Final Engineering Report

Brief summery-report of the functioning of Mr. Afif Abouraphaels power plant of patent no US 6990809, and an engineering study of his new invention (SELFPROPELLED ENERGY GENERATOR) that includes a power plant of the above mentioned patent, in addition to a modular hydraulic air compressor. CONTENTS 1. Historical development 2 Engineering planning 2.1 Gas system 2.1.1 Compression phase 2.1.2 Heating phase 2.1.3 Expansion phase 2.2 Liquid system 2.2.1 Water‟s down flowing through a fall pipe 2.2.2 Water pumping by main water-circulating pump 2.2.3 Providing heat to the expanding compressed air of the ascending containers 2.3 Mechanical system 2.3.1 Water pumps 2.3.2 Bucket turbine 2.3.3 Power generator 3 Ragged Chutes Hydraulic Air Compressor supplying compressed air to said power plant 4 Conclusion 5 Literature

1. Historical development Mr. Arthur G. Platt [1] registered patent no US 2135110 that comprises a renewable energy power generating apparatus including a water-filled pool, an endless chain looping around lower and upper cogwheels, containers attached to chain links where only ascending containers receive compressed air in bottom of pool during the functioning of said apparatus (fig. 1). Said ascending containers are propelled by a growing buoyant force during their ascent. According to Boyle'‟s Law, the volume of compressed air injected into each ascending container expands and displaces an increasing quantity of water at shallower depths due to lower hydrostatic pressure. The weight of the water displaced by air in ascending containers creates a steady torque on the axle of the upper cogwheel. The resultant rotation is transformed into an abundant source of energy adaptable to a wide range of applications.

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The needed compressed air for the functioning of Mr. Platt‟s apparatus was to be supplied if needed by all kind of conventional compressors or by Taylor‟s type hydraulic air compressors [2], as the one that was built in Cobalt-Ontario in 1910 [3] and [4] and that supplied the mines of the Cobalt area with their needed compressed air until 1981. Said Taylor‟s type hydraulic air compressor is an effective air compressing apparatus where a huge quantity of air is compressed by flowing water of waterways at a condition to have a difference in height in the waterway‟s bed in order to be able to build effectively a water down-take pipe that communicates with a first end of an underground tunnel which communicates at its second end with a water up-take tail pipe that discharges water back into Fig. 1 Cross-sectional view of Platt‟s power the bed of said waterway. apparatus. The basic principle that is employed in Taylor‟s type hydraulic air compressors is essentially the same as for all hydraulic air compressors. This basic principal consists of a stream of water to be allowed to fall in a vertical down-take pipe where air bubbles are entrained by falling water on beginning of its down motion through a mixing head in order to form an airwater mix. The entrained air is then compressed by the weight of the down flowing water. Then, when the direction of flow changes suddenly to the horizontal and the velocity of said flow is lessen, the air bubbles will be liberated then, and may be collected in a suitable container or separating chamber from which compressed air will be carried out by a suitable piping system (Fig. 2).

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Fig. 2 Cross-sectional view of Ragged Chutes’ hydraulic air compressor By Taylor. Mr. Afif Abou-Raphael [5] has invented an effective air injection system for ascending containers of the apparatus that was invented in 1937 by Mr. Platt. This injection system of patent no CA 2328580 or US 6990890 helps transferring effectively compressed air coming from a compressor to the ascending containers of Mr. Platt‟s apparatus without any lost of air bubbles, that means without energy lost at the lower cogwheel‟s level in bottom of said power plant‟s pool, while Mr. Platt had compressed air bubbles supplied ineffectively to ascending containers. 2 Engineering planning

The needed engineering study of this invention according to its extraordinary potential is the calculation of the total useful energy of the self-propelled energy generator that equals the total addition of all lost and net energy of the system including the modular hydraulic air compressor according to the equation (2.1): Etotal net energy  ( E Pumps  Edrag  Eheat  Emechanic )  Euseful

(2.1)

And because of the multitude of mediums of said self-propelled energy generator, the present engineering study is divided into three chapters.  Chapter 1 that includes the study of air cycle of the gas system.  Chapter 2 that includes the study of water cycle of the liquid system.  Chapter 3 that includes the study of the mechanical system that includes all pumps (Main water transferring pumps) and (secondary water transferring pumps that are needed for 3

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water-flow„s to fulfil the continuity equation), a bucket turbine and an electrical generator as it is shown in fig.3.

Gas system Air cycle

Mechanical system

Pump

Bucket turbine

Generator

Water cycle Liquid system

Fig. 3 Schematic view, showing all of gas, liquid and mechanical systems of the apparatus. It is of course understood that a forth chapter that includes the study of the energy output of said power plant of invention [5], is needed alongside the study of chapters 1, 2 and 3. 2.1 Gas system Air is the only gas element in the system of said self-propelled energy generator the subject of the present invention, where the cycle from the time atmospheric air enters the system letting us to take advantage of its physical properties, until it exits said system heated at atmospheric pressure too, is an open cycle. The following are phases to be followed in order to have a detailed study of the abovementioned air-open cycle that permits us to calculate the system‟s lost and positive energy 2.1.1 Compression phase

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We take a pre-determined quantity of atmospheric air with volume V0 , pressure p 0 and air temperature t 0 . First of all, an airflow discharge pressure of said modular hydraulic air compressor of the actual self-propelled energy generator has to be pre-determined. Study of these variations of air-physical properties to the volume V1 , pressure p1 , and the temperature t1 , From the time the predetermined atmospheric airflow enters the air-water mixing head entrained by falling water into the head-pipe, until said air-water mix reaches the lower air-water separating device.

Fig. 4 Schematic simplified cross-sectional view of a self-propelled energy generator. Variations of an adiabatic study of all air-physical properties according to equations (2.2) and (2.3), see literature [6], [8], [9] and [10] p V1  V0  0 (2.2) p1

p  t1  t 0   1   p0 

 1 

(2.3)

Real study of said physical properties, where the reality of this process is that air bubbles of the falling air-water mix from the mixing head until the lower air-water separating device, are steadily compressed by the weight of the column of water that exists between the pool‟s water surface and the depth where said bubbles are located. The consequences of that compression, is a huge elevation of the air bubbles‟ temperature, where a big quantity of heat will be lost to the surrounding water that lowers the air temperature according to (2.4). 5

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T1 t1' t1

(2.4)

In the lower air-water separating device the real air temperature will be t1' and the real water temperature will be T1 . 2.1.2 Heating phase Heating is the phase where we return to the compressed air a part of the lost heat that was due to the direct contact of air with water. This phase is the heat exchange that permits to elevate air temperature to t1 , where t1 should not exceed 90 degrees in order to keep the surrounding water‟s temperature below 100 Celsius that avoids water ebullition and evaporation according to (2.5)

t1  t1  90

(2.5)

Thus, in order to complete this phase without losing a big amount of energy, the heat exchanger could be supplied with a part of the lost heat that is generated through the functioning of the water-transferring pumps and the main electrical generator. The quantity of heat that can be useful in this phase can be calculated as follow:

Q1  m  cv  (t1  t1 )

(2.6)

Where: Q1 Heat quantity m Quantity of air passing in the heat exchanger c v Specific heat at constant volume. This heating phase is beneficial to air cycle in two points: 

The elevation of air temperature that lowers the energy lost of the system and,



the elevation of compressed air pressure p1 in the heat exchanger where this beneficial elevation of air pressure at this level of the air cycle could be done without the need of any additional air compressor.

2.1.3 Expansion phase The expansion phase starts from the injection of a pre-determined quantity of hot air into ascending containers. But, the physical properties of this quantity of compressed air present inside said ascending containers change during the air ascent toward the pool‟s water surface, where the hydrostatic pressure that exerts on this air is lighter according to the depth of every

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container. Thus, the consequences of this low pressure, is volume expansion and colder temperature of this quantity of air. Thus, the equation (2.7) is used to calculate the changes of air temperature without heat exchange.

p  t 2  t1   0   p1 

 1 

(2.7)

Where: t 2 Air temperature at the end of air-expansion phase without heat exchange t1 Temperature of compressed air exiting the heat exchanger p1 Pressure of compressed air exiting the heat exchanger  Isentropic constant. Thus, because t2 is a very low temperature, the water that surrounds the expanding imprisoned air becomes ice. But, in order to avoid ice formation in the water cycle, we try to distribute hot water that exits the main water-transferring pump all along the ascending route of the ascending containers, from bottom of pool until the dumping of air at the surface of water of said pool. This hot water distribution permits us to use the heat that was gained by water in the first phase, while, the calculation of the quantity of that heat can be calculated as follow:

Q2  k  A  t

(2.8)

Where:

Q2 Heat quantity k Heat transfer coefficient A Transfer surface area t Difference of temperature between air temperature inside ascending container and water temperature that surrounds the container. Because this part of the air cycle is a function of the ascending linear speed of the containers, thus, the useful heat-gain in this part of this cycle can be calculated as follow: W '

Q2  h2 v

(2.9)

Where: W ' Heat gain Q2 Quantity of heat h2 (Height of the column of water) or Depth from pool‟s water surface until bottom of pool where compressed air is injected v Ascending container‟s linear speed

That means the ascending containers‟ linear speed has to provide a heat balance in this part of this cycle. Thus, the control of the containers‟ ascending linear speed can be done through the injected quantity of compressed air that can be calculated according to 7

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W

m R  t  1

(2.10)

Where: W quantity of heat needed for air in order to keep the cycle‟s balance m Quantity of air R Gas constant  Isentropic constant t  t1  t 2 t1 Temperature of compressed air exiting the heat exchanger t 2 Temperature of air exiting the air cycle Thus, in order to provide a good functioning between air cycle and liquid- water cycle, without having ice accumulation, and to reduce the heat lost, it is always very important to calculate iteratively the rotation speed of the mechanical system of the bucket turbine according to equations (2.8), (2.9) and (2.10), because this part of this cycle is the one that can allow a bigger energy production. But, because water is the element that is used in the liquid cycle, and water has a liquid specific character between 0 and 100 Celsius (0
2.2 Liquid system Water is the liquid element in this part of the apparatus, and Figure 4 shows the water cycle that is a closed cycle. For a good understanding of said liquid system, we are going to divide the water cycle to 3 phases as in the study of air cycle. 2.2.1 Water’s down flowing through a fall pipe This phase starts at an air-water mixing head placed in the upper water reservoir of said apparatus, where air bubbles are mixed with falling water that rushes downwardly through said fall pipe toward the lower air-water separating device. In this phase, the continuity equation has always to be respected as long said apparatus is in operation.

dm 0 dt

(2.11) 8

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Where: m Flow mass t Time  0 air water of Thus, In order to study the equation (2.11), we take a pre-determined Flow mass m

an air-water mix at a temperature T0 , a pressure p 0 and a speed v 0 This pre-determined mass has to fulfil the continuity equation too at the exit of the fall pipe in said lower separating  1air water , temperature T1 , pressure device with different physical properties, Flow mass m p1 ,and speed v1  0( air water)  m  1( air water) m

(2.12)

 0 water  (1  k 0 )  m  0air  k1  m  1water  (1  k1 )  m  1air k0  m

(2.13)

Where:

k 0 and k1 are ratios of air-water mixes at the upper water reservoir and at the lower separating device.

k0   0water  (1  k0 )   0air  A0  v0  k1  1water  (1  k1 )  1air  A1  v1

(2.14)

Considering that the diameter D of the fall pipe does not change from top to bottom. Then A0  A1 And as water is an incompressible liquid  0 water  1water , then we simplify (2.14)

  0 air  1air  v k0  (1  k0 )    v0  k1  (1  k1 )  0 water  0 water  1  

(2.15)

Where the values of  0 air and 1air are very small comparing with 0 water . Then after simplification, equation (2.15) becomes (2.16).

k 0  v0  k1  v1

(2.16a)

Or

v1 

k0  v0 k1

(2.16b)

Thus, the calculation process of water temperature‟s change is very easy, because the quantity of heat gained by water is the same quantity of heat that is lost by air during its compression cycle. Lost heat by air:

Qair  mair  cv  t  mair  cv  (t1  t 0 )

(2.17) 9

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Gained heat by water:

Qwater  mwater  c F  T  mwater  c F  (T1  T0 )

(2.18)

Because (2.17) and (2.18) are equals, then:

T1  T0 

cv mair   (t1  t 0 ) c F mwater

(2.19)

Where cv and cF are the specific heat constants for air and water

 j  At 20 Celsius, c F  4190  .  kg.K  Where:

T0 Water‟s temperature at the top of the fall pipe t1 Can be calculated from equation (2.3) mair and mwater are the weight of the pre-determined quantity of air and water that exit from the fall pipe to the lower separating device. 2.2.2 Water pumping by main water-circulating pump This phase begins at the lower air-water separating device and ends at the exits of the hot water distributing pipes that are affixed face to the ascending containers and used to spry hot water around said ascending containers. Thus, it is mandatory that the equation of water continuity has to be respected at this point of this phase. And because air is separated from the air-water mix in the lower separating device, and in order to respect the continuity equation, it is imperative to provide an equal quantity of water by a secondary water-circulating pump that is controlled by a level sensor in order to control the acceptable lower level of water in said lower separating device, during the functioning of the apparatus.

A1  v1  A2  v2  A1  v1

(2.20)

Where:

A1 and v1 are the section‟s surface area of pipe and speed of water by the secondary watercirculating pump In this phase, main and secondary pumps do not affect the water‟s physical properties at all; their only work is to provide a continuous water-circulation between their intake and their outlet respectively that means they do not need to provide water pumping to a certain head.

2.2.3 Providing heat to the expanding compressed air of the ascending containers 10

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In this phase, heat has to be provided to the expanding air inside said ascending containers in order to close up the isothermal compressing cycle of air without letting ice formation inside said ascending containers. Thus, the lost heat during phase 1 of the air compression process (phase 1 in air cycle), and that is recuperated by water contained inside the lower separating device, will be given back to the expanding air by circulating this hot water around said ascending containers through the above mentioned pipes that are affixed face to these ascending containers. After circulating around said ascending containers and giving heat to the expanding air, this water floats to the pool‟s surface in order to start a new cycle.

2.3 Mechanical system The Mechanical system of this apparatus has three independent parts: 2.3.1 Water pumps These pumps are divided into two groups: A-

Main pumps: The main function of a main pump is to provide a continuous water circulation in said closed liquid system of said apparatus as shown in figure 4. This type of circulation-pump does not require a lot of energy because of its simple function where water-circulation is done without any head.

B-

Secondary pumps: The main function of a secondary pump is to transfer water from the main pool into said lower separating device during the functioning of the apparatus, in order to respect the continuity equation for the above referred main pumps as shown in figure 4. The functioning of these secondary pumps is intermittent, because water is needed into said lower separating device only when water reaches the lower acceptable level. In addition, these secondary pumps can be replaced if needed, by valves that can provide equally, the needed water for the good functioning of said main pumps. Moreover the control of these secondary pumps or said valves can be done through (min-max level sensors).

Of course, the needed energy for the good functioning of all main and secondary pumps is a function of the needed airflow. This energy is a lost one, and according to the engineering studies of many different examples of this apparatus, the value of this energy was between 15% and 22% of the total energy output of said power plant of any studied self-propelled energy generator.

2.3.2 Bucket turbine This bucket turbine is an endless chain of buckets moving around upper and lower cogwheels as shown in figure 3 and 4. In addition said bucket turbine is always built solid, in a way that supports the result drive force developed by the buoyant force of the total volume of 11

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imprisoned compressed air into ascending containers. This buoyant force can be calculated according to the following equation

n

Fres  Vi   water  g i 1

(2.21)

Where: n Number of ascending containers between upper and lower cogwheels. Vi Compressed air volume in container i  water Water density g Gravity Thus, before calculating the final energy of the above mentioned force, we should calculate the drag that affects directly this part of the mechanical system according to the following equation:

Fw   

 water 2

 v2  A

(2.22)

Where:

 Drag resistance  water Water density A Area of container v Linear speed of containers

And in order to facilitate the calculation of this drag, we consider the up or down moving containers as a pipe having one diameter D. The drag resistance of the up and down moving containers is calculated according to [10] and [12]

1   

h D

(2.23)

Where:

 , is the pipes‟ Coefficient of resistance that can be calculated according to Nikuradse [12].   k    1,14  2. lg   D  

2

(2.24)

Where: k is the roughness of tube‟s surface. In our case k = 0.2-0.5 [mm] 12

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For the five containers that drag in bottom of pool, the value of drag according to [10] is:  2  1  1,05 Thus, the total value of drag can be calculated as follow:

  2. 1  5. 2

(2.25)

The resulting useful force of any power plant, can be calculated as follow: Fuseful  Fres  Fdrag

(2.26)

Then, from this useful force, it is possible to calculate the resulting energy of said power plant without taking in consideration all of the lost energy of the pumps, of all mechanical friction of the system, and of the air heating, according to the following equation: Eres  Fuseful  L  2    

(2.27)

Where: L Driving radius that is equal to the sum of: driving wheel‟s radius, thickness of endless chain and container‟s radius.  Rotating speed 2.3.3 Power generator This power generator is an electrical generator that produces the calculated useful energy that goes through distributing lines and the lost energy used by said main and secondary water pumps, after deducting all of the added lost energy in drag, in mechanical friction and in air heating. This means, the result of equation (2.1) of this study is equal to the value of the final positive energy of this generator. The above mentioned mechanical system is the most important part of this self-propelled energy generator. Thus, the lost mechanical energy is the biggest among all of the lost energy of this apparatus. And because this machine is the first machine in its kind, then, it is difficult to say how much the exact value of this mechanical energy lost is. But, in sum it is friction caused by the rotation of the wheels‟ shafts in their bearings, by direct contact between cogwheels and endless chain, and by the power transmission systems. In the present time with the precision of the mechanical construction, we can give a primary value for this mechanical energy lost in the order of about 15% from the total produced energy. The following chart gives percentage of calculated and approximate values for energy lost of the apparatus.

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Eres

100 %

E drag

(2-4) %

E pump

(16-23) %

E heat

(6-23) %

Emechanical

(15) %

Euseful

(35-61) %

3 Ragged Chutes Hydraulic Air Compressor supplying compressed air to said power plant

During the study of this power plant I made sure to study it with compressed air being supplied by the ragged chutes that is located in one of the coldest area of the planet. Surely, the result came very positive and encouraging. While, if the same power plant would be located in a hot area and a similar hydraulic air compressor located in the same hot area supplies the compressed air, thus, the energy output of the power plant would be much higher. STUDY OF THE USEFULL POWER OF A POWER PLANT THAT WORKS WITH COMPRESSED AIR PRODUCED BY THE RAGGED CHUTES FOR ONE STAGE Distance from surface of water to the opening of m 85,00 bottom vertical container Rotation speed of driving wheel per minute rpm 10 Linear speed of chain m 0,76 Length of container m 0,75 Radius of container m 0,46 Radius of driving wheel. m 0,91 Atmospheric pressure bar 1,0133 Temperature of injected heated air into ascending °C 90 containers Temperature of water that surrounds the ascending °C 20 container Driving radius, or distance between the center of the m 1,37 driving shaft and the center of gravity of the container Free airflow per minute m³/min 37,755 Hydrostatic pressure at opening of bottom vertical bar 8,50 container Volume of expanded air in all ascending containers m³ 14,63 Output energy without any lost MW 0,205 Lost energy by DRAG [3,76]% MW 0,0077 Lost energy by mechanical friction 15% MW 0,0307 Lost energy by Heating [23]% MW 0,0476 Ragged Chutes doesn‟t need pumps because of the MW 0 14

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Montreal River Useful output energy from 37,755 m³ of air

MW

0,119

according to the following calculations, and, if full airflow of the ragged chutes would be used in an appropriate power plant having the needed number of stages that can contain this airflow, thus, the results would be as follow:  Number of stages needed to contain the full airflow of 1132.66m³: 1132.66m³/ 37,755m³ (One stage) = 30 stages.  Full potential-energy production out of full airflow of 1132.66m³: 0,119MW x 30 = 3,56MW. The ragged chutes compressor was using a water flow of 22.7 m³/sec in order to produce the 40000 cfm or 1132.66 m³ of free airflow, while the average full water flow of the Montreal River is about 67.5 m³/sec. Then, if this full water flow were to be used in a bigger hydraulic compressor, the following airflow would be produced: (67.5m³ / 22.7m3) x 1132.66m³ = 3368.0185m³ Thus, the full potential energy of this airflow would be: (3368.0185m³ / 1132.66m³) x 3,56MW  10.5 MW. It should be understood of course that the ragged chutes does not need neither main nor secondary water transferring pumps, that makes energy production according to this technology much higher then energy being produced through the new invention. But, because waterways do not exist wherever we need them to be, then, the use of the new technology of said (Self-propelled energy generator) would be highly recommended in replacing conventional power generation. In addition, said power plant can be built in shallower pools if needed where more stages can be used in order to produce enough energy without having the risk to having ice accumulation in the buckets. 4 Conclusion

In the beginning when I was approached by the inventor to do an engineering study for his invention, I thought that he was loosing his time, because a lot of people before him have studied the issue without getting any positive result, and that it is unlikely to produce energy from nothing, and that perpetual motion machine does not exists. But, because of my technical curiosity I decided to see from where this positive energy is coming. Thus, I decided to search deeper, and then I started reading the documents including the patents‟ texts; searching for mistakes the inventor has committed, while being sure to find them.

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When I didn‟t find any mistake whatsoever, I got attached to the issue and I started revising very carefully the calculations that were done by the inventor. Happily and surprisingly, I came up with a positive result. And the following are my findings: This invention is a unique Self- propelled energy generator that includes a unique submerged air “Bucket Turbine”, powered By the volume (not the pressure) of compressed air produced by unique modular hydraulic air compressors. The subject of this invention: 1-

Is self-propelled and it eliminates all of the disadvantages of conventional power generators (wind intensity, solar-beam, etc.) while ensuring ease of operation and an ecological process that uses non-polluting, renewable and clean energy. In addition this apparatus needs only atmospheric air and a recycled limited quantity of water.

2-

Has the capacity to be located anywhere in the world including cities, remote areas, mountains or deserts, and to produce any amount of cheap energy according to the needed design without any limitation whatsoever. Moreover, this extraordinary machine that is self-propelled can produce clean and renewable energy even in the coldest regions of the globe.

3-

Includes a power generating plant of the type described in the Canadian patent no CA 2328580 or in US patent no US 6990809 that uses the compressed air volume as fuel instead of air pressure, and a modular hydraulic air compressor that produces artificially the needed airflow for the good functioning of said power plant by circulating same water in a closed and looping path in order to entrain and compress air according to the same basic principle of all hydraulic air compressors, including Taylor‟s type hydraulic air compressors that were the biggest in the world in their kind. But said basic principle is used in this modular hydraulic air compressor in a better, easy and efficient way, where air is compressed and expanded in an isothermal process.

Thus, this self-propelled energy generator can produce for the first time in history a huge amount of positive energy, of course, without forgetting that this clean and renewable energy generation can be without limitations and without the use of any conventional outside source of energy. In addition, this apparatus needs only maintenance after it is started, and, the use of this technology could reduce drastically pollution and greenhouse gases.

5 Literature

[1]

[1] Arthur G. Platt: Power apparatus. /1938/ Patent no US2135110 Charles Havelock Taylor: Hydraulic Air-Compressor. /1908/ Patent no US892772 [3] Arthur A. Cole: Mining and power development. /1910/ Toronto [4] Allan Auclair: Ragged chutes. /1957/ Canadian mining journal. 16

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[5] Afif Abouraphael: Hydroelectric power plant designed to transform the potential energy of compressed gas into mechanical and electrical energy through the potential energy of liquid. 2003 patent no CA2328580 or 2006 patent no US6990809 [6] William L. Haberman and James E.A. John: Engineering Thermodynamics with Heat Transfer. 1989 [7] Joseph H. Spurk: Einfürung in die Theorie der Strömungen. Springer 1996 [8] Reiner Decher: Energy conversion systems, Flow Physics and Engineering. /1994/ Oxford University Press [9] Hans Dieter Baehr: Thermodynamik. Springer /1988/ [10] H. E. Siekmann: Strömungslehre. Springer 2000 [11] M. Halük Aksel, O. Cahit Eralp: Gas Dynamics. /1994/ Prentice Hall [12] E. Truckenbrodt: Fluidmechanik Band I and II. /1989/ Springer

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