KR20200128594A - A system for high efficiency energy conversion cycle by recycling latent heat of vaporization - Google Patents

Abstract

The present invention relates to a method and a generator (system) for a high-efficiency energy conversion cycle by recycling latent heat during evaporation. In one embodiment, the present invention can achieve improved efficiency by reducing the amount of waste heat discharged to the atmosphere in the conventional power plant cycle design by generating multiple turbine cycles, and the latent heat during evaporation of the first cycle is the second cycle. The waste heat of the second cycle (latent heat during evaporation) is transferred to the input of the third cycle and continues in this way. Only waste heat from the final cycle is released to the atmosphere.

Description

A system for high efficiency energy conversion cycle by recycling latent heat during evaporation {A SYSTEM FOR HIGH EFFICIENCY ENERGY CONVERSION CYCLE BY RECYCLING LATENT HEAT OF VAPORIZATION}

The present invention relates generally to power generation, and more specifically, to a multistage system for a power generation turbine that is driven efficiently.

Currently, most of the electricity in the world is used to generate electricity by heating water with high pressure and high temperature steam and then rotating a turbine that rotates a generator. To heat the water, any number of means can be used, such as solar, coal, gas, nuclear power, and the like. When high pressure water vapor enters the turbine, the water vapor collides with the turbine blades and provides some of its energy to the turbine. After the water vapor collides with the turbine blades in large numbers, the water vapor loses a significant amount of energy, is discharged from the turbine and flows into a condenser at low pressure, cooling the water vapor until it becomes water. The pump then pumps the water back to the high pressure input of the cycle and heats it up again with steam and the cycle continues.

The problem with this setup is that the condenser must remove the latent heat during evaporation so that the water vapor must be converted back to a liquid, and the pump must be able to pump the fluid back to the beginning of the cycle using only minimal energy. After that, the energy is discarded to the surroundings as waste heat. In the case of water, the latent heat of evaporation is almost 2257 kJ/Kg, which corresponds to a fairly large amount of energy. This is between 40-60% (depending on operating temperature) or more of the total thermal energy added to the hydraulic fluid per cycle. Therefore, it is difficult to achieve 40% efficiency even for the best power plants. If such waste latent heat can be used and converted to electricity, the efficiency of any power plant can be significantly improved.

There are a number of existing power cycles, and the existing power cycles, for example, ranking cycles and other cycles, have a problem that their efficiency is very limited due to a large amount of low-grade waste heat that must be discharged to the atmosphere or the surroundings. Most of the latent heat during evaporation (or condensation) must be released as waste heat, which significantly limits the efficiency of any cycle.

The present invention provides a system (generator) and method for a high-efficiency energy conversion cycle by recycling latent heat during evaporation. It should be noted that the above is not intended to limit the scope of the invention to only the features described herein.

The condenser must remove the latent heat from evaporation to convert the water vapor back to liquid, and the pump must be able to pump the fluid back to the beginning of the cycle using only minimal energy. Then, this energy (latent heat) is discarded to the surroundings as waste heat. Therefore, it is difficult to achieve 40% efficiency even for the best power plants.

The present invention solves the above-mentioned technical problems effectively and at low cost by not discharging latent heat during evaporation of any stage to the atmosphere and transferring it to the next input stage. It provides a mechanism that can significantly increase efficiency.

In one embodiment, the basic object of the present invention is to solve the drawbacks/defects mentioned in the prior art by increasing the efficiency in converting heat into electricity in all existing and future power plants.

In one embodiment, the present invention provides a method of converting thermal energy into electrical energy in a power plant with high efficiency using current technology.

In one embodiment, the efficiency improved by the present invention is realized by reducing the amount of waste heat released to the atmosphere in existing power plant cycle designs.

In one embodiment, in the present invention, the latent heat at the time of evaporation of the first cycle is transferred to the input stage of the second cycle, and the waste heat of the second cycle (latent heat at the time of evaporation) is transferred to the input stage of the third cycle. It provides a mechanism for generating multiple turbine cycles, which then continues as such. Only waste heat from the final cycle is released to the atmosphere.

In one embodiment, the present invention makes it possible to significantly improve the efficiency of a power plant by using latent waste heat and converting the latent waste heat into electricity. In addition, the waste heat exchange mechanism can be used with any heat based power system, even though the final output is a certain form of non electrical output. .

In one embodiment, the present invention improves the efficiency of any power cycle by transferring the latent heat during evaporation of any stage to the input stage of the next stage instead of discharging it to the atmosphere.

In one embodiment, if the working fluid and turbine discharge temperature and pressure are appropriately selected, the present invention can transfer all the latent heat during evaporation to the next stage, and thus transfer the hydraulic oil of that stage to the desired temperature. It makes it possible to significantly reduce the amount of energy required to heat. Accordingly, after the first stage, the efficiency of all stages is significantly improved, and accordingly, the overall efficiency is also significantly improved.

In order to improve the overall performance of any power cycle by transferring the latent heat during evaporation of any stage to the next stage instead of discharging it to the atmosphere, embodiments of the present invention provide a plurality of aspects of this patent application. do. The plurality of aspects provide a system and method for a high-efficiency energy conversion cycle by recycling latent heat during evaporation. The technical solution is as follows:

In another aspect, a multistage generator with at least a two stage system is described. The generator comprises: a first stage power cycle comprising a first hydraulic oil, a boiler, a turbine, a heat exchanger, a pump, etc. and configured to generate electricity; And a second stage power cycle comprising a second hydraulic oil, a boiler, a turbine, a heat exchanger, a pump, etc., and configured to generate electricity, wherein the second hydraulic oil is waste heat generated from the first stage cycle for generating electricity (evaporation and / Or latent heat during condensation).

In yet another aspect, a method for generating electricity using a generator having at least two stages of power cycle is provided. The method includes: generating electricity by using a first stage power cycle comprising a first hydraulic oil, a boiler, a turbine, a heat exchanger, a pump, and the like; And generating electricity using a second stage latent heat exchange mechanism and a turbine cycle containing the second hydraulic oil; The second hydraulic oil absorbs waste heat (latent heat during evaporation and/or condensation) generated from the first stage in a latent heat exchange mechanism for generating electricity.

In one embodiment of the present invention, the low quality waste heat of the first stage is transferred to the input stage of the second cycle, and the waste heat of the second cycle is transferred to the input stage of the third cycle, and thereafter continues as such. . The more stages there are, the better the final overall efficiency will be, but adding more stages will cost more. In addition, it may not be possible to find a sufficient number of hydraulic fluids with the correct physical properties to have an unlimited number of stages. In describing the above process in detail, a two stage will suffice to explain the present concept and thus the following description will follow a two stage system.

The detailed description of the present invention is described with reference to the accompanying drawings. In the drawings, the leftmost number of the reference numerals indicates the first appearing reference numeral. Throughout this specification, the same reference numerals are used to indicate similar configurations and components.
1 is a schematic diagram of a conventional power plant cycle (prior art).
Fig. 2 is a schematic diagram of a multistage cycle that achieves very high efficiency according to an embodiment of the present invention.
3 is a diagram illustrating an example of a two-stage system when water and ammonia are used as hydraulic oils according to an embodiment of the present invention.
4 illustrates a method for generating electricity using a generator with at least two stages of latent heat exchange mechanism in accordance with an embodiment of the present invention.
5 is a diagram illustrating a method performed during a first stage latent heat exchange mechanism 1000 according to an embodiment of the present invention.
6 is a diagram illustrating a method performed during a second stage latent heat exchange mechanism 2000 according to an embodiment of the present invention.

The following description clearly describes the technical solutions of the embodiments of the present invention with reference to the accompanying drawings. These embodiments are only a part, not all, of the embodiments of the present invention. Those skilled in the art will appreciate that other embodiments according to the embodiments of the present invention are also within the protection scope of the present invention.

In the following, a detailed description of one or more embodiments of the present invention is provided along with accompanying drawings illustrating the concept of the present invention. The present invention has been described with respect to these embodiments, but is not limited thereto. The scope of the invention is defined solely by the claims, and the invention includes various alternatives, modifications and equivalents. Various specific contents are described below in order to understand the present invention in detail. These contents are provided as specific examples and the invention may be practiced in accordance with the claims without any or all of these specific contents. For clarity, technical matters known in the technical field to which the present invention belongs will not be described in detail.

It should be noted that in order to better understand this explanation, it is necessary to at least understand the basic thermodynamic concepts.

Now, referring to FIG. 1, a diagram illustrating the basic concept of a conventional power plant cycle as a prior art.

Although the various aspects described for a high-efficiency energy conversion cycle by recycling the latent heat upon evaporation may be implemented in any number of different systems, environments, and/or configurations, the above embodiments relate to the following representative systems. Is described.

Turning now to Fig. 2, a schematic diagram of a multistage cycle is shown that realizes very high efficiency according to an embodiment of the present invention.

In one embodiment, the low quality waste heat of the first stage is transferred to the input stage of the second cycle, and the waste heat of the second cycle is transferred to the input stage of the third cycle, and thereafter continues as such. . The more stages there are, the better the final overall efficiency will be, but adding more stages will cost more. In addition, it may not be possible to find a sufficient number of hydraulic fluids with the correct physical properties to have an unlimited number of stages.

In one embodiment, in order to describe the process in detail, a two-stage is sufficient to describe the concept, and thus the following description is a description according to a two-stage system.

Now, referring to FIG. 3, a diagram illustrating an example of a two-stage system when water and ammonia are used as hydraulic oils according to an embodiment of the present invention are illustrated.

In one embodiment, for the sake of simplicity, only one high and low pressure turbine is shown in stage A (1000) and only one single stage turbine is shown in stage B (2000). In addition, descriptions of all conventional techniques for improving cycle efficiency and performance, such as heat storage, open feed water heaters, and other small variations, are intentionally excluded. All existing techniques for improving efficiency can still be used on any stage with an improved design. All thermal and physical property values mentioned in this entire document can be found on the U.S. National Standards and Technology (NIST) website (www.nist.com) or a more specific website (webbook.nist.gov/chemistry/fluid). have.

In one embodiment, a wide range of fluids may be used in the improved system of several stages (1000 or 2000), but for illustrative purposes, in this specification, water is used as the first hydraulic oil in stage A (1000) and stage B (2000). Ammonia is used as the second hydraulic oil. Stage A (1000) is the first stage, and liquid water is delivered from point 13 by pump A 1 to boiler A 2 at high pressure, such as at 250 bar (or any other desired pressure). In boiler 2, liquid water is heated to a high temperature, such as 600° C. (or any other desired temperature) and exits boiler A 2 at point 10 as a supercritical or heated fluid. The high temperature and high pressure supercritical fluid is expanded in high pressure turbine 3 and after a significant temperature and pressure drop, returns to boiler A 2, reheated to 600° C. at 50 bar (or any other desired temperature and pressure) and produces efficiency. So that it is sent to the low pressure turbine 4 for final energy extraction.

In the existing system, water vapor/steam is discharged from the turbine in an almost vacuum state at point 11 and the latent heat upon evaporation (or condensation) is removed as waste heat in the condenser using cooling water. Accordingly, water vapor can be converted back to a liquid at point 12 and this liquid can be pumped back into the system at high pressure to repeat the cycle.

In the present invention, water vapor is discharged from the low pressure turbine A 4 at a sufficiently high pressure and temperature at point 11 so that latent heat energy can be transferred to the second hydraulic oil, and the hydraulic oil used in the above example is ammonia. It is the main part that is different from technology. Accordingly, when compared with the existing prior art, the efficiency at stage A (1000) may be slightly reduced, but all latent heat of stage A (1000) during evaporation is discarded into the atmosphere instead of being disposed of in the heat exchanger. A100) is delivered to the hydraulic oil of stage B (2000), which is different from the existing conventional technology. In the process of transferring this latent heat energy to stage B (2000), water vapor/vapor in stage A (1000) is converted back to liquid at point 12, and this water vapor/vapor is converted to liquid at point 12 by condensation pump A 1 at the input stage ( 13) can be pumped back.

In one embodiment, since stage B (2000) has already absorbed a large amount of latent heat energy of stage A (1000), much less energy must be added to stage B (2000) to achieve the desired temperature. By absorbing the latent heat energy of water vapor in stage A (1000) in heat exchanger A 100), ammonia has already been converted to hot and high pressure vapor at point 14. In the above example, one of ordinary skill in the art will understand that, at the selected pressure and temperature, ammonia at point 14 is a vapor. However, hydraulic oil B, in this case ammonia, can be discharged from heat exchanger A 100 as a liquid, vapor, or supercritical liquid or supercritical vapor at point 14, depending on the desired operating pressure for stage B. Then, the hydraulic oil flows into the boiler B 5, where the hydraulic oil is heated to the desired temperature before entering the turbine B 6 at point 15. When exiting turbine B 6 at low pressure at point 16, ammonia enters heat exchanger B 100, where the ammonia is cooled down to liquid at point 17. Pump B 7 then pumps the liquid ammonia at high pressure (which may be subcritical, critical or supercritical pressure) at point 18.

In one embodiment, when the latent heat upon evaporation is transferred from stage A (1000) to stage B (2000), a significant amount of the total energy amount is added to stage B (2000), in order to obtain ammonia at the desired temperature. There is much less energy that needs to be added to B(2000). Thus, after the first stage, all stages will operate with very high efficiency, and thus will remain to compensate for a slight reduction in efficiency in stage A (1000).

In one embodiment, each stage can be separated from the other stages, with no fluid mixing at any stage at different stages.

In one embodiment, different fluids may be used in each stage. One skilled in the art will appreciate that the same fluid may be used in subsequent stages, but at lower pressures.

In one embodiment, different pressures and temperatures may be used at each stage, as desired, and depending on the requirements of the system/power plant.

In one embodiment, the present invention may use any of the existing technologies, such as heat storage, open water heaters, multi-stage turbines, and the like, and may also be used in each individual stage.

In one embodiment, the present invention may be used as any heat source, such as, but not limited to, coal, solar heat, nuclear power, and the like.

In one embodiment, the latent heat upon evaporation in any stage is transferred to the input stage of the next stage at a sufficiently high temperature and pressure resulting in a complete or partial phase change from liquid to vapor or supercritical vapor, the process In the first stage, the vapor can be converted to a liquid.

In one embodiment, in all stages, but in the final stage, the turbine discharge pressure may be above atmospheric pressure and ambient temperature.

In one embodiment, depending on the individual requirements, any number of stages may be selected and hydraulic oil may be selected.

It should be understood that in one embodiment, the efficiency of the first stage of the conversion from heat to electricity may be slightly smaller compared to the efficiency possible with current designs. Later stages may have "virtual" efficiencies, which may even exceed 100%, as described below.

In one embodiment, for best results (but not necessarily), the hydraulic oil of A (1000) may have the highest critical point temperature. Each subsequent stage, eg stage 2000, may have a hydraulic oil having a lower critical point temperature than the previous stage. Thus, the fluid chosen for the first stage is generally water.

In one embodiment, the present invention can be used as a low stage gas fired plant.

In one embodiment, in addition to the heat exchanger 100, a heat pump may be used to transfer heat from one stage to the next. While heat pumps can consume energy and reduce efficiency, they can eliminate the reduction in temperature that may have to be maintained in the heat exchanger in some cases to transfer energy. If there is no decrease in temperature in the heat exchanger, better efficiency may be provided, and thus, it may be helpful to eliminate energy consumed by the heat pump. For example, a heat exchanger may be used to transfer a bulk of energy while maintaining a temperature difference, and a final amount of energy may be transferred using a heat pump so that no temperature difference exists. It can be used at the end stage.

In one embodiment, a multi stage electric power generation apparatus with at least a two stage system is described. The generator comprises: a first stage power cycle 1000 comprising a first hydraulic oil (not shown), configured for power generation, and generating waste heat (latent heat during evaporation and/or condensation); And it includes a second hydraulic oil (not shown) and is configured for power generation and is composed of a second stage power cycle 2000 that generates waste heat (latent heat during evaporation and/or condensation), the second hydraulic oil for power generation. All waste heat generated from the first stage power cycle (latent heat during evaporation and/or condensation) is absorbed.

In one embodiment, the first power generating stage is: a first means (1) configured to pass the first hydraulic oil at high pressure, which is heated by receiving the first hydraulic oil at high pressure and heating the first hydraulic oil to a high temperature. Or second means (2) configured to produce superheated fluid or vapor, third means (3) configured to receive the heated fluid/vapor and expand said fluid/vapor until it drops to a specified temperature and pressure. And a fourth means 4, and hydraulic oil discharged from the power extraction stage at low pressure and temperature together with waste heat (latent heat during evaporation and/or condensation).

In one embodiment, the present invention includes a heat exchanger mechanism 100, wherein the heat exchanger mechanism 100 converts waste heat (latent heat during evaporation and/or condensation) generated from the first stage 1000 into a second stage ( 2000) to convert the second hydraulic oil into a high temperature and high pressure fluid or steam.

In one embodiment, the heat exchanger mechanism 100 receives the first hydraulic oil vapor from the fourth means 4 during the first stage power cycle 1000 so that the first hydraulic oil vapor is converted into a liquid form. Cooled until it is configured to pass through the first means (1); Alternatively, it is configured to receive the second hydraulic oil vapor from the seventh means 7 during the second stage power cycle 2000 and heat the second hydraulic oil vapor with the waste heat energy of stage A (1000).

In one embodiment, the second stage power cycle comprises: a fifth means configured to receive a second hydraulic oil in liquid or vapor form at high temperature and high pressure and heat the second hydraulic oil in liquid or vapor form with high temperature and high pressure steam ( 5); It receives the heated steam at high and high pressure, generates electricity from the steam, is discharged from the power extraction stage at low pressure and low temperature as latent heat during evaporation and/or condensation, and waste heat (latent heat) is transferred to the next stage, or A sixth means (6) configured to flow into the heat exchanger (200) discharged into the furnace; And a seventh means 7 configured to pass the second hydraulic oil in liquid form at high pressure.

Turning now to Fig. 4, a diagram illustrating a method for generating electricity using a generator having at least two stages of latent heat exchange mechanism according to an embodiment of the present invention.

The order in which the methods are described is not intended to be limiting and any number of the described method steps may be combined in any order to implement the method or alternative methods. In addition, individual steps may be omitted from the method unless departing from the scope of the subject matter described herein. In addition, the method may be implemented in any suitable hardware, firmware, or combination thereof. However, in order to facilitate explanation, in the embodiments described below, the method may be considered to be implemented with the generator described above.

In step 402, electricity is generated using the first hydraulic oil. The method is described when describing FIG. 5.

In step 404, latent heat (waste heat) during evaporation and/or condensation of the first hydraulic oil is transferred to the second hydraulic oil physically separated from the first fluid. In this process, the first hydraulic oil is converted from the vapor to the liquid phase.

In step 406, after all the waste heat of the first stage is absorbed, the second hydraulic oil is further heated to achieve a desired temperature to generate electricity. The electricity generation method is described in the description of FIG. 6.

In step 408, after power extraction, the remaining energy (waste heat) of the second hydraulic oil may be transferred as waste heat to the surrounding or to the third hydraulic oil.

Turning now to Fig. 5, a diagram illustrating a method performed during a first stage power cycle 1000 according to an embodiment of the present invention.

In step 502, the first hydraulic oil is passed at high pressure using the first means 1.

In step 504, the first hydraulic oil is received at high pressure by the second means 2. The second means 2 heats the first hydraulic oil to a high temperature to produce a heated fluid.

In step 506, the heated fluid is received by the third means (3) and the fourth means (4). The third means 3 and the fourth means 4 are expanded until the heated fluid drops to a certain temperature and pressure to generate electricity.

At step 508, any existing means can be used as desired to improve the efficiency.

In step 510, the waste heat (latent heat) generated in the stage is transferred to the second stage hydraulic oil in the latent heat exchange mechanism A 100. In this process, the first hydraulic oil is converted back to the liquid phase and provided to the first means (1) and the cycle is repeated at stage A (1000).

Turning now to Fig. 6, a diagram illustrating a method performed during a second stage power cycle 2000 according to an embodiment of the present invention.

In step 602, the second hydraulic oil is passed at high pressure using the seventh means 7.

In step 604, the second hydraulic oil of stage B (2000) absorbs all waste heat (latent heat during evaporation and/or condensation) of the first hydraulic oil of stage A (1000), and the temperature and energy content in the process rise significantly. .

In step 606, the second hydraulic oil is discharged from the heat exchanger mechanism 100 at high temperature and high pressure, provided that the latent heat from A (1000) is provided to the second hydraulic oil, and to high temperature and high pressure by the fifth means 5 It is received and further heated to the final temperature when desired.

In step 608, the second hydraulic oil is introduced into the sixth means 6 at high temperature and high pressure for energy generation.

At step 610, any existing means may be used as desired to improve the efficiency.

In step 612, the excess waste heat generated in the second stage 2000 is transferred to or dissipated to the third hydraulic oil or discharged to the atmosphere by the heat exchanger 200. In this process, the second hydraulic oil is converted back to the liquid phase and provided to the seventh means 7 and the cycle is repeated at stage B (2000).

It should be noted that the large amount of energy released in the phase change from water vapor to liquid water can only be removed with the phase change (complete or partial) in another liquid, in this example ammonia. An alternative to this is a method using the existing technology that uses large amounts of cooling water from rivers or seas, in which case the latent heat is lost to the surroundings as low temperature waste heat. The present invention is capable of transferring all the latent energy of the hydraulic oil from a relatively low pressure to the high pressure input of another turbine cycle. With appropriate selection of hydraulic oil, pressure and temperature, any desired efficiency can be achieved.

In one embodiment, selecting the temperature and pressure or the cooling water used is an example to help understand the process, and any temperature or pressure or cooling water may be used depending on individual conditions. The important point is that the latent heat is not discharged to the atmosphere as waste heat, but the turbine discharge pressure and temperature are appropriately selected according to the cooling water and transferred to the next stage. The reason it can exceed the limit set by the Carnot Equation is that in any system that uses a phase change to extract energy from heat, this Carnot equation can be applied in practice. An obvious example to support this proposition is the fact that no system in operation even comes close to the efficiency set by the Carnot formula. In any system using phase change, the actual maximum efficiency under ideal conditions is defined as:

Efficiency =

here,

은 KJ/Kg 단위의 킬로그램 당 전체 에너지 입력,

Is the total energy input per kilogram in KJ/Kg,

은 터빈 배출 압력에서 kJ/Kg 단위의 증발 잠열이다.

Is the latent heat of evaporation in kJ/Kg at the turbine discharge pressure.

In the above formula, the water vapor discharged from the turbine is not saturated steam. If saturated steam is acceptable or desired, the latent heat value should be adjusted accordingly. In the case where two stages are used as described earlier in this specification, the above formula is as follows:

Efficiency =

here,

은 단 A에서 KJ/Kg 단위의 킬로그램 당 에너지 입력,

Is the energy input per kilogram in KJ/Kg in just A,

는 단 B에서 KJ/Kg 단위의 킬로그램 당 에너지 입력,

Is the energy input per kilogram in KJ/Kg in just B,

는 단 A에서 터빈 배출 압력에서 kJ/Kg 단위의 증발 잠열,

Is the latent heat of evaporation in kJ/Kg at turbine discharge pressure in stage A,

는 단 B에서 터빈 배출 압력에서 kJ/Kg 단위의 증발 잠열,

Is the latent heat of evaporation in kJ/Kg at turbine discharge pressure in stage B,

는 단 A 및 B 사이에 존재할 수 있는 상이한 흐름 속도(flow rate)를 상쇄하기 위한 흐름 계수(flow factor)로서, [단 B의 질량 흐름 속도(mass flow rate)]/[단 A의 질량 흐름 속도]로 정의될 수 있다.

Is the flow factor to compensate for the different flow rates that may exist between stages A and B, where [mass flow rate of stage B]/[mass flow rate of stage A Can be defined as ].

Similarly, for more than two stages, the above formula is:

Efficiency =

은 [단 n의 질량 흐름 속도]/[단 A의 질량 흐름 속도]이다. Where n is the number of stages,

Is [mass flow rate of stage n]/[mass flow rate of stage A].

Given the energy loss, the above formula is:

Efficiency =

는 전체 시스템에서의 전체 에너지 손실이다. here,

Is the total energy loss in the whole system.

From the above formulas, the following conclusions/points can be obtained:

1) The larger the number of stages, the greater the overall efficiency will be.

2) With an unlimited number of stages in an ideal system, the efficiency will approach 100%. However, in practice, it will be difficult to find enough hydraulic oil for this and the output will decrease as each stage is added, and accordingly, the number of stages is reduced to 3 or 4 stages to optimize both output and cost. It would be best to limit it.

3) From the above formulas, it is possible to increase the efficiency of the system by simply selecting the hydraulic oil with low latent heat during evaporation. This is the exact opposite of what happens. The above formulas show what can happen under ideal conditions, i.e. no energy, heat, friction or other losses. In practical conditions, if a low latent heat fluid is used, the condensation and feed water pump will require a large portion of the total amount of energy produced. Besides its chemical properties, water would be the best choice due to its very large latent heat of evaporation. The higher the latent heat of evaporation, the larger the expansion volume generated during the phase change, and the expansion ratio of water vapor becomes very large by enabling the turbine to be driven efficiently. It has a very small relative power requirement.

4) Only the latent heat of the final stage is released to the atmosphere.

5) The formulas described above will be applied to any system that uses a phase change to convert thermal energy into any other form of energy available.

6) In the current design, in order to attempt and maximize energy extraction, water vapor is usually discharged from the turbine as saturated vapor and damages the low pressure turbine blades. In this design, there is no need to extend the turbine blade life.

Working example: theoretical results

The following examples will show the advantages of the design described in the present invention. Its purpose is only to help explain the concept and not in any aspect to limit the scope of the design according to the invention to the specific fluids, temperatures and pressures used in the process. At point 10, when the supercritical fluid is at a pressure of 250 bar at 600° C., it has an enthalpy of 3493 kJ/Kg. In the current design (assuming no reheat or any other efficiency improvement techniques), when discharged from the turbine at 0.1 bar pressure, it has an enthalpy of about 2450 kJ/Kg, of which about 2257 kJ/Kg is As latent heat during evaporation (or condensation) that is removed to the atmosphere as low-grade waste heat, only about 35% ((3493-2257)/3493) efficiency is generated accordingly. Now, this 2257kJ/Kg of waste heat is not released to the atmosphere and it is necessary to confirm that it is a very efficient system.

As an example, at point 11, water vapor is discharged from the turbine and enters condenser A at a pressure of 10 bar at 180° C., which when discharged from the turbine will have an enthalpy of about 2777 kJ/Kg. In condenser A, this thermal energy is transferred to stage B where the hydraulic oil is ammonia at 100 bar at point 18 with an enthalpy of 536 kJ/Kg and a temperature of 40°C. The fluids in cycles A and B are completely separated from each other, and it is necessary that the fluids are not in direct contact at any location. Thereby, different stages can be operated at different pressures and temperatures, and can be adjusted according to the conditions of the stage. At a pressure of 100 bar, the ammonia will undergo a phase change above 125.17°C, except that in A the water vapor will undergo a phase change below 179.88°C at 10 bar. This temperature difference will enable the transfer of energy from stage A to stage B in heat exchanger A, where the ammonia is converted from the liquid phase to the vapor phase, and in stage A the water vapor is cooled to a liquid and then pumped to a higher pressure to complete the cycle. Will continue. Since the phase of ammonia changes from liquid to vapor, a large amount of energy arranged by the phase change from water vapor to liquid water can be absorbed. When ammonia is discharged from heat exchanger A with an enthalpy of 1831 kJ/Kg at 180° C., it absorbs all potential energy in the water at stage A.

In order to match the amount of energy that must be transferred between stages, the flow rate of stage B may be higher or lower than the flow rate of stage A. In heat exchanger A, water vapor discharges 2027 kJ/Kg (2777 kJ/Kg-750 kJ/Kg), and ammonia can only absorb 1295 kJ/Kg (1831 kJ/Kg-536 kJ/Kg). In this particular example, in order to transfer all this energy, the mass flow rate of ammonia must be 1.56 times (2027 kJ/Kg/1295 kJ/Kg) greater than the mass flow rate of water to absorb all of the energy required to convert it into a liquid. . If a lower or higher flow rate ratio is desired for the ammonia cycle, simply increase or decrease the temperature at stage A and the turbine discharge pressure depending on the conditions.

A temperature difference of about 50° C. is maintained in the heat exchanger so that energy can be transferred from one stage to the next, and a heat pump can be used to transfer the final amount of energy when desired or when necessary. If a smaller or larger temperature difference is desired, the calculation will be adjusted accordingly. In addition, a heat pump can be used to transfer heat from one stage to the next, in which case the temperature difference can be zero or even negative if necessary in certain cases. Accordingly, slightly higher efficiencies can occur at each stage, but the energy used by the heat pump must also be considered to determine if this is desirable.

The system shown in FIG. 3 may cause the efficiency of stage A to be slightly reduced, but if the latent heat of stage A is transferred to the input of stage B and the hydraulic oil is made into high-pressure steam at point 14, as shown in FIG. For raising the ammonia temperature from 180° C. to 420° C. and about 781 kJ/Kg (2612 kJ/Kg-1831 kJ/Kg=781 kJ/Kg), only a little extra energy is required in boiler B. In comparison, 3484kJ/Kg is added to A. This is the "virtual" efficiency for just B, resulting in ((2612-1637)/(2612-1831))*100 = 125%. The average efficiency for the first two stages is (total energy output)/(total energy input)=((3493-2926)+(3667-2777)+1.56*(2612-1637))/(3493-750+3667 -2926+1.56*(2612-1831)) = 63.3%. This number is, of course, an approximation because no energy loss is taken into account. However, using only two simple stages (using only one reheat in stage A), the design already significantly exceeds all the performance limits possible with the current design system. Stage 3 will have an efficiency that exceeds the efficiency set by the Carnot formula and will negate it. With an unlimited number of stages and ideal systems, you can actually approach an efficiency of nearly 100%.

The representative embodiments discussed above can provide certain advantages. While not necessarily required to practice aspects of this specification, these advantages may include:

-The cost per unit of power will decrease. For the same amount of electricity output, pollution will be reduced as less fuel is burned.

-Due to pollution, the global temperature is at risk of a significant increase, which can be significantly eliminated.

-According to another advantage, with a relatively small additional investment, the existing electricity generation performance will be significantly increased.

Those skilled in the art will understand that various means are used in the present invention. Each means is a specific device for performing the specific functions discussed above. For example,

-The first means and the seventh means may include, but are not limited to, pumps and devices with functions similar to those of the pump.

-The second and fifth means may include, but are not limited to, the boiler and devices with functions similar to those of the boiler.

-The third means, the fourth means, and the sixth means may include, but are not limited to, high-pressure turbines and low-pressure turbines, and devices with functions similar to those of high-pressure/low-pressure turbines.

In the present invention, a method of implementing a system for a high-efficiency energy conversion cycle by recycling latent heat during evaporation has been described with specific configuration features and/or methods, but the claims need not be limited only to the features or methods described above. You have to understand the facts. The specific features and methods described above are described as an example for implementing a system for a high efficiency energy conversion cycle by recycling latent heat during evaporation.

The examples mentioned in this specification are not intended to limit the scope of the design according to the present invention, but only to help understand the basic concept of the design. The important fact is that, instead of being released to the atmosphere as currently practiced, the latent heat (waste heat) during evaporation/condensation is transferred to the next stages, increasing the efficiency of heat in the electrical conversion. Further, as described herein, all designs with slight modifications or alternatives, using latent heat during evaporation/condensation (waste heat), are also covered within the scope of the present invention.

Claims (18)

In a multi-stage generator having at least two stages of latent heat exchange mechanism, the generator is:
-A first stage power cycle comprising a first hydraulic oil and configured to generate electricity to produce turbine discharge steam comprising latent heat energy upon evaporation and/or condensation;
-A second stage power cycle comprising a second hydraulic oil and configured to generate electricity; And
-A third stage power cycle comprising a third hydraulic oil and configured to generate electricity; Including,
After the second hydraulic oil is compressed to a high pressure by a pump, it is introduced into a heat exchanger common to both the first stage and the second stage power cycle at high pressure and low temperature, and complete phase in both the first hydraulic oil and the second hydraulic oil. Absorb the latent heat of evaporation and/or condensation generated from the first stage power cycle at a pressure and temperature high enough to cause a change; After that,
The second hydraulic oil is superheated before entering a turbine stage to generate electricity, after which the hydraulic oil is condensed in a liquid form by transferring the latent heat to the next stage or discharged to the atmosphere, After that, the hydraulic oil is introduced into the pump again to repeat the cycle,
The third stage power cycle exceeds a value set by Carnot equations, resulting in the efficiency of the multistage generator to nullify it. A multistage generator having a latent heat exchange mechanism of at least two stages.
The method of claim 1,
The first hydraulic oil is heated by steam and the second hydraulic oil is heated by steam having an operating temperature and pressure independent of the first hydraulic oil. A multistage generator having a latent heat exchange mechanism of at least two stages.
The method of claim 1,
The first stage power cycle is:
-First means configured to pass through the first hydraulic oil at high pressure;
-Comprising a second means, wherein the second means is configured to receive the first hydraulic oil at high pressure and heat the first hydraulic oil to a high temperature to generate heated fluid/steam, and
-A third means and a fourth means, wherein the third and fourth means receive the heated fluid/steam and expand it until it drops to a specific temperature and pressure, so as to reduce the temperature and pressure. A multistage generator with at least two stages of latent heat exchange mechanism configured to pass heated fluid through the latent heat exchange mechanism.
The method of claim 3,
The multistage generator comprises a heat exchanger mechanism, wherein the heat exchanger mechanism is configured to transfer the latent heat generated from the first stage power cycle to the second hydraulic oil in the second stage power cycle. Multistage generator with a latent heat exchange mechanism.
The method of claim 4,
The second stage power cycle is:
-Comprising a fifth means, said fifth means being configured to receive said second hydraulic oil in liquid or vapor form at high temperature and high pressure, and heat said second hydraulic oil in vapor form to a desired operating temperature;
-Comprising a sixth means, wherein the sixth means receives the heated steam at high temperature and high pressure, and generates electric power from the steam that is discharged from the generator at low temperature and pressure and enters another heat exchanger to generate power from the third stage power. Transfer to the cycle or exhaust to the atmosphere;
-A multistage generator with a latent heat exchange mechanism of at least two stages, characterized in that it comprises a seventh means configured to pass the second hydraulic oil at high pressure.
The method of claim 5,
The heat exchanger mechanism is:
-During said first stage power cycle, receiving said first hydraulic oil vapor from said fourth means, cooling it until it is converted to liquid form, and passing through said first means; or
-At least two stages of latent heat exchange, characterized in that during the second stage power cycle, the second hydraulic oil vapor is received from the sixth means, cooled until it is converted into a liquid form, and passed to the seventh means. Multi-stage generator with mechanism.
The method of claim 1,
At least two, characterized in that all hydraulic oils are selected from a group of fluids suitable for use as hydraulic fluids, operated at pressures and temperatures independent of each other, and different pressures and temperatures can be used at all stages if necessary. Multistage generator with a staged latent heat exchange mechanism.
The method of claim 1,
A multistage generator having a latent heat exchange mechanism of at least two stages, characterized in that different hydraulic oils are used in different stages and cannot be physically separated and mixed.
The method of claim 1,
The latent heat of vaporization in the first stage significantly increases the temperature and energy content, and is transferred to the second stage at a pressure and temperature sufficiently high to cause a phase change from the liquid of the second hydraulic oil to steam or supercritical steam. , In the phase change, a multistage generator having a latent heat exchange mechanism of at least two stages, characterized in that the vapor in the first stage is converted to a liquid.
The method of claim 9,
A multistage generator with at least two stages of latent heat exchange mechanism, characterized in that the phase change from liquid to vapor or supercritical vapor of the second hydraulic oil is a complete phase change or a partial phase change.
The method of claim 1,
The first hydraulic oil and the second hydraulic oil are selected with a physical property that allows easy transfer of latent heat energy from one stage to the next in a latent heat exchange mechanism. .
The method of claim 1,
A multistage generator with at least two stages of latent heat exchange mechanism, characterized in that the latent heat exchange mechanism is configured for use with any heat-based power system despite the final output being a certain type of non electrical output.
The method of claim 1,
Any of the individual stages has at least two stages of latent heat exchange mechanism, characterized in that it is configured to operate at sub-critical, critical, or super critical temperature and pressure when desired. Multistage generator.
A method for generating electricity using a generator having at least two stages of power cycle, the method comprising:
-In a first stage power cycle comprising a first hydraulic oil, generating a turbine exhaust steam containing electric power and latent heat upon evaporation and/or condensation;
-Generating power, and latent heat upon evaporation and/or condensation, in a second stage power cycle comprising a second hydraulic oil; And
In the third stage power cycle including the third hydraulic oil, generating power and waste heat; Including,
After the second hydraulic oil is compressed to a high pressure by a pump, it is introduced into a heat exchanger common to both the first and second stage power cycles at high pressure and low temperature, and is completely phased in both the first and second hydraulic oils. Absorbs latent heat during evaporation and/or condensation generated from the first stage power cycle at a pressure and temperature sufficiently high to cause a change; After that
The second hydraulic oil is superheated before entering the turbine stage to generate electricity, and thereafter, the hydraulic oil is condensed in a liquid form by transferring the latent heat to the next stage or discharged to the atmosphere. , After that, the hydraulic oil is introduced into the pump again to repeat the cycle,
The third stage power cycle exceeds the value set by the Carnot equations and causes the efficiency of the multistage generator to nullify it. Way for you.
The method of claim 14,
-Passing said first hydraulic oil at high pressure by first means;
-Receiving, by second means, the first hydraulic oil at high pressure;
-Heating the first hydraulic oil to a high temperature by a second means;
-By a third means, said heated fluid having a lowered temperature and pressure to receive said heated fluid, expand it until it drops to a certain temperature and pressure, and reheat said fluid with a lowered temperature and pressure. Passing the fluid through a second means, the heated fluid having the reduced temperature and pressure being reheated;
-Generating, by means of a fourth means, electricity from steam produced at high and low pressures or at intermediate pressures; And
-Generating, by means of the fourth means, low-temperature and pressure-releasing steam, containing latent heat energy upon evaporation and/or condensation; electricity using a generator with at least two-stage power cycle, characterized in that it comprises Method for generating.
The method of claim 14,
Using a heat exchanger mechanism, the latent heat generated from the first stage power cycle at the time of evaporation and/or condensation is exchanged for the second hydraulic oil in the second stage power cycle, and the second hydraulic oil is changed to vapor or phase. A method for generating electricity using a generator having at least two stages of power cycle, comprising the step of converting to a heated fluid that is heated.
The method of claim 15,
-Receiving said second hydraulic fluid in vapor form or phase change, from a heat exchanger mechanism, using a fifth means, at high temperature and pressure;
-Heating the second hydraulic oil in vapor form to a required temperature using fifth means;
-Using a sixth means, receiving steam heated at high temperature and high pressure, generating electricity from steam generated at low temperature and low pressure containing latent heat upon evaporation and/or condensation and discharged from the sixth means ; And
-A method for generating electricity using a generator with at least two power cycles, characterized in that it comprises the step of passing said second hydraulic oil at high pressure, using a seventh means.
The method of claim 17,
-Receiving said first hydraulic oil vapor from said fourth means during said first stage power cycle, using a heat exchanger mechanism, cooling until converted to liquid form, and passing it through said first means; or
-Receiving the second hydraulic oil vapor from the sixth means during the second stage power cycle, using a heat exchanger mechanism, cooling until it is converted into a liquid form, and passing it through the seventh means; And
-Using a heat exchanger mechanism, discharging or transferring the latent heat upon evaporation to the next stage after the second stage power cycle. How to create.

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