WO2010035927A1

WO2010035927A1 - Thermal energy recovery system

Info

Publication number: WO2010035927A1
Application number: PCT/KR2009/000292
Authority: WO
Inventors: 김성완
Original assignee: 주식회사 자이벡
Priority date: 2008-09-23
Filing date: 2009-01-20
Publication date: 2010-04-01

Abstract

Disclosed is a thermal energy recovery system which recovers and utilizes thermal energy generated by the operation of an engine, said thermal energy recovery system comprising i) an engine which has an inlet port for introducing inflow fluid and an outlet port for discharging outflow fluid, and which transfers energy to the inflow fluid to change the state of the inflow fluid or convert the energy of the inflow fluid into energy of another form, ii) an inlet pipe which is connected to the inlet port of the engine, and enables the inflow fluid to flow to supply the inflow fluid to the engine, iii) an inflow fluid accelerator which is connected to the inlet pipe to increase the transfer speed of the inflow fluid being introduced into the engine, iv) an outlet pipe which is connected to the outlet port of the engine, and enables the outflow fluid to flow, the state of which is changed in the engine, to the outside of the engine, v) a heat exchanger which is mounted on the outlet pipe, and which enables an actuating fluid to flow to recover thermal energy from the outflow fluid, and vi) a recovery pipe which interconnects the heat exchanger and the inflow fluid accelerator, and supplies the actuating fluid, the state of which is changed by the thermal energy acquired from the outflow fluid, to the inflow fluid accelerator.

Description

Thermal energy recovery system

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.

On the other hand, 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. Unlike the existing power generation technology (fuel combustion steam generation turbine drive generator drive), there is no combustion process or driving device, so it is not only high efficiency but also a relatively low harmful component contained in exhaust gas.

Such 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. For reference, 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 according to an embodiment of the present invention, 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. In communication with the outlet of the heat exchanger, the working fluid in the vaporized state can be supplied to the input fluid accelerator.

It may include an output fluid accelerator which is connected to the outlet pipe from the rear of the heat exchanger to increase the transfer speed of the output fluid. 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.

As described above, according to the present invention, there is an effect that can improve the energy efficiency of the engine by recovering the heat energy released to the outside after the action in the engine to be delivered to the fluid supplied to the engine to convert the flow rate of the fluid. .

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.

In addition, 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.

1 is a schematic diagram showing a thermal energy recovery system according to an embodiment of the present invention.

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.

3 is a partially cutaway perspective view illustrating the fluid accelerator shown in FIG. 2 in combination.

4 is an axial cross-sectional view of the fluid accelerator shown in FIG. 2 in combination.

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.

7 is a schematic diagram showing a conventional compressor system.

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.

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.

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.

12 is a schematic diagram showing a conventional direct combustion gas turbine system.

13 is a schematic diagram showing a conventional indirect combustion gas turbine system.

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.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings so that those skilled in the art may easily implement the present invention. As those skilled in the art would realize, the described embodiments may be modified in various different ways, all without departing from the spirit or scope of the present invention. In the drawings, parts irrelevant to the description are omitted in order to clearly describe the present invention, and like reference numerals designate like elements throughout the specification.

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.

Referring to FIG. 1, 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. In this case, the first input fluid and the second input fluid may be different types of input fluid.

For example, when the engine 10 is a compressor, the input fluid may be air, and the output fluid may be high temperature and high pressure air. In order to function as the compressor, electrical or mechanical energy is supplied from the outside to compress air as an input fluid.

When the engine 10 is an internal combustion engine, the input fluid may be air and fuel, and 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.

When the engine 10 is a boiler, the input fluid may be air (O ₂ ) and fuel, and 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.

When the engine 10 is a fuel cell, 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 ).

When the engine 10 is a gas turbine, 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. In addition, the working fluid may be mainly used water, the operation of the working fluid will be described in detail below.

Table 1

Example (Institution)	compressor	An internal combustion engine	Boiler	Fuel cell	Gas turbine
Example (Institution)	compressor	An internal combustion engine	Boiler	Fuel cell	Direct combustion method	Indirect combustion method
First input fluid	air	air	Air (oxygen)	Air (oxygen)	air	air
Second input fluid	-	fuel	fuel	fuel	fuel	-
High temperature output fluid (pressure, temperature)	Air (7 atmospheres, 300 ℃ or more)	Exhaust gas (atmospheric pressure, 800 ℃)	Exhaust gas (350 ℃)	Exhaust gas (650 ~ 1,000 ℃)	Exhaust gas (800 ~ 900 ℃)	Air (600 ~ 700 ℃)
Working fluid	water	water	water	water	water	water
Power	Mechanical power input	Mechanical power output	Heat output	Power output	Mechanical power output	Heat input
Power	Mechanical power input	Mechanical power output	Heat output	Power output	Mechanical power output	Mechanical power output

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.

In the system of the present embodiment, 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. Here, "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. As such, 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. .

On the other hand, 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.

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.

Referring to FIG. 2, 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.

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.

3 and 4, 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. For example, 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. In addition, 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.

As shown in FIG. 2, 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.

That is, 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.

As shown in FIG. 3, when the outer body 210 and the inner body 220 are spaced apart by 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.

As described above, since the plurality of protrusions 234 are spaced apart and the working fluid is supplied to the space between the protrusions 234, the working fluid may be uniformly divided and introduced into the fluid accelerator 20. .

Meanwhile, 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. At this time, 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. At this time, 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.

As such, when the curved surface 226 is formed at a portion where the guide passage 227 and the discharge guide portion 223 meet, 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.

On the other hand, 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.

In this structure, 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. In addition, when a working fluid having a high pressure flows into the fluid accelerator 20, 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.

5 is a plan view illustrating a spacer applied to the fluid accelerator shown in FIG. 2, and FIG. 6 is a plan view illustrating a modification of the spacer.

Referring to FIG. 5, 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.

Meanwhile, referring to FIG. 6, 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. In the spacer 330 according to the present modification, 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.

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.

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.

Referring to FIG. 7, in the conventional compressor 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.

Referring to FIG. 8, in the heat energy recovery system according to the present embodiment, 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. Into the heat exchanger (36), 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.

In the heat energy recovery system according to the present embodiment, 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.

In addition, 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.

On the other hand, 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).

9, 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. And 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. In addition, water is introduced into the heat exchanger 46 into the working fluid.

Therefore, due to the heat radiated by the exhaust gas discharged through the internal combustion engine 40, 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. As 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. .

Therefore, in the existing internal combustion engine, part of the output is consumed by pumping power for air intake and exhaust gas discharge, whereas in the heat energy recovery system according to the present embodiment, 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.

In 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.

In addition, increasing the amount of air flowing into the internal combustion engine can provide more fuel. As a result, a relatively higher output can be obtained than the size of the internal combustion engine. In the case of automobile engines, the engine of the same size and weight can produce a greater power output, thereby improving fuel economy.

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.

Referring to FIG. 10, in the conventional boiler 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.

Referring to FIG. 11, in the heat energy recovery system according to the present embodiment, 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.

According to the heat energy recovery system according to the present embodiment, 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.

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.

Referring to FIG. 12, 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. 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.

Referring to FIG. 13, 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.

Referring to FIG. 14, in the heat energy recovery system according to the present embodiment, 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.

In the heat energy recovery system according to the present embodiment, 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, and FIG. 17 is a thermal energy recovery system according to a fifth embodiment of the present invention. It is a schematic diagram shown.

Referring to FIG. 15, 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. Wherein 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. In the cathode 73, hydrogen ions (H ⁺ ), electrons (e ⁻ ), and oxygen (O ₂ ) are combined to generate water (H ₂ O) together with heat.

Referring to FIG. 16, in the conventional fuel cell system, 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. At this time, 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.

Referring to FIG. 17, in the heat energy recovery system according to the present embodiment, 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. For example, 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.

Although the preferred embodiments of the present invention have been described above, the present invention is not limited thereto, and various modifications and changes can be made within the scope of the claims and the detailed description of the invention and the accompanying drawings. Naturally, it belongs to the scope of the invention.

Claims

An engine having an inlet for inflow of the input fluid and an outlet for discharging the output fluid, the engine for transmitting energy to the input fluid to change the state of the input fluid or to convert the energy of the input fluid into other forms of energy;

An inlet pipe connected to an inlet of the engine and circulating the input fluid to supply to the engine;

An input fluid accelerator connected to the inlet pipe to increase a conveying speed of the input fluid flowing into the engine;

An outlet pipe connected to an outlet of the engine and configured to distribute an output fluid whose state is changed in the engine to the outside of the engine;

A heat exchanger mounted to the outlet pipe and configured to recover thermal energy from the output fluid while circulating a working fluid;

And a recovery tube connecting the heat exchanger and the input fluid accelerator to supply the working fluid whose state is changed by obtaining thermal energy from the output fluid to the input fluid accelerator.
The method of claim 1,

The input fluid accelerator has a tubular shape, and includes a convex portion curved toward the center, and an acceleration portion having an intake nozzle for communicating the interior of the convex portion with the recovery tube.
The method of claim 1,

The heat exchanger has an inlet and an outlet,

The working fluid is introduced through the inlet of the heat exchanger and receives heat energy from the output fluid and is discharged through the outlet in a vaporized state.

The recovery pipe is in communication with the outlet of the heat exchanger is a thermal energy recovery system for supplying the working fluid in the vaporized state to the input fluid accelerator.
The method of claim 3, wherein

And an output fluid accelerator configured to be connected to the outlet pipe at the rear of the heat exchanger to increase a transfer speed of the output fluid.
The method of claim 4, wherein

The output fluid accelerator has a pipe shape, and includes a convex portion curved toward the center, and an acceleration portion having an intake nozzle for communicating the interior of the condensation portion with the recovery tube.
The method of claim 5,

And a discharge port of the heat exchanger is connected to a suction nozzle of the output fluid accelerator to supply the vaporized working fluid to the output fluid accelerator.
The method of claim 1,

The engine has a plurality of different inlets, the inlet pipe is connected to each of the different inlets for the thermal energy recovery system for supplying different types of input fluid.
The method of claim 1,

Wherein said working fluid is water.
The method of claim 1,

The engine is a heat energy recovery system is a compressor for compressing the input fluid by receiving electrical or mechanical energy from the outside.
The method of claim 1,

The engine is a heat energy recovery system is an internal combustion engine that generates power to the outside while the fuel and air flows into the input fluid to explode inside the engine.
The method of claim 1,

Wherein the engine is a heat energy recovery system is a boiler to inject the fuel and air into the input fluid to generate heat energy while burning inside the engine to vaporize the water flowing through the engine to discharge in the steam state.
The method of claim 1,

The engine is a heat energy recovery system that is a gas turbine that generates mechanical power using heat energy.
The method of claim 1,

The engine is a heat energy recovery system that is a fuel cell that generates electricity by introducing air and fuel into the input fluid to cause electrochemical action inside the engine.