Patent Application
20220325636
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.
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.
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.
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.
Several developments have been carried out in relation to a power generating machine system.
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.
In the United States patent document numbered U.S. Pat. No. 6,729,136B2 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.
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.
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.
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.
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.
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.
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.
Another aim of the invention is to provide a power generating machine system which eliminates the cancerous effects and toxicities caused by CO, CO2 and NOx, sulphur oxides, lead compounds, petrol and diesel steam, emitted out of the exhausts of petrol, diesel fuel and LPG engines.
The power generating machine system provided to reach the aims of the invention has been illustrated in the attached FIGURES.
According to these figures;
FIGURE is the schematic view of the power generating machine system.
The parts in the figures have each been numbered and their references have been listed below.
A force machine system comprising the parts of;
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 (4) and turbine opening I (15).
If necessary, isoentropical expansion needs to be supported in the turbine I (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.
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 m3/kg depending on the amount of sprayed liquid.
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 I (2) pressure via the pump II (9).
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). 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.
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 ηit=0.90 ve ηip=0.80 when the pump and turbine indicated yields are taken into consideration.
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;
Thermodynamic features in 1 atmosphere of air: air=−25° C., m=28.9586 g/mol
P1=10,0 MPa, h1=217.055kj/kg
T1=248K, s1=152.164j/mol·K→
P2=3.72284MPa, h2=158.983kj/kg
S2=S1=152.164j/mol·K
P3=2.87207 MPa, h3=147.393 kj/kg
s3=s1=152.164 j/mol·K
P4=1.04961 MPa, h4=112.559 kj/kg
s4=s1=152.164 j/mol·K
P5=1,04961 MPa h5=244.873 kj/kg
T5=248 K s5=173.689 j/mol·K
P6=0.101325MPa h5=125.706kj/kg
s6=s5=173.689 j/mol·K T6=126.8 K
S6=ss=ss+x(sb−ss)
173,689=86.268+x(162,41−86,268)
173,689−86.268=76.142x
x=1.148 (at the superheated vapour region)
v7=30.21455 mol/l→v7=0.00114289 m3/kg
h7=−3651.11 j/mol→h7=−126.080 kj/kg
−WPa=v7 (P8−P7)→−WPa=0.00114289 (1049.61−101.325)=1.084 kj/kg
−WPa=1.084 kj/kg
−WPa−h8−h7→1.084=h8+126.080→h8=−124.996 kj/kg
P9=1.04961 MPa v9=25.058 mol/l→v9=0.00137809 m3/kg
h9=−1,967.8 j/mol→h9=−67,952 kj/kg
−WPb=v9(P10−P9)→−WPb=0.00137809(2872.07−1,049.6)
−WPb=2.511 kj/kg
−WPb=h10−h9→2.511=h10+67.952→h10=−65.411 kj/kg
P11=2.87207 MPa v11=19.278 mol/l→v11=0.00179127 m3/kg
h11=−475.47 j/mol→h11=−16.419 kj/kg
−WPc=v11(P12−P11)→−WPc=0.00179127(3722.84−2872.07)
−WPc=1.524 kj/kg
−WPc=h12−h11→1.524=h12+16.419→h12=−14.899 kj/kg
P13=3.72284 MPa v13=14.198 mol/l→v13=0.00243218 m3/kg
h13=478.83 j/mol→h13=16.535 kj/kg
−WPd=v13(P14−P13)→−WPd=0.00243218(10,000−3,722.84)
−WPd=15.267 kj/kg
−WPd=h14−h13→15.267=h14−16.535→h14=31.802 kj/kg
Calculations regarding Enthalpy points, pump works and condensed masses;
h1 = 217.055 kj/kg
h2 = 158.983 kj/kg
h3 = 147.393 kj/kg
h4 = 112.559 kj/kg
h5 = 244.873 kj/kg
h6 = 125.706 kj/kg
h7 = 126.080 kj/kg
h8 = −124.996 kj/kg
h9 = −67.952 kj/kg
m1=0.180 kg, m2=0.189 kg, m3=0.152 kg, m=0.520 kg
−WPa=1.084 kj/kg, WPb=2.511 kj/kg, −WPc=1.524 kj/kg, −WPd=15.267 kj/kg
m1(h2−h13)=(1−m1)(h13−h12)→m1(158.983−16.353)=(1−m1)(16.553+14.895)
142.63m1=31.43−31.43m1→142.63m1+31.43m1=31.43
m1=0.180 kg
m2(h3−h11)=(1−m1−m2)
m2(147,393+16.419)=(1−0.180−m2)(−16.419+65.441)
163.812m2=40.198−49.022m2→m2=0.189kg
m3(h4−h9)=(1−m1−m2−m3)(h9−h8)
m3(112.559+67.952)=(1−0.180−0.189−m3)(−67.952+124.996)
180.511m3=35.995−57.044m3
180.511m3+57.044m4=35.995→m3=0.151kg
m=m1+m2+m3=0.180+0.188+0.0151=0.52kg
W=Specific job;
WT=h1−h2+(1−m1)(h2−h3)+(1−m1−m2)(h3−h4)+(1−m)(h5−h6)
WT=217.055−158.983+(1−0.180)(158.983−147.393)+(1−0.180−0.189) . . . x(147.393−112.559)+(1−0.520)(244.873−125.706)=
WT=146.756kj/kg
Wnet=WT−(1−m)WPa−(1−m+m3)WPb−(1−m+m2+m3)WPc−WPd
Wnet=128.131 kj/kg
q=h1−h14+(1−m)(h5−h4)
q=217.055−31.802+(1−0.520)(244.873−112.559)
q=185.253+63.511=248,764 kj/kg, q=248.764 kj/kg
ηtherma=Wnet/q=128.131/248.764=%51.51,ηthermal=%51.51
Capacity of 1 kg fluid;
k=Wnet/(1−m)=128.131/(1−0.520)=266.939kj/kg, k=266.939kj/kg
Capacity for M=400 kg reservoir;
Irreversibility effect and Real Cycle;
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.
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;
Has been accepted as, ηit=0.90, ηip=0.80
Wit=WT·ηit=146.756×0.90=132.080kj/kg, Wit=132.080kj/kg
−Wip=Wp/ηip=(WT−Wnet)/ηip=(146−756−128.131)/0.8
−Wip=23.281 kj/kg
Wnet,i=Wit−Wip=132.080−23.281=108.799 kj/kg
Wnet,i=108.799 kj/kg
ηthermal=(132.080−23.281)/((217.055−35.619)+(1−0.520)(244.873−112.559))
ηthermal=%44.42
Yield provided by 1 kg liquid air: k=Wnet/1−m=108.799/1−0.52
k=226.664kj/kg
Capacity of M=400 kg reservoir
Thermodynamic calculations relating to the Invention;
Thermodynamic features of air in the atmosphere: air=+35° C., m=28.9586 g/mol
P1=10.0 MPa, h1=289.446 kj/kg
T1=308K, s1=159.752j/mol·K
P2=3.72284MPa, h2=211.815kj/kg
S1=S2=159.752 j/mol·K
P3=2,87207 MPa, h3=196.241 kj/kg
s3=s1=159.752j/mol·K
P4=1.04961 MPa h4=149.421 kj/hg
s4=s1=159.752 j/mol·K
P5=1,04961 MPa h5=306.352 kj/kg
T5=308 K s5=180.121 j/mol·K
P6=0.101325 MPa h6=157.217 kj/kg
s6=s5=180.120 j/mol·K T6=157.88 K
s6=s5+x(sb−ss)
180,121=86.268+x(162,41−86,268)
180,121−86.268=76.142x
x=1.232 (at the superheated vapour region)
v7=30.21455 mol/l→v7=0.00114289 m3/kg
h7=−3651.11 j/mol→h7=−126.080 kj/kg
−WPa=v7(P8−P7)→−WPa=0.00114289 (1049.61−101.325)=1.084 kj/kg
−WPa=1.084 kj/kg
−WPa=h8−h7→1.084=h8+126.080Θh8=−124.996 kj/kg
P9=1.04961 MPa v9=25.058 mol/l→v9=0.00137809 m3/kg
h9=−1,967.8j/mol→h9=−67,952 kj/kg
−WPb=v9(P10−P9)→−WPb=0.001378085 (2872.07−1,049.61)
−WPb=2.511 kj/kg
−WPv=h10−h9→2.511=h10+67.952→h10=−65.411 kj/kg
P11=2.87207 MPa v11=19.278 mol/l→v11=0.00179127 m3/kg
h11=−475.47 j/mol→h11=−16.419 kj/kg
−WPc=v11(P12−P11)→−WPc=0.00179127(3722.84−2872.07)
−WPc=1.524 kj/kg
−WPc=h12−h11→1.524=h12+16.419→h12=−14.899 kj/kg
P13=3.72284 MPa v13=14.198 mol/l→v13=0.00243218 m3/kg
h13=478.83 j/mol→h13=16.535 kj/kg
−WPd=v13(P14−P13)→−WPd=0.00243218(10,000−3,722.84)
−WPd=15.267 kj/kg
−WPd=h14−h13→15.267=h14−16.535→h14=31.802 kj/kg
Calculations regarding Enthalpy points, pump works and condensed masses;
h1 = 289.446 kj/kg
h2 = 211.815 kj/kg
h3 = 196.24 kj/kg
h4 = 149.421 kj/kg
h5 = 306.352 kj/kg
h6 = 157.217 kj/kg
h7 = −126.080 kj/kg
h8 = −124.996 kj/kg
h9 = −67.952 kj/kg
md1=0.139 kg, m2=0.161 kg, m3=0.145 kg, m=0,445 kg
−WPa=1.084 kj/kg, −WPb=2.511 kj/kg, −WPc=1.524 kj/kg, −WPd=15.267 kj/kg
m1(h2−h13)=(1-m1)(h13−h12)→m1(211.815−16.353)=(1−m1)(16.553+14.895)
195.28m1=31.43−31.43m1→195.28m1+31.43m1=31.43
m1=0.139 kg
m2(h3−h1)=(1−m1−m2)(h11−h10)
m2(196,24+16.419)=(1−0.39−m2)(−16.419+65.441)
212.66m2+49.022m2=42.208→m2=0.161 kg
m3(h4−h9)=(1−m1−m2−m3)(h9−h8)
m3(149.421+67.952)=(1−0.139−0.161−m3)(−67.952+124.996)
217.373m3=39.931−57.044m3
217.373m3+57.044m1=39.931→m3=0.145 kg
m=m1+m2+m3=0.139+0.161+0.0145=0.445 kg
WT=h1-h2+(1−m1)(h2−h3)+(1−m1−m2)(h3−h4)+(1−m)(h5−h6)
WT=206.584 kj/kg
Wnet=WT−(1−m)WPa−(1−m+m3)WPb−(1−m+m2+m3)WPc−WPd
Wnet=187.645 kj/kg
q=h1−h14+(1−m)(h5−h4)
q=289.446−31.802+(1−0.445)(306.352−149.421)
q=257.644+87.097=344,741 kj/kg, q=344.741 kj/kg
ηthermal=Wnet/q=187.645/344.741=%54.43,ηthermal=%54.43
Capacity of 1 kg fluid;
k=Wnet/(1−m)=187.645/(1−0.445)=338.099 kj/kg, k=338.099 kj/kg
Capacity for M=400 kg reservoir;
Irreversibility effect and Real Cycle;
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.
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;
Has been accepted as, ηit=0.90, ηip=0.80.
Wit=WT,ηit=206.584.090=185.926 kj/kg, Wnet=185.926 kj/kg
−Wip=Wp/ηip=(WT−Wnet)/ηip=(206−584−187.645)/0.8
−Wip=23.674 kj/kg
Wnet,i=Wit−Wip=185.926−23.674=162.252 kj/kg
Wnet,i=162.252 kj/kg
Yield provided by 1 kg liquid air: k=Wnet/1−m=162.252/1−0.445
k=292.346 kj/kg
Capacity of M=400 kg reservoir
| Number | Date | Country | Kind |
|---|---|---|---|
| 2019/12112 | Aug 2019 | TR | national |
This application is the national phase entry of International Application No. PCT/TR2019/050938, filed on Nov. 11, 2019, which is based upon and claims priority to Turkish Patent Application No. 2019/12112, filed on Aug. 8, 2019, the entire contents of which are incorporated herein by reference.
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/TR2019/050938 | 11/11/2019 | WO |
