Hydraulic-compression power central heating system and method

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

1. Field of the Invention

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.

2. Description of the Related Art

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.

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.

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.

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.

CHP customers usually have the following demands:

1. Low Capital Cost.

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.

2. Low life Cycle Cost.

The primary motivator for the investment in CHP solutions is the high efficiency and the associated cost savings in the long term.

3. High Reliability and Availability.

Many industrial processes need continuous operation and therefore small scale and easy to maintain gas turbines are demanded.

4. Short Delivery Time.

CHP plant systems can be designed for rapid installation that may retrofit to an existing plant.

5. Customized Solutions.

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.

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.

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.

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.

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.

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.

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.

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

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.

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.

It is the primary objective of the present invention to generate thermal energy on a repeated basis at a very low cost.

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.

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.

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.

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.

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,

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.

It is an object of the invention to achieve a zero-emission system.

It is another object of the invention that is easier and less costly to maintain.

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.

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.

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.

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.

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.

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.

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.

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.

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.

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.

These and other objects of the present invention will be more evident as depicted by the drawings.

DESCRIPTION OF THE DRAWINGS

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 12a 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 31a and 32a 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.

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 16a.)

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 16a, 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.)

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 16a, 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 19a that goes into the steam turbine 21, in front of it, has two bypass sections 19b and 19c, with two valves 30 and 31 that enable to completely bypass the steam turbine 21, or enable part of the steam 20a to proceed to the central-district heating closed cycle pipe line 19a, while at the same time part of steam 20a generated goes through the steam turbine 21. Compression piston 14 is non-conductive.

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 16a 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.

FIG. 6. is a cross sectional view, showing how the circulation steam 20a 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 19a 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

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 16a, to 1/17 of its' initial volume 16, if pre-compression volume 16, temperature is 27 C+and pre-compression pressure is 1.0×10 Pa:
T2=T1(V1/V2)=(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.)

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 13a 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 19a 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 31a and 32a and two valves 31 and 32 in front of the steam turbine 21, l. at least one pump 30 to pump the steam 20a through and back into the thermal equilibrium oil volume 18, m. at least one pre-heating unit 24 for the returning fluid 20a o. at least two layers of strong insulation 18b on circulation pipe 19a as well as on external sides of the heat transfer volumes 16 and 18 and pre-heating unit 24.

With reference to FIG. 1, the structure with at least two cylinders 12 and 15, are connected with a hydraulic pipe 13a. 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 12a is preferably made of the NFC (Near frictionless carbon coating) material. This new material'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 12a 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 13a, that is to compress the gas volume 16. Large area piston 14 upper and lower sides are separated by wall 14a. The frictionless coating within cylinder 15 and for the piston 14 is 15a. 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 16a 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 20a 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 32a, 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 20a to proceed to the central-district heating closed cycle pipe line 19a, while at the same time, part of steam 20a generated goes through the steam turbine 21, or; c) goes straight through turbine 21 first and then proceeds to the closed cycle pipe line 19a. 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 20a closed cycle pipe is 19a, the booster pump 30, pre-heat conditioner 24 increases the temperature of returning lower temperature working gas 20a, 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 20a, steam turbine is 21, radiators 22, centrally heated residential and/or commercial buildings 23.

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 16a with increased temperature-initially an adiabatic process for the gas compressed 16a, which then becomes isovolumetric; as the volume of the compressed gas 16a remains compressed and does not change during the heat conduction period.

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' 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 16a, 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 18a and 18b 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.

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 16a 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.

For the calculation of the pressure, following second formula applies:
P2=P1(v1/v2)=(1.0×10 Pa)(17)>49 atm   (2)

(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.)

The net work done by the circulation fluid (working gas,) can be approximated by the following third formula: (Basis the internal energy U.)
U2−U1=Delta U=Q−W. (Q+Energy added, W=Work.)
U2−1=U=−W   (3)

(Initially adiabatic, adiabatic compressions are repeatable.)

With reference to FIGS. 2, 4, and 5, when the working gas 20a attains thermal equilibrium and becomes superheated steam 20a, this working gas 20a is distributed through the insulated pipe 19a. First, in topping cycle with high pressure through steam turbine 21 and then through the pipe 19a to radiators 22, the working gas 20a also provides heating of premises. Then working fluid 20a 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.

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 16a: The compressed volume 16a 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 20a circulates, that is within the oil volume 18. Pressure and temperature sensors.
• Volume 20a, 21, 22, 24, 30, 31a, 32a: The Radiators (22) and pipes (19a) and working gas circulation volume (20a,) that runs within 19a, pre-heating conditioner unit (24,) and the steam turbine (21,) the booster pump (30,) the double bypass pipes (31 a and 32a.) Temperature and pressure sensors for each volume and medium of circulation and circulation section.
• Volume 27: The loop back hot gas 16a feedback volume. Pressure and temperature sensors.

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.

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 16a: (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+t1));
  • (Reverse thruster shaft) End (t1);

While (1)

• • Open valve 28;
  • Wait (Frequency);
  • Open valve 29;
  • If (Pre-compression Gas temperature<<27 C);
  • Frequency=A; (High frequency: Every 5 minutes.)
  • Else if (Gas temperature<<270 C);
  • Frequency=C; (Middle frequency: Every 10 minutes.)
  • Else if (Gas temperature<550 C);
  • Frequency=E; (Base load frequency: Every 15 minutes.)

This initialization and then gradually reaching the desired base load parameter of compressed gas 16a, 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.

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 16a, as follows:

While not stopped   (1)

• • Temperature=Get Oil Temperature (t1);
  • Frequency=Get frequency (Oil Temperature);
  • Thrust shaft(t2);
  • Wait (frequency);
  • Open valve (28);
  • Close valve (28);
  • Retract shaft (t3);
  • Open valve (29);
  • Close valve (29);
  • Thrust shaft (t4);

While do

• • Power Generation=Get Power Output (e);
  • If (Power Output>Optimal e);
  • Keep bypass valves (30) open and bypass valve (31) closed;
  • If (Power Output<Optimal e);
  • Close bypass valves (30) and (31);
  • If (Heat Generation<Optimal t);
  • Open bypass valves (30) and (31);
  • Else if (Oil temperature>600 C);
  • Set frequency=G; (Overheated frequency: Every 40 minutes.)

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 16a, 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.

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.

With reference to FIG. 6, in cross sectional view it shows how the circulation steam 20a 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 20a of the residential and/or commercial buildings 23 and return within a closed cycle insulated pipe 19a 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.

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.

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.

Claims

1. An energy conversion system for use by the thrust of a steel shaft that is periodically activated by an energy source coupled to an electro-mechanical means, to convert the mechanic force of the thrust provided by the steel shaft into usable thermal energy comprising:

a. a steel shaft of linear motion-thrust that provides sudden thrusts on a periodic basis in order to move a first piston.

b. a first cylinder with a first working chamber located between a first piston and a top section of the first cylinder.

c. a second cylinder with a second working chamber located between second piston and a top section of the second cylinder.

d. wherein said second cylinder and second piston are of a predetermined diameter size larger than the said first cylinder and said;

e. first piston, and bottom section of said first cylinder is connected to a bottom section of said cylinder via a hydraulic link;

f. a steel shaft to push and reposition the top section of said first piston within the first working chamber.

g. an electro-mechanic means that provides the thrust motion to the said steel shaft and the said electro-mechanic means that re-positions the said first piston back to its pre-thrust position.

h. wherein said electro-mechanic motion means with a slower regulated motion re-positions the said first piston back to the initial pre-thrust position.

i. a direct heat exchange medium from the compressed-heated gas volume, made of a U shaped concave copper metal interface that is in communication with said static oil volume inside said heat exchanger.

j. a spiral fluid-working gas pipe circulation section within said static oil volume.

k. a booster pump for circulating the working fluid within the spiral pipe section, within the said static oil volume and throughout the closed cycle working gas circulation system.

l. a double path bypass pipe and two valves that provide flexibility of steam distribution between the steam turbine for power generation and central heating closed cycle circulation pipe flow;

m. one side of the closed topping cycle pipe that transfers the superheated steam generated to a steam turbine of non-condensing type;

o. at least one flow-meter and temperature sensor and transmitter to calculate energy used at each building and/or at each section of the buildings.

2. The system of claim 1, where in said energy source coupled to said electro-mechanical means is a renewable energy source.

3. The system of claim 1, wherein the said heat exchanger comprises of spiral pipes surrounded by a static oil volume.

4. The system of claim 3, further comprising a heat conduction concave copper metal interface conduction means, in communication with said thermal stabilization oil volume, adjacent and in heat transfer contact with said oil volume.

5. The system of claim 1, wherein the said predetermined diameter of large area piston size, is four times larger.

6. The system of claim 1, wherein said hydraulic link comprises of a hydraulic oil.

7. A method of generating thermal energy from the regularly repeatable mechanical thrusts of a shaft comprising the steps of:

connecting second side of a small diameter piston/cylinder combination via hydraulic link to a second side of a larger diameter piston/cylinder combination;

adiabatically compressing a gas on a first side of said large diameter piston/cylinder combination by placing a first side of said small diameter piston/cylinder combination in communication with a means for exerting force thereon by the electro-mechanically moved shaft;

conducting heat from said heated gas into a static oil volume by using the concave heat conduction surface area, in order to establish a thermal stabilization oil volume; and,

circulating said steam pipes within said static oil volume and transferring said high pressure steam first in a topping cycle through a steam turbine and then through a closed cycle working gas pipe line that is connected to radiators, with the flexibility and option to allocate more steam power for the power generation turbine(s) or for the central-district heating circulation, or to establish an optimal balance between power generation and heating needs based on the site-specific needs.

8. The method of claim 7, wherein said large diameter piston/cylinder combination is four times the diameter of said smaller piston/cylinder combination.

9. The method of claim 7, further comprises filling said hydraulic link with a hydraulic oil.

10. The method of claim 7, further comprising the step of being in direct communication with the thermal conductivity copper concave interface that conducts heat to a thermal stability oil area in communication with said compressed-heated gas and in heat transfer contact with said heat exchange gas compression volume.

11. The method of claim 7, wherein the step of placing said small diameter/piston cylinder combination in communication with a shaft thrust further comprises using the said steel shaft to provide thrust on the first small diameter/piston cylinder combination, by an electro-mechanical thrusting means.

12. The method of claim 11, further comprising the step of reversing the motion of the thrust of the shaft that is connected to the first side of the small diameter/piston cylinder combination, by changing the direction of the electro-mechanic motion means.

13. The method of claim 12, further comprising the step of completing a cycle by re-positioning the first side of the small diameter/piston cylinder combination using the slower and controlled reversal of the electro-mechanic motion of the said shaft.

14. The method of claim 13, further comprising the step of repeating the thrust of said shaft by moving the steel shaft with electro-mechanic means again to push the first side small diameter/piston cylinder combination in direct connection with said steel shaft.

15. The method of claim 14, further comprising the step of repeating the cycle at a predetermined time interval at base load operation.

16. The method of claim 15, further comprising the step of repeating the cycle at base load operation condition is every 15 minutes.

17. The method of claim 15, further comprising the step of repeating the thrust based on the static thermal stability oil volume temperature, that is able to adjust the frequency, based on the temperature and pressure readouts, where determination of proper frequency of repeating the compression-decompression cycle is made possible with a fully computerized control.

18. The method of claim 7, wherein the step of conducting heat from said compressed gas at the range of 550-600 C into the thermal stability static oil volume, increases the temperature range of the said temperature stability oil volume, to the temperature range of 450-500 C, only after four repeated compressions.

19. The method of claim 7, wherein the step of adiabatic compression of a gas on a second side of said large diameter/piston cylinder combination, further comprises compressing the gas to 1/17 of its initial volume.