LT4813B

LT4813B - Method and apparatus of converting heat to useful energy

Info

Publication number: LT4813B
Application number: LT1999098A
Authority: LT
Inventors: Alexander I. Kalina; Richard I. Pelletier; Lawrence B. Rhodes
Original assignee: Exergy,Inc
Priority date: 1999-08-04
Filing date: 1999-08-04
Publication date: 2001-07-25
Also published as: LT99098A

Abstract

Invention is intended for the mean of actualisation of the thermodynamic cycle and the device to do it. Heated flow of operating gas, having components both of the low and the high boiling points is separated and the component with the low boiling point is expanded transforming solar energy into the usable form and receiving expanded, relatively fat current. This expanded flow is separated into two parts, one of which is further expanded, receiving energy and the used flow, while the other part is extracted. Lean, unexpanded flow and the used fat flow are connected together in the re-generation system with the extracted flow, thus deriving again the operating flow, which is effectively heated in the heater, receiving later separated heated operating flow of gas.

Description

Išradimas skirtas termodinaminio ciklo, kurio metu šiluma paverčiama naudinga energija, realizavimui.The invention relates to the implementation of a thermodynamic cycle in which heat is converted into useful energy.

Šiluminė energija gali būti naudingai paversta mechanine arba elektrine energija. Žemos temperatūros šaltinių šiluminės energijos pavertimo elektros energija būdai yra svarbi energijos generavimo sritis, todėl yra reikalinga padidinti tokios žemos temperatūros šilumos pavertimo elektros energija efektyvumą.Thermal energy can usefully be converted into mechanical or electrical energy. Techniques for converting thermal energy from low temperature sources into electricity are an important area of power generation and it is therefore necessary to increase the efficiency of converting such low temperature heat to electricity.

Šilumos šaltinio energija gali būti paversta mechanine energija ir po to elektros energija, naudojant darbinį skystį, kuris yra išplečiamas ir regeneruojamas uždaroje sistemoje, veikiančioje termodinaminiu ciklu. Darbinį skystį gali sudaryti skirtingų virimo temperatūrų komponentai, ir darbinio skysčio sudėtis gali būti modifikuota skirtingose vietose sistemos viduje, siekiant padidinti operacijos efektyvumą. Sistemos, paverčiančios žemos temperatūros šilumą į elektros energiją, yra aprašytos Alexander I. Kalina JAV patentuose Nr.Nr. 4346561, 4489563, 4982568 ir 5029444. Be to, sistemos su daugiakomponenčiais darbiniais skysčiais aprašytos Alexander I. Kalina JAV patentuose Nr.Nr. 4548043, 4586340-, 4604867, 4732005, 4763480, 4899545, 5095708, 5440882, 5572871 ir 5649426.The heat source energy can be converted into mechanical energy and then electrical energy using a working fluid that is expanded and regenerated in a closed system operating on a thermodynamic cycle. The working fluid may consist of components at different boiling points, and the composition of the working fluid may be modified at different locations within the system to increase the efficiency of the operation. Systems for converting low temperature heat into electricity are described in U.S. Pat. 4346561, 4489563, 4982568, and 5029444. In addition, systems with multi-component working fluids are described in U.S. Patent No. 5,101,197 to Alexander I. Kalina. 4548043, 4586340-, 4604867, 4732005, 4763480, 4899545, 5095708, 5440882, 5572871 and 5649426.

Išradime atskleistas termodinaminio ciklo realizavimo būdas ir sistema. Darbinė srovė, susidedanti iš žemos temepratūros virimo taško komponento ir aukštesnės temperatūros virimo taško komponento, yra šildoma išorinės šilumos šaltiniu (pavyzdžiui, žemos temperatūros šaltiniu), siekiant‘sukurti pašildytą darbinę t, dujų srovę. Pašildyta darbinę dujų srovė atskiriama pirmajame separatoriuje, gaunant pašildytą riebią dujų srovę, turinčią santykinai daugiau žemos temperatūros virimo taško komponento, ir liesą srovę, turinčią santykinai mažiau žemos temperatūros virimo taško komponento. Pašildyta riebi dujų srovė išplečiama, transformuojant srovės energiją į naudingą formą ir gaunant išplėstą, panaudotą riebią srovę. Tuomet liesa srovė ir išplėsta, panaudota riebi srovė vėl sujungiami, gaunant darbinę srovę.The invention discloses a method and system for realizing a thermodynamic cycle. The operating current, consisting of the low temperature boiling point component and the higher temperature boiling point component, is heated by an external heat source (e.g., a low temperature source) to produce a heated operating t gas. The heated operating gas stream is separated in the first separator to produce a heated greasy gas stream having a relatively lower low boiling point component and a lean current having a relatively lower low boiling point component. The heated fatty gas stream is expanded by transforming the jet energy into a usable form and obtaining an expanded, utilized greasy current. The lean current and the expanded, used fat current are then reconnected to provide operating current.

Konkretūs išradimo variantai gali turėti vieną ar daugiau toliau išvardintų ypatybių. Darbinė srovė kondensuojama, perduodant šilumą pirmajame šilumokaityje žemesnės temperatūros šaltiniu, ir po to jos slėgis padidinamas.Specific embodiments of the invention may have one or more of the following features. The operating current is condensed by transferring heat to the first heat exchanger at a lower temperature source and then the pressure is increased.

Įvyksta dviejų stadijų - pirmosios ir antrosios - išsiplėtimas, ir dalinai išsiplėtusio skysčio srovė ekstrahuojama tarp pirmosios ir antrosios stadijų bei sujungiama su liesa srove. Separatorius tarp pirmosios ir antrosios stadijų perskiria dalinai išsiplėtusi skystį j garus ir skystį, ir dalis arba visi garai persiunčiami į antrąją stadiją, kita garų dalis gali būti sujungta su skysčiu ir po to su liesa srove. Antrasis šilumokaitis rekuperatyviai didesniu slėgiu perduoda naujai sudarytosios daugiakomponentės darbinės srovės šilumą (prieš kondensavimą) kondensuotai daugiakomponentei darbinei srovei. Trečiasis šilumokaitis perduoda liesos srovės šilumą darbinei srovei, išėjusiai iš antrojo šilumokaičio. Darbinė srovė perskiriama į dvi sroves, viena iš kurių pašildoma išorine šiluma, kita pašildoma ketvirtajame šilumokaityje liesos srovės šiluma; po to abi srovės sujungiamos, gaunant pašildytą dujų darbinę srovę, kuri atskiriama separatoriuje.There are two stages of expansion, the first and the second, and the flow of the partially expanded fluid is extracted between the first and second stages and connected to the lean stream. The separator separates the partially expanded liquid into a vapor and a liquid between the first and second stages, and part or all of the vapor is passed to the second stage, the other part of the vapor being connected to the liquid and then to the lean stream. The second heat exchanger transfers the heat (pre-condensation) of the newly formed multicomponent operating current to the condensed multicomponent operating current at a recuperatively higher pressure. The third heat exchanger transmits the lean current heat to the operating current exiting the second heat exchanger. The operating current is divided into two currents, one heated by external heat and the other heated by a fourth heat exchanger in the form of lean current heat; the two currents are then combined to produce a heated gas operating current which is separated in the separator.

Išradimas turi vieną ar daugiau toliau išvardintų privalumų. Išradimu galima padidinti žemos temperatūros šilumos pavertimo elektros srove efektyvumą, pranokstantį standartinių Rankine ciklų efektyvumą.The invention has one or more of the following advantages. The present invention can increase the efficiency of converting low temperature heat to electric current beyond the performance of standard Handle cycle.

Kiti išradimo privalumai ir ypatybės paaiškės iš toliau sekančių konkrečių_; jo realizavimo variantų ir iš apibrėžties.Other advantages and features of the invention will become apparent from the following specifics _; of its embodiments and by definition.

Fig.1 yra termodinaminės sistemos, skirtos paversti žemos temperatūros šaltinio šilumą naudinga forma, diagrama.Fig. 1 is a diagram of a thermodynamic system for converting low temperature source heat into a useful form.

Fig.2 yra kitas fig.1 sistemos variantas, leidžiantis ekstrahuotai srovei ir visiškai išnaudotai srovei turėti kompozicijas, skirtingas nuo aukšto slėgio srovės.Fig. 2 is another embodiment of the system of Fig. 1 which allows the extracted current and the fully utilized current to have compositions different from the high pressure current.

Fig.3 yra supaprastinto varianto diagrama, kuriame’; nėra ekstrahuotos srovės.Fig. 3 is a simplified diagram showing '; no current is extracted.

Fig.4 yra dar labiau supaprastinto varianto diagrama.Fig.4 is a diagram of an even simplified version.

Fig.1 parodyta termodinaminio ciklo sistema naudingai energijai (pavyzdžiui, mechaninei ir vėliau elektros) gauti iš išorinio šilumos šaltinio. Šiame pavyzdyje išorinis šilumos šaltinis yra žemos temperatūros šilumą atidavusio vandens srovė, kuri teka keliu, pažymėtu rodyklėmis 25-26, per šilumokaitį HE-5 ir šildo uždaro termodinaminio ciklo darbinę srovę 117-17. 1 lentelėje pateikti fig.1 skaitmenimis pažymėtų taškų parametrai. Tipiniai išeities iš sistemos rezultatai pateikti 5 lentelėje.Fig. 1 shows a thermodynamic cycle system for obtaining useful energy (for example mechanical and subsequently electrical) from an external heat source. In this example, the external heat source is a low-temperature jet of water that flows through a path marked by arrows 25-26 through a heat exchanger HE-5 and heats a closed thermodynamic cycle operating current 117-17. Table 1 shows the parameters of the digitized dots in Fig. 1. Typical system exit results are shown in Table 5.

Fig.1 sistemos darbinė srovė yra daugiakomponentė darbinė srovė, susidedanti iš žemos temperatūros virimo taško komponento ir aukštos temperatūros virimo taško komponento. Geriausiu atveju tokia darbine srove gali būti amoniako-vandens mišinys, du ar keli angliavandeniai, du ar keli freonai, angliavandenių ir freonų mišiniai ar pan. Paprastai darbine srove gali būti bet kokio skaičiaus junginių mišiniai, turintys puikias termodinamines ir tirpumo charakteristikas. Optimaliausiu atveju naudojamas vandens ir amoniako mišinys. Sistemoje, pavaizduotoje fig.1, darbinė srovė yra tos pačios sudėties nuo taško 13 iki taško 19.The operating current of the system of Fig. 1 is a multicomponent operating current consisting of a low temperature boiling point component and a high temperature boiling point component. Ideally, such a working stream may be an ammonia-water mixture, two or more carbohydrates, two or more freons, a mixture of carbohydrates and freons, or the like. Usually, the working stream can be any number of compound mixtures having excellent thermodynamic and solubility characteristics. A water / ammonia mixture is ideally used. In the system of FIG. 1, the operating current is of the same composition from point 13 to point 19.

Pradedant diskusiją apie fig.1 pavaizduotą sistemą ties turbinos T išėjimu, reikia pažymėti, kad srovė taške 34 yra išplėsta, panaudota, riebi srovė. Ši srovė vadinama “riebia todėl, kad turi daug žemos temperatūros virimo taško komponento. Ji yra žemo slėgio srovė, ir bus sumaišyta su liesesne, absorbuojančia srove, turinčia 12 taško parametrus, siekiant sukurti tarpinės sudėties darbinę srovę, turinčią 13 taško parametrus. Srovė taške 12 vadinama “liesa” todėl, kad turi mažai žemos temperatūros virimo taško komponento.As we begin the discussion of the system of Fig. 1 at the exit of the turbine T, it should be noted that the current at 34 is an extended, utilized, oily current. This current is called 'greasy because it has a high low boiling point component. It is a low pressure jet, and will be mixed with a leaner, absorbing jet having 12-point parameters to create an intermediate composition operating current having 13-point parameters. The current at point 12 is called "lean" because it has a low low boiling point component.

Esant bet kokiai temperatūrai, tarpinės sudėties darbinė srovė taške 13 gali būti kondensuota žemesniame slėgyje, nei riebesnė srovė taške 34. Tai leidžia ekstrahuoti daugiau energijos iš turbinos T ir padidina proceso efektyvumą.At any temperature, the intermediate operating current at point 13 can be condensed at a lower pressure than the fatty current at point 34. This allows more energy to be extracted from the turbine T and increases process efficiency.

Darbinė srovė taške 13 yra dalinai kondensuojama. Ši srovė įeina į šilumokaitį HE-2, kur ji ataušinama, ir išeina iš šilumokaičio HE-2, turėdama 29 taško parametrus. Ji vis dar yra tik dalinai, bet ne visiškai, kondensuota. Dabar srovė įeina j šilumokaitį HE-1, kur ji ataušinama aušinimo vandens srove 23-24 ir, tuo būdu, yra visiškai kondensuojama, įgaudama 14 taško parametrus. Tuomet darbinės srovės, turinčios 14 taško parametrus, slėgis padidinamas, gaunant 21 taško parametrus. Taške 21 darbinė srovė įeina į šilumokaitį HE-2, kur ji yra rekuperatyviai pašildoma darbine srove taškuose 13-29 (žr. aukščiau) ir įgauna 15 taško parametrus. Darbinė srovė, turinti 15 taško parametrus, įeina j šilumokaitį HE3, kur ji pašildoma ir įgauna 16 taško parametrus. Tipiniu atveju, taškas 16, nors ir galėtų, bet neturi būti tikslus virimo taškas. Darbinė srovė taške 16 perskiriama j dvi dalis: pirmąją darbinės srovės dalį 117 ir antrąją darbinės srovės dalį 118. Pirmoji darbinės srovės dalis, turinti 117 taško parametrus, paduodama j šilumokaitį HE-5, iš kurio ji išeina, turėdama 17 taško parametrus. Ji pašildoma išorinio šilumos šaltinio srove 25-26. Antroji darbinės srovės dalis 118 įeina j šilumokaitį HE-4, kur ji pašildoma rekuperatyviai, įgaudama 18 taško parametrus. Išėjusios iš šilumokaičių HE-4 ir HE-5 abi darbinių srovių dalys sujungiamos, gaunant pašildytą darbinę dujų srovę su 19 taško parametrais. Šios srovės dalį arba ją visą sudaro garai. Geriausiu atveju, taške 19 tik dalis srovės paverčiama garais. Taške 19 darbinė srovė turi tą pačią tarpinę kompoziciją, kuri buvo gauta taške 13, visiškai kondensuota taške 14, kurios slėgis buvo padidintas taške 21 ir kuri buvo iš anksto pašildyta iki taškų 15 ir 16 parametrų. Ji jeina į separatorių S. Čia ji perskiriama į “riebius” sočiuosius garus, vadinamus “pašildyta riebia dujų srove, turinčia taško 30 parametrus, ir liesą sotųjį skystį, vadinamą “liesa srove”, turinčia 7 taško parametrus. Liesa srovė (sotusis skystis) taške 7 jeina į šilumokaitį HE-4, kur jis ataušta, šildydamas darbinę srovę 118-18 (žr. aukščiau). Liesa srovė taške 9 išeina iš šilumokaičio HE-4 su 8 taško parametrais. Jos slėgis pakeliamas iki tinkamai parinkto lygio, suteikiant jai taško 9 parametrus.The operating current at point 13 is partially condensed. This current enters the heat exchanger HE-2, where it is cooled, and exits the heat exchanger HE-2, having a 29-point setting. It is still only partially, but not completely, condensed. The current now enters the heat exchanger HE-1, where it is cooled by a cooling water stream 23-24 and is thus fully condensed, gaining 14 points. The operating current, which has 14-point parameters, is then pressurized to 21-point parameters. At point 21, the operating current enters the heat exchanger HE-2, where it is recuperatively heated by operating current at points 13-29 (see above) and acquires the parameters of point 15. The operating current, with 15-point settings, enters the heat exchanger HE3, where it is heated to 16-point settings. Typically, point 16, though it could, does not have to be an exact boiling point. The operating current at point 16 is divided into two parts: a first operating current portion 117 and a second operating current portion 118. The first operating current portion having point 117 parameters is fed to a heat exchanger HE-5 from which it exits with 17 point settings. It is heated by an external heat source current of 25-26. The second part of the operating current 118 enters the heat exchanger HE-4, where it is heated recuperatively, gaining 18 points. Exit from HE-4 and HE-5 heat exchangers, both operating currents are combined to provide a heated operating gas flow with 19-point settings. Some or all of this current consists of vapor. At best, at point 19, only part of the current is converted to steam. At point 19, the operating current has the same intermediate composition as obtained at point 13, fully condensed at point 14, the pressure of which was increased at point 21, and which was preheated to the parameters of points 15 and 16. It enters the separator S. Here it is divided into a "greasy" saturated vapor known as "a heated greasy gas stream having point 30 parameters and a lean saturated liquid called a" lean stream "having point 7 parameters. The lean current (saturated liquid) at point 7 enters the heat exchanger HE-4 where it cools, heating the operating current 118-18 (see above). Lean current at point 9 exits the HE-4 heat exchanger with point 8 parameters. Its pressure is raised to a properly selected level, giving it the parameters of point 9.

Dabar grįžkime prie taško 30. Pašildyta riebi dujų srovė (sotieji garai) išeina iš separatoriaus S. Ši srovė jeina į turbiną T, kur ji išsiplečia, sumažindama savo slėgį, ir suteikia naudingą mechaninę energiją turbinai T, naudojamai generuoti elektrą. Dalis išplėstos srovės, turinčios taško 32 parametrus, ekstrahuojama iš turbinos T tarpiniame slėgyje (maždaug tokiame pačiame kaip ir taške 9), ir ši ekstrahuota srovė 32 (priklausanti “antrajai daliai dalinai išplėstos riebios srovės, “pirmoji dalis bus išplėsta vėliau) taške 9 sumaišoma su liesa srove, gaunant kombinuotą srovę su 10 taško parametrais. Liesa srovė, turinti 9 taško parametrus, tarnauja kaip ekstrahuotosios srovės 32 absorbuojanti srovė. Gautoji srovė (liesa srovė ir antroji dalis), turinti 10 taško parametrus, įeina į šilumokaitį HE-3, kur ji ataušta, atiduodama šilumą darbinei srovei 15-16, iki 11 taško parametrų. Srovės, turinčios 11 taško parametrus, slėgis padidinamas iki 34 taško parametrų, gaunant 12 taško parametrus.Let us now return to point 30. The heated fatty gas stream (saturated vapor) leaves the separator S. This stream enters the turbine T where it expands, reducing its pressure, and provides useful mechanical energy for the turbine T used to generate electricity. Part of the expanded current having the parameters of point 32 is extracted from the turbine T under intermediate pressure (approximately the same as at point 9) and this extracted current 32 (belonging to the "second part of the partially expanded fatty current," the first part will be expanded later) with lean current to produce a combined current with 10-point parameters. The lean current having 9-point parameters serves as an absorbing current for the extracted current 32. The incoming current (lean current and second part) having 10-point parameters enters the heat exchanger HE-3, where it cools, providing heat to operating current 15-16, to 11-point parameters. For a jet having 11-point parameters, the pressure is increased to 34-point parameters to obtain 12-point parameters.

Ne visa įtekėjusi į turbiną T srovė buvo ekstrahuota išplėstame būvyje taške 32. Likusioji dalis, priklausanti pirmajai daliai, išplečiama, sumažinant jos slėgį iki tinkamai pasirinkto dydžio, ir išeina iš turbinos T taške 34. Ciklas užsidaro.Not all of the inlet current to the turbine T was extracted in expanded state at point 32. The remainder of the first part is expanded by reducing its pressure to a properly selected size and exits the turbine at point 34. The cycle closes.

Fig.1 aprašytame variante ekstrahentas taške 32 turi tą pačią kompoziciją, kaip ir srovės taškuose 30 ir 34. Variante, parodytame fig.2, turbina turi pirmąją pakopą T-1 ir antrąją pakopą T-2, dalinai išplėsta riebi srovė išeina iš turbinos aukštesnio slėgio pakopos T-1 taške 31. Fig.2 pažymėtųjų taškų parametrai pateikti 2 lentelėje. Tipinė fig.2 pavaizduotos sistemos išeiga pateikta 6 lentelėje.In the embodiment described in Fig. 1, the extractor at point 32 has the same composition as the current at points 30 and 34. In the variant shown in Fig. 2, the turbine has a first stage T-1 and a second stage T-2, pressure steps at T-1 point 31. The parameters of the marked points of Fig. 2 are given in Table 2. The typical yield of the system shown in Figure 2 is given in Table 6.

Kaip matyti fig.2, dalinai išplėsta riebi srovė po pirmos turbinos palopos T-1 perskiriama j pirmąją dalį 33, kuri išplečiama toliau žemesnio slėgio turbinos palopoje T-2, ir antrąją dalį 32, kuri sujungiama su liesa srove taške 9. Dalinai išplėsta riebi srovė įeina j separatorių S-2, kur ji perskiriama į garus ir skystį. Antrosios dalies kompozicija taške 32 parenkama taip, kad būtų optimizuotas jos efektyvumas, sumaišant ją su srove taške 9. Separatorius S-2 leidžia suliesint! srovę 32 iki sočiojo skysčio lygio separatoriuje S-2 esančiame slėgyje ir temperatūroje; šiuo atveju, srovė 33 būtų sotieji garai, turintys charakteristikas, gautas separatoriuje S-2. Pasirenkant maišymo metu srovės 133 kiekį, sočiojo skysčio ir sočiųjų garų kiekis srovėje 32 gali būti įvairus.As can be seen in Fig. 2, the partially expanded fatty stream after the first turbine port T-1 is divided into a first section 33, which is further expanded in a lower pressure turbine chamber T-2, and a second section 32, which is connected to the lean stream at point 9. the current enters the separator S-2, where it is separated into vapor and liquid. The composition of the second part at point 32 is selected to optimize its efficiency by mixing it with the jet at point 9. Separator S-2 allows blending! current 32 to the saturated fluid level at pressure and temperature in separator S-2; in this case, the current 33 would be a saturated vapor having the characteristics obtained in a separator S-2. The amount of saturated liquid and saturated vapor in stream 32 may be varied by selecting the amount of stream 133 during mixing.

Fig.3 pateiktasis variantas skiriasi nuo fig.1 tuo, kad neturi šilumokaičio HE-4, ir čia nėra dalinai išplėstos turbinos palopoje srovės ekstrahento. Fig. 3 pavaizduotame variante pašildyta srovė, išeinanti iš separatoriaus S, yra nukreipiama tiesiai į šilumokaitį HE-3. Fig.3 pažymėtųjų taškų parametrai pateikti 3 lentelėje. Tipinė sistemos išeiga pateikta 7 lentelėje.The embodiment shown in Fig. 3 differs from Fig. 1 in that it does not have a HE-4 heat exchanger and there is no flow extraction solvent for the partially expanded turbine in the palopo. FIG. In the embodiment shown in Fig. 3, the heated current leaving the separator S is directed directly to the heat exchanger HE-3. The parameters of the marked points in Fig.3 are shown in Table 3. The typical system yield is shown in Table 7.

Fig.4 pateiktasis variantas skiriasi nuo fig.3 tuo, kad nėra šilumokaičio HE-2. Pažymėtųjų taškų charakteristikos pateiktos 4 lentelėje. Tipinė sistemos išeiga pateikta 8 lentelėje. Kadangi be šilumokaičio HE-2 proceso efektyvumas sumažėja, šis variantas ekonomiškai rekomenduotinas ten, kur energijos padidėjimas neatperka šilumokaičio.The embodiment shown in Fig. 4 differs from Fig. 3 in that there is no HE-2 heat exchanger. The characteristics of the marked points are presented in Table 4. The typical system yield is shown in Table 8. Because the HE-2 process efficiency is reduced without the heat exchanger, this option is economically recommended where the increase in energy does not reward the heat exchanger.

Bendru atveju šio išradimo būdo įgyvendinimui gali būti panaudota standartinė įranga. Tuo būdu, tokie įrenginiai, kaip šilumokaičiai, rezervuarai, siurbliai, turbinos, vožtuvai ir jungiamieji elementai, naudojami Rankine cikluose, gali būti panaudoti šio išradimo būdo realizavimui.In general, standard equipment may be used to implement the present invention. Thus, devices such as heat exchangers, reservoirs, pumps, turbines, valves, and fittings used in manual cycles can be utilized to practice the present invention.

Aprašytuose šio išradimo variantuose darbinis skystis yra išplečiamas, suteikiant postūmį įprasto tipo turbinai. Tačiau aukšto slėgio darbinio skysčio išplėtimas, kurio metu sumažėja jo slėgis ir atpalaiduojama energija, gali būti atliktas bet kokiomis tinkamomis priemonėmis, žinomomis šios srities specialistams.Tuo būdu atpalaiduota energija gali būti saugoma ar panaudojama bet kokiu žinomu šios srities specialistams būdu.In the embodiments of the present invention, the working fluid is expanded to give a boost to a conventional type of turbine. However, the expansion of the high pressure working fluid, which reduces its pressure and releases energy, can be accomplished by any suitable means known to those skilled in the art. In this way, the released energy can be stored or utilized in any manner known to those skilled in the art.

Aprašytųjų variantų separatoriai gali būti įprasti svorio jėgos separatoriai, pavyzdžiui, rezervuarai. Bet kokie įprasti prietaisai, naudojami suformuoti iš vienos srovės dvi ar kelias sroves, turinčias skirtingas kompozicijas, gali būti panaudoti liesos srovės ir riebios srovės suformavimui iš darbinės skysčio srovės.The separators of the embodiments described may be conventional gravity separators, such as reservoirs. Any conventional device used to form a single stream of two or more currents having different compositions can be used to form a lean current and a fat current from a working fluid stream.

Kondensatorius gali būti bet koks žinomas šilumos pašalinimo prietaisas, pavyzdžiui, kondensatoriumi gali būti toks šilumokaitis, kaip vandens aušinimo sistema, ar kitokios rūšies kondensavimo prietaisas.The condenser may be any known heat removal device, for example, the condenser may be a heat exchanger such as a water cooling system, or another type of condensing device.

Šio išradimo ciklo realizavimui gali būti panaudoti įvairių rūšių šilumos šaltiniai.Various types of heat sources can be utilized to carry out the cycle of the present invention.

LENTELĖTABLE

P psiA P psiA X X T’F T'F HBTU/lb HBTU / lb G/G30 G / G30 Srautas Ib/h Flow rate Ib / h Fazė Phase 325.22 325.22 .5156 .5156 202.81 202.81 82.29 82.29 .5978 .5978 276,778 276,778 Sotskystis Soot fluid 305.22 305.22 .5156 .5156 169.52 169.52 44.55 44.55 .5978 .5978 276,778 276,778 Sk 28° See 28 ° 214.26 214.26 .5156 .5156 169.50 169.50 44.55 44.55 .5978 .5978 276,778 276,778 Dr .9997 Dr .9997 214.26 214.26 .5553 .5553 169.52 169.52 90.30 90.30 .6513 .6513 301,549 301,549 Dr .9191 Dr. 9191 194.26 194.26 .5533 .5533 99.83 99.83 -27.79 -27.79 .6513 .6513 301,549 301,549 Sk 53° See, 53 ° 85.43 85.43 .5533 .5533 99.36 99.36 -29.79 -29.79 .6513 .6513 301,549 301,549 Dr .9987 Dr.9987 85.43 85.43 .7000 .7000 99.83 99.83 174.41 174.41 1 1 463,016 463,016 dr .6651 Dr. 6651 84.43 84.43 .7000 .7000 72.40 72.40 -38.12 -38.12 1 1 463,016 463,016 SotSkystis Sot Liquid 350.22 350.22 .7000 .7000 94.83 94.83 -13.08 -13.08 1 1 463,016 463,016 Sk 73° 73 ° 335.22 335.22 .7000 .7000 164.52 164.52 65.13 65.13 1 1 463,016 463,016 SotSkystis Sot Liquid 335.22 335.22 .7000 .7000 164.52 164.52 65.13 65.13 .8955 .8955 463,016 463,016 SotSkystis Sot Liquid 335.22 335.22 .7000 .7000 203.40 203.40 302.92 302.92 .8955 .8955 414,621 414,621 Dr .5946 Dr.5946 335.22 335.22 .7000 .7000 164.52 164.52 65.13 65.13 .1045 .1045 463,016 463,016 SotSkystis Sot Liquid 325.22 325.22 .7000 .7000 197.81 197.81 281.00 281.00 .1045 .1045 48,395 48,395 Dr .6254 Dr. 6254 325.22 325.22 .7000 .7000 202.81 202.81 300.63 300.63 1 1 463,016 463,016 Dr .5970 Dr.5970 355.22 355.22 .7000 .7000 73.16 73.16 -36.76 -36.76 1 1 463,016 463,016 Sk96° Sk96 ° 84.93 84.93 .7000 .7000 95.02 95.02 150.73 150.73 1 1 463,016 463,016 Dr .6984 Dr.6984 325.22 325.22 .9740 .9740 202.81 202.81 625.10 625.10 .4022 .4022 186,238 186,238 SotGarai SotGars 214.26 214.26 .9740 .9740 170.19 170.19 601.53 601.53 .0535 .0535 24,771 24,771 Dr .0194 Dr.0194 85.43 85.43 .9740 .9740 104.60 104.60 555.75 555.75 .3487 .3487 161,771 161,771 Dr .0467 Dr .0467 • • Vanduo Water 64.40 64.40 32.40 32.40 9.8669 9,8669 4,568,519 4,568,519 Vanduo Water 83.54 83.54 51.54 51.54 9.8669 9,8669 4,568,519 4,568,519 • • Vanduo Water 208.40 208.40 176.40 176.40 5.4766 5.4766 2,535,750 2,535,750 Vanduo Water 169.52 169.52 137.52 137.52 5.4766 5.4766 2,535,750 2,535,750

LENTELĖTABLE

P psiA P psiA X X PF PF HBTU/lb HBTU / lb G/G30 G / G30 Srautas Ib/h Flow rate Ib / h Fazė Phase 325.22 325.22 .5156 .5156 202.81 202.81 82.29 82.29 .5978 .5978 276,778 276,778 Sotskystis Soot fluid 305.22 305.22 .5156 .5156 169.52 169.52 44.55 44.55 .5978 .5978 276,778 276,778 Sk 28° See 28 ° 214.19 214.19 .5156 .5156 169.48 169.48 44.55 44.55 .5978 .5978 276,778 276,778 Dr .9997 Dr .9997 214.19 214.19 .5553 .5553 169.52 169.52 89.23 89.23 .6570 .6570 304,216 304,216 Dr .9191 Dr. 9191 194.19 194.19 .5533 .5533 99.74 99.74 -29.96 -29.96 .6570 .6570 304,216 304,216 Sk 53° See, 53 ° 85.43 85.43 .5533 .5533 99.53 99.53 -29.96 -29.96 .6570 .6570 304,216 304,216 Dr .9992 Dr.9992 85.43 85.43 .7000 .7000 99.74 99.74 173.96 173.96 1 1 463,016 463,016 dr .6658 Dr. 6658 84.43 84.43 .7000 .7000 72.40 72.40 -38.12 -38.12 1 1 463,016 463,016 SotSkystis Sot Liquid 350.22 350.22 .7000 .7000 94.83 94.83 -13.18 -13.18 1 1 463,016 463,016 Sk 73° 73 ° 335.22 335.22 .7000 .7000 164.52 164.52 65.13 65.13 1 1 463,016 463,016 SotSkystis Sot Liquid 335.22 335.22 .7000 .7000 164.52 164.52 65.13 65.13 .8955 .8955 463,016 463,016 SotSkystis Sot Liquid 325.22 325.22 .7000 .7000 203.40 203.40 302.92 302.92 .8955 .8955 414,621 414,621 Dr .5946 Dr.5946 325.22 325.22 .7000 .7000 164.52 164.52 65.13 65.13 .1045 .1045 463,016 463,016 SotSkystis Sot Liquid 355.22 355.22 .7000 .7000 197.81 197.81 281.00 281.00 .1045 .1045 48,395 48,395 Dr .6254 Dr. 6254 325.22 325.22 .7000 .7000 202.81 202.81 300.63 300.63 1 1 463,016 463,016 Dr .5978 Dr.5978 355.22 355.22 .7000 .7000 73.16 73.16 -36.76 -36.76 1 1 463,016 463,016 Sk 96° 96 ° 84.93 84.93 .7000 .7000 94.96 94.96 150.38 150.38 1 1 463,016 463,016 Dr .6989 Dr.6989 325.22 325.22 .9740 .9740 202.81 202.81 625.10 625.10 .4022 .4022 186,238 186,238 SotGarai SotGars 214.26 214.26 .9740 .9740 170.63 170.63 602.12 602.12 .4022 .4022 186,238 186,238 Dr .0189 Dr.0189 214.26 214.26 .9224 .9224 104.63 104.63 539.93 539.93 .0593 .0593 27,437 27,437 Dr .1285 Dr. 1285 214.69 214.69 .9829 .9829 170.63 170.63 612.87 612.87 .3430 .3430 158,800 158,800 SotGarai SotGars 85.43 85.43 .9829 .9829 102.18 102.18 564.60 564.60 .3430 .3430 158,800 158,800 Dr .0294 Dr.0294 214.69 214.69 .5119 .5119 170.63 170.63 45.44 45.44 .0076 .0076 3,527 3,527 SotSkystis Sot Liquid • • Vanduo Water 64.40 64.40 32.40 32.40 9.8666 9,8666 4,568,371 4,568,371 Vanduo Water 83.50 83.50 51.50 51.50 9.8666 9,8666 4,568,371 4,568,371 • • Vanduo Water 208.40 208.40 176.40 176.40 5.4766 5.4766 2,535,750 2,535,750 Vanduo Water 169.52 169.52 137.52 137.52 5.4766 5.4766 2,535,750 2,535,750

LENTELĖTABLE

# # P psiA P psiA X X T°F T ° F HBTU/lb HBTU / lb G/G30 G / G30 Srautas Ib/h Flow rate Ib / h Fazė Phase 10 10th 291.89 291.89 .4826 .4826 203.40 203.40 80.72 80.72 .6506 .6506 294,484 294,484 Sotskystis Soot fluid 11 11th 271.89 271.89 .4826 .4826 109.02 109.02 -23.56 -23.56 .6506 .6506 294,484 294,484 Sk 89° 89 ° 12 12th 75.35 75.35 .4826 .4826 109.07 109.07 -23.56 -23.56 .6506 .6506 294,484 294,484 Dr .9994 Dr .9994 13 13th 75.35 75.35 .6527 .6527 109.02 109.02 180.50 180.50 1 1 452,648 452,648 Dr .6669 Dr.6669 14 14th 74.35 74.35 .6527 .6527 72.40 72.40 -47.40 -47.40 1 1 452,648 452,648 SotSkystis Sot Liquid 15 15th 316.89 316.89 .6527 .6527 103.99 103.99 -12.43 -12.43 1 1 452,648 452,648 Sk64° Sk64 ° 16 16th 301.89 301.89 .6527 .6527 164.52 164.52 55.41 55.41 1 1 452,648 452,648 SotSkystis Sot Liquid 17 17th 291.89 291.89 .6527 .6527 203.40 203.40 273.22 273.22 1 1 452,648 452,648 Dr .6506 Dr.6506 21 21st 321.89 321.89 .6527 .6527 73.04 73.04 -46.18 -46.18 1 1 452,648 452,648 Sk 97° 97 ° 29 29th 74.85 74.85 .6527 .6527 100.84 100.84 146.74 146.74 1 1 452,648 452,648 Dr .7104 Dr. 7104 30 30th 291.89 291.89 .9693 .9693 203.40 203.40 631.64 631.64 .3494 .3494 158,164 158,164 SotGarai SotGars 34 34 75.35 75.35 .9693 .9693 108.59 108.59 560.44 560.44 .3494 .3494 158,164 158,164 Dr .0474 Dr .0474 23 23rd Vanduo Water 64.40 64.40 32.40 32.40 8.1318 8.1318 3,680,852 3,680,852 24 24th • • Vanduo Water 88.27 88.27 56.27 56.27 8.1318 8.1318 3,680,852 3,680,852 25 25th • • Vanduo Water 208.40 208.40 176.40 176.40 5.6020 5.6020 2,535,750 2,535,750 26 26th _ee Vanduo Water 169.52 169.52 137.52 137.52 5.6020 5.6020 2,535,750 2,535,750

LENTELĖTABLE

# # P psiA P psiA X X T°F T ° F HBTU/lb HBTU / lb G/G30 G / G30 Srautas Ib/h Flow rate Ib / h Fazė Phase 10 10th 214.30 214.30 .4059 .4059 203.40 203.40 80.05 80.05 .7420 .7420 395,533 395,533 Sotskystis Soot fluid 11 11th 194.30 194.30 .4059 .4059 77.86 77.86 -55.30 -55.30 .7420 .7420 395,533 395,533 Sk118° Sk118 ° 12 12th 52.48 52.48 .4059 .4059 78.17 78.17 -55.30 -55.30 .7420 .7420 395,533 395,533 Sk 32° See 32 ° 29 29th 52.48 52.48 .5480 .5480 104.46 104.46 106.44 106.44 1 1 533,080 533,080 Dr .7825 Dr. 7825 14 14th 51.98 51.98 .5480 .5480 72.40 72.40 -60.06 -60.06 1 1 533,080 533,080 SotSkystis Sot Liquid 21 21st 244.30 244.30 .5480 .5480 72.83 72.83 -59.16 -59.16 1 1 533,080 533,080 Sk 98° See, 98 ° 16 16th 224.30 224.30 .5480 .5480 164.52 164.52 41.26 41.26 1 1 533,080 533,080 SotSkystis Sot Liquid 17 17th 214.30 214.30 .5480 .5480 203.40 203.40 226.20 226.20 1 1 533,080 533,080 Dr.742 Dr.742 30 30th 214.30 214.30 .9567 .9567 203.40 203.40 646.49 646.49 .2580 .2580 137,546 137,546 SotGarai SotGars 34 34 52.48 52.48 .9567 .9567 114.19 114.19 571.55 571.55 .2580 .2580 137,546 137,546 Dr .0473 Dr .0473 23 23rd • • Vanduo Water 64.40 64.40 32.40 32.40 5.7346 5.7346 3,057,018 3,057,018 24 24th Vanduo Water 93.43 93.43 61.43 61.43 5.7346 5.7346 3,057,018 3,057,018 25 25th • • Vanduo Water 208.40 208.40 176.40 176.40 4.7568 4.7568 2,535,750 2,535,750 26 26th Vanduo Water 169.52 169.52 137.52 137.52 4.7568 4.7568 2,535,750 2,535,750

LENTELĖTABLE

Techninės charakteristikos KCS34 Pirmas variantasSpecifications KCS34 First variant

Turbinos galingumas Pt 30 Tūris Turbine power Pt 30 Volume 58.34 kg/s 4044.45 l/s 58.34 kg / s 4044.45 l / s 463016 Ib/val 514182 fT3/val 463016 Ib / hr 514182 fT3 / h Priimta šiluma Accepted heat 28893.87 kW 28893.87 kW 212.93 BTU/lb 212.93 BTU / lb Neišnaudota šiluma Unused heat 25578.48 kW 25578.48 kW 188.50 BTU/lb 188.50 BTU / lb Σ turbinos entalpijos kritimas Σ drop in turbine enthalpy 3500.22 kW 3500.22 kW 25.80 BTU/lb 25.80 BTU / lb Turbinos darbas Turbine work 3258.81 kW 3258.81 kW 24.02 BTU/lb 24.02 BTU / lb Padavimo Siurblys ΔΗ 1.36, galingumas Feeding pump ΔΗ 1.36, power 196.51 kW 196.51 kW 1.45 BTU/lb 1.45 BTU / lb Padavimo siurblys+ aušinimo siurblys, galingumas Feed pump + cooling pump, power 364.36 kW 364.36 kW 3.00 BTU/lb 3.00 BTU / lb Bendras darbas Group work 2820.46 kW 2820.46 kW 23.21 BTU/lb 23.21 BTU / lb Skersinė išeiga Transverse yield 3184.83 kWe 3184.83 kWe Ciklo išeiga Cycle yield 3008.85 kWe 3008.85 kWe Visa išeiga Total yield 2820.46 kWe 2820.46 kWe Bendras šiluminis efektyvumas Total thermal efficiency 9.76% 9.76% Antrasis slenkstis The second threshold 17.56% 17.56% Antrojo slenksčio efektyvumas Second-threshold efficiency 55.58% 55.58% Specifinis Brine suvartojimas Specific Brine Consumption 899.05 lb/kWh 899.05 lb / kWh Specifinė galingumo išeiga Specific power output 1.11 Wh/lb 1.11 Wh / lb

LENTELĖTABLE

Techninės charakteristikos KCS34 Antr s variantasTechnical Specifications KCS34 Secondary variant

Turbinos galingumas Turbine power 58.34 kg/s 58.34 kg / s 463016 Ib/val 463016 Ib / hr Pt 30 Tūris Pt 30 Volume 4044.45 l/s 4044.45 l / s 514182 fT3/val 514182 fT3 / h Priimta šiluma Accepted heat 28893.87 kW 28893.87 kW 212.93 BTU/lb 212.93 BTU / lb Neišnaudota šiluma Unused heat 25578.48 kW 25578.48 kW 188.50 BTU/lb 188.50 BTU / lb Σ turbinos entalpijos kritimas Σ drop in turbine enthalpy 3500.22 kW 3500.22 kW 25.80 BTU/lb 25.80 BTU / lb Turbinos darbas Turbine work 3258.81 kW 3258.81 kW 24.02 BTU/lb 24.02 BTU / lb Padavimo Siurblys ΔΗ 1.36, galingumas Feeding pump ΔΗ 1.36, power 196.51 kW 196.51 kW 1.45 BTU/lb 1.45 BTU / lb Padavimo siurblys+ aušinimo siurblys, galingumas Feed pump + cooling pump, power 408.52 kW 408.52 kW 3.01 BTU/lb 3.01 BTU / lb Bendras darbas Group work 2820.46 kW 2820.46 kW 23.21 BTU/lb 23.21 BTU / lb Skersinė išeiga Transverse yield 3258.81 kWe 3258.81 kWe Ciklo išeiga Cycle yield 3062.30 kWe· 3062.30 kWe · Visa išeiga Total yield 2850.29 kWe 2850.29 kWe Bendras šiluminis efektyvumas Total thermal efficiency 9.86% 9.86% Antrasis slenkstis The second threshold 17.74% 17.74% Antrojo slenksčio efektyvumas Second-threshold efficiency 55.60% 55.60% Specifinis Brine suvartojimas Specific Brine Consumption 899.65 lb/kWh 899.65 lb / kWh Specifinė galingumo išeiga Specific power output 1.12Wh/lb 1.12Wh / lb

LENTELĖTABLE

Techninės charakteristikos KCS34 trečias variantasSpecifications Third variant of the KCS34

Turbinos galingumas Turbine power 57.03 kg/s 57.03 kg / s 452648 Ib/val 452648 Ib / hr Pt 30 Tūris Pt 30 Volume 4474.71 l/s 4474.71 l / s 568882 fT3/val 568882 fT3 / hr Priimta šiluma Accepted heat 28893.87 kW 28893.87 kW 217.81 BTU/lb 217.81 BTU / lb Neišnaudota šiluma Unused heat 25754.18 kW 25754.18 kW 194.14 BTU/lb 194.14 BTU / lb Σ turbinos entalpijos kritimas Σ drop in turbine enthalpy 3300.55 kW 3300.55 kW 24.88 BTU/lb 24.88 BTU / lb Turbinos darbas Turbine work 3072.82 kW 3072.82 kW 23.16 BTU/lb 23.16 BTU / lb Padavimo Siurblys ΔΗ 1.36, galingumas Feeding pump ΔΗ 1.36, power 170.92 kW 170.92 kW 1.29 BTU/lb 1.29 BTU / lb Padavimo siurblys+ aušinimo siurblys, galingumas Feed pump + cooling pump, power 341.75 kW 341.75 kW 2.58 BTU/lb 2.58 BTU / lb Bendras darbas Group work 2731.07 kW 2731.07 kW 20.59 BTU/lb 20.59 BTU / lb Skersinė išeiga Transverse yield 3072.82 kWe 3072.82 kWe Ciklo išeiga Cycle yield 2901.89kWe 2901.89kWe Visa išeiga Total yield 2731.07kWe 2731.07kWe Bendras šiluminis efektyvumas Total thermal efficiency 9.45% 9.45% Antrasis slenkstis The second threshold 17.39% 17.39% Antrojo slenksčio efektyvumas Second-threshold efficiency 54.34% 54.34% Specifinis Brine suvartojimas Specific Brine Consumption 928.48 Ib/kVVh 928.48 Ib / kVVh Specifinė galingumo išeiga Specific power output 1.08Wh/lb 1.08Wh / lb Šiluma, tekusi garo katilui Heat flowing to the steam boiler 15851.00 kW 15851.00 kW 577.22 BTU/lb 577.22 BTU / lb Neišnaudota šiluma Unused heat 10736.96 kW 10736.96 kW 390.99 BTU/lb 390.99 BTU / lb

LENTELĖTABLE

Techninės charakteristikos KCS34 Ketvirtas variantasSpecifications KCS34 Fourth variant

Turbinos galingumas Pt 30 Tūris Turbine power Pt 30 Volume 67.17 kg/s 7407.64 l/s 67.17 kg / s 7407.64 l / s 533080 Ib/val 941754 fT3/val 533080 Ib / hr 941754 fT3 / hr Priimta šiluma Accepted heat 28893.87 kW 28893.87 kW 184.94 BTU/lb 184.94 BTU / lb Neišnaudota šiluma Unused heat 26012.25 kW 26012.25 kW 166.50 BTU/lb 166.50 BTU / lb Σ turbinos entalpijos kritimas Σ drop in turbine enthalpy 3020.89 kW 3020.89 kW 19.34 BTU/lb 19.34 BTU / lb Turbinos darbas Turbine work 2812.45 kW 2812.45 kW 18.00 BTU/lb 6pm BTU / lb Padavimo Siurblys ΔΗ 1.36, galingumas Feeding pump ΔΗ 1.36, power 147.99 kW 147.99 kW 0.95 BTU/lb 0.95 BTU / lb Padavimo siurblys+ aušinimo siurblys, galingumas Feed pump + cooling pump, power 289.86 kW 289.86 kW 1.86 BTU/lb 1.86 BTU / lb Bendras darbas Group work 2522.59 kW 2522.59 kW 16.15 BTU/lb 16.15 BTU / lb Skersinė išeiga Transverse yield 2812.45 kWe 2812.45 kWe Ciklo išeiga Cycle yield 2664.46 kWe 2664.46 kWe Visa išeiga Total yield 2522.59 kWe 2522.59 kWe Bendras šiluminis efektyvumas Total thermal efficiency 8.73% 8.73% Antrasis slenkstis The second threshold 17.02% 17.02% Antrojo slenksčio efektyvumas Second-threshold efficiency 51.29% 51.29% Specifinis Brine suvartojimas Specific Brine Consumption 1005.22 lb/kWh 1005.22 lb / kWh Specifinė galingumo išeiga Specific power output 0.99 Wh/lb 0.99 Wh / lb

IŠRADIMO APIBRĖŽTISDEFINITION OF INVENTION

Claims

DEFINITION OF INVENTION

A method of realizing a thermodynamic cycle comprising heating an operating stream consisting of a low temperature boiling point component and a higher temperature boiling point component to obtain a heated operating gas stream, comprising: dividing the heated operating gas stream in a first separator; obtaining a heated fatty gas stream having relatively more low temperature boiling point component and a lean current having relatively less low temperature boiling point component;

extends the heated greasy gas stream and converts the current energy into useful energy to produce an expanded, utilized greasy current; and combines the lean current with the extended, applied fat current to produce the operating current.

2. A method according to claim 1, characterized by condensing the operating current obtained by combining the two currents before heating it with an external heat source, transferring heat to the low temperature source in the first heat exchanger, and subsequently increasing the operating current pressure.

3. A process according to claim 1, characterized in that it extends the operating current in two steps, in the first step partially extends the heated greasy gas stream, divides this partially expanded greasy stream into two parts, in the second step extends the first portion to obtain an expanded spent grease stream. connects the second part to the lean current before connecting the lean current to the expanded, used gas stream.

4. A method according to claim 2, characterized in that, prior to condensing the working current, it transmits its heat to the working current in the second heat exchanger after being pressurized but before being heated by an external heat source.

5. The method of claim 2, further comprising transmitting, in the third heat exchanger, lean current heat to the operating current after its pressure has been increased but before being heated by an external heat source.

6. The method of claim 4, further comprising transmitting, in the third heat exchanger, lean current heat to the operating current, previously heated by the second heat exchanger, but prior to heating it by an external heat source.

7. The method of claim 2, further comprising dividing the operating current by increasing its pressure, but heating the first portion of the operating current with an external heat source, heating the first portion of the operating current with an external heat source, a portion of the current with the second portion of the operating current to produce a heated operating gas stream.

8. The method of claim 7, further comprising transmitting, in the third heat exchanger, lean current heat to a second portion of the operating current.

9. A method according to claim 1, characterized by heating the external heat source in the fifth heat exchanger.

10. A method according to claim 3, characterized in that the operating current, consisting of a partially expanded fatty current, is divided into two parts, the first part consisting of vapor and the second part consisting of a liquid.

11. The method of claim 10, wherein said vapor is coupled to said liquid to form a second portion.

12. The method of claim 2, further comprising transmitting, in the third heat exchanger, lean current heat with a second portion to the operating current before heating it to an external heat source.

13. A thermodynamic cycle realization device comprising a heater heating an operating current consisting of a low temperature boiling point component and a high temperature boiling point component to provide a heated working gas stream, characterized in that it has a first separator for receiving the heated one. operating gas stream and providing a heated fatty gas stream having a relatively low boiling point component and a lean current having a relatively lower boiling point component, an expander to receive the fatty gas stream and converting the jet energy into a usable energy, and a first jet mixer for connecting the lean current to the expanded, used jet stream and to supply the operating current, the jet mixer output is connected to the heater input.

14. The apparatus of claim 13, further comprising a first heat exchanger and a pump disposed between the first jet mixer and the heater, the first heat exchanger for condensing the operating current by transferring heat to the low temperature source, and the pump for increasing the heat output operating pressure.

15. Apparatus according to claim 13, characterized in that the expander comprises: a first expansion stage, receiving a heated greasy gas stream and delivering a partially expanded greasy current, a current divider receiving and dividing the partially expanded greasy current, and a second expansion section; a step receiving and expanding the first portion to provide an expanded spent grease current, a second jet mixer for connecting the second portion to the lean jet before connecting the lean current to the expanded spent grease jet in the first jet mixer.

16. The apparatus of claim 14, further comprising a second heat exchanger for transferring the heat of the operating stream prior to condensation to the same operating stream after its pressure has been increased by the pump but before heating in the heater by an external heat source.

17. The apparatus of claim 14, further comprising a third heat exchanger for transmitting lean current heat to the operating current after its pressure has been increased by the pump but prior to heating in the heater by an external heat source.

18. The device of claim 16, further comprising a third heat exchanger for transmitting lean current heat to the operating current after receiving heat from the second heat exchanger but prior to heating it in the heater by an external heat source.

19. The device of claim 14, wherein:

a current divider for dividing the operating current already exited from the pump but prior to heating the heater to an external heat source, to a first operating current heated by the heater to obtain a first operating current portion and a second operating current to a third current mixer for connecting the heated the first portion of the operating current with the second portion of the operating current providing a heated operating gas stream,

20. The apparatus of claim 19, further comprising a fourth heat exchanger for transmitting lean current heat to the second working portion of the current.

21. The apparatus of claim 13, wherein the heater is a sixth heat exchanger.

22. The device of claim 15, wherein the current separator comprises a second separator for receiving a partially expanded greasy current and for separating it into vapor and liquid.

23. The device of claim 22, wherein the current separator comprises a fourth current mixer for combining the vapor from the second separator with the liquid from the second separator to form a second portion.

24. The apparatus of claim 15, further comprising a heat exchanger for transmitting lean current heat with a second portion to the operating current prior to heating it in the heater to an external heat source.