KR20170077159A - 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 that is discharged into the atmosphere in an existing plant cycle design by creating multiple turbine cycles, and the latent heat during evaporation in the first cycle The waste heat of the second cycle (latent heat at the time of evaporation) is transmitted to the input of the third cycle, and so on. Only the waste heat of the final cycle is discharged to the atmosphere.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a system for recycling a latent heat at the time of evaporation and for a high-efficiency energy conversion cycle,

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates generally to power generation, and more particularly, to a multi-stage system for a power turbine that is driven efficiently.

Currently, most electricity in the world is used to heat water to high pressure and high temperature steam, and then to turn the turbine spinning the generator to generate electricity. Any number of means may be used to heat the water, such as solar heat, coal, gas, nuclear power, and the like. When high pressure water vapor enters the turbine, the water vapor collides with the turbine blade 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 considerable amount of energy, is discharged from the turbine, flows into the condenser at low pressure, and the water vapor cools until the water vapor becomes water. Thereafter, the pump is pumped back to the high pressure input of the cycle and heated again with steam, and the cycle is repeated over and over again.

The problem with this configuration is that the condenser must be able to remove the latent heat of evaporation and convert the water vapor back into liquid, and the pump must be able to pump the fluid back to the beginning of the cycle using only minimal energy. The energy is then discarded as surrounding heat as waste heat. In the case of water, the latent heat upon evaporation is approximately 2257 kJ / Kg, which corresponds to a considerable amount of energy. This is between 40-60% (depending on operating temperature) or more of the total heat energy added to the working fluid per cycle. Therefore, it is difficult to achieve an efficiency of 40% even for even the best power plant. 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 conventional power cycles, where conventional power cycles, such as ranking cycles and other cycles, have a very limited efficiency due to the large amount of low waste heat that must be discharged to the atmosphere or to the surroundings. Most of the latent heat during evaporation (or condensation) must be discharged as waste heat, which significantly limits the efficiency of any cycle.

The present invention provides a system (generator) and method for 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 the features described herein.

The condenser should convert the vapor back into liquid by removing latent heat during evaporation and the pump should be able to pump the fluid back to the beginning of the cycle using only minimal energy. This energy (latent heat) is then discarded as waste heat. Therefore, it is difficult to achieve an efficiency of 40% even for even the best power plant.

The present invention solves the aforementioned technical problem effectively and at low cost by transferring the latent heat upon evaporation of any stage to the input stage of the next stage without discharging it to the atmosphere, Thereby providing a mechanism that can significantly increase the efficiency.

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

In one embodiment, the present invention provides a method of converting thermal energy to 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 discharged into the atmosphere in existing plant cycle designs.

In one embodiment, the present invention is characterized in that the latent heat at the time of evaporation of the first cycle is transferred to the input stage of the second cycle, the waste heat (latent heat at the time of evaporation) of the second cycle is transferred to the input end of the third cycle , And so on, thus providing a mechanism for generating multiple turbine cycles. Only the waste heat of the final cycle is discharged into the atmosphere.

In one embodiment, the present invention utilizes waste latent heat and converts waste latent heat into electricity to significantly improve the efficiency of the power plant. The waste heat exchange mechanism can also be used with any heat based power system, even though the final output is a particular type of non-electrical output .

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

In one embodiment, by appropriately selecting the working fluid and the turbine discharge temperature and pressure, the present invention can deliver all the latent heat during evaporation to the next stage, Thereby making it possible to remarkably reduce the amount of energy required for heating. Thus, after the first stage, the efficiency of all stages is significantly improved, and the overall efficiency is thereby significantly improved.

In order to improve the overall performance of any power cycle by transferring the latent heat upon evaporation of any stage to the input stage of the next stage instead of venting to the atmosphere, embodiments of the present invention provide a plurality of aspects of the present patent application do. The plurality of aspects recycle the latent heat upon evaporation to provide a system and method for a high efficiency energy conversion cycle. The technical solutions are as follows:

In yet another aspect, a multi-stage generator having at least a two-stage system is described. The generator includes: a first stage power cycle including a first hydraulic fluid, a boiler, a turbine, a heat exchanger, a pump, etc. and configured to generate electricity; And a second stage power cycle including a second operating fluid, a boiler, a turbine, a heat exchanger, a pump, etc. and being configured to generate electricity, the second operating fluid comprising waste heat (evaporation and / Or latent heat at the time of condensation).

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

In one embodiment of the present invention, the low-grade waste heat of the first stage is delivered to the input of the second cycle, the waste heat of the second cycle is delivered to the input of the third cycle, and so on . The more stages there are, the better the overall overall efficiency will be, but the more steps you add, the more expensive it will cost. In addition, it may not be possible to find a sufficient number of hydraulic oils with the correct physical properties to have an unlimited number of stages. In describing the process in detail, two stages are sufficient to illustrate this concept, and the following description will follow a two stage system.

The detailed description of the invention is set forth with reference to the accompanying drawings. In the drawings, the leftmost digit of the reference numerals indicate the first reference numerals. Throughout this specification, like reference numerals are used to denote like components and components.
1 is a schematic diagram of a conventional plant cycle (prior art);
2 is a schematic diagram of a multi-stage cycle implementing very high efficiency in accordance with one embodiment of the present invention.
Figure 3 illustrates an example of a two-stage system in which water and ammonia are used as the working oil in accordance with one embodiment of the present invention.
Figure 4 illustrates a method for generating electricity using a generator having at least two stages of latent heat exchange mechanisms in accordance with one embodiment of the present invention.
Figure 5 illustrates a method performed during the first stage latent heat exchange mechanism 1000 in accordance with one embodiment of the present invention.
Figure 6 illustrates a method performed during the second stage latent heat exchange mechanism 2000 in accordance with one embodiment of the present invention.

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

In the following, detailed description of one or more embodiments of the present invention is provided in the accompanying drawings which illustrate the concept of the present invention. While the invention has been described in terms of such embodiments, it is not limited thereto. The scope of the invention is defined solely by the claims, and the invention includes various alternatives, modifications and equivalents. In the following, various specific details are set forth in order to provide a thorough understanding of the present invention. These are provided as specific examples, and the present invention may be practiced in accordance with the claims without any part or all of these specific details. For clarity, technical details known in the art to which the present invention belongs will not be described in detail.

It is important to note that at least a basic concept of thermodynamics needs to be understood in order to better understand this explanation.

1 is a diagram illustrating a basic concept of an existing power plant cycle as a prior art.

While various aspects described for recycling latent heat during evaporation and for a high efficiency energy conversion cycle may be implemented in any number of different systems, environments, and / or shapes, .

Turning now to FIG. 2, there is shown schematically a multistage cycle that achieves very high efficiency in accordance with one 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, the waste heat of the second cycle is transferred to the input of the third cycle, and so on . The more stages there are, the better the overall overall efficiency will be, but the more steps you add, the more expensive it will cost. In addition, it may not be possible to find a sufficient number of hydraulic oils with the correct physical properties to have an unlimited number of stages.

In one embodiment, in order to describe the process in detail, it will be sufficient to describe the concept in two stages, and therefore the following description is based on a two stage system.

Turning now to FIG. 3, which illustrates an example of a two-stage system where water and ammonia are used as the working oil in accordance with one embodiment of the present invention.

In one embodiment, for purposes of simplicity, only one high pressure and low pressure turbine is shown in stage A 1000, and only one stage in stage B is shown in stage B 2000. In addition, the description of all conventional techniques for improving cycle efficiency and performance, such as heat storage, open feed water heaters and other minor modifications, has been intentionally excluded. All existing techniques for improving efficiency can still be used for all stages with improved design. All of the thermal and physical property values mentioned in these full texts can be found on the National Institute of Standards and Technology (NIST) website (www.nist.com) or on more specific websites (webbook.nist.gov/chemistry/fluid). have.

In one embodiment, water is used as the first working fluid in stage A (1000), and stage B (2000) is used as the first working fluid, although for purposes of illustration, a wide variety of fluids may be used in an improved system of several stages (1000 or 2000) Ammonia is used as the second working oil. Stage A 1000 is the first stage and liquid water is delivered from boiler 13 to boiler A 2 at a high pressure, for example, 250 bar (or any other desired pressure) by pump A 1. In the boiler 2, the liquid water is heated to a high temperature, for example 600 ° C (or any other desired temperature), and discharged from the boiler A 2 at point 10 as a supercritical or heated fluid. The high temperature and high pressure supercritical fluids expand in the high pressure turbine 3 and return to boiler A 2 after significant temperature and pressure drop to reheat to 600 ° C at 50 bar (or any other desired temperature and pressure) Pressure turbine 4 for final energy extraction.

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

In the present invention, the water vapor can be discharged from the low-pressure turbine A 4 at a sufficiently high pressure and temperature at the point 11, and the latent heat energy can be transferred to the second working oil. The working oil used in this example is ammonia, Technology and other major parts. Thus, compared to the prior art, the efficiency at stage A 1000 can be slightly reduced, but all the latent heat of stage A 1000 during evaporation is replaced by a heat exchanger A100) to the operating oil of stage B (2000), which is different from the existing prior art. In the process of transferring this latent heat energy to stage B (2000), the vapor / steam of stage A (1000) is again converted to liquid at point (12), which is condensed by condensing pump A 1 at high pressure 13). ≪ / RTI >

In one embodiment, since stage B (2000) has already absorbed large amounts of latent heat energy in stage A (1000), there is much less energy to be added to stage B (2000) to achieve the desired temperature. By absorbing the latent heat energy of steam of stage A (1000) in heat exchanger A 100, ammonia has already been converted to high temperature and high pressure steam at point (14). In this example, one of ordinary skill in the art will understand that at a selected pressure and temperature, at point 14, ammonia is vapor. However, the hydraulic oil B, in this case ammonia, may be discharged from heat exchanger A 100 as liquid, vapor, or supercritical liquid or supercritical vapor at point 14, depending on the desired operating pressure for stage B. Subsequently, the working oil flows into the boiler B5, where the working oil is heated to the desired temperature before entering the turbine B6 at point 15. When discharged from turbine B 6 at low pressure at point 16, ammonia enters the heat exchanger B 100 where the ammonia is cooled until it becomes liquid at point 17. The pump B 7 then pumps the liquid ammonia at point 18 to a high pressure (which may be a critical, critical or supercritical pressure).

In one embodiment, when the latent heat upon evaporation is transferred from stage A 1000 to stage B 2000, a significant amount of total energy is added to stage B 2000, There is much less energy to be added to B (2000). Thus, after the first stage, all stages will operate at a very high efficiency, thus compensating for some efficiency reduction in stage A 1000.

In one embodiment, each stage can be separate from the other stages, and no fluid is mixed at any stage in the different stages.

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

In one embodiment, different pressures and temperatures may be used at each stage, at will and at the requirements of the system / plant.

In one embodiment, the present invention can use any of the existing techniques, such as heat storage, open feed water heater, multi-stage turbine, etc., and can be used in each individual stage.

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

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

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

In one embodiment, in accordance with the individual requirements, any number of stages may be selected and the hydraulic fluid selected.

In one embodiment, it should be appreciated that the first stage efficiency of conversion from heat to electric furnace may be slightly less than the efficiency available in the current design. Future stages may have "virtual" efficiency, which may exceed 100%, even as described below.

In one embodiment, for best results (although not necessarily), the working fluid of stage A 1000 may have the highest critical temperature. Each subsequent stage, e.g., stage 2000, may also have a working oil having a lower critical temperature than the previous stage. Thus, the fluid selected 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 heat exchanger 100, a heat pump may be used to transfer heat from one end to the next. Although a heat pump can consume energy and reduce efficiency, it can eliminate temperature reductions that may have to be maintained in heat exchangers in some cases to deliver energy. Without a reduction in temperature in the heat exchanger, it is possible to provide better efficiency and thus help to eliminate the energy consumed by the heat pump. For example, a heat exchanger can be used to deliver a bulk of energy while maintaining the temperature difference, and the final energy amount can be delivered using a heat pump such that no temperature difference exists. It can be used at the end stage.

In one embodiment, a multi-stage electric power generation apparatus having at least two stage systems is described. The generator includes: a first stage power cycle 1000 that includes a first hydraulic fluid (not shown) and is configured for power generation and generates waste heat (latent heat during evaporation and / or condensation); And a second stage power cycle 2000 that includes a second hydraulic fluid (not shown) and is configured for power generation and generates waste heat (latent heat during evaporation and / or condensation), the second hydraulic oil Absorbing all waste heat (latent heat during evaporation and / or condensation) generated from the first stage power cycle.

In one embodiment, the first power generating stage comprises: a first means (1) configured to pass a first operating fluid at a high pressure, a second means for receiving the first operating fluid at a high pressure, (3) configured to receive the heated fluid / steam and to expand the fluid / steam until it drops to a specific temperature and pressure, a second means (2) configured to generate a superheated fluid or vapor, And fourth means (4), and a working fluid discharged from a 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 in which the waste heat (latent heat during evaporation and / or condensation) generated from the first stage 1000 is transferred to a second stage 2000) to convert the second operating fluid to high-temperature and high-pressure fluid or steam.

In one embodiment, the heat exchanger mechanism 100 receives the first hydraulic fluid from the fourth means 4 during the first stage power cycle 1000 such that the first hydraulic fluid is converted to liquid form Or to pass it to the first means (1); Or to receive the second working fluid from the seventh means 7 during the second power cycle 2000 and to heat the second working fluid with the waste heat energy of the stage A 1000.

In one embodiment, the second stage power cycle comprises: fifth means adapted to receive the second working fluid in liquid or vapor form at high temperature and pressure and to heat the second working fluid in the liquid or vapor form into high temperature and high pressure steam 5); The steam is discharged from the power extraction stage at low pressure and low temperature by evaporation and / or condensation, and the waste heat (latent heat) is transferred to the next stage, A sixth means (6) configured to be introduced into the heat exchanger (200) which is discharged to the heat exchanger (200); And a seventh means (7) configured to pass the second working fluid in liquid form at high pressure.

Turning now to FIG. 4, there is illustrated a method for generating electricity using a generator having at least two stages of latent heat exchange mechanisms in accordance with one 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 methods or alternative methods. Also, individual steps may be omitted from the methodology, as long as they do not depart 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, for ease of explanation, in the embodiments described below, the method may be considered implemented with the generator described above.

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

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

In step 406, after all of the waste heat of the first stage has been absorbed, the second operating oil may be further heated to implement the desired temperature to produce electricity. The electric generation method is described in the description of FIG.

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

Turning now to FIG. 5, which illustrates a method performed during a first stage power cycle 1000 in accordance with one embodiment of the present invention.

In step 502, the first working fluid is passed at high pressure using the first means 1.

In step 504, the first operating fluid is received by the second means 2 at a high pressure. The second means (2) heats the first operating fluid 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 inflated until the heated fluid has dropped to a certain temperature and pressure for electrical generation.

At step 508, any conventional means may be used at any time to improve efficiency.

In step 510, the waste heat (latent heat) generated in the stage is transferred from the latent heat exchange mechanism A 100 to the second-stage working oil. In this process, the first working fluid is again converted 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, which illustrates a method performed during a second stage power cycle 2000 in accordance with one embodiment of the present invention.

In step 602, the second working fluid is passed through the seventh means 7 at a high pressure.

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

In step 606, the second working fluid is discharged from the heat exchanger mechanism 100 at high temperature and high pressure, the latent heat from the A 1000 is supplied to the second working fluid, and the fifth fluid 5 is supplied at high temperature and high pressure And is further heated to a final temperature at the desired time.

In step 608, the second operating oil flows into the sixth means 6 at a high temperature and a high pressure for energy generation.

In step 610, any conventional means may be used at any time to improve efficiency.

In step 612, excess waste heat generated in the second stage 2000 is delivered to the third working fluid or diverted or discharged to the atmosphere by the heat exchanger 200. In this process, the second working oil is again converted into the liquid phase and supplied to the seventh means 7, and the cycle is repeated at the stage B (2000).

It should be noted that the large amount of energy exiting the phase change from water vapor to liquid water can only be removed by phase change (complete or partial) in another liquid, in this example ammonia. An alternative is to use existing techniques that use large amounts of cooling water from the river or sea, in which case latent heat is lost to the environment as cryogenic waste heat. The present invention is able to transfer all latent energy of the operating fluid from the relatively low pressure to the high pressure input of another turbine cycle. By selecting the operating fluid, pressure and temperature appropriately, any desired efficiency can be achieved.

In one embodiment, the choice of temperature and pressure or cooling water used is an example to help understand the process, and any temperature or pressure or cooling water may be used depending on the individual conditions. The important point is that latent heat is not discharged to the atmosphere as waste heat, but the turbine exhaust pressure and temperature are appropriately selected and delivered to the next stage depending on the cooling water. The reason for exceeding the limit set by the Carnot Equation is that such a Karno formula can actually be applied to any system that uses phase change to extract energy from the heat. A clear example that supports this proposition is that any system in operation can not even come close to the efficiency set by the Carnot 's formula. In any system utilizing 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 of 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 steam 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 a two-stage is used as described earlier in this specification, the formula is as follows:

Efficiency =

here,

은 단 A에서 KJ/Kg 단위의 킬로그램 당 에너지 입력,

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

는 단 B에서 KJ/Kg 단위의 킬로그램 당 에너지 입력,

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

는 단 A에서 터빈 배출 압력에서 kJ/Kg 단위의 증발 잠열,

Is the latent heat of evaporation in kJ / Kg at the turbine discharge pressure at 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 for canceling the different flow rates that may exist between stages A and B [mass flow rate of stage B] / [mass flow rate of stage A ].

Similarly, in the case of more than two stages, the 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 n / mass flow rate of A].

Given energy loss, the formula is:

Efficiency =

는 전체 시스템에서의 전체 에너지 손실이다. here,

Is the total energy loss in the overall system.

From the above formulas, the following conclusions can be drawn:

The larger the number of stages, the greater the overall efficiency.

2) Using an unlimited number of stages in an ideal system, the efficiency will approach 100%. In practice, however, it will be difficult to find enough hydraulic fluid to do this, and as each stage is added, the output will decrease, and thus the number of stages can be reduced to three or four 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 operating fluid with low latent heat during evaporation. This is the opposite of what happens. The formulas show that they can occur under ideal conditions: energy, heat, friction or other loss-free conditions. In practical conditions, if low latent heat fluids are used, condensate and feedwater pumps will require a large proportion of the total energy generated. In addition to its chemical properties, water will be the best choice due to the very large latent heat of evaporation. The higher the latent heat of evaporation, the greater the expansion volume generated during the phase change, and the more efficiently the turbine is driven, the greater the expansion ratio of the steam. And 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 apply to any system that uses phase change to convert thermal energy to any other available energy form.

6) In current designs, to try and maximize energy extraction, water vapor is generally discharged from the turbine as saturated steam and damages the low pressure turbine blades. In this design, there is no need to extend the life of the turbine blade.

Operation example : Theoretical results

The following example will illustrate the benefits of the design described in the present invention. The purpose is only to aid in explaining the concept, and in no way is it intended to limit the scope of the design according to the invention to the particular fluid, temperature and pressure used in the process. At point 10, the supercritical fluid has an enthalpy of 3493 kJ / Kg when it is at a pressure of 250 bar at 600 < 0 > C. It has an enthalpy of about 2450 kJ / Kg when it is discharged from the turbine at 0.1 bar pressure, assuming there is no reheat or any other efficiency improvement technique, of which about 2257 kJ / Kg As latent heat at the time of evaporation (or condensation) to be removed to the atmosphere as low-grade waste heat, only about 35% ((3493-2257) / 3493) of efficiency is generated accordingly. It is now necessary to ensure that this 2257 kJ / Kg of waste heat is not discharged to the atmosphere and is a very efficient system.

As an example, at point 11, water vapor is evacuated from the turbine and introduced into the condenser A at a pressure of 10 bar at 180 DEG C, and the enthalpy when discharged from the turbine will be about 2777 kJ / Kg. In condenser A, this thermal energy is delivered to stage B, where the working 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 one another and it is necessary that the fluids are not in direct contact at any location. Thereby, the 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, while in A, the water vapor will undergo a phase change at 10 bar to below 179.88 ° C. This temperature difference will allow energy transfer 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 the liquid and then pumped to a higher pressure, It continues. Since the phase of ammonia is changed from liquid to vapor, a large amount of energy arranged by phase change from water vapor to liquid water can be absorbed. When ammonia is discharged from heat exchanger A at an enthalpy of 1831 kJ / Kg at 180 ° C, it absorbs all the potential energy in water at stage A.

The flow rate of stage B may be higher or lower than the flow rate of stage A so as to match the amount of energy that must be transferred between stages. In heat exchanger A, the water vapor exits 2027 kJ / Kg (2777 kJ / Kg-750 kJ / Kg) and ammonia can absorb only 1295 kJ / Kg (1831 kJ / Kg-536 kJ / Kg). In this particular example, to deliver all of this energy, the mass flow rate of ammonia must be greater by 1.56 times (2027 kJ / Kg / 1295 kJ / Kg) than the mass flow rate of water to absorb all of the energy required to convert it to liquid . If lower or higher flow rate ratios are desired for the ammonia cycle, simply increase or decrease the temperature of the stage A and the turbine discharge pressure according to 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 deliver the final positive energy when desired or as needed. If less or greater temperature differences are desired, the calculations will be adjusted accordingly. Also, a heat pump can be used to transfer heat from one stage to the next, in which case the temperature difference may be zero or even negative if necessary in certain cases. Thus, although slightly higher efficiencies may occur at each stage, the energy used by the heat pump should also be considered to determine if this is desirable.

The system shown in FIG. 3 can cause the efficiency of stage A to be slightly reduced, but if the latent heat of A is delivered to input B and the hydraulic fluid is at high pressure steam at point 14, Only a small amount of extra energy is required in boiler B for increasing the ammonia temperature from 180 ° C to 420 ° C and about 781 kJ / Kg (2612 kJ / Kg-1831 kJ / Kg = 781 kJ / Kg). Comparing this, A of 3484 kJ / Kg is added. This is the efficiency of "virtual" for stage B ((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 an approximation because we have not considered any energy loss. However, if only two simple stages are used (but only one reheat is used in A), the design will already exceed all possible performance limits for the current design system. The third stage will have efficiency exceeding the efficiency set by the Karno formula and will invalidate it. With an unlimited number of stages and an ideal system, you can actually approach nearly 100% efficiency.

The exemplary embodiments discussed above may provide specific advantages. Although not necessarily required to practice the aspects of the present specification, these advantages may include the following:

- Cost per unit of power will decrease. For the same amount of electrical output, less fuel will burn and contamination will decrease.

- Due to contamination, the Earth is at risk of a significant increase in temperature, which can be significantly eliminated.

- According to another advantage, the relatively small additional investment alone will significantly increase the existing electricity generating capacity.

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

The first and seventh means may include but are not limited to devices having a function similar to that of the pump and pump.

The second and fifth means may include but are not limited to devices having a function similar to that of the boiler and the boiler.

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

Although the present invention describes a method for recycling a latent heat upon evaporation to implement a system for a high-efficiency energy conversion cycle with certain constituent features and / or methods, it should be understood that the claims are not limited to the features or methods described above You must understand the facts. These specific features and methods are described as an example for recycling the latent heat upon evaporation to implement a system for a high efficiency energy conversion cycle.

The examples referred to in this specification are not intended to limit the scope of the design according to the invention, but merely to aid in understanding the basic concepts of the design. Importantly, instead of being discharged to the atmosphere as is currently practiced, latent heat (waste heat) during evaporation / condensation is transferred to the next stages, thereby increasing the efficiency of heat conversion. Also, as described herein, all designs with slight modifications or alternatives, using latent heat (waste heat) during evaporation / condensation, are also contemplated within the scope of the present invention.

Claims (18)

A multistage power generator having at least two stages of latent heat (waste heat) exchange mechanism, said generator comprising:
A first stage power cycle comprising a first hydraulic fluid and configured to generate electricity to generate turbine discharge steam comprising latent heat (waste heat) energy during evaporation and / or condensation; And
- a second stage power cycle comprising a second hydraulic fluid and configured to generate electricity,
Wherein the second hydraulic oil absorbs latent heat (waste heat) during evaporation and / or condensation generated from the first stage power cycle for electricity generation. 2. The apparatus according to claim 1, wherein the first working oil is heated by steam and the second working oil is heated by steam having an operating temperature and pressure independent of the first working oil, characterized in that it has at least two stages of latent heat Multistage generator. 2. The method of claim 1, wherein the first stage power cycle comprises:
- first means configured to pass through the first operating fluid at high pressure;
The second means being adapted to receive the first working fluid at a high pressure and to heat the first working fluid to a high temperature to produce a heated fluid /
The third and fourth means comprise means for receiving the heated fluid / steam and expanding the heated fluid / steam until it drops to a specific temperature and pressure, (Heat exchange) mechanism for passing the heated fluid through the waste heat exchange mechanism at a predetermined temperature and pressure. The system of claim 1, wherein the multi-stage generator includes a heat exchanger mechanism, wherein the heat exchanger mechanism is configured to transfer waste heat generated from the first stage power cycle to a second working oil in a second stage power cycle. A multistage generator with two stages of latent heat (waste heat) exchange mechanism. 2. The method of claim 1 wherein the second stage power cycle comprises:
- fifth means, said fifth means being adapted to receive a second working fluid in the form of a liquid or vapor at a high temperature and a high pressure and to heat the second working fluid in the vapor form to a desired operating temperature;
And a sixth means configured to receive the heated steam at a high temperature and a high pressure and to generate electricity from the steam, wherein the steam is discharged from the generator at low and low pressures and flows into another heat exchanger to transfer the waste heat to a third stage power cycle To the atmosphere;
- a seventh means configured to pass the second hydraulic fluid at high pressure. ≪ Desc / Clms Page number 20 > 6. The heat exchanger mechanism according to any one of claims 1 to 5, further comprising:
- during the first stage power cycle, receiving the first hydraulic fluid from the fourth means and cooling the first hydraulic fluid until the first hydraulic fluid is converted to a liquid form and passing it to the first means; or
Characterized in that during the second stage power cycle it is configured to receive the second working fluid from the sixth means and to cool it to the seventh means until the second working fluid vapor is converted into a liquid form, A multistage generator with a latent heat exchange mechanism. 2. The method of claim 1, wherein all the hydraulic fluids are selected from fluid groups configured for use as a hydraulic fluid, operated at independent pressures and temperatures relative to each other, (Waste heat) exchange mechanism, characterized in that at least two stages of latent heat (waste heat) exchange mechanism can be used. The multi-stage power generator according to claim 1, characterized in that at least two stages of latent heat (waste heat) exchange mechanisms are preferably used, wherein different working oils are used for different stages and can not be physically separated and mixed. The method of claim 1 wherein the latent heat at the first stage of evaporation is transferred to the second stage at a temperature and pressure that significantly increases the temperature and energy content and is phase-changed from the liquid to the vapor of the second operating fluid or supercritical steam Wherein the steam of the first stage in the process is converted into a liquid. 10. The multi-stage power generator according to claim 9, wherein the phase change from the liquid to the vapor or supercritical steam of the second working fluid is a complete phase change or a partial phase change. 2. The method of claim 1, wherein the fluid is selected to be a physical property that allows latent heat energy to be easily transferred from one end to the next in a latent heat exchange mechanism. Multistage generator. The method of claim 1, wherein the waste heat exchange mechanism is configured to be used with all of the heat-based power systems, even though the final output is a particular type of non-electrical output. ) Multistage generator with exchange mechanism. The multi-stage generator (1) according to claim 1, wherein any stage of the individual stages is configured to operate at a critical, critical, or supercritical temperature and pressure at will. . A method for generating electricity using a generator having at least a two-stage power cycle, the method comprising:
- generating a turbine exhaust steam containing power and waste heat (latent heat during evaporation and / or condensation) in a first stage power cycle comprising a first operating fluid; And
- generating power and waste heat (latent heat in evaporation and / or condensation) in a second stage power cycle comprising a second operating fluid,
Wherein the second hydraulic oil absorbs waste heat (latent heat in evaporation and / or condensation) generated from the first stage in a heat exchange mechanism for generating electricity, and generates electricity using a generator having at least two stages power cycle Lt; / RTI > 15. The method of claim 14,
Passing the first hydraulic fluid at high pressure by first means;
- receiving a first hydraulic fluid at a high pressure, by a second means;
- heating the first operating fluid to a high temperature by a second means;
A third means for receiving the heated fluid, expanding the fluid until it drops to a specific temperature and pressure, and delivering the heated fluid at a lowered temperature and pressure to reheat the fluid at the lowered temperature and pressure, To a second means, wherein the heated fluid is reheated to a lowered temperature and pressure;
- generating electricity from the steam produced at high temperature and low pressure or intermediate pressure by means of fourth means;
Generating a low temperature and low pressure discharge steam containing latent heat energy at the time of evaporation and / or condensation by means of a fourth means; generating electricity using a generator having at least two stages of power cycles; Lt; / RTI > 15. The method of claim 14, wherein the heat exchanger mechanism is used to exchange the latent heat of evaporation and / or condensation generated from the first stage power cycle with the second operating fluid in the second stage power cycle, Wherein the step of converting the electrical power into a converted heated fluid comprises converting at least two power cycles into a heated fluid. 15. The method of claim 14,
- receiving the second hydraulic fluid from the heat exchanger mechanism, at a high temperature and a high pressure, in vapor form or in a phase-changing heated fluid, using the fifth means;
- heating the second working fluid in vapor form to a required temperature, using the fifth means;
- using the sixth means to receive steam heated at high and high pressures, generate electricity from the resulting steam, and vent from the sixth means at low and low pressures containing latent heat during evaporation and / or condensation ; And
- passing the second hydraulic fluid at high pressure using the seventh means. ≪ RTI ID = 0.0 > - < / RTI > 15. The method of claim 14,
- using a heat exchanger mechanism to cool the first hydraulic fluid from the fourth means during the first stage power cycle until it is converted to a liquid form and pass it to the first means; or
- using a heat exchanger mechanism, during the second stage power cycle, cooling the second hydraulic fluid from the sixth means until it is converted to a liquid form and passing it to the seventh means; And
- discharging or transferring the latent heat during evaporation to the next stage after the second stage power cycle using a heat exchanger mechanism to generate electricity using at least two stage power cycle Way.

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