POWER GENERATION MACHINE SYSTEM

Description

Technical Field

[0001] The invention is related to a power generating system connected to the thermodynamic field similar to a steam power plant that can be used both mobile and in a fixed manner, which uses fluid liquid nitrogen and / or liquid air mixture and atmosphere air as an energy source.Prior Art

[0002] Water and water vapor is used in the steam power plants of the art. In steam power plants, additionally a boiler is present. In these boilers various fuels such as LPG, diesel oil, fuel oil, natural gas etc., are used. Some of these power plants operate according to the supercritical rankine cycle. In the steam power plants in such closed systems, liquid and steam is heated at a constant pressure and is then cooled. The fluid inside the pump is isoentropically compressed and the fluid inside the turbine can be isoentropically expanded. Differences in kinetic and potential energy are neglected and the heat transfer in a heat exchanger is carried out at a constant pressure. Continuous process conditions apply and heat loss in the heat exchanger, tanks, pipes and turbines are negligibly isolated. The properties of the fluid are kept constant, heat transfer in axial length is minimal and continuity equation is continuously provided.

[0003] In order to obtain the real cycle of steam engines, it is necessary to take into account the required difference in order to overcome frictional losses occurring at various points and heat losses and to provide heat transfer in the heaters.

[0004] Due to isoentropical compression and expansion division processes that are a crucial part of the compression process and the expansion process in a turbine, differences occur in thermodynamic features.

[0005] Several developments have been carried out in relation to a power generating machine system.

[0006] In the patent document numbered GB1214758A of the prior art, overloaded steam generators with super charge apparatus comprising a compressor and a gas turbine is disclosed.

[0007] In the United States patent document numbered US6729136B2 of the prior art, an energy generating power plant for a utility device which is used to expand and contract a liquid metal similar to mercury in order to actuate alternatively a piston, a crank shaft and following this an actuator using liquid nitrogen and a heated transfer fluid is disclosed. By operating the piston to control the various solenoid valves and pumps, timing is provided by allowing the liquid nitrogen to flow into a jacket around a reservoir containing the liquid metal, thereby allowing the piston to cool during the return movement. When suitable, the heated transfer fluid, is pumped with different jacket housing in order to force the remaining nitrogen and thereby to heat the liquid metal and drive the piston by means of force impact. The process is continued such that continuous power is provided to the utility device.

[0008] The patent document numbered GB787808A of the prior art, discloses a thermal power plant used to heat seawater and propel a marine tanker. The plant consists of a working environment in which a gaseous working environment flowing in a closed cycle is increased to a higher pressure in a compressor, and then said working environment is heated and following this said environment is discharged from the turbine which emits heat to the working environment that has been compressed inside a heat exchanger before being re-compressed.

[0009] In the Chinese patent document numbered CN107035447A of the prior art, compressed critical carbon dioxide energy, and a heat storage system and the operation method thereof is disclosed. The system is formed of a motor, a compressor, a low pressure super critical carbon dioxide storage tank, a cooler, a heat accumulator, a high temperature oil tank, a high pressure super critical carbon dioxide storage tank, a low temperature oil pump and low temperature heating oil.

[0010] Patent document numbered US2016 / 363007A1 discloses a method for generating electricity by means of a nuclear power plant and a liquid vaporization apparatus involves, during a first period, producing heat energy by means of the nuclear power plant and using the heat energy to vaporize water or to heat water vapour, expanding the water vapour formed in a first turbine and using the first turbine to drive an electricity generator in order to produce electricity, vaporizing liquefied gas coming from a cryogenic store in order to produce pressurized gas, reheating the pressurized gas with a part of the water vapour intended for the first turbine of the nuclear power plant and expanding the pressurized fluid in a second turbine to produce electricity and, during the second period, liquefying the gas to be vaporized. But, in the present application, the liquid heated with heater IV (4) via a ventilator by using atmosphere air. Also, the heater IV (4) directly connected with Turbine I (5). So, %100 of flow rate is using in present application. Also, pump I (8) disclosed in present invention located between the Heater I (1) and reservoir (7) wherein pump I (8) is configured to draw liquid nitrogen or liquid air in the reservoir (7) at atmospheric pressure, pump up a pressure of the liquid obtained from the reservoir (7), and spray liquid steam onto the first heater (1).

[0011] Patent document numbered US2006 / 266039A1 discloses a method to integrate collected solar thermal energy into the feedwater system of a Rankine cycle power plant. The hot oil 6 fed from the Hot Oil Storage Tank is then directed to a new feedwater heater X that provides heat in addition to or in substitution for the heat provided by the steam extraction 8 to the upstream heater. Typically, the hot oil would be on the "shell side" of the feedwater heater X and the feedwater, because it would be at a much higher pressure, would be on the "tube side" of the feedwater heater. It is anticipated that most retrofit applications would consist of substituting heat provided by the hot oil 6 for the high pressure extraction steam 8. In this manner, design operating parameters of the economizer is maintained and additional generating capacity may be realized since more steam would then be available to expand through the Steam Turbine. The cooled oil 7 is then returned to storage and eventually cold oil 5 is returned to the solar loop for reheating. But, in the present application, the liquid heated with heater IV (4) via a ventilator by using atmosphere air. Also, the heater IV (4) directly connected with Turbine I (5). So, %100 of flow rate is using in present application. Also, pump I (8) disclosed in present invention located between the Heater I (1) and reservoir (7) wherein pump I (8) is configured to draw liquid nitrogen or liquid air in the reservoir (7) at atmospheric pressure, pump up a pressure of the liquid obtained from the reservoir (7), and spray liquid steam onto the first heater (1).

[0012] Patent document numbered US2010 / 212318A1 discloses a solar thermal power plant is provided comprising a solar collection system and a steam-electric power plant. The tube radiation absorbers contain a thermal fluid therein, such as oil (phenyls) which are commercially available, such as under the trade name Therminol ®< VP-1. According to different embodiments, the thermal fluid may also be one of steam / water, molten salts, carbon dioxide, and helium. Thus, the thermal fluid is heated as it flows through the tube radiation absorbers 15. Reflectors, such as parabolic reflectors, may be provided in order to further heat the thermal fluid, as is well known in the art. But, in the present application, the liquid heated with heater IV (4) via a ventilator by using atmosphere air. Also, the heater IV (4) directly connected with Turbine I (5). So, %100 of flow rate is using in present application.Also, pump I (8) disclosed in present invention located between the Heater I (1) and reservoir (7) wherein pump I (8) is configured to draw liquid nitrogen or liquid air in the reservoir (7) at atmospheric pressure, pump up a pressure of the liquid obtained from the reservoir (7), and spray liquid steam onto the first heater (1).

[0013] Patent document numbered US4003786A discloses thermal energy storage and utilization system. High pressure steam comes from the nuclear reactor or constant output fossil fuel furnace and boiler 1 and passes through conduit 2. Conduit 3 draws a major portion of the steam off from conduit 2 and feeds this steam to turbine 4. Another portion of the primary high pressure steam passes through valve 7 to conduit 8 which leads the steam to interstage steam reheat unit 6. Interstage steam from turbine 4 passes by means of conduit 5 through unit 6 where it is reheated before being fed to turbine 9. Spent steam from turbine 9 passes through conduit 10 to condenser 11. Condensate from 11 passes through conduit 12 to pump 13 and thence to conduit 14. Conduit 14 introduces the water to water-steam heat exchanger 15 which exchanger is heated by extraction steam taken from turbine 9 through line L and which exchanger also receives condensate from exchangers 17 (which are fed by lines L from turbine 9) through conduit 18. Condensate from exchangers 17 and 15 passes through conduit 19 to condenser 11. But, in the present application, the liquid heated with heater IV (4) via a ventilator by using atmosphere air. Also, the heater IV (4) directly connected with Turbine I (5). So, %100 of flow rate is using in present application. Also, pump I (8) disclosed in present invention located between the Heater I (1) and reservoir (7) wherein pump I (8) is configured to draw liquid nitrogen or liquid air in the reservoir (7) at atmospheric pressure, pump up a pressure of the liquid obtained from the reservoir (7), and spray liquid steam onto the first heater (1).

[0014] However the present steam machines obtained as a result of the developments in the art leads to air pollution as they use fossil fuels. Due to this reason the power generating machine system subject to the invention has been required to be developed.Aim of the Invention

[0015] The aim of this invention is to provide a power generating machine system which eliminates air pollution, where the exhaust discharges only atmospheric air and does not cause any pollution.

[0016] Another aim of the invention is to provide a power generating machine system which saves the world from greenhouse effect, reduces global warming, stops the glaciers from melting and enables to cool the earth and which obtains continuous energy from the atmosphere.

[0017] Another aim of the invention is to provide a power generating machine system which is not harmful to the environment as it uses air instead of fossil fuel.

[0018] Another aim of the invention is to provide a power generating machine system which eliminates the cancerous effects and toxicities caused by CO, CO 2 and NO x , sulphur oxides, lead compounds, petrol and diesel steam, emitted out of the exhausts of petrol, diesel fuel and LPG engines.Detailed Description of the Invention

[0019] The power generating machine system provided to reach the aims of the invention has been illustrated in the attached figures.

[0020] According to these figures; Figure 1: Is the schematic view of the power generating machine system.

[0021] The parts in the figures have each been numbered and their references have been listed below. 1. Heater I 2. Heater II 3. Heater III 4. Heater IV 5. Turbine I 6. Turbine II 7. Reservoir 8. Pump I 9. Pump II 10. Pump III 11. Pump IV 12. Valve 13. Turbine opening I 14. Turbine opening II 15. Turbine opening III 16. Exhaust opening

[0022] The system according to the invention is described in claim 1.

[0023] In the system subject to the invention the superheated steam from the heater IV (4) located inside the heater IV (4) heated by means of air, enters into the turbine I (5). The superheated steam expands and is operated isoentropically in the turbine I (5). The expanded superheated steam in the turbine I (5), is transferred to heater I (1), heater II (2) and heater III (3) respectively by means of the turbine opening I (13), turbine opening II (14) and turbine opening III (15).

[0024] If necessary, isoentropical expansion needs to be supported in the turbine II (6) and turbine I (5) located in the system subject to the invention. Following this steam is re-heated until ambient temperature is reached with the heater IV (4). The heated steam operates isoentropically and is discharged.

[0025] Liquid nitrogen or liquid air in the reservoir (7) at atmospheric pressure is drawn from the reservoir (7) with the aid of a pump I (8). Pump I (8) pumps the liquid obtained from the reservoir (7) up to a pressure of 8.925 bars. Liquid steam obtained from the pump I (8) is sprayed onto the heater I (1). Steam can be condensed up to m 3< / kg depending on the amount of sprayed liquid.

[0026] The steam condensed in the heater I (1) is transferred to the heater II (2) via the pump II (9). The cool liquid pumped from the heater (1) is sprayed to the heater II (2). Due to the sprayed liquid, steam received from the turbine opening II (14) of the turbine I (5) is condensed depending on the amount of steam and the temperature of cool steam. The steam condensed in the heater I (1) is transferred to heater II (2) pressure via the pump II (9).

[0027] The cold liquid pumped from heater I (1) is sprayed to Heater II (2) and the cold liquid pumped from heater II (2) is sprayed to the heater (III). Steam received from the turbine opening I (13) is condensed depending on the amount of steam and the temperature of cool steam. The pump III (10) pumps the liquid obtained from heater II (2) and transfers it to heater III (3). The heater III (3) sprays the liquid received from pump III (10) to heater IV (4) and the liquid obtained from heater (III) is pumped to heater IV (4). The pump III (10) pumps the liquid obtained from heater III (3) to heater IV (4). The heater IV (4), heats the liquid received from pump III (10) via a ventilator by using atmosphere air and the system is completed.

[0028] In order to obtain the real cycle of steam engines, it is necessary to take into account the required difference in order to overcome frictional losses occurring at various points and heat losses and to provide heat transfer in the heaters. This value is accepted as +5K in calculations. It has been accepted that heat flow to the environment from the pump and the turbines is accepted to be zero. Said losses have been accepted to be η it =0.90 ve η ip =0.80 when the pump and turbine indicated yields are taken into consideration.

[0029] According to a different embodiment of the invention, number of heaters can be changed according to turbine numbers and machine size located in the system.Thermodynamic calculations relating to the Invention;

[0030] Thermodynamic features in 1 atmosphere of air: air = -25°C, m=28.9586 g / mol P (MPa)0.09129(MP a )0.101325(MP a )0.10245(MP a )h (j / mol)-3702.1 / 2198.3h s / h b -3,645.9 / 2221.2s (j / mol.K)85.624 / 163.09s s / s b 86.334 / 162.34v (mol / dm 3< )30.357v s 30.200T (K)78T79 0.101325−0.091290.10245−0.09139=hs+3,702.1−3,645.9+3,702.1→hs=−3651.11j / mol = Ss − 85.624 86.334 − 85.624 → s s = 86.268 j / mol . K = Vs − 30.357 30.200 − 30.357 → v s = 30.21455 mol / l = T − 78 79 − 78 → T = 78.91 K = hb − 2198 , 3 2221.2 − 2198.3 → h b = 2 , 219.1 j / mol = Sb − 163.09 162.34 − 163.09 → s b = 162.41 j / mol P1=10,0MPa,h1=217.055kj / kgT1=248K,s1=152.164j / mol.K→ T240248250h5,985.3h 1 6,360.7s150.94s 1 152.47 248−240250−240=h1−5,985.36,360.7−5,985.3→h1=6,285.62j / mol = S 1 − 150 , 94 152.47 − 150 , 94 → s 1 = 152.164 j / mol . K P2=3.72284MPa,h2=158.983kj / kgS2=S1=152.164j / mol.KP=2.0MPa s151.50152.169152.69h3,822.5h 2.0 4004.9 152.164−151.50152.69−151.50=h2.0−3,822.54,004.9−3.822.5→h2.0=3,924.28j / molP=5.0MPa s151.90152.164153.69h5,053.8h 5.0 5.419,6 152.164−151.90153.69−151.90=h5.0−5,053.85,419.6−5,053.8→h5.0=5,107.75j / mol P2.03.722845.0H3,924.28h 2 5,107.75 3.722.84−2.05.0−2.0=h2−3,924.285,107.75−3,924.28→h2=4,603.92j / molP3=2.87207MPa,h3=147.393kj / kgs3=s1=152.164j / mol.KP=2.0MPa s151.50152.164152.69h3,882.5h 2.0 4,004.9 152.164−151.50152.69−151.50=h2.0−3,882.54,004.9−3,882.5→h2.0=3,924.285j / molP=5.0MPa s151.90152.164153.69h5,053.8h 5.0 5,419.6 152.164−151.90153.69−151.90=h5.0−5,053.85,419.6−5,053.8h5.0=5,107.75j / mol → p2.02.872075.0h3,924.28h 3 5,107.75 2.87207−2.05.0−2.0=h3−3,924.285,107.75−3,924.28→h3=4,268.30j / molP4=1.04961MPa,h4=112.559kj / kgs4=s1=152.164j / mol.K s152.13152.164152.70h3,220.6h 1.0 3,292.1 152.164−152.13152.70−152.13=h1.0−3,220.63,292.1−3,220.6→h1.0=3,224.86j / molP=2.0MPa s151.50152.164152.69h3,822.5h 2.0 4,004.9 152.164−151.50152.69−151.50=h2.0−3,822.54,004.9−3,822.5→h2.0=3,924.285j / mol p1.01.049612.0h3,224.86h 4 3,924.28 1,04961−1.02.0−1.0=h4−3,224.863,924.28−3,224.86→h4=3,259.55j / molP5=1,04961MPah5=244.873kj / kgT5=248Ks5=173.689j / mol.K T240248250h6,857.4h 1.0 7,155.5s173.01s 1.0 174.23 248−240250−240=h1.0−6,857.47,155.5−6,857.4→h1.0=7,095.885j / mol = s 1.0 − 173.01 174.23 − 173.01 → s 1 , 0 = 173.99 j / mol . K P=2.0MPa T240248250h6,756.1h 2.0 7,062.2s166.92S2.0168.17 248−240250−240=h2.0−6,756.17,062.2−6,756.1→h2.0=7,000.98j / mol = s 2.0 − 166.92 168.17 − 166.92 → s 2.0 = 167.92 j / mol . K p1.01.049612.0h7,095.88h 5.0 7,000.98s173.99s 5 167.92 1.04961−1.02.0−0.1=h5−7,095.887,000.98−7,095.88→h5=7,091.172j / mol = s 5 − 173.99 167.92 − 173.99 → s 5 = 173.689 j / mol . K P6=1.101325MPah6=125.706kj / kgs6=s5=173.689j / mol.KT6=126.8Ks6=ss=ss+xsb−ss173,689=86.268+x162,41−86,268173,689−86.268=76.142xx=1.148atthesuperheatedvapourregion s173.50173.689173.96h3,616.0h 6 3,675.1T126T6128 173.689−173.50173.96−173.50=h6−3,616.03,6751−3,616.0→h6=3,640.28j / mol = T 6 − 126 128 − 126 → T 6 = 126.8 K P7=0.101325MPav7=30.21455mol / l→v7=0.00114289m3 / kgh7=−3651.11j / mol→h7=−126.080kj / kg−WPa=v7P8−P7→−WPa=0.001142891049.61−101.325=1.084kj / kg−WPa=1.084kj / kg−WPa=h8−h7→1.084=h8+126.080→h8=−124.996kj / kgP9=1.04961MPav9=25.058mol / l→v9=0.00137809m3 / kgh9=−1,967.8j / mol→h9=−67,952kj / kg−WPb=v9P10−P9→−WPb=0.001378092872.07−1,049.6−WPb=2.511kj / kg−WPb=h10−h9→2.511=h10+67.952→h10=−65.411kj / kgP11=2.87207MPav11=19.278mol / l→v11=0.00179127m3 / kgh11=−475.47j / mol→h11=−16.419kj / kg−WPc=v11P12−P11→−WPc=0.001791273722.84−2872.07−WPc=1.524kj / kg−WPc=h12−h11→1.524=h12+16.419→h12=−14.899kj / kgP13=3.72284MPav13=14.198mol / l→v13=0.00243218m3 / kgh13=478.83j / mol→h13=16.535kj / kg−WPd=v13P14−P13→−WPd=0.0024321810,000−3,722.84−WPd=15.267kj / kg−WPd=h14−h13→15.267=h14−16.535→h14=31.802kj / kgCalculations regarding Enthalpy points, pump works and condensed masses;

[0031] h 1 = 217.055 k j / k g h 6 = 125.706 k j / k g h 11 = -16.419 k j / k g h 2 = 158.983 k j / k g h 7 = 126.080 k j / k g h 12 = -14.895 k j / k g h 3 = 147.393 k j / k g h 8 = -124.996 k j / k g h 13 = 16.535 k j / k g h 4 = 112.559 k j / k g h 9 = -67.952 k j / k g h 14 = 31.802k j / k g h 5 = 244.873 k j / k g h 10 = -65.441 k j / k g m1=0.180kg,m2=0.189kg,m3=0.152kg,m=0,520kg−WPa=1.084kj / kg,WPb=2.511kj / kg,-WPc=1.524kj / kg,−WPd=15.267kj / kgm1h2−h13=1−m1h13−h12→m1158.983−16.353=1−m116.553+14.895142.63m1=31.43−31.43m1→142.63m1+31.43m1=31.43m1=0.180kgm2h3−h11=1−m1−m2m2147,393+16.419=1−0.180−m2−16.419+65.441163.812m2=40.198−49.022m2→m2=0.189kgm3h4−h9=1−m1−m2−m3h9−h8m3112.559+67.952=1−0.180−0.189−m3−67.952+124.996180.511m3=35.995−57.044m3180.511m3+57.044m3=35.995→m3=0.151kgm=m1+m2+m3=0.180+0.188+.0151=0.52kgW=Specificjob;WT=h1−h2+1−m1h2−h3+1−m1−m2h3−h4+1−mh5−h6WT=217.055−158.983+1−0.180158.983−147.393+1−0.180−0.189x147.393−112.559+1−0.520244.873−125.706=WT=58.072+9.504+21.980+57.200=146.756WT=146.756kj / kgWnet=WT−1−mWPa−1−m+m3WPb−1−m+m2+m3WPc−WPdWnet=146.756−1−0.5201.084−1−0,520+0.1522.511+1−0.520+0.152+0.189….x1.524−15.267Wnet=146.756−0.520−1.758−1.251−15.267Wnet=128.131kj / kgThermal Efficiency;

[0032] q = h 1 − h 14 + 1 − m h 5 − h 4 q = 217.055 − 31.802 + 1 − 0.520 244.873 − 112.559 q = 185.253 + 63.511 = 248 , 764 k j / k g , q = 248.764 kj / kg η thermal = W net / q = 128.131 / 248.764 = % 51.51 , η thermal = % 51.51Capacity of 1 k g fluid;

[0033] k = W net / 1 − m = 128.131 / 1 − 0.520 = 266.939 kj / kg , k = 266.939 kj / kgCapacity for M= 400 kg reservoir;

[0034] K = k . M 3600 = 266.938 400 / 3600 = 29.660 kWh , K = 29.660 kWhIrreversibility effect and Real Cycle;

[0035] In order to obtain the real cycle of steam engines, it is necessary to take into account the required difference in order to overcome frictional losses occurring at various points and heat losses and to provide heat transfer in the heaters.

[0036] Due to isoentropical compression and expansion division processes that are a crucial part of the compression process and the expansion process in a turbine, differences occur in thermodynamic features. It has been accepted that heat flow to the environment from the pump and the turbine is accepted to be zero. Said losses are as follows when pump and turbine indicated yields are taken into consideration;

[0037] Has been accepted as, η it = 0.90, η ip = 0.80 W it = W T ⋅ η it = 146.756 x 0.90 = 132.080 k j / k g , W it = 132.080 k j / k g − W ip = W p / η ip = W T − W net / η ip = 146 − 756 − 128.131 / 0.8 − W ip = 23.281 k j / k g W net , i = W it − W ip = 132.080 − 23.281 = 108.799 k j / k g W net , i = 108.799 k j / k g η thermal = Wit − Wip h 1 − h 14 + 1 − m h 5 − h 4 → h 14 = h 13 + h 14 − h 13 / η ip = 16.535 + 31.802 − 16.535 / 0.8 → h 14 = 35.619 k j / k g η thermal = 132.080 − 23.281 / 217.055 − 35.619 + 1 − 0.520 244.873 − 112.559 η thermal = % 44.42

[0038] Yield provided by 1kg liquid air: k = W net / 1 − m = 108.799 / 1 − 0.52 k = 226.664 k j / k g

[0039] Capacity of M=400 kg reservoir K = k . M / 3600 = 226.664 400 / 3600 → K = 25.185 kWhThermodynamic calculations relating to the Invention;

[0040] Thermodynamic features of air in the atmosphere: air = +35°C, m=28.9586 g / mol P (MPa)0.09129(MP a )0.101325(MP a )0.10245(MP a )h (j / mol)-3702.1 / 2198.3h s / h b -3,645.9 / 2221.2s (j / mol.K)85.624 / 163.09s s / s b 86.334 / 162.34v (mol / dm 3< )30.357v s 30.200T (K)78T78.91 0.101325−0.091290.10245−0.09139=hs+3,702.1−3,645.9+3,702.1→hs=−3651.11j / mol = Ss − 85.624 86.334 − 85.624 → S s = 86.268 j / mol . K = Vs − 30.357 30.200 − 30.357 → v s = 30.21455 mol / l = T − 78 79 − 78 → T = 78.91 K = hb − 2198 , 3 2221.2 − 2198.3 → h b = 2 , 219.1 j / mol = Sb − 163.09 162.34 − 163.09 → s b = 162.41 j / mol P1=10,0MPa,h1=289.446kj / kgT1=308K,s1=159.752j / mol.K T300308310h8,114.2h 1 8,448.9s158.88s 1 159.97 308−300310−300=h1−8,144.28,448.9−8114.2→h1=8,381.96j / mol = S 1 − 158 , 88 159.97 − 158 , 88 → s 1 = 159.752 j / mol . K P2=3.72284MPa,h2=211.815kj / kgS1=S2=159.752j / mol.KP=2.0MPa s159.58159.752160.42h5,187.6h 2.0 5,348.6 159.752−159.58160.42−159.58=h2.0−5,187.65,348.6−5.187.6→h2.0=5,220.57j / molP=5.0MPa s159.66159.752160.94h6,787.4h 5.0 7.114,6 159.752−159.66160.94−159.66=h5.0−6,787.47,114.6−6,787.4→h5.0=6,810.92j / mol P2.03.722895.0H5,220.57h 2 6,810.92 3.72284−2.05.0−2.0=h2−5,220.576,810.92−5,220.57→h2=6,133.876j / molP3=2,87207MPa,h3=196.241kj / kgs3=s1=159.752j / mol.KP=2MPa s159.58159.752160.42h5,187.6h 2.0 5,348.6 159.752−159.58160.42−159.58=h2.0−5,187.65,348.6−5,187.6h2.0=5,220.57j / molP=5.0MPa s159.66159.752160.94h6,787.4h 5.0 7,114.6 159.752−159.66160.94−159.66=h5.0−6,787.47,114.6−6,787.4→h5.0=6,810.92j / mol p2.02.872075.0h5,220.57h 3 6,810.92 2.87207−2.05.0−2.0=h3−5,220.576,810.92−5,220.57→h3=5,682.87j / molP4=1.04961MPah4=149.421kj / kgs4=s1=159.752j / mol.K s159.62159.752160.63h4,259.6h 1.0 4,418.16 159.752−159.62160.63−159.62=h1.0−4,259.64,418.16−4,259.6→h1.0=4,280.38j / molP=2.0MPa s159.58159.752160.42h5,187.6h 2.0 5,348.6 159.752−159.58160.42−159.58=h2.0−5,187.65,348.6−5,187.6→h2.0=5,220.57j / mol p1.01.049612.0h4,280.38h 4 5,220.57 1,04961−1.02.0−1.0=h4−4,280.385,220.57−4,280.38→h4=4,327.02j / molP5=1,04961MPah5=306.352kj / kgT5=308Ks5=180.121j / mol.K T300308310h8,638.1h 1.0 8,933.6s179.64s 1.0 180.61 308−300310−300=h1.0−8,638.18,933.6−8,638.1→h1.0=8,874.5j / mol = s 1.0 − 179.64 180.61 − 179 , 64 → s 1 , 0 = 180.416 j / mol . K P=2.0MPa T300308310h8,574.3h 2.0 8,874.3s173.68s 2.0 174.67 308−300310−300=h2.0−8,574.38,874.3−8,574.3→h2.0=8,814.3j / mol = s 2.0 − 173.68 174.7 − 173.68 → s 2.0 = 174.472 j / mol . K p1.01.049612.0h8,874.5h 5 8,814.3s180.416s 5 174.472 1.04961−1.02.0−1.0=h5−8,874.58,814.3−8,874.5→h5=8,871.51j / mol = s 5 − 180.416 174.472 − 180.416 → s 5 = 180.121 j / mol . K P6=0.101325MPah6=157.217kj / kgs6=ss=180.120j / mol.KT6=157.88Ks6=s5+xsb−ss180,121=86.268+x162,41−86,268180,121−86.268=76.142xx=1.232atthesuperheatedvapourregion s179.59180.121180.51h4,468.3h 6 4,614.7T155T6160 180.121−179.59180.51−179.59=h6−4,468.34,614.7−4,468.3→h6=4,552.798j / mol ~ = T 6 − 155 160 − 155 → T 6 = 157.88 K P7=0.101325MPav7=30.21455mol / l→v7=0.00114289m3 / kgh7=−3651.11j / mol→h7=−126.080kj / kg−WPa=v7P8−P7→−WPa=0.001142891049.61−101.325=1.084kj / kg−WPa=1.084kj / kg−WPa=h8−h7→1.084=h8+126.080→h8=−124.996kj / kgP9=1.04961MPav9=25.058mol / l→v9=0.00137809m3 / kgh9=−1,967.8j / mol→h9=−67,952kj / kg−WPb=v9P10−P9→−WPb=0.0013780852872.07−1,049.61−WPb=2.511kj / kg−WPb=h10−h9→2.511=h10+67.952→h10=−65.411kj / kgP11=2.87207MPav11=19.278mol / l→v11=0.00179127m3 / kgh11=−475.47j / mol→h11=−16.419kj / kg−WPc=v11P12−P11→−WPc=0.001791273722.84−2872.07−WPc=1.524kj / kg−WPc=h12−h11→1.524=h12+16.419→h12=−14.899kj / kgP13=3.72284MPav13=14.198mol / l→v13=0.00243218m3 / kgh13=478.83j / mol→h13=16.535kj / kg−WPd=v13P14−P13→−WPd=0.0024321810,000−3,722.84−WPd=15.267kj / kg−WPd=h14−h13→15.267=h14−16.535→h14=31.802kj / kgCalculations regarding Enthalpy points, pump works and condensed masses;

[0041] h 1 = 289.446 k j / k g h 6 = 157.217 k j / k g h 11 = -16.419 k j / k g h 2 = 211.815 k j / k g h 7 = -126.080 k j / k g h 12 = -14.895 k j / k g h 3 = 196.24 k j / k g h 8 = -124.996 k j / k g h 13 = 16.535 k j / k g h 4 = 149.421 k j / k g h 9 = -67.952 k j / k g h 14 = 31.802k j / k g h 5 = 306.352 k j / k g h 10 = -65.441 k j / k g m1=0.139kg,m2=0.161kg,m3=0.145kg,m=0,445kg−WPa=1.084kj / kg,−WPb=2.511kj / kg,−WPc=1.524kj / kg,−WPd=15.267kj / kgm1h2−h13=1−m1h13−h12→m1211.815−16.353=1−m116.553+14.895195.28m1=31.43−31.43m1→195.28m1+31.43m1=31.43m1=0.139kgm2h3−h1=1−m1−m2h11−h10m2196,24+16.419=1−0.39−m2−16.419+65.441212.66m2+49.022m2=42.208→m2=0.161kgm3h4−h9=1−m1−m2−m3h9−h8m3149.421+67.952=1−0.139−0.161−m3−67.952+124.996217.373m3=39.931−57.044m3217.373m3+57.044m3=39.931→m3=0.145kgm=m1+m2+m3=0.139+0.161+.0145=0.445kgWT=h1−h2+1−m1h2−h3+1−m1−m2h3−h4+1−mh5−h6WT=289.446−211.815+1−0.139211.815−196.24+1−0.139−0.161…=196.24−149.421+1−0.446306.352−157.217=WT=77.631+13.410+32.773+82.770=206.584WT=206.584kj / kgWnet=WT−1−mWPa−1−m+m3WPb−1−m+m2+m3WPc−WPdWnet=206.584−1−0.4451.084−1−0,445+0.1452.511−1−0.445+0.161+0.145….X=1.524−15.267Wnet=206.584−0.602−1.758−1.312−15.267Wnet=187.645kj / kgThermal Efficiency;

[0042] q = h 1 − h 14 + 1 − m h 5 − h 4 q = 289.446 − 31.802 + 1 − 0.445 306.352 − 149.421 q = 257.644 + 87.097 = 344 , 741 k j / k g , q = 344.741 kj / kg η thermal = W net / q = 187.645 / 344.741 = % 54.43 , η thermal = % 54.43Capacity of 1 k g fluid;

[0043] k = W net / 1 − m = 187.645 / 1 − 0.445 = 338.099 kj / kg , k = 338.099 kj / kgCapacity for M= 400 kg reservoir;

[0044] K = k . M 3600 = 338.099 400 / 3600 = 37.57 kWh , K = 37.57 kWhIrreversibility effect and Real Cycle;

[0045] In order to obtain the real cycle of steam engines, it is necessary to take into account the required difference in order to overcome frictional losses occurring in various amounts and heat losses and to provide heat transfer in the heaters.

[0046] Due to isoentropical compression and expansion division processes that are a crucial part of the compression process and the expansion process in a turbine, differences occur in thermodynamic features. It has been accepted that heat flow to the environment from the pump and the turbines are accepted to be zero. Said losses are as follows when pump and turbine indicated yields are taken into consideration;

[0047] Has been accepted as, η it = 0.90, η ip = 0.80. W it = W T . η it = 206.584.090 = 185.926 k j / k g , W it = 185.926 k j / k g − W ip = W p / η ip = W T − W net / η ip = 206 − 584 − 187.645 / 0.8 − W ip = 23.674 k j / k g W net , i = W it − W ip = 185.926 − 23.674 = 162.252 k j / k g W net , i = 162.252 k j / k g η i , thermal = Wit − Wip h 1 − h 14 + 1 − m h 5 − h 4 → h 14 = h 13 + h 14 − h 13 / η ip = 16.535 + 31.802 − 16.535 / 0.8 → h 14 = 35.619 k j / k g η i , net = 185.926 − 23.674 / 289.446 − 35.619 + 1 − 0.520 306.352 − 149.421 η i , net = % 49.42

[0048] Yield provided by 1kg liquid air: k = W net / 1 − m = 162.252 / 1 − 0.445 k = 292.346 k j / k g Capacity of M=400 kg reservoir

[0049] K = k . M / 3600 = 292.346 400 / 3600 → K = 32.483 kWh

Claims

1. A power generation machine system which uses fluid liquid nitrogen and / or liquid air mixture and atmosphere air as an energy source, comprising, - Heater I (1) located in the system, - Heater II (2) connected to the heater I (1), - Heater III (3) connected to the heater II (2), - Pump II (9) located between the heater I (1) and the heater II (2), - Pump III (10) located between the heater II (2) and the heater III (3), - Pump IV (11) located between the heater III (3) and the heater IV (4), characterized in that it further comprises - Heater IV (4) whose one end is connected to the heater I (1) and the other end to a turbine I (5) wherein the heater IV (4), heats the liquid received from pump III (10) via a ventilator by using atmosphere air, - Turbine I (5) connected to the heater IV (4) wherein the superheated steam expands and is operated isoentropically in turbine I (5), - Turbine II (6) connected to the heater IV (4), - Reservoir (7) connected to the heater I (1), - Pump I (8) located between the heater I (1) and reservoir (7) wherein pump I (8) is configured to draw liquid nitrogen or liquid air in the reservoir (7) at atmospheric pressure, pump up a pressure of the liquid obtained from the reservoir (7), and spray liquid steam onto the first heater (1).

2. A power generating machine system according to claim 1, characterized by comprising a valve (12) located between the heater I (1), and heater II (2), heater II (2) and heater III (3) and heater III (3) and heater IV (4).

3. A power generating machine system according to any of the preceding claims characterized by comprising a turbine opening I (13) which enables connection between the turbine I (5) and the heater I (1).

4. A power generating machine system according to any of the preceding claims characterized by comprising a turbine opening II (14) which enables connection between the turbine I (5) and the heater II (2).

5. A power generating machine system according to any of the preceding claims characterized by comprising a turbine opening III (15) which enables connection between the turbine I (5) and the heater III (3).

6. A power generating machine system according to any of the preceding claims characterized by comprising an exhaust opening (16) located on the turbine II (6).