-axis direction in FIG. 2). It is connected to the outer body 210 including the receiving portion 214 is formed with a suction nozzle 216 for introducing the working fluid, and the inner body is inserted into the receiving portion 214 and the step portion 221 is formed along the outer peripheral surface 220, and a plurality of protrusions 234 installed between the outer body 210 and the inner body 220.
  • FIG. 3 is a partial cutaway perspective view of the fluid accelerator shown in FIG. 2 in combination, and FIG. 4 is an axial cross-sectional view.
  • the outer body 210 is made of a tubular (pipe) structure of the outer cylinder, the receiving is disposed behind the inlet guide 212 and the inlet guide 212 disposed in the front It comprises a portion 214.
  • the inflow guide 212 is formed so that the inner diameter gradually decreases from the front end toward the direction of travel of the input fluid (or output fluid) in the y-axis direction in FIG. 3.
  • the inner circumferential surface 212a is convex toward the axis center. It may be made of curved surfaces. Accordingly, the speed of the fluid passing through the inlet guide 212 is faster and the pressure is lowered.
  • the inner circumferential surface 212a of the inflow guide portion 212 is connected to the support surface 212b, which supports the inner circumferential surface 212a and the receiving portion 214, and is connected to the central axis of the receiving portion 214. It is formed perpendicular to the.
  • Receiving portion 214 is made of a cylindrical pipe (pipe) structure having a space in which the inner body 220 is fitted, the suction nozzle 216 is located in the front portion of the receiving portion 214 is opened to the outer peripheral surface Can introduce working fluid At this time, the working fluid introduced through the suction nozzle 216 has a pressure higher than atmospheric pressure.
  • the suction nozzle 216 is connected to the recovery pipe 12 may serve as a passage for supplying the working fluid into the receiving portion (214).
  • the inner body 220 is formed of a cylindrical tube (pipe) structure that is fitted to the receiving portion 214, as shown in Figure 2, the step portion 221 is formed in the front portion.
  • the stepped portion 221 has an outer diameter smaller than the inner diameter of the receiving portion 214 and is formed along the outer circumference of the inner body 220. Accordingly, as shown in FIG. 2, a space is formed between the stepped portion 221 and the accommodation portion 214, which becomes a distribution passage 225.
  • the distribution passage 225 is connected to the suction nozzle 216 to allow the working fluid introduced through the suction nozzle 216 to flow along the outer circumference of the inner body 220.
  • protrusions 234 are disposed between the outer body 210 and the inner body 220 to axially space the outer body 210 and the inner body 220, and the protrusions 234. ) Is formed to protrude from the inner circumferential surface of the ring-shaped spacer 230.
  • the spacer 230 is composed of the support 232 and the projections 234, the projections 234 are projected toward the center (C) of the support 232 and predetermined along the inner peripheral surface of the support 232 Spaced apart at intervals.
  • Support 232 is spaced apart from the inner body 220 is installed to abut the inner surface of the receiving portion 214, the front end of the inner body 220 is installed to abut the protrusions 234.
  • an induction passage 227 through which working fluid flows between neighboring protrusions 234 is provided. Is formed.
  • the guide passage 227 is formed along a distal end of the inner body 220, a plurality of spaced apart, the working fluid is introduced into the discharge guide 223 through the guide passage 227.
  • the working fluid may be uniformly divided and introduced into the fluid accelerator 20. .
  • first and second surfaces the surfaces of the outer body 210 and the inner body 220 facing each other with the guide passage 227 interposed therebetween in the receiving portion 214 of the outer body 210 may be referred to as first and second surfaces, respectively.
  • the first surface is formed perpendicular to the central axis of the receiving portion 214 and the second surface forms a curved surface 226 at least partially curved towards the discharge guide 223.
  • the first surface and the second surface may be directed toward the discharge guide unit 223 while the second surface is bent toward the central axis while maintaining a constant gap and the second surface is bent first. (See also enlargement of the hospital in FIG. 4).
  • a tubular discharge guide part 223 is formed at the rear of the curved surface 226, and the discharge guide part 223 is a moving direction of the input fluid (or output fluid) from the curved surface 226 (y-axis in FIG. 4). Direction), the inner diameter gradually increases.
  • the minimum inner diameter of the curved surface 226 may be formed to be the same as the minimum inner diameter of the discharge guide 223, so that the input fluid (or output fluid) introduced along the inlet guide 212 is discharge guide ( 223 is discharged stably.
  • the working fluid flowing into the inner body 220 flows toward the discharge guide part 223 along the curved surface 226 by the Coanda effect.
  • the Coanda effect means that the fluid proceeds in the direction where the energy is least consumed. If the curve appears in front of the flow direction, the fluid flows along the curved direction of the curve. This allows us to predict in advance the direction in which the fluid will travel.
  • the working fluid can be easily guided toward the discharge guide portion 223.
  • the fluid accelerator 20 according to the present embodiment is formed of a material having excellent corrosion resistance and excellent durability such as stainless steel, aluminum, or engineering plastic that can withstand high temperatures.
  • the outer body 210 and the inner body 220 may be coupled by interference fit, or may be fixed by welding or the like in the state in which the inner body 220 is fitted to the outer body 210, the accommodation of the outer body 210 It is also possible to form a female screw on the inner circumferential surface of the portion 214 and to form a screw thread on the outer circumferential surface of the inner body 220 to be screwed together.
  • the working fluid may be introduced into the fluid accelerator 20 through the suction nozzle 216, the distribution passage 225, and the guide passage 227.
  • a vacuum space V is formed at the rear of the induction passage 227. Due to the vacuum space (V), the inflow of the input fluid (or output fluid) is amplified and the conveying speed is increased, and the input fluid (or output fluid) of about 25 times of the working fluid introduced into the suction nozzle 216 is accelerated. 20 may flow into the interior.
  • FIG. 5 is a plan view illustrating a spacer applied to the fluid accelerator shown in FIG. 2
  • FIG. 6 is a plan view illustrating a modification of the spacer.
  • the spacer 230 of the present exemplary embodiment includes a ring-shaped support 232 and a plurality of protrusions 234 protruding from an inner circumferential surface thereof, and the protrusions 234 are supported by the support 232. It is arranged to face the center (C) of.
  • These protrusions 234 form the induction passage 227 of the fluid accelerator 20 according to the present embodiment, and the working fluid introduced through the suction nozzle 216 at a high speed toward the central axis of the receiving portion 214. Will contribute to spraying.
  • the spacer 330 includes a ring-shaped support 332 and a plurality of protrusions 334 protruding from an inner circumferential surface of the support 332.
  • the protrusions 334 are arranged to face away from the center of the support 332. That is, the protrusions 334 are formed to be inclined to form a set angle (a) with the inner circumference of the support 332, the angle (a) is made of an angle smaller than 90 degrees.
  • the working fluid When spraying the working fluid introduced through the guide passage formed by the protrusions 334, the working fluid forms a vortex and flows toward the central axis of the receiving portion 214 by the force of the inputted input fluid.
  • FIG. 7 is a schematic diagram showing a conventional compressor system
  • Figure 8 is a schematic diagram showing a heat energy recovery system according to a first embodiment of the present invention, the heat energy recovery is provided with a heat exchanger, a recovery tube and a fluid accelerator in the compressor system System.
  • air at room temperature and pressure is introduced into the compressor 30 and discharged into high-temperature and high-pressure air.
  • the discharged high-temperature and high-pressure air is stored in the storage tank 32. .
  • the stored high temperature, high pressure air may be used as compressed air by the user after the temperature is dropped through the freezer 34. Water condensed with water in the air during the temperature drop in the freezer 34 may be discharged through the outlet.
  • a fluid accelerator 38 is provided at the front (inlet side) of the compressor 30, and a heat exchanger is disposed at the rear (outlet side) of the compressor 30.
  • 36 is provided, the fluid accelerator 38 and the heat exchanger 36 is connected via a recovery pipe 37.
  • water is introduced into the working fluid by the pump (35) to obtain thermal energy from the high temperature output fluid discharged from the compressor (30) and through the recovery pipe (37) in a vaporized state. Supplied to the fluid accelerator 38.
  • the water used as the working fluid absorbs heat energy from the exhaust gas of the high temperature compressor 30 while circulating the heat exchanger 36 to become a high pressure steam. Relatively, the temperature at the outlet side of the compressor 30 is lowered (as the temperature is lowered) and the pressure is lowered, and as a result, the required power of the compressor 30 for air compression can be reduced.
  • the air compressed by the compressor 30 is cooled in the freezer 34 to remove moisture.
  • the exhaust gas is already deprived of heat energy in the heat exchanger 36, and thus, the air in the freezer 34 is cooled in comparison with the conventional air. The effect of reducing the load can be expected.
  • the working fluid which is a high temperature, high pressure steam while passing through the heat exchanger 36 is supplied to the fluid accelerator 38 to drive it (increasing the speed of the input fluid), which is necessary for inflow of air into the compressor 30. It can function to provide power, thereby also having the effect of reducing the required power of the compressor (30).
  • FIG. 9 is a schematic diagram showing a heat energy recovery system according to a second embodiment of the present invention, in which an internal combustion engine is provided with a heat exchanger, a recovery tube, and a fluid accelerator.
  • the inlet pipe 41 is connected to the inlet of the internal combustion engine 40
  • the outlet pipe 43 is connected to the outlet
  • the fluid accelerator 48 is adjacent to the inlet and the inlet pipe 41 and Connected.
  • the heat exchanger 46 is provided on the outer surface of the outlet pipe 43
  • the recovery pipe 47 is connected to the side of the heat exchanger 46 and the fluid accelerator 48.
  • water is introduced into the heat exchanger 46 into the working fluid.
  • the water in the heat exchanger 46 is heated and supplied to the fluid accelerator 48 through the recovery pipe 47 in the form of vaporized vapor. do.
  • the steam is injected into the input fluid passing through the fluid accelerator 48 through the side suction nozzle of the fluid accelerator 48, the input fluid may be accelerated and supplied to the internal combustion engine 40 by the action of the fluid accelerator 48. .
  • the fluid in front of the internal combustion engine 40 (inlet side) Accelerator 48 can reduce the power burden required for air intake, and the heat exchanger 46 through which the working fluid flows lowers the temperature of the exhaust gas, lowers the pressure, and ultimately reduces the exhaust power requirement. Will be. That is, the waste heat to be discarded can be recovered to improve the efficiency of the internal combustion engine.
  • the internal combustion engine 40 in particular, by amplifying the inflow of air relative to the fuel, it is possible to induce complete combustion, thereby improving energy efficiency and reducing the smoke emitted due to incomplete combustion.
  • FIG. 10 is a schematic diagram showing a conventional boiler system
  • Figure 11 is a schematic diagram showing a heat energy recovery system according to a third embodiment of the present invention, the heat energy recovery with a heat exchanger, a recovery tube and a fluid accelerator in the boiler system System.
  • air and fuel are supplied through an inlet of the boiler 50, and the supplied air and fuel are burned in the boiler 50 and generate heat.
  • the boiler 50 also absorbs the heat energy generated in the combustion process while being supplied and distributed from the outside to be discharged from the boiler 50 in a gas (vapor) state, thereby performing a heating function.
  • a blower 52 is provided on the air inlet side of the boiler 50 to inlet air, and a blower 53 is provided on the outlet side of the boiler 50 to exhaust high-temperature exhaust gas.
  • an input fluid accelerator 58 is provided in an inlet passage of air (inlet side) of the front of the boiler 50, and a rear (outlet side) of the boiler 50 is provided.
  • the heat exchanger 56 and the output fluid accelerator 59 are sequentially provided in the exhaust gas discharge passage.
  • the heat exchanger 56 is connected to the input fluid accelerator 58 and the output fluid accelerator 59 through the recovery pipe 57, respectively, and is a working fluid that absorbs the heat energy of the exhaust gas while flowing into the heat exchanger 56. Water is supplied to the input fluid accelerator 58 and the output fluid accelerator 59 in a vaporized state, respectively.
  • the waste heat discarded together with the exhaust gas is driven to drive the input fluid accelerator 58 and the output fluid accelerator 59 so that the blower 52 and the expensive blower in the existing system ( 53) can be omitted, and the power required by these blowers 52 and the blowers 53 can be reduced. Further, the omission of the mechanically driven blower 52 and the blower 53 can be expected to reduce the maintenance cost.
  • FIG. 12 is a schematic diagram showing a conventional direct combustion gas turbine system
  • Figure 13 is a schematic diagram showing a conventional indirect combustion gas turbine system
  • Figure 14 is a thermal energy recovery system according to a fourth embodiment of the present invention As a schematic diagram, it is a heat energy recovery system provided with a heat exchanger, a recovery pipe, and a fluid accelerator in a gas turbine system.
  • the conventional direct combustion gas turbine system passes air through the compressor 60 to compress the air, and then supplies the air to the combustion chamber 61, and supplies the combustion chamber with fuel to burn the exhaust gas generated after combustion.
  • the turbine 62 By passing gas through the turbine 62, the turbine 62 is rotated to obtain mechanical power.
  • the compressor 60 is connected to the turbine 62 and the shaft to obtain a compressive force of air from the rotational kinetic energy of the turbine 62.
  • the conventional indirect combustion gas turbine system has a heat exchanger 63 disposed in place of the combustion chamber 61 in comparison with the direct combustion gas turbine system so that the air passing through the compressor 60 is transferred to the heat exchanger ( Thermal energy is obtained while passing through 63, and the exhaust gas thus obtained passes through the turbine 62, thereby rotating the turbine 62 to obtain mechanical power.
  • an input fluid accelerator 68 is provided in an inflow passage of air (inlet side) of the front of the compressor 60, and the rear (outlet side) of the turbine 62.
  • the heat exchanger 66 and the output fluid accelerator 69 are sequentially provided in the exhaust gas discharge passage.
  • the heat exchanger 66 is connected to the input fluid accelerator 68 and the output fluid accelerator 69 through a recovery pipe 67, respectively, and is a working fluid absorbing thermal energy of exhaust gas while being flowed into the heat exchanger 66. Water is supplied to the input fluid accelerator 68 and the output fluid accelerator 69 in a vaporized state, respectively.
  • the input fluid accelerator 68 and the output fluid accelerator 69 may be driven using the heat energy of the exhaust gas passing through the turbine 62, and thus the efficiency of the gas turbine system. You can expect an improvement.
  • FIG. 15 is a schematic diagram illustrating the operation of a fuel cell
  • FIG. 16 is a schematic diagram illustrating a conventional fuel cell system
  • FIG. 17 is a thermal energy recovery system according to a fifth embodiment of the present invention. It is a schematic diagram shown.
  • the fuel cell (module) is basically configured such that the anode 75 and the cathode 73 are in contact with the electrolyte membrane 71 interposed therebetween.
  • the fuel electrode (75) is a fuel of hydrogen (H 2) supplied to the hydrogen ion (H +) and electrons (e -), the air electrode through the decomposed with, where hydrogen ions (H +) is an electrolyte membrane (71) Moving to 73, electrons (e ⁇ ) generate current through an external circuit.
  • hydrogen ions (H + ), electrons (e ⁇ ), and oxygen (O 2 ) are combined to generate water (H 2 O) together with heat.
  • air O 2 and fuel H 2 are supplied through an inlet of a fuel cell (module) 80, and the supplied air O 2 and fuel H are supplied.
  • 2 produces power through an electrochemical reaction in the fuel cell (module) 80 and discharges exhaust gas including water (H 2 O) and heat.
  • a blower 82 is provided in the passage through which the air of the fuel cell (module) 80 flows in order to introduce the air, and a exhaust fan 83 is provided in the passage in which the exhaust gas is discharged, thereby exhausting the exhaust gas. can do.
  • a part of the power produced by the fuel cell (module) 80 may be used to operate the blower 82.
  • the temperature of the exhaust gas is about 650 degrees Celsius for MCFC and about 1,000 degrees Celsius for SOFC.
  • an input fluid accelerator 88 is provided in an inflow passage of air (inlet side) of the front of the fuel cell (module) 80, and the fuel cell (module)
  • the heat exchanger 86 and the output fluid accelerator 89 are sequentially provided in the rear (outlet side) exhaust gas discharge passage of the 80.
  • the heat exchanger 86 is connected to the input fluid accelerator 88 and the output fluid accelerator 89 through a recovery pipe 87, respectively, and is a working fluid absorbing thermal energy of exhaust gas while being flowed into the heat exchanger 86. Water is supplied to the input fluid accelerator 88 and the output fluid accelerator 89 in a vaporized state, respectively.
  • the efficiency of the fuel cell system is about 53% in the case of MCFC, and the blower 82 and the blower 83 consume approximately 10% of the generated power of the fuel cell system. Therefore, if the blower 82 and the blower 83 are not used, the efficiency may be improved by 10% or more.
  • a stack of 250-kw fuel cells produces 280 kw, of which 30 kw is consumed by the fuel cell system itself to drive a blower, a blower, etc., so that the net power is 250 kw. That is, since the fluid accelerator provided in the system of the present embodiment does not consume a separate required power, the efficiency can be improved.

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  • 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

L'invention concerne un système de récupération d'énergie thermique pour la récupération et l'utilisation de l'énergie thermique produite par le fonctionnement d'un moteur. Ce système comprend i) un moteur à orifice d'entrée de fluide d'entrée et un orifice de sortie de fluide de sortie, transférant l'énergie au fluide d'entrée pour modifier l'état de ce fluide ou en convertir l'énergie sous une autre forme, ii) une conduite d'entrée reliée à l'orifice d'entrée du moteur, et permettant au fluide d'entrée de s'écouler vers le moteur, iii) un accélérateur de fluide d'entrée relié à la conduite d'entrée pour augmenter la vitesse de transfert du fluide d'entrée pénétrant dans le moteur, iv) une conduite de sortie reliée à l'orifice de sortie du moteur, et permettant au fluide de sortie de s'écouler à l'extérieur, l'état de ce fluide étant modifié dans le moteur, v) un échangeur thermique monté sur la conduite de sortie, et permettant à un fluide d'activation de s'écouler pour récupérer l'énergie thermique depuis le fluide de sortie, et vi) une conduite de récupération reliant entre eux l'échangeur thermique et l'accélérateur de fluide d'entrée, et fournissant le fluide d'activation, dont l'état est modifié par l'énergie thermique acquise depuis le fluide de sortie, à l'accélérateur de fluide d'entrée.
PCT/KR2009/000292 2008-09-23 2009-01-20 Système de récupération d'énergie thermique WO2010035927A1 (fr)

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KR10-2008-0093061 2008-09-23

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8844291B2 (en) 2010-12-10 2014-09-30 Vaporgenics Inc. Universal heat engine
CN107364309A (zh) * 2017-08-22 2017-11-21 青岛大学 一种汽车尾气余热回收利用系统
US11137177B1 (en) 2019-03-16 2021-10-05 Vaporgemics, Inc Internal return pump

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5402938A (en) * 1993-09-17 1995-04-04 Exair Corporation Fluid amplifier with improved operating range using tapered shim
KR19980036793A (ko) * 1996-11-19 1998-08-05 박병재 배기정화 효율 향상장치
JP2889915B2 (ja) * 1989-03-02 1999-05-10 カール ヘインツ メーゲンビヤー 水蒸発器
JP2001165002A (ja) * 1999-11-09 2001-06-19 Caterpillar Inc 内燃機関の排気ガス循環システムのための吸入ベンチュリ
KR100708369B1 (ko) * 2006-03-07 2007-04-19 안재혁 폐가스 배기 제어시스템

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2889915B2 (ja) * 1989-03-02 1999-05-10 カール ヘインツ メーゲンビヤー 水蒸発器
US5402938A (en) * 1993-09-17 1995-04-04 Exair Corporation Fluid amplifier with improved operating range using tapered shim
KR19980036793A (ko) * 1996-11-19 1998-08-05 박병재 배기정화 효율 향상장치
JP2001165002A (ja) * 1999-11-09 2001-06-19 Caterpillar Inc 内燃機関の排気ガス循環システムのための吸入ベンチュリ
KR100708369B1 (ko) * 2006-03-07 2007-04-19 안재혁 폐가스 배기 제어시스템

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8844291B2 (en) 2010-12-10 2014-09-30 Vaporgenics Inc. Universal heat engine
CN107364309A (zh) * 2017-08-22 2017-11-21 青岛大学 一种汽车尾气余热回收利用系统
CN107364309B (zh) * 2017-08-22 2023-08-04 青岛大学 一种汽车尾气余热回收利用系统
US11137177B1 (en) 2019-03-16 2021-10-05 Vaporgemics, Inc Internal return pump

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