Abstract:
This is a system that converts an energy input, preferably a renewable source generated thrust of a shaft, to useable thermal energy for an efficient non-combustion based central heating system with cogeneration capability. System enables the force applied by the shaft to be multiplied through a Pascal hydraulic link between a small piston and the large piston. The large piston compresses the gas. A static oil thermal stabilization volume facilitates thermal equilibrium condition with the working gas, where heat conduction is established between the gas compressed by the large piston and through the medium of static oil volume, and steam is used to heat residential and/or commercial buildings. After a pre-determined time, the thrust of the shaft is reversed ending a cycle. A non-combustion, hydraulic power generated compression based central heating and cogeneration system is presented as what is new in the art.

Description:
BACKGROUND OF THE INVENTION  
       [0001]     1. Field of the Invention  
         [0002]     This present invention relates to central heating systems, and more particularly to a central heating system with cogeneration capability that utilizes an electrical input energy, preferably from a renewable origin, to enable a shaft to make repeatable thrusts by the use of an electromechanical means.  
         [0003]     2. Description of the Related Art  
         [0004]     Central heating systems are in some countries used as the primary heating means for residential and commercial premises. Demand for efficient and lower cost central heating is increasing on a worldwide basis. Internationally, the trend indicates that majority of residential and commercial building heating will shift to cogeneration and central heating means, as it is more efficient. Current central heating systems still use fossil fuels such as oil or natural gas and therefore the cost of energy used is relatively high. Unless there is a technology shift, it is expected that worldwide power related CO2 emission would rise at least by 60% from 1997 by 2020. Therefore, EU commission aims to double the contribution of Cogeneration of Heat and Power (CHP) solutions from 9% to 18% by 2010.  
         [0005]     Since certain distribution standards have become standard in the industry, central heating systems must be compatible to capacities of these standards. Therefore, based on this constraint, increases in efficiency in a standard size central heating system is possible either by increasing the density of energy on a given system and heat transfer area of a central heating unit or by improving the cost efficiency of energy used, that is, to have a lower cost of energy source, or a combination of low cost energy source and technical innovation. The trend has been moving away from fossil fuels towards increasing the efficiencies of renewable energy generation methods.  
         [0006]     The technologies involved in central heating products generally are in one of the following categories: a) Technologies that pertain to a specific energy source, such as a fossil fuel, natural gas and coal, or electric or renewable, b) Technologies that pertain to the design of the heat exchange assembly that serves the efficient transfer heat, c) Technologies that pertain to the control of waste heat and cogeneration and/or turbo-feedback systems.  
         [0007]     Among the most important central heating performance measurements are: a. Thermal load density, that is preferably high, b. The annual load factor, that is preferably high. A high load density is needed in order to cover the capital investment of the transmission and distribution system that constitutes the majority of the capital cost. The yearly load factor is important because the total system is capital intensive. Therefore, central heating systems are more applicable to: 1. Industrial complexes, 2. Densely populated urban areas, 3. High density building clusters with high thermal loads. District-central heating is best suited for areas that have high building and population densities-where the climate is cold. 4. Where insulation maximization can be realized, it is very important to minimize loses as heat is transferred from one point to the other.  
         [0008]     CHP customers usually have the following demands:  
         [0000]     1. Low Capital Cost.  
         [0009]     Power and heat generation is a major need to support some core industrial processes, or capital funds are limited, as it may be the case for small size industries.  
         [0000]     2. Low life Cycle Cost.  
         [0010]     The primary motivator for the investment in CHP solutions is the high efficiency and the associated cost savings in the long term.  
         [0000]     3. High Reliability and Availability.  
         [0011]     Many industrial processes need continuous operation and therefore small scale and easy to maintain gas turbines are demanded.  
         [0000]     4. Short Delivery Time.  
         [0012]     CHP plant systems can be designed for rapid installation that may retrofit to an existing plant.  
         [0000]     5. Customized Solutions.  
         [0013]     The demand for power and heat are usually site specific. Therefore, a plant concept with standard core components that can be adapted to meet the specific needs of the site provides the solutions that are needed by the customers.  
         [0014]     Reliability and low operational cost is the number one priority for users. Therefore, different renewable energy systems and arrangements have been designed to achieve such improvements.  
         [0015]     Prior art central heating systems developed are of two main types: Those that are based on a conventional combustion means with high energy density and related heat transfer mechanisms and those that are based on a renewable energy source with a relatively low energy density. Prior art central heating systems consist of a burning chamber and a heat transfer unit, a working gas, a distribution system. Even the most improved combustion systems cause air pollution. The energy output as a result of burning the natural gas—which has high energy density is also costly, as the source is not a renewable source.  
         [0016]     Although the energy density of the renewable source is not as high as the fossil fuels, an improved technology can compensate for the lower energy density of the renewable source. An improved, non-combustion technology of a specific type is the main concern of this invention.  
         [0017]     Space heating and cooling use 46% of all energy consumed in U.S. residential buildings. Water heating accounts for an additional 14%. This is a very high total of 60% for residential heating and cooling needs only.  
         [0018]     Operational cost is related to three important issues: 1) Energy type; fossil fuel—burner type or renewable type, 2) Heat transfer. Among various causes, the main causes of energy losses are the lack of a proper heat stability reservoir that establishes a long term internal heat stability, a thermally stable volume-for which less energy would be needed to keep it stable at a certain temperature range in the long run, despite the low energy density of a renewable energy source and, 3) Insulation efficiency. A complete and strong insulation reduces energy losses.  
         [0019]     Another problem with the combustion-based systems is the product life of the burner tends to be short. The burning process and vibrations shortens the product life expectancy.  
         [0020]     Former central heating and cogeneration systems do not have a means to generate energy that can multiply the energy input and at the same time can utilize a renewable energy source, that results in a non-combustion and zero emission and an apparatus with a means of very low cost energy generation. A search in this field indicated that there is no prior art directly germane to the present invention.  
       SUMMARY OF THE INVENTION  
       [0021]     From the foregoing, it may be appreciated that a need has arisen for a method and apparatus for a central heating system with cogeneration capability that avoids the constraints of the prior art. This method and apparatus can generate thermal energy without a combustion—burning process for the purposes of cogeneration of electricity and primarily central heating of residential and/or commercial premises with very low energy cost.  
         [0022]     In accordance with the present invention, the above shortcomings of the former art central heating systems, are effectively overcome by a compression—hydraulic power central heating system that can utilize and multiply the energy input, preferably a renewable energy input, in order to use such renewable energy input to move a hydraulic piston. A steel shaft moves the said piston that transmits this mechanical energy to another piston and multiplies the force that is applied initially to compress a gas suddenly with this multiplied force.  
         [0023]     It is the primary objective of the present invention to generate thermal energy on a repeated basis at a very low cost.  
         [0024]     It is an object of the invention to provide a system that can be primarily applied for the central heating purposes, where the size of the plant can be made proportional to the site specific needs to establish the best efficiency, for example to establish a central heating system for a dense area of residential units and/or commercial buildings.  
         [0025]     The system can be established of several units adjacent to each other, or at a certain optimal distance on the central heating area, so that each complements the other for higher capacity applications and optimal efficiency. This configuration of plurality of several units connected to one large central heating and cogeneration system and closed cycle circulation, is not depicted in the drawings. Therefore, the system can be a customized solution with standardized core components, individually adaptable to site specific needs and requirements, very large or small.  
         [0026]     This invention is based on the following principles of physics: 
    1. The non-compressibility of fluids in an enclosed container with an oil, especially the Pascal hydraulic-which is a force multiplier device;     2. Compressibility of gases, especially of a gas of low density and high compressibility, (Initially adiabatic, then isovolumetric basis stable gas volume,) Preferably an industrial gas mixture of which the temperature can be increased to said high temperatures when compressed;     3. Thermal stability reservoir that consists of a static oil volume of hydrocarbon or carbon-tetrachloride type fluid, or molten salt, all of which have a much wider range between their freezing and boiling points than water, hence one of these choices would establish a thermal stability volume. What is meant by thermal stability is that, it would take less energy for example, the kcal of heat, to raise the temperature of a said fluid mentioned above, as compared to the heat to raise the temperature of a water reservoir of same mass.    
 
         [0030]     The heat transfer means is as follows: 
    a. The volume of gas of which the temperature is increased in the compression volume conducts heat directly through conduction with a metal medium, which is the best heat conductor, that is to the concave copper interface that has a high thermal conductivity;     b. The thermal stabilization oil volume that is-a static volume-where the oil is not circulated to any other area, and establishes a stable high heat reservoir without phase change and being a fluid, it also has good thermal stability and conductivity;     c. The spiraling pipes within this oil volume are also made of metal-copper and hence have good thermal conductivity-where heat transfer is again by conductivity from the oil that surrounds these pipes to the circulation steam-working gas and that reaches thermal equilibrium with this oil volume.    
 
         [0034]     It is an object of the present invention to provide a high reliability central heating system that does not depend on fossil fuels, coal or natural gas for the primary heat source and therefore,  
         [0035]     It is an object to provide a system that can eliminate the dependence on fossil fuels and the possibility of becoming non-functional or very inefficient as a result of fossil fuel, coal or natural gas shortages.  
         [0036]     It is an object of the invention to achieve a zero-emission system.  
         [0037]     It is another object of the invention that is easier and less costly to maintain.  
         [0038]     It is an object of the present invention to provide a central heating system with cogeneration capability, that could be an independent auto-production or total energy system type of system for a factory, hospitals, university campuses, military installations or commercial complexes or a group of residential buildings.  
         [0039]     It is another object of the invention that is also related to the above objective, to provide a central heating system with cogeneration capability that can provide customized solutions with standard components that are individually adaptable, to meet the site specific needs and requirements.  
         [0040]     It is an object of the invention to provide a central heating system, in which the means of thermal energy generation of repeated compressions cause the operational temperatures to reach the base load operation conditions, in a relatively short time.  
         [0041]     It is another object of the invention to provide a central heating system with cogeneration capability of which the ability to run on a continuous base load operation condition, is independent of external variables like seasonal changes, day—night cycles, and weather conditions.  
         [0042]     It is another object of the invention to provide a considerable reduction of the cost of energy, that is considered to be desirable and therefore to enable the return on investment to be realized in a shorter period, as compared to any fossil fuel-combustion type systems.  
         [0043]     It is further an object of the invention, in a first embodiment, to provide a central heating system that is optimal in terms of a very low cost operational input energy, that is based on a renewable energy source.  
         [0044]     It is further an object of the present invention, in a second embodiment, to provide primarily a central heating system that includes at least one or several steam turbine cogeneration unit(s) for electric power generation.  
         [0045]     It is further an object of the present invention to provide a central heating system that provides a more stable heat reservoir for the heat equilibrium function, as compared to the less stable, on and off variable heat supply of the combustion based system that does not have a specific heat stability reservoir-mass.  
         [0046]     It is further an object of the invention to provide a wear-resistant central heating system that through the elimination of fossil fuel or natural gas burning, and by the use of a frictionless material makes it possible to have a product with a longer life.  
         [0047]     It is further an object of the present invention to provide a central heating system which is subject of a low cost OEM production and compatible to existing central-district residential and/or commercial heating, with regard to technical methods and labor, and accordingly is then subject of reasonable prices of sale to the consuming entities and public, thereby making the said central heating system economically available to the end users.  
         [0048]     These and other objects of the present invention will be more evident as depicted by the drawings. 
     
    
     DESCRIPTION OF THE DRAWINGS  
       [0049]      FIG. 1 . is a cross sectional depiction of the system, showing the electro mechanic thruster component  9 , the input mechanic power shaft  10 , of which the function is to provide force on a regular basis and thereby to move suddenly the first piston  11 , that moves within cylinder  12  and transmit the force applied to the hydraulic oil  13 . The very low friction internal surface coating  12   a  is of the first cylinder  12  for the frictionless gliding of the first piston  11 . In this drawing the thruster shaft  10  is not moved by the electro-mechanic thruster component  9  yet and therefore hydraulic oil  13  has not transmitted the force applied by the first piston  11 . Large area piston  14  is also at the pre-compression position. On the right side is the representation of buildings  23  with the radiators  22  which provide central heating. The bypass pipes  31   a  and  32   a  and valves  31  and  32  that enable to bypass the steam turbine  21 . The steam turbine  21  is depicted as one unit in the drawings, but there can be more than one unit—but is shown as a single unit in drawings  1 - 3  and  6  for clarity. It is not shown in drawings  4  and  5 .  
         [0050]      FIG. 2 . is a cross sectional view of the system, showing the motion of the shaft  10  and shows how the force applied by the first piston  11  gets multiplied at the larger area compression piston  14 , via the hydraulic oil  13 , (Initial adiabatic heating of compressed gas in volume  16   a .)  
         [0051]      FIG. 3 . is a cross sectional view of the system, showing how the small area piston  11  and therefore large area piston  14  are re-positioned back to the initial position by reversing the thrust motion of the electro-mechanic shaft  9 , and thereby the shaft  10  makes the small area piston to move back to the pre-compression position. The compressed gas volume  16   a , becomes volume  16  again as it is de-compressed due to the direction reversal of the shaft  10 . Note, after decompression is completed, a hot-gas feedback from volume  27  back into volume  16  occurs through the valve  29 . (Shown in  FIG. 6 .)  
         [0052]      FIG. 4 . is an enlarged cross sectional view of the compression side of the system, showing how after the compression compresses volume  16  into volume  16   a , heat conduction starts and heat is conducted into the heat stabilization static oil volume  18 , through the concave copper heat conduction interface  17 . Furthermore, the pipe  19   a  that goes into the steam turbine  21 , in front of it, has two bypass sections  19   b  and  19   c , with two valves  30  and  31  that enable to completely bypass the steam turbine  21 , or enable part of the steam  20   a  to proceed to the central-district heating closed cycle pipe line  19   a , while at the same time part of steam  20   a  generated goes through the steam turbine  21 . Compression piston  14  is non-conductive.  
         [0053]      FIG. 5 . is an enlarged cross sectional view of the system, showing how before the compression piston  14  returns to the pre-compression position and make volume  16   a  to be decompressed back to volume  16 , at the end of the compression duration and before de-compression is initiated, the valve  28  opens and transfers part of the hot compressed gas into volume  27 .  
         [0054]      FIG. 6 . is a cross sectional view, showing how the circulation steam  20   a  moves within the spiral pipes  20 , that reach thermal equilibrium with the static oil volume  18 , as these pass through the static oil volume  18  and then reach the radiators  22  at the centrally heated residential or commercial buildings  23 -radiators  22  and buildings are shown on the right side. Closed cycle insulated pipe  19   a  through the pump  30  and pre-heat conditioner unit  24 , re-entry pipe section  25 , returns into the thermal equilibrium with static oil volume  18 , to attain thermal equilibrium with the static oil volume  18 , again. Also shown is the hot feedback gas entry from volume  27  into the volume  16  just before the next compression starts, through valve  29 . 
     
    
     DESCRIPTION OF THE PREFERRED EMBODIMENTS  
       [0055]     Following first formula explains the initial adiabatic condition, which results from the sudden compression of the large area compression piston  14 , compressing and changing the gas volume to  16   a , to 1/17 of its&#39; initial volume  16 , if pre-compression volume  16 , temperature is 27 C+and pre-compression pressure is 1.0×10 Pa: 
 
 T 2 =T 1( V 1/ V 2)=(300 K)×(17)=1,004 K=675 C   (1) 
 
 (If air with Gamma=1.40 is compressed. Another low density, highly compressible industrial gas maybe used that would be more suitable for this purpose.) 
 
         [0056]     The system consists of; a. at least one source of renewable energy such as wind or solar energy; b. at least one shaft  10  that is electro-mechanically moved periodically to push the hydraulic piston  11 , c. at least one pipe  13   a  that communicates the hydraulic oil  13  to the other piston  14 ; d. at least one other piston  14  that gets moved by the first hydraulic oil  13  and compresses at least one gas volume  16 , f. at least one highly conductive metal interface  17  that directly conducts heat generated by the compression to the stationary oil volume  18 , g. at least one stationary oil volume  18 , h. at least one spiraling pipe volume  20  that runs through said oil volume  18 , where said spiraling pipe volume  20  attains thermal equilibrium with the stationary oil volume  18 . i. at least one strongly insulated steam distribution pipe  19   a  and radiators  22  that are placed within the residential and/or commercial buildings  23 , j. at least one steam turbine  21  of non-condensing-back pressure type that operates basis topping cycle in a cogeneration set up, where the exhaust steam is used for the central heating process, k. at least two bypass pipe paths  31   a  and  32   a  and two valves  31  and  32  in front of the steam turbine  21 , l. at least one pump  30  to pump the steam  20   a  through and back into the thermal equilibrium oil volume  18 , m. at least one pre-heating unit  24  for the returning fluid  20   a  o. at least two layers of strong insulation  18 b on circulation pipe  19   a  as well as on external sides of the heat transfer volumes  16  and  18  and pre-heating unit  24 .  
         [0057]     With reference to  FIG. 1 , the structure with at least two cylinders  12  and  15 , are connected with a hydraulic pipe  13   a . The electro-mechanic thruster  9  that suddenly pushes the shaft  10 , is not activated yet. The function of the electro-mechanic thruster  9  is to provide force on a regular basis and thereby to move suddenly the first piston  11 , that moves within cylinder  12  and transmit the force applied to the hydraulic oil  13 . Hence this shows the condition before compression. The frictionless internal surface coating  12   a  is preferably made of the NFC (Near frictionless carbon coating) material. This new material&#39;s coefficient of friction is less than 0.001 and has very strong wear resistance and durability that reduce material and energy losses. Commercial field tests of this material has been started and Argonne National Laboratory works with Front Edge Technology, Inc. (Baldwin Park, Calif.); and Stirling Motors, Inc. (Ann Arbor, Mich.); and Diesel Technology Company (Wyoming, Mich.) to develop the near-frictionless coating to increase efficiency, extend wear life, and reduce maintenance costs. Surface coating  12   a  of the first cylinder  12  is for the frictionless gliding of the first piston  11 . The upper and lower sides of the piston  11  is separated by a wall  11  a. The hydraulic oil  13  transmits the force applied by the shaft  10  via piston  11  to piston  14  through pipe  13   a , that is to compress the gas volume  16 . Large area piston  14  upper and lower sides are separated by wall  14   a . The frictionless coating within cylinder  15  and for the piston  14  is  15   a . The heat conduction interface is the concave and U shaped copper interface  17 . Valve  28  is for transferring part of the compressed gas at the end of compressed state into loop-back volume  27 . Valve  29  is for providing a feedback gas from volume  27  into the volume  16 , after volume  16   a  decompression is completed. The heat stability static oil volume  18  is for obtaining a temperature stability range in order to facilitate thermal equilibrium condition with the spiral pipes  20  that circulates therein, which in a topping cycle method, provides the steam  20   a  that is first used to generate power through a steam turbine  21  and then heat the residential and/or commercial buildings that circulates through the radiators  22 . A bypass section that has two bypass passage pipes  31  a and  32   a , with two valves  31  and  32  that enable; a) a complete bypass of the steam turbine  21 , or; b) that alternatively enable part of the steam  20   a  to proceed to the central-district heating closed cycle pipe line  19   a , while at the same time, part of steam  20   a  generated goes through the steam turbine  21 , or; c) goes straight through turbine  21  first and then proceeds to the closed cycle pipe line  19   a . Thereby, the balance between the power generation and heat generation is made adjustable to a considerable extent. This would provide the flexibility to increase the power or the heat generation, based on the site-specific demands that may change in time. The working gas  20   a  closed cycle pipe is  19   a , the booster pump  30 , pre-heat conditioner  24  increases the temperature of returning lower temperature working gas  20   a , so that it can reach thermal equilibrium within the spiral pipe section  20  within the static oil volume  18  in short time, the return pipe to volume  18 , is pipe  25 , circulated steam  20   a , steam turbine is  21 , radiators  22 , centrally heated residential and/or commercial buildings  23 .  
         [0058]     With reference to  FIG. 2 , after small area piston  11  is displaced as it is pushed by the thrust of the electro-mechanic thruster  9 , and the steel shaft  10  provides the thrust that moves the small piston  11 , and the hydraulic oil  13  transmits the force applied to the other side of large area compression piston  14 , which multiplies the force applied by a factor of four at the larger area piston  14 . The gas  16   a  with increased temperature-initially an adiabatic process for the gas compressed  16   a , which then becomes isovolumetric; as the volume of the compressed gas  16   a  remains compressed and does not change during the heat conduction period.  
         [0059]     With reference to  FIG. 3  depicted in cross sectional view is how, as the system returns to the pre-compression volume  16  state, and as the shaft  10 , reverses its&#39; direction-this time slowly-in order to repeat the sudden thrust so that the first side piston  11  can be moved again to the apposite direction and thereby becomes ready for the next thrust. Most of the thermal energy from the base load temperature of 600 C that is generated within compressed volume  16   a , is conducted to the heat stabilization oil volume  18 , through the concave copper interface  17 , which has both an enlarged area-due to the concave and overall U shape for heat conduction maximization and a high thermal conductivity of 400 W/m.K in SI units due to the copper metal. The upper piston  14  is non-conductive. Strong double insulation layers  18   a  and  18   b  insulates the static thermal stability oil volume  18 , preferably made of an insulator Styrofoam or better. As decompression occurs, valves  28  and  29  are closed and part of the hot gas from the previous compression is retained within volume  27  and held without pressure change.  
         [0060]     With reference to  FIGS. 2, 3 ,  5 , and  6  the high gas temperature of about 550-600 C would not be reached at the very first compression. However, since the compressions are repeated, the adiabatic temperature increases generated by several compressions could be re-supplied, back into volume  16 , via the loop-back pipe and volume  27 , through valve  28 , out of the loop volume  27 , and through valve  29 , back into volume  16 . After each de-compression of piston  14 , a gas with higher temperature feedback is supplied and the compression following starts with a higher pre-compression gas  16  temperature. After only several compressions, a higher and more stable gas  16   a  temperature range of about 550-600 C can be reached. Thereby the frequency of compressions can be reduced, which would further result in decrease of the wear and tear and the operational input energy needed.  
         [0061]     For the calculation of the pressure, following second formula applies: 
 
 P 2 =P 1( v 1/ v 2)=(1.0×10 Pa)(17)&gt;49 atm   (2) 
 
         [0062]     (if compressed air-gas is used with Gamma=1.40 and the initial temperature is 27 C. with initial pressure of 1.0×10 Pa.)  
         [0063]     The net work done by the circulation fluid (working gas,) can be approximated by the following third formula: (Basis the internal energy U.) 
 
 U 2− U 1=Delta  U=Q−W.  ( Q +Energy added,  W =Work.) 
 
 U 2−1 =U=−W    (3) 
 
         [0064]     (Initially adiabatic, adiabatic compressions are repeatable.)  
         [0065]     With reference to  FIGS. 2, 4 , and  5 , when the working gas  20   a  attains thermal equilibrium and becomes superheated steam  20   a , this working gas  20   a  is distributed through the insulated pipe  19   a . First, in topping cycle with high pressure through steam turbine  21  and then through the pipe  19   a  to radiators  22 , the working gas  20   a  also provides heating of premises. Then working fluid  20   a  returns to oil volume  18  with lower than thermal equilibrium temperature and at a lower pressure after having been circulated through all radiators  22 , and enter first the pre-heating unit  24 , then through the return pipe  25  into the spiral pipe section  20  to reach the thermal equilibrium temperature with static thermal stability oil volume  18 , again.  
         [0066]     The system would be monitored and controlled by a computer. System operation parameters are based on the following volumes and their pressure and temperature control and monitoring: (with the same numbers that are given in the drawings:) 
    Volume  13 : Hydraulic oil for transmitting the force applied. Pressure sensor.     Volume  16 : Pre-compression volume  16  adjacent to the piston  14  upper section. Pressure and temperature sensors.     Volume  16   a : The compressed volume  16   a  that is compressed to 1/17 of its initial volume  16 . Pressure and temperature sensors.     Volume  18 : The static thermal stability oil volume  18 . Pressure and temperature sensors.     Volume  20 : The spiral pipes section  20 , within which the working gas  20   a  circulates, that is within the oil volume  18 . Pressure and temperature sensors.     Volume  20   a ,  21 ,  22 ,  24 ,  30 ,  31   a,    32   a : The Radiators ( 22 ) and pipes ( 19   a ) and working gas circulation volume ( 20   a ,) that runs within  19   a , pre-heating conditioner unit ( 24 ,) and the steam turbine ( 21 ,) the booster pump ( 30 ,) the double bypass pipes ( 31  a and  32   a .) Temperature and pressure sensors for each volume and medium of circulation and circulation section.     Volume  27 : The loop back hot gas  16   a  feedback volume. Pressure and temperature sensors.    
 
         [0074]     System operation conditions are based on two main phases: 
    1. Before base load: This is before reaching the temperature range of 450-500 C within the static thermal stability oil volume  18 .     2. Post base load: After the temperature of the static thermal stability oil volume  18  reaches 450-500 C range is stabilized.    
 
         [0077]     The data coming from these sensors would be monitored continuously by the computer. Before the base load operation condition is reached, the computer would do initialization with the following initialization fourth algorithm, based on the pre-compressed gas  16  and compressed gas  16   a : (Power on-initialization): 
        Do   (4)     If (shaft is not in start up position, position shaft to start up position);     Frequency=Get frequency (Pre-compression Gas temperature)     (Activate thruster shaft) Start (to);     Wait (frequency—(to+t 1 ));     (Reverse thruster shaft) End (t 1 );        
 
         [0084]     While (1) 
        Open valve  28 ;     Wait (Frequency);     Open valve  29 ;     If (Pre-compression Gas temperature&lt;&lt;27 C);     Frequency=A; (High frequency: Every 5 minutes.)     Else if (Gas temperature&lt;&lt;270 C);     Frequency=C; (Middle frequency: Every 10 minutes.)     Else if (Gas temperature&lt;550 C);     Frequency=E; (Base load frequency: Every 15 minutes.)        
 
         [0094]     This initialization and then gradually reaching the desired base load parameter of compressed gas  16   a , provides the temperature range of 550-600 C, and therefore static thermal stability oil volume  18  temperature of 450-500 C would be reached due to specified time interval repeated compressions and heat conduction through copper interface  17 . Assuming about 10% to 12% losses.  
         [0095]     After base load conditions are reached, the computer would start operational and monitoring functions with the fifth algorithm that is based on the static thermal stability oil  18  temperature instead of the pre-compression gas volume  16  and the compressed gas volume  16   a , as follows:  
         [0096]     While not stopped   (1) 
        Temperature=Get Oil Temperature (t 1 );     Frequency=Get frequency (Oil Temperature);     Thrust shaft(t 2 );     Wait (frequency);     Open valve ( 28 );     Close valve ( 28 );     Retract shaft (t 3 );     Open valve ( 29 );     Close valve ( 29 );     Thrust shaft (t 4 );        
 
         [0107]     While do 
        Power Generation=Get Power Output (e);     If (Power Output&gt;Optimal e);     Keep bypass valves ( 30 ) open and bypass valve ( 31 ) closed;     If (Power Output&lt;Optimal e);     Close bypass valves ( 30 ) and ( 31 );     If (Heat Generation&lt;Optimal t);     Open bypass valves ( 30 ) and ( 31 );     Else if (Oil temperature&gt;600 C);     Set frequency=G; (Overheated frequency: Every 40 minutes.)        
 
         [0117]     With reference to  FIG. 4 , it is an enlarged cross sectional view of the compression side of the system, showing how after the piston  14  compression compresses gas volume  16  into volume  16   a , heat conduction starts and heat is conducted into the heat stabilization static oil volume  18 , through the concave, and overall U shaped copper heat conduction interface  17 . The upper side of compression piston  14  is made of a non-conductive material.  
         [0118]     With reference to  FIG. 5 , is an enlarged cross sectional view of the system, showing how before the compression piston  14  returns to the pre-compression position, at the end of the compressed state and after heat conduction duration is completed, the valve  28  opens and transfers part of the hot compressed gas into volume  27 . Thereby, there is a hot feedback gas, of which the pressure remains higher within volume  27  than the pressure of gas volume  16 , for a hot gas feedback through the valve  29  after the decompression is completed. This makes the gas volume  16  to receive a hot gas feedback that makes it to start out with a higher pre-compression temperature for the next compression.  
         [0119]     With reference to  FIG. 6 , in cross sectional view it shows how the circulation steam  20   a  moves within the spiral pipes  20 , that reach thermal equilibrium with the static oil volume  18 , as it passes within spiral pipes  20  through the static oil volume  18  and then first go through the steam turbine  21  and then reach the radiators  22  as working gas  20   a  of the residential and/or commercial buildings  23  and return within a closed cycle insulated pipe  19   a  through the booster pump  30  and pre-heat conditioner unit  24 , so that when it enters the thermal equilibrium environment within static oil thermal stability volume  18 , via return pipe  25 , it reaches the thermal equilibrium condition with the static oil volume  18 , in a shorter time and avoids a heat shock, in order to attain thermal equilibrium with the static oil volume  18 , again quickly. Also shown in  FIG. 6  is the following: As the de-compression move of the large piston  14  is completed, the hot feedback gas entry from volume  27  into the volume  16  occurs through the valve  29 , just before the next compression starts. This is in order to increase the efficiency of next compression. This makes the next compression to be started with a higher temperature pre-compression gas  16 .  
         [0120]     In compliance with the statute, the invention described herein has been described in language more or less specific as to structural features. It should be understood, however, that the invention is not limited to the specific features shown, since the means and construction shown is comprised only of the preferred embodiments for putting the invention into effect. The invention is therefore claimed in any of its forms or modifications within the legitimate and valid scope of the amended claims, appropriately interpreted in accordance with the doctrine of equivalents.  
         [0121]     The device and the method mentioned heretofore have novel features that result in a new device and method for high reliability and efficiency central heating system, which is not anticipated, rendered obvious, suggested, or even implied by any of the prior art central heating systems, either alone or in any combination thereof.