Patent Publication Number: US-2011068575-A1

Title: Hybrid integrated cogeneration system and method

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application claims priority to Canada patent application 2,680,571, filed 16 Sep. 2009, which is hereby incorporated by reference herein. 
     TECHNICAL FIELD 
     In the field of cogeneration (CHP) systems and more particularly to a new zero emission triple integrated cogeneration system. The heating system is combined with a chilled-water central air conditioner to provide a triple integrated system with air conditioning, water based central heating or forced air based heating for existing forced air infrastructure and service hot-water. A second embodiment relates to a higher capacity triple integrated system cogeneration plant with zero emission. 
     BACKGROUND ART 
     Housing apartment units and multi-family units usually use a central heat source such as a boiler or a forced-air system using gas fired or electric resistance furnaces for space heating. All these systems are mostly energy inefficient. 
     In order to solve these energy inefficiencies, different methods have been proposed. For example, a heating system is disclosed to provide an improvement in the combined configuration for better efficiency, by Talbert et al (U.S. Pat. No. 6,109,339) that discloses a triple integrated system to provide room air heating, and cooling and domestic hot water. 
     In order to utilize cogeneration and to be able to respond to a plurality of different demands of thermal energy, a cogeneration system apparatus is disclosed by Togawa, et al. (U.S. Pat. No. 6,290,142) including an improvement in hot-water storage and re-heating of hot water, that enables it to respond to two different thermal loads. 
     With respect to space heating, combustion gases from direct air heating are used to heat a water tank. Doherty (U.S. Pat. No. 2,354,507) and Biggs (U.S. Pat. No. 5,361,751) both use warm combustion gases for the space heating, to heat potable water in a water tank. Due to the need for dual burners, such systems are large size and therefore are costlier. Clawson (U.S. Pat. No. 5,046,478) uses a combustion gas heat exchanger to heat a potable water to be used for air heating. Woodin (U.S. Pat. No. 4,848,416) discloses an instantaneous heat exchanger. 
     The demand for highly efficient and low cost cogeneration is increasing world-wide. In the last decade of the century, more than 100 billion watts of new electric generating capacity will be needed in the U.S. and greater than 500 GW (e) will be needed in the rest of the world. Unless there is a widespread applicable technological improvement, a very conservative estimate predicts that world-wide power related CO2 emission would rise more than 60 percent from 1997 by 2020. Warnings are coming from respectable U.S. and international scientific institutions about serious threats on ecosystems. The global climate change-breakdown will cause great economic damages; substantial economic losses have already occurred as ecosystems have started to fail. Based on the UK Meteorological Office data, since the beginning of the industrial age, up to the year 2000, significant rises in average temperatures occurred within a 140 years period; since the year 1860, being indicative that within next 140 years temperature increases could be exponential. Therefore, the European Union Commission aims to double the contribution of combined heating and power (CHP) solutions from 9 percent to at least 18 percent by 2010. The new climate campaign, which is gathering momentum as the current world economic crisis has surfaced, and a recent report by the Oak Ridge National Laboratory prove that large scale international investment into renewable energy systems would create a new economy which would generate large scale new employment throughout the world, and nearly one million highly skilled new jobs in the U.S.A. alone. 
     Each year 17 million vehicles are manufactured in the U.S. further increasing the energy demand. The electric-battery vehicle is the future in the automotive sector and electrical power driven economy requires an inexpensive source of electricity. 
     The trend indicates that eventually there will be a synergy of conventional technologies with proven high technologies to improve renewable energy output. Only this will enable hybrid-renewable energy systems of highest efficiency and the lowest cost production. This system aims to lead this trend by having operational renewable energy input from relatively few wind generators and few solar panels for this innovation. 
     Most important central heating performance measurements are: a. Thermal load density that is preferably high, and; b. Annual load factor; that is 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. 
     Central heating systems are best for: 1. Industrial complexes; 2. Populated urban areas; 3. High density building clusters with high thermal loads: Central heating is best suited for areas that have high building and population densities—where the climate is cold; and, 4. Where the efficiency of insulation can be maximized. 
     End user priorities are reliability, long term low operational costs and reasonable price and compactness for onsite generation. Prior art cogeneration and 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 based on a renewable energy source with low energy densities. 
     Energy consumed in U.S. residences for space heating-cooling accounts for 46 percent of all residential energy consumption. Service water-heating accounts for an additional 14 percent. This is a total of 60 percent for residential needs. That is, 60 percent of all energy consumed is of low energy quality type of utilization. Hence, there is need for cogeneration to be applied as widespread as possible, as it is more efficient; thermo-dynamic energy is not converted back from the electrical power generated, nor is heat wasted. 
     Operational cost is related to: 1. Energy type; fossil fuel—burner type or renewable type; 2. Heat transfer efficiency; 3. Insulation type and efficiency; and, 4. Cogeneration-CHP efficiency. 
     SUMMARY OF INVENTION 
     From the foregoing, it may be appreciated that a need has arisen for a system and method for a cogeneration system and triple integrated system with air conditioning, central heating and service hot-water that avoids energy inefficiencies of the prior art. 
     It is an object of the present invention to provide a cogeneration apparatus capable of supplying thermodynamic energy efficiently to satisfy a plurality of different energy demands. 
     It is another object of the present invention to provide as a first feature of the invention, a system that ideally receives operational energy input from a low cost renewable prime energy source, such as wind and solar, but can also get operational energy from the utility grid. The system can also be paralleled to the utility grid for electrical energy output, thereby also increases the resiliency of the national energy infrastructure by offsetting transmission loses and limiting congestion. It is recommended to utilize existing wind farms for operational energy input or small capacity wind or solar energy input to be integrated to the invention system. Hence, for both for wind and solar, a large energy surplus gets stored. 
     It is another object of the present invention to provide as a second feature of the present invention, at least a set of infrared radiation members to provide infrared radiation as thermo-dynamic energy for the molten salt containing TES volume through a special enclosure that closely approximates an ideal blackbody container condition therein which results in a high stability total kinetic energy and stable average kinetic energy TES. 
     It is another object of the present invention to provide as a third feature of the invention, to establish a stable TES that enables high efficiency capacity utilization within a much shorter period relative to prior art systems to reach their most efficient system capacity utilization, with a substantially shorter initial power load period. 
     It is another object of the present invention as a fourth feature of the invention, to secure and keep the system functional with a secondary backup means that is always ready to backup the main thermo-dynamic energy means if it fails or when it is under maintenance. 
     It is another object of the present invention to provide as a fifth feature of the invention, wherein at least one cylindrical container, in which the thermo-dynamic energy of the working gas gets intensified within cylindrical volume quickly; and the energy density level increasing means becomes comparable to combustion based systems of comparable capacity in energy density level. 
     It is another object of the present invention to provide as a sixth feature of the present invention, a total TES molten salt mass that is greater by mass than the total working gas mass by a certain proportion, which is used to heat the working gas, to maximize thermo-dynamic stability of the TES. 
     It is another object of the present invention to provide as a seventh feature of the present invention, several steam turbines that utilize the high pressure steam generated to generate electrical energy and the working gas passing the turbines is circulated and utilized for central heating of residential and/or commercial premises. 
     It is another object of the present invention to provide as a eighth feature of the invention, a service hot water storage tank that heats service hot water and a hot oil storage tank for drawing heat to heat the refrigerant coils for the central air conditioning which are circulated therein, both tanks are heated by the waste heat from the thermal storage volume to provide a triple integrated system, providing a high total system efficiency throughout all seasons. 
     It is another object of the present invention to provide as a ninth feature of the present invention, to enable optimal distribution of working gas between the steam turbine power generation and the central heating. 
     It is another object of the present invention to provide, as a tenth feature of the present invention, a TES volume that enables flexibility of using different, alternative types of thermal storage materials that can be used and that are easy to maintain, overhaul, drain out, change and refill. 
     In the second embodiment, it is an object of the invention to provide as an eleventh object, to enable modular capacity increase for higher capacity cogeneration. 
     It is another object of the present invention to provide as an twelfth feature, a system that achieves a minimized waste heat system and therefore, provides a zero thermal pollution system; there is no combustion and no exhaust-no exhaust heat loss, therefore the system is ideal for the international greenhouse gases trading scheme. 
     It is another object of the present invention to provide as a thirteenth feature, an invention system that enables high energy quality utilization. Thermal energy generated is utilized directly as thermal energy for central heating and air conditioning. 
     It is another object of the present invention to provide as a fourteenth feature of the system, a system that provides power cogeneration which provides very high flexibility in terms of enabling different sizes and a wide range of capacity scalability. 
     It is another object of the present invention to provide as a fifteenth feature of this cogeneration system, of which the rated capacity to run on the highest capacity factor operation condition does not entail high economic and environmental opportunity costs and is independent of external variables and constraints like; ideal geographic locations with best sunny or windy conditions, ideal ebb and tide, day-night cycles, a need for large areas of land for the installation as in large area solar panels and large wind turbine farms, scarcity of fuels and unstable fuel prices, pollution control costs as in combustion plants, erosion and loss of valuable land, as in flooding of land for hydroelectric dams, tradeoff of degrading of valuable farming soil as in bio-fuels. That is, this system can avoid a substantial part of these high economic and externality costs by eliminating majority of these means. 
     It is another object of the present invention to provide as a sixteenth feature of the system, a wear-resistant cogeneration system that by eliminating and not having moving components-friction or combustion chambers as the main energy generation means, thereby also eliminates the green-house gas emissions as a zero emission system and is compatible with the 350 ppm CO2 objective, and has high durability and longer product life cycle. 
     It is another object of the present invention to provide as a seventeenth feature of the present invention to be subject of a relatively low cost OEM or subcontracted manufacturing and can be compatible to existing central residential and commercial heating and power generation, in technical means and labor and accordingly is then subject of reasonable prices of sale to the consuming and operating entities and end users, despite high profit margins on system sales and also enables high operational profit margins, thereby makes said cogeneration and the second embodiment of cogeneration of power and central heating plant to provide significant economic gains to all energy sectors and end users. 
     It is another object of the present invention to provide as a eighteenth feature of the invention, a system that provides OEM power generation, thermo-dynamic processing engineering companies the flexibility to choose different means to integrate the system with process heat or other industrial processes—by integrating related devices to this system and which can utilize the high stability thermo-dynamic base of this invention. 
     It is another object of the present invention to provide as a nineteenth feature of the invention, a system that does not have moving parts like pistons or combustion related volumes, pressure vessels, therefore the system operates without vibration and is very silent. 
     It is another object of the present invention to provide as a twentieth feature of the invention, to keep the main system technical features secret and make these sections accessible to only expert company personnel and make it tamper proof and inaccessible to others. 
     The objects of the current invention will be evident as depicted by the drawings. 
    
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         FIG. 1  is a cross sectional depiction of the entire system that is made of at least one unit with a set of infrared radiation providing emitters that radiate into a closed container which approximates a blackbody container condition therein and this volume is in contact with one TES volume that is located above the infrared radiation closed container. Cross section reference lines A, B, C, D are for  FIGS. 5 ,  6 ,  7 ,  8  of top closure removed views for in depth view from top. Backup energy input also depicted. 
         FIG. 2  is a cross sectional view of the system as depicted when infrared radiation input occurs through the main means that provides thermo-dynamic energy to the double surface container that has an atomic and molecular structure that maximizes absorption below the TES. 
         FIG. 3  is a cross sectional view of the system unit, it shows the TES molten salt volume, receiving thermo-dynamic energy through the double surface container; wherein the total kinetic energy gets stabilized. 
         FIG. 4  is a cross sectional view of system unit, TES volume side, shows one of the triple integrated system components of service hot water tank and sections—as integrated and located around one half of the TES volume enclosure cylindrical external surface area. Also shown is water based flow and central heating of premises. 
         FIG. 5  is a top view with top closure of one TES volume completely removed showing the molten salt TES volume with the working gas pipe circulating within the molten salt TES along the cross section A. 
         FIG. 6  is a top view with top closure of one TES volume completely removed showing the thermo-dynamic energy emitting double surface container surface area below the molten salt containing TES, along cross section B. 
         FIG. 7  is a top view with top closure of one TES volume completely removed showing concentric ring area surface to which secondary backup infrared radiation emitters provide radiation upon, along cross section C. 
         FIG. 8  is a top plan view with top closure-frame completely removed of one TES unit and the energy density increasing means container on top not shown and which is viewed from top showing the circular secondary backup infrared radiation emitter, surrounding the main means of the infrared radiation emitter members that are shown at the center, along cross section D. 
         FIG. 9  shows in top plan view four units combination as the modularly enlarged capacity system, with only one energy density increasing means cylindrical container, likewise the system can be modularly enlarged with only two units combined, with one larger energy density increasing cylindrical container, transmission and distribution system is common to all four, two units system not depicted. 
         FIG. 10  is a cross sectional view of the alternative central forced air distribution duct, if forced air is chosen instead of water based radiator system. 
         FIG. 11  is a top view of the TES top section with cylindrical energy increasing means container located above the TES, showing the alternative viewing direction depicted in next drawing of  FIG. 13 , to the direction along  107 - 107 . 
         FIG. 12  is the cross sectional view of the cylindrical container volume, along the line  107 - 107 . It shows the working gas spiral pipe section that absorbs infrared radiation, with high absorption coated paint located at the center of the cylindrical container, where the energy density gets increased by infrared radiation devices. 
         FIG. 13  is the focused depiction of the container that closely approximates blackbody container condition. 
         FIG. 14  is the cross sectional and three dimensional perspective view combination showing how the small inlet channels reach the middle molten salt volume of the circular pipe. 
         FIG. 15 , shows how the infrared radiation emitter members and the secondary backup radiation emitters and the infrared radiation application volume below the TES, are contained and made tamper proof and inaccessible to unauthorized people. 
     
    
    
     LIST OF REFERENCE NUMERALS USED 
     
         
         
           
               1 . Operational electricity input from a renewable prime energy source such as wind and solar (preferred prime energy). 
               2 . Operational electricity input from the utility grid (alternative prime energy). 
               3 . Closed container  4  internal volume that closely approximates an ideal blackbody container  4  condition therein with lower surface  4   c  with an area of radiant energy absorption double surface container  4  that has a structurally strong atomic and molecular formation maximizing absorption. 
               3   a.  Infrared radiation emitter members, each positioned in its housing on the circular structure  84 . 
               3   b.  Area corresponding to the surface area of each radiation emitter member  3   a.    
               3   c.  Air flow grids for cooling emitter members  3   a,  from below infrared emitter members  3   a.    
               3   d.  Air in and outflow channels through the circular structure  84  that houses infrared radiation emitter members  3   a,  which enable cooling of infrared emitters  3   a  and volume  4   a  from below. 
               4 . Radiant energy absorption double surface container, preferably made of carbon-carbon composite or another composite with very high radiant energy absorption rate, and this container is one solid structure made of upper surface  4   b  and circular sections  4   d,  surfaces facing the molten salt TES volume  69 , are coated with Ni3Al or another state of the art coating, the internal volume  3  is the internal volume of the container  4  which approximates a blackbody condition hence heat is absorbed by the surfaces  4   b,    4   d.    
               4   a.  Infrared radiation  74 , enclosed radiation throughput volume. 
               4   b.  Upper surface of the double surface container  4 . 
               4   c.  Lower surface of the double surface container  4 . 
               4   d.  Container  4  circular sections between upper surface  4   b  and  4   c,  where the container  4  is a single structure and  4   d  are the circular corners on left and right sides in cross sectional view. 
               5 . External insulation layer of the TES  69  that is moisture proof. 
               6 . Internal semi-insulation layer facing the service hot water volume  13  and refrigerant gas coil heating oil volume  20 . 
               7 . TES molten salt tank volume  69  enclosure frame-wall, of which internal surface is coated with non-corrosive coating of Ni3Al or another state of the art coating, (if not made of concrete). 
               8 . Working gas spiral pipe coated with PYROMARK trademark paint or another state of the art high absorption paint which gets infrared radiant energy within the cylindrical container  68 . 
               8   a.  The vertical section of the working gas pipe  70  before it enters the cylindrical container  68 , exiting the TES  69 , which then becomes working gas spiral pipe  8  therein. 
               9 . Air volume within cylindrical container  68 . 
               9   a.  Air pressure release two-way air valve for the contracting/expanding air within unit  68 . 
               10 . TES  69  molten salt volume drainage valve. 
               11 . TES  69  molten salt volume filling pipe. 
               12 . Condensed returning working gas  50  and lower pressure steam post turbines re-entry pre-heater unit pre-steam generator unit, utilizing the feedback steam which gets utilized by steam turbines  30  and  27  first. 
               13 . Service hot water tank volume-left side that is around ½ of the total cylinder surface area of the TES volume  69  enclosure  7  circumference (left). 
               14 . Pre-heater unit for service hot water volume  13  input. 
               15 . TES volume conduction material with desired level heat conduction properties-cylindrical external surface area  15  facing the semi-insulation layer  6  for service hot water and refrigerant gas coil heating oil volume  20 , on enclosure frame-wall  7 . 
               16 . Service hot water circulation outgoing pipe (left side in drawings). 
               17 . Service hot water temperature sensor and regulator unit-outgoing (left). 
               18 . Service hot water tank-water supply entry pipe (left). 
               19 . Refrigerant gas (freon-12 or di-chlorodifluoromethane type, which boils at −29.8 C). 
               20 . Refrigerant gas coil heating oil volume that is around approximately ½ of the total cylindrical surface area of the TES volume steel enclosure circumference (right side). 
               21 . Refrigerant gas heater spiral coil section within volume  20  (right side). 
               22 . Refrigerant dissipation coils (right). 
               23 . Refrigerant gas coils condenser (right). 
               24 . Refrigerant gas second pump. 
               25 . Working gas pipe exiting TES  69 , pre turbine  27  and  30 . 
               26 . Steam power distribution valve on pipe  25 , pre-turbines  27  and  30 . 
               27 . Steam turbine and generator, (primary mover, steam turbine  1 ). 
               28 . Working gas pipe exiting steam power distribution valve  26 , pre turbine  30 . 
               29 . and  29   a.  Post turbines steam pressure-temperature electronic sensors on pipes  31  and  32  ( FIGS. 1 ,  2 ,  3  only). 
               30 . Steam turbine and generator, (primary mover, steam turbine  2 ). 
               31 . Working gas closed cycle central heating circulation pipe-past turbine  27 . 
               32 . Working gas closed cycle central heating circulation pipe-past turbine  30 . 
               33 . High pressure working gas-pre turbines. 
               34 . Radiators ( FIG. 4 ). 
               35 . Residential and/or commercial buildings ( FIGS. 4 and 10 ). 
               36 . Central air conditioning chilled water tank unit located next to TES (right,  FIG. 1 ). 
               37 . Chilled water unit outgoing distribution pipe for central air conditioning. 
               38 . Cogeneration TES unit  1  in the four units combined TES plant configuration ( FIG. 9 . reference numbers  39 ,  38   a,    39   a,  all are about  FIG. 9 ). 
               38   a . Cogeneration TES unit  3  in the four modular units combined TES plant configuration. 
               39 . Cogeneration TES unit  2  in the four modular units combined TES plant configuration. 
               39   a.  Cogeneration TES unit  4  in the four modular units combined TES plant configuration. 
               40 . Chilled water output temperature sensor exiting chilled water volume  48  pipe  37  ( FIG. 1 ). 
               41 . Refrigerant gas  19 —expansion valve (right). 
               42 . Second pump for the returning condensed working gas  50  back to TES pipe section. 
               43 . Chilled water unit closed cycle cooler coils in water chiller unit  36 . 
               44 . Second pump for regulating the flow rate of returning condensed working gas  50  back into the returning working gas  50  re-entry pre-heater pre-steam generator unit  12 . 
               45 . Working gas closed cycle circulation pipes  31  and  32  united as a single feedback steam pipe back into working gas pre-heater pre-steam generator unit  12 . 
               46 . Chilled water tank water supply pipe (right side). 
               47 . Pressure sensor unit ( FIGS. 4 and 10 ). 
               48 . Chilled water unit internal chilled water volume (see  FIG. 1 ). 
               49 . Feedback working gas recycling pump ( FIGS. 4 and 10 ). 
               50 . Returning working gas—post central heating premises  35 . 
               51 . The modularly enlarged higher capacity working gas (not in drawings). 
               52 . The modularly enlarged higher capacity working gas and total TES volume configuration, with two units combined (no drawing). 
               53 . The modularly enlarged higher capacity working gas and total TES volume configuration of  FIG. 9 , with four units integrated. 
               54 . Top view of the common higher capacity larger energy density increasing means cylindrical container, located on top in the middle of the modularly enlarged capacity four units higher capacity working gas and total TES volume ( FIG. 9 ). configuration. 
               55 . Forced air space heating outlet points—in residential and commercial premises  35  ( FIG. 10 ). 
               56 . The four modular integrated units TES configuration plant common chilled water unit located next to the TES, for central air conditioning ( FIG. 9 ). 
               57 . Utility grid electrical input connection control board to the four units configuration plant ( FIG. 9  only). 
               58 . Refrigerant return coil into the refrigerant gas coil heating oil volume. 
               59 . Refrigerant pump. 
               60 . First cooled water general distribution and return pump (not shown in drawings). 
               61 . Second cooled water general distribution and return pump (not shows in drawings). 
               62 .  FIG. 9 , wind turbine electrical energy input collector and transformer. 
               63 . 100 percent renewable energy electrical energy cable connection ( FIG. 9 ). 
               64 . Working gas pipe  25  electronic steam pressure control sensor (only in  FIG. 1 ). 
               65 . Refrigerant gas compressor. 
               66 . Container  4  temperature control electronic sensor (not shown in the drawings). 
               67 . Concentric ring surface for backup infrared radiation below molten salt TES  69 . 
               68 . A cylindrical container-volume outside the TES  69  for the fast energy density increasing means of the working gas with the spiral pipe section  8  therein. 
               69 . TES molten salt volume that contains the double surface circular pipe  89 . 
               70 . Working gas pipe section in flat and wide form which is within the double wall-surface circular pipe  89 . 
               71 . Infrared members within the cylindrical container-volume  68 . 
               72 . Pressure and heat transfer medium tight lockable lid that enables access into the molten salt TES volume  69  for repairs, after molten salt is emptied. 
               73 . Working gas flow rate and pre-heater thermostat and temperature control electronic sensor-timer control board, integrated with control boards of  1  and  2 . 
               74 . Infrared radiation that is applied through the volumes  4   a  and  9 . 
               75 . Radiated temperature of the upper surfaces  4   b  and  4   d  of the container  4 . 
               76 . Molten salt volume  69  temperature prior to infrared radiation  74  input. 
               77 . Wait periods of non-radiation between radiation periods, when heat continues to get conducted into TES  69 . 
               78 . Secondary backup radiation emitters below TES  69  for the concentric ring surface  67 . 
               79 . Independent circuit operational electricity input control board for the secondary-backup means infrared member for the concentric ring surface  67 . 
               80 . Air tight closure that enables access to energy density increasing means cylindrical container  68 , which is accessible to only expert company personnel. 
               81 . TES thermostatic sensor electronically connected to control boards; to integrated board  73  with  1 ,  2 , and to sensor  66 . 
               82 . The separation wall of which TES facing surface area is  15 , of the service hot water tank  13  and the refrigerant hot oil tank  20 , where each are around one-half circumference of the cylindrical TES  69  side wall, for heat utilization from TES  69 . 
               83 . Circular structure holding infrared radiation emitter members  3   a  with air flow grid  3   c  for cooling. 
               84 . Heat exchanger for hydronic coil to forced air heating-air handler of  FIG. 10 . 
               85 . A group of wind turbines of the 100 percent renewable energy configuration ( FIG. 9 ). 
               86 . Central forced air distribution duct alternative to water based system ( FIG. 10 ). 
               87 . Radiant energy input openings of closed container  4 , that enables inflow into volume  3  through bottom surface  4   c  of interface  4  that closely approximates a blackbody condition. 
               88 . Static electricity discharge grounding line connection. 
               89 . Double surface circular pipe within the TES  69 , which contains the working gas pipe  70 . 
               90 . Small inlet channels between the walls of the double surface circular pipe  89  that let molten salt to enter the middle volume  91  of the circular pipe  89 . 
               91 . Molten salt containing middle-central volume of double surface circular pipe  89 . 
               92 . Double surface circular pipe  89 , internal volume containing the flat and wide working gas pipe  70  which circulates therein. 
               92   a.  Inner wall of the double surface circular pipe  89 . 
               92   b.  External wall of the double surface circular pipe  89 . 
               93 . Internal structural supports between the outer  92   b  and inner  92   a  walls of the double surface circular pipe  89  positioned as oppositely located pairs within volume  92 , ( FIG. 14 ). 
               94 . Enclosure that makes infrared emitters  3   a  and radiation volume  4   b,  and the approximate ideal blackbody container  4  inaccessible to unauthorized people. 
               95 ,  95   a.  Closures of  94  which can be opened only by the expert company personnel. 
               96 . Foundation upon which the system and the TES stands on. 
               97 . Central heating distribution steam pipe connecting to steam to water heat exchanger, post steam power distribution valve  26 , for water based central heating circulation, or to the heat exchanger for hydronic coil to forced air heating-air handler  84 . 
               97   a.  Returning central heating distribution hot water pipe, post residential and/or commercial buildings. 
               97   b.  Returning central heating distribution forced air pipe returning to the heat exchanger  84  for hydronic coil to forced air heating-air handler, post residential and/or commercial buildings. 
               98 . Steam to water heat exchanger for the central heating circulation. 
               99 . Water based central heating water pump, post steam to water heat exchanger  98 . 
               99   a.  Central heating distribution forced air pipe pump. 
               100 . Post steam to water heat exchanger  98 , or heat exchanger for hydronic coil to forced air heating-air handler  84  pipe that connects back to pre-heater pre-steam generator unit  12 . 
               101 . TES volume top side frame which gets mounted after the double surface circular pipe  89  gets assembled in first. 
           
         
       
    
     DESCRIPTION OF EMBODIMENTS 
     This invention is based on the following principles and method combination: 
     1. An energy efficiency increasing means which utilizes lower installation cost, substantially smaller scale-capacity solar or wind energy installation operational energy input; where the increased energy efficiency differential of this means with at least 90 percent and the ability to store this high stability thermo-dynamic energy, is substantially greater than the energy generation efficiency that can be due to a large scale-capacity stand alone solar panels installation or a large stand alone wind farm installation. Because large scale wind farms and solar panels peak electrical energy generation capacities cannot be stored and have to be unloaded at un-economic rates, whereas with this system for both for wind and solar, almost all of the renewable energy surplus gets stored with high efficiency; 
     2. Industrial scale state of the art high quality infrared radiant energy emitters, of which the radiation is applied on a high technology carbon-carbon composite or metal alloy material with very high radiant energy absorption rate and which therefore is also a good emitter, applied on a container  4  that emits thermo-dynamic energy into the molten salt containing TES  69  located above it. The container  4  is to closely approximate an ideal blackbody condition, with the radiant energy absorption angled surfaces  4   b  and  4   d.  Wherein, surfaces  4   b  and  4   d  facing the TES  69  molten salt volume have a non-corrosive coating of Ni3Al or another state of the art coating. A secondary concentric ring area  67  is a distinct and separate surface area under the same TES  69  circular bottom platform for the backup means and a third separate infrared radiation  74  providing members  71  are within a cylindrical container  68 , spiral pipe section  8  made of highly corrosion resistant stainless/lined steel pipe with a coating of PYROMARK paint or a higher quality state of the art high absorption paint, is for the fast energy intensity increasing means; 
     3. A strongly insulated total kinetic energy stable and high temperature TES  69  molten salt reservoir with an internal non-corrosive coating of Ni3Al type applied on ASTM-SA210 grade 1 or ASTM-SA213-T-11 type of steel. The above mentioned coatings are not imperative, a coating that acts as an anti-corrosion layer against molten salt at a continuous high temperature operation range of 500-550 degrees Centigrade can be applied. Operation of the Aircraft Reactor Experiment (ARE) during the 50s and the Molten Salt Reactor Experiment (MSRE) in the 60s have proven the compatibility of a fluoride fuel mixture with Ni-based container alloys at maximum operating temperature of 710 degrees Centigrade. Hence, Ni-based container alloys can be considered. Zn—Mg coated steel sheet is another means in the industry that could be considered for the TES  69  molten salt tank internal surfaces. Instead of steel or alloy, concrete would be a good choice for a lower cost molten salt TES  69  container tank and also to avoid corrosion. Within the TES  69 , located is the double surface circular pipe  89  containing the flat and wide working gas pipe  70 . The double surface circular pipe  89  enables the molten salt to enter the middle volume  91  of the steam generator pipe  89  through small inlet channels  90  but the flat and wide working gas pipe  70  is contained separately within the walls  92   a,    92   b  in internal volume  92  of the double-wall double surface circular pipe  89  and is protected from the molten salt. Flat and wide working gas pipe  70  is circulated within volume  92  and wherein both flat side surfaces of pipe  70  face the double surface circular pipe  89  walls  92   a  and  92   b;  so thermo-dynamic energy gets conducted into the flat and wide working gas pipe  70  by solid to solid heat conduction and on both sides maximized area. 
     4. The TES  69  has a larger total mass as compared to the total working gas mass and depending on the engineering choices would contain of one of the following: A static oil volume of hydrocarbon or carbon-tetrachloride type fluid, but ideally purified high density molten salt that is highly stable for continuous high temperature operation with high average heat conductivity, contains a high specific heat capacity medium that enables first equation condition that is derived from the qualify facility (QF) status formula, which instead reads as: 
       Power output+½ Useful Thermal Output/Energy Input&gt;&gt;42.5 percent (in one year;)   (1).
 
     5. A method of periodically providing infrared radiation with lower energy input phase first and then repeating the same, where each one reduced energy input interval lasts longer than a full on radiation period, along with off intervals in between, hence having longer periods of lower operating temperature input ranges and lower, efficient energy consumption spread in time, once the system starts to operate at base load. 
     The heat transfer means is as follows: 
     a. The infrared radiation application  74  area-volume  4   a  is below the enclosed container  4 , and wherein the enclosed container  4  closely approximates an ideal blackbody container  4  condition therein with bottom surface  4   c  and upper surface  4   b  facing the enclosed container  4  internal volume  3 , and the periodic infrared radiant energy  74  results in emitting the absorbed thermo-dynamic energy by the blackbody container  4 , preferably made of a structurally strong composite material with very high radiant energy absorption rate and high temperature endurance, of which external bottom surface of  4   c  is the surface subject to direct radiant energy, wherein the radiant energy absorption and emitting is also increased due to the slightly larger surface area because of an angled surface structure and double surface structure radiant energy absorption container  4 , wherein the angular plane with an angle that is at least downward-negative 10 degrees as compared to zero degrees horizontal and extends from one higher midpoint at the center, therefore is conical in form, which is a mid point on the vertical, referenced as line H represented by a 90 degrees intermittent vertical line (as shown in  FIG. 13 ). instead of being zero degrees horizontal, and is located on the central part of the bottom surface of cylindrical TES  69 . That is, the bottom of TES  69  made up by the double surface radiant energy absorption ideal blackbody approximating container  4 , which is slightly conic. Based on the basic heat transfer equation applied to a heat exchanger, second equation: 
         q=U A ( Ta−Tb )   (2);
 
     Where q is the rate of transfer and U the overall transfer coefficient; A is the surface area for heat transfer and (Ta−Tb) the average temperature difference. The area A of thermo-dynamic energy emitting surface area total is thereby made larger by the double surface container  4  surface area at the center of the container  4  bottom of the cylindrical TES  69  that is in the form of a double surface container  4  with an angled surface and has an enclosed volume  3 , hence the rate of thermo-dynamic energy transfer increases. 
     b. The fast energy density increasing section volume within the cylindrical container  68  is air. 
     c. The spiraling pipe section  8 , located within the cylindrical container  68  for direct heat exchange by the fast energy density increasing means has high infrared radiation absorption rate coating of durable PYROMARK brand paint with high absorption rate of 95 percent, or a better state of the art coating, and is made of a material with a structurally strong atomic and molecular composition which maximizes radiant energy absorption—such as highly corrosion resistant stainless/lined steel, and the spiral section  8  is continuation of pipe  8   a  coming out of TES  69  vertically, and this section circulating working gas pipe  8  is in a spiral shape to increase the total radiant energy transfer area, wherein radiant energy is provided by infrared radiation  74 , thereby the energy density of the steam-working gas  33  is increased efficiently and swiftly. 
     d. Within TES  69 , is hot-service water tank volume  13  surrounding the center part of the TES, utilizing the TES  69  waste heat for indirect heat exchange, with an internal semi-insulation layer  6  that is around the molten salt volume is enclosure side wall  7 , cylindrical wall external surface area  15  and faces the internal semi-insulation layer  6  that covers the TES  69  molten salt that is enclosed within the enclosure side wall  7 , and water is stabilized at 75 degrees Centigrade in service hot water tank volume  13 , and utilizes waste heat from the TES  69 . 
     e. A service hot water temperature mixer-regulator unit  17  for outgoing service hot water, that avoids water temperatures above a pre-selected upper threshold range of about 60-70 degrees Centigrade, it is utilized for heated water output for shower, dish-washing, washing machine or other appliances. 
     f. Within TES  69 , is air conditioner refrigerant  19  heating tank  20  for indirect heat exchange with internal refrigerant coil spiral  21  that runs within the oil tank  20 , that contains an oil stabilized at a range of 70-80 degrees Centigrade, likewise surrounds the other ½ of the external surface area  15  of the molten salt TES  69  of the cylindrical enclosure side wall  7 , and also utilizes the waste heat to enable substantially less compression time for the refrigerant  19  to function with heat input from the molten salt TES  69 , by the internal semi-insulation layer  6 . The balanced waste heat utilization is made possible by insulation layer  6 . 
     The fast energy density increasing means high efficiency is enforced by the utilization of the electronic sensor controlled working gas  33  flow control board  73  and returning working gas  50  pre-heater unit  12  that increases the pre-TES  69  entry temperature of the returning working gas  50 , and with the total-kinetic energy stabilization factor with a high stability temperature range within the TES  69 , which is the main contributor in the stabilization of the temperature of the working gas  33 , this combination results in about 70 percent of the working gas  33  volume per cycle to pass through the spiral pipes section  8  within the cylindrical container  68 , that is within the fast energy density increasing means, to arrive into the spiral section  8  with at least 500 degrees Centigrade, wherein the flow is without fluctuation in temperature per cycle, and only about 30 percent of the total working gas  33  volume circulating within the spiral pipe section  8  per cycle to pass through with an average kinetic energy that arrives at about 350 degrees Centigrade to be swiftly raised to 500-550 degrees Centigrade. Said spiral pipe section  8  is located at the center of cylindrical container volume  68 . 
       FIG. 1  is a cross sectional depiction of the entire system that is made of at least one unit with infrared radiation  74  application volume  4   a  and upper blackbody surface  4   b  and circular corner sections  4   d  of the container  4  located below the cylindrical TES  69 . 
     The double surface circular pipe  89  is within the TES  69 , and therein the flat-wide working gas pipe  70  is circulated. Small inlet channels  90  between the two walls  92   a  and  92   b  of the double surface circular pipe  89  let molten salt to enter into the middle volume  91  of the circular pipe  89 , thereby both surfaces  92   a  and  92   b  are subject to heat transfer, and the flat and wide working gas pipe  70  is circulated within volume  92  (see  FIG. 14 ). and is protected from direct contact with the molten salt. Also shown is the renewable energy electrical input and control box-panel  1 —integrated in control board  73  and to secure backup operational energy, the system is also connected to electrical input from the utility grid that may be through a non-renewable energy input control box- 2 —also integrated into one control board  73  controlling energy input for the infrared radiation units  3   a.  All of the triple integrated system components and sections—as integrated and located around the TES  69 , enclosure wall  7  depicted. Cross sections A, B, C and D horizontal reference intermittent lines are about drawings  5 ,  6 ,  7  and  8  respectively, indicated in  FIG. 1 , as the relative vertical positions and corresponding to top views in drawings  5 ,  6 ,  7  and  8 . The vertical reference intermittent line H (shown only in  FIG. 13 ) and horizontal reference intermittent lines C meet with 90 degrees and this is to indicate how the container  4  is at least negative 10 degrees angled. The concentric ring surface  67  below the TES  69  for the system backup means, secured by the infrared radiation  74  providing members  78  below the molten salt TES  69 , are also shown. Working gas pipe section  70  exiting the TES  69  vertically as pipe section  8   a,  enters the fast energy increasing cylindrical container  68 , and becomes the working gas spiral pipe  8  therein. The TES volume  69  top side frame  101  is assembled onto the TES  69  later to enable to mount the double surface circular working gas pipe  89  into the TES  69  first during manufacturing. 
     In the context of keeping the system as a trade secret or to avoid reverse engineering, the technical details and know-how of the main critical system features of at least; the circular structure  83  holding infrared radiation emitter members  3   a  with air inflow grids  3   c  along with air in and outflow channels  3   d,  which are for cooling the emitter members  3   a  and volume  4   a,  radiant energy inflow openings  87  of the approximate ideal blackbody container  4 , bottom surface  4   c  of container  4  that closely approximates a blackbody condition therein, infrared radiation  74  application volume  4   a,  the container  4  which is made of double surfaces  4   b  and  4   c  and corner sections  4   d,  the cylindrical container  68  fast energy density increasing means, all of these sections are kept secret and are to be made accessible to only expert company maintenance personnel and made tamper proof and inaccessible to others. 
     With reference to  FIG. 1  again, the cylindrical structure  83  holds at least a multitude of infrared radiation emitters  3   a  at its bottom section, which are located in a series, positions the infrared radiation emitter members  3   a  preferably of ceramic heater type with 90 percent or higher electrical energy to radiant energy conversion efficiency, in between housings  3   b  and where each infrared emitter member  3   a  emits radiation  74  through housings  3   b  into the radiation input through volume  4   a,  where each housing  3   b  corresponds in area to the surface area of each emitter member  3   a,  where emitters  3   a  are mounted on the cylindrical structure  83 , wherein this approximate ideal blackbody container  4  internal volume  3  has below an angular lower surface  4   c,  also of the double surface container  4  with an angular plane of at least downward negative 10 degrees angle, and said container  4  walls have a structurally strong atomic and molecular composition that maximizes radiant energy absorption of at least 97 percent and emits thermo-dynamic energy into the TES  69 , through the blackbody container  4  upper surface  4   b  and circular corners  4   d.  The lower blackbody surface  4   c  of the double surface container  4  has high temperature durability, the emitters  3   a  are directed to the lower surface  4   c  of the blackbody container  4 , thereby the infrared radiation  74  within the range of 300-650 degrees Centigrade. provides periodically radiant energy into the container  4 , and surfaces  4   b  and  4   d  transfer heat into the molten salt TES  69  spread in time efficiently. The first embodiment TES  69  highest temperature is 550 degrees Centigrade. Static electricity grounding line  88  discharges static. 
     Referring to  FIG. 1  again, the molten salt volume TES  69  is a highly stable medium in terms of the temperature range-stability, with high total kinetic energy therein, which in turn heats circulating working gas  33  within molten salt TES  69 , in the flat and wide working gas pipe  70  which is within the circular pipe  89 , which facilitates a working gas  33  that reaches a high temperature even before it enters the fast energy density increasing means cylindrical container  68 , of which the closure  80  can be opened only by expert company personnel. The temperature stability of a minimum of 350 degrees Centigrade is secured and working gas  50  returns via pipe  97   a  back first into pre-steam generator unit  12  to become steam again and then gets into the pipe  70 . The spiral pipe section  8  with infrared radiation absorbing coating and the working gas  33  proceed to circulate therein, which in a topping cycle method provides the high pressure pre-turbine steam  33  with about 1500 psig that is first used to generate power through steam turbines  27  and  30 , and then heat the residential and/or commercial buildings  35  that circulates through the radiators  34 . 
     Post turbine pipes  31  and  32 : Enables working gas-steam  33  post turbines  27  and  30  to proceed for feedback; to the closed cycle feedback steam pipe  45  and back into working gas pre-heater pre-steam generator unit  12 . The returning working gas  50  closed cycle central heating circulation returns through pipe  97   a  at a range of 40-65 degrees Centigrade, pre-heater unit  12  is for increasing the temperature of returning lower temperature working gas  50  post central heating, unit  12  which is a heat exchanger unit generating pre-steam before it enters the TES  69 , of which the feedback steam also re-enters TES  69 , to turn the condensate returning working gas  50  into steam again and the condensed hot water at about 60 degrees Centigrade, swiftly becomes steam  33  at least at 270 degrees Centigrade prior entering the circular pipe  89  within the TES  69 , so that it can reach thermal equilibrium with the TES  69  very quickly and energy efficiently, that is within the molten salt TES  69  circular pipe  89  flat and wide working gas pipe section  70 , and then goes through spiral section  8  within energy density increasing cylindrical container  68 . 
     The return condensed working gas  50  return pipe  97   a  leads into the TES  69 , returning circulated working gas  50  after being pumped by pumps  42  and  44  (see  FIG. 4 ). of which the pumping speeds are fully adjustable and run on a slower flow mode in coordination to assist working gas to reach desired temperature within the TES  69 , for the fresh working gas  33  to heat up to superheated steam  33  at 550 degrees Centigrade within the flat and wide working gas pipe  70 . For the forced air system, the returning closed cycle pipe  97   b  re-enters the heat exchanger for hydronic coil to forced air heating-air handler  84 , instead. 
     With reference to  FIG. 1  again, shown is also the service hot-water outgoing pipe line  16  of service hot-water heat transfer and thermal equilibrium tank  13  that is located around the other ½ cylindrical external surface area  15  of the TES  69 , that is covered with the semi-insulation layer  6 . 
     Service hot-water, water input goes through the pre-heater unit  14 . Also shown is air conditioner refrigerant gas coils  21  combined with an air conditioner and chilled-water unit  36  to provide a central air conditioning. 
     Air conditioner refrigerant heating coil  21  that runs within volume  20  is compressed by refrigerant gas compressor  65  and also heated by the waste heat from the enclosure wall  7  and semi-insulation layer  6  that is around the molten salt TES  69  cylindrical container wall  7 . 
     The refrigerant  19  is heated to about 70 degrees Centigrade and its temperature and pressure increases by thermal input and compression combination. Pump units  24  and  59  are used to pump the refrigerant  19 . The heat dissipation coils  22  allow refrigerant  19  to dissipate its&#39; heat. As it cools, refrigerant  19  condenses into liquid form and goes through an expansion valve  41 ; the expansion valve  41  enables a low pressure evaporated and cold refrigerant  19  to proceed to the central air conditioning chilled-water unit  36 , wherein it cools water to 4.4 and 7.2 degrees Centigrade. This chilled water is then piped out with pipes  37  through the buildings  35 . 
     With reference to  FIG. 2  is a cross-sectional view of the system as depicted when infrared radiation  74  input is provided through the radiation input volume  4   a,  onto the surface  4   c  and the surface  4   c  has at least two or more radiant energy  74  inflow openings  87 . Furthermore, radiated surface  4   c  also conducts heat through the container  4  circular corner sections  4   d  and the radiant energy in the enclosed container volume  3  is absorbed by interfaces  4   b,    4   c  and  4   d,  incident energy absorbed is shown as arrows within volume  3 , radiation input is shown as straight arrows with small gaps within the radiation throughput volume  4   a.    
     With reference to  FIG. 3  depicted in cross sectional view, depicting how thermo-dynamic energy is emitted into the TES  69  through the container  4 , and which has high radiant energy absorption rate and that maximizes thermo-dynamic energy emitting and preferably is made of a structurally strong material that has an atomic and molecular composition that maximizes absorption and is a double surface blackbody container  4  with an internal volume  3 , depicted is emitting with small arrows coming out of upper blackbody surfaces  4   b  and  4   d  of container  4 , as the upper surface  4   b  of container  4  emits energy into the TES  69  molten salt. 
     A strong insulation layer  5  insulates the TES  69 , of one internal semi-insulation layer  6  within tanks  13  and  20  and one overall TES  69  insulator layer  5  of strong insulator. 
     The net work W done by the 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− U 1= U=−W    (3);
 
     (TES  69  heat is replenished regularly and keeps a highly stable total kinetic energy). 
     With reference to  FIG. 4 , when the working gas  33  attains thermal equilibrium and becomes superheated steam  33  at least at 550 degrees Centigrade, this working gas  33  is distributed through the insulated output pipe  25 . First, in topping cycle with high pressure through steam turbine  27  and  30  then with reduced steam temperature and lower pressure through the past turbine closed cycle steam feedback pipe  45  back to pre-heater unit pre-steam generator unit  12  and then into pipe  89  within the TES  69 . 
     The returning working gas  50  returns to TES molten salt volume  69  condensed and at a lower pressure after having been circulated through all radiators  34 , first re-enters the pre-heater unit  12 , where the working gas  50  re-entry temperature is increased to pre-steam before it re-enters the TES  69 , through the return pipe  97   a  to the section within molten salt TES  69  to reach thermal equilibrium in the circular pipe  89  that contains the flat and wide working gas pipe  70 , again. Also seen is the water based steam to water heat exchanger  98 , which gets steam heat input by the central heating steam provider pipe  97 , the water based central heating pump  99  pumps hot water to the residential and/or commercial buildings  35 , with hot water radiators  34 . Pipe  100  takes exiting lower temperature steam from steam to water heat exchanger  98 , and enters into the pre-heater pre-steam generator unit  12 . 
     With reference to  FIG. 5 , it is a top plan view with top closure-frame  101  completely removed of one TES  69  unit, and the fast energy density increasing means cylindrical container  68  not shown, which is viewed from top showing the molten salt TES  69  volume that contains the double surface circular pipe  89 , with one half hatched view of the top outer wall of the circular pipe  89 , hatched on the upper side of the drawing, to show the flat and wide working gas pipe section  70  circulating around the molten salt containing middle volume  91  therein ( 91  not visible in this drawing), both made of highly corrosion resistant stainless/lined steel. 
     The TES  69  internal containers for service hot water tank  13  and the refrigerant gas coil heating oil volume  20  have separation wall  82  and is connected to the external wall  7 , thereby separates service hot water volume  13  from refrigerant gas coil heating oil volume  20 . 
     The service hot water tank  13  on the left side, that covers one-half the circumference of the TES  69 , the other one-half of the circumference of the TES  69  is covered by refrigerant gas heating oil volume tank  20  (right) that contains refrigerant coils  21 , double surface circular pipe  89  and flat and wide working gas pipe  70  is depicted along cross section A. 
     Working gas pipe section  70  exits the TES  69  vertically as pipe section  8   a,  enters the fast energy increasing cylindrical container  68 , and becomes the working gas spiral pipe  8  therein—seen here as top plan view. 
     With reference to  FIG. 6  it is a top plan view with top closure-frame completely removed of one TES  69  unit and the fast energy density increasing means container  68  not shown, which is viewed from top showing the surface top areas of surface  4   b  and circular corner section  4   d  along cross section B, below the molten salt TES  69  volume. Also are seen from top the service hot water tank  13  on the left side that covers one-half the circumference of the TES  69  and the other one-half of the circumference of the TES  69  is covered by the refrigerant heating oil volume tank  20  on the right that contains the refrigerant coils  21 . 
     With reference to  FIG. 7 , it is a top plan view with top closure-frame completely removed of one TES  69  unit and the fast energy density increasing means container  68  not shown, which is viewed from top showing the backup concentric ring surface area  67  along cross section C, which receives radiation from a set of circularly positioned secondary backup infrared radiation emitters  78 . Also are seen from top, the lower surface  4   c  which is subject to periodic infrared radiation with at least two or more openings  87 . Also seen is service hot water tank  13  on the left side that covers one-half the circumference of the TES  69  and the other one-half of the circumference of the TES  69  is covered by the refrigerant heating oil volume tank  20  on the right that contains the refrigerant coils  21 . 
     With reference to  FIG. 8 , it is a top plan view with top closure-frame completely removed of one TES  69  unit and the fast energy density increasing means container  68  not shown, which is viewed from top showing the circular secondary backup infrared radiation emitters  78 , that is around the main means of the infrared radiation  74  emitter members  3   a,  which are at the center, are shown along cross section D with two series of emitters  3   a  one encircling the one in the middle. 
     Also are seen from top the service hot water tank  13  on the left side that covers one-half the circumference of the TES  69  and the other one-half of the circumference of the TES  69  is covered by the refrigerant heating oil volume tank  20  on the right that contains the refrigerant coils  21 . 
     With reference to  FIG. 9 , shows in top plan view four TES  69  units combination as the modularly enlarged capacity system  54  as a whole, with only one larger fast energy density increasing means cylindrical container  68 , each TES  69  unit is depicted as  38 ,  39 ,  38   a,    39   a,  hence the four units combined enables to modularly increase the system capacity. 
       FIG. 9  also depicts the 100 percent renewable prime energy configuration, where operational energy is provided from existing wind farms or with a relatively low total cost-small number of new wind turbines  85  illustrated as being the origin source sufficient to provide operational input energy. The transmission and distribution system is shared by all four TES  69  units, hence it becomes more efficient. 
     The common cold water chiller unit  56 , for the central air conditioning is also depicted; the chilled water output pipe  37  is for central air conditioning. The system can be a relatively compact, a 300 kW capacity system or relatively compact, relative to a higher output capacity, a modularly integrated higher capacity system with the integration of two, four, six, eight, and more modular and larger-higher capacity TES  69  units. Alternatively, as one high capacity TES  69  unit, the integrated system has higher capacity working gas  51 , (single large TES not depicted) increasing overall system output capacity to about 15 MW capacity for small power plant type of capacity output. For example, one TES  69  unit has 300 kW capacity, when the TES  69  volume is enlarged the capacity of one TES  69  unit becomes 1 MW and when 15 units of these enlarged capacity TES  69  units are integrated at one site, it becomes a 15 MW plant. Any capacity between 300 kW and 15 MW is possible. 
     With reference to  FIG. 10 , it is a cross sectional view of the alternative central forced air distribution duct  86 , heat exchanger for hydronic coil to forced air heating-air handler  84  if forced air is chosen over water based radiators  34  system. 
     With reference to  FIG. 11 , is a top view of the TES  69  top section with cylindrical fast energy increasing means container  68  located above the TES  69 , showing the alternative viewing direction depicted in the next drawing  FIG. 13 , towards the direction along  107 - 107 . 
     With reference to  FIG. 12 , it is the sectional view of the cylindrical container  68  volume, along the line  107 - 107 . It shows the working gas infrared radiation  74  absorbing paint coated spiral pipe section  8  that is located at the center of the cylindrical container  68 , receiving radiation  74  and where the fast energy density gets increased by at least four infrared radiation emitters  71  positioned to provide radiation from four different directions, with 90 degrees differential in radiation path between each emitter, located on and emitting from the inner surface walls of the cylindrical container  68  facing the center of the cylindrical container  68 . Each emitter  71  is depicted as further away from the viewer, the nearest one being the one at the bottom. Infrared radiation  74  indicated as triple arrows with intermittent lines from each emitter  71 , directed to spiral pipe  8 . 
     With reference to  FIG. 13 , it is the larger, focused depiction of the container  4  that closely approximates a blackbody condition surfaces  4   b,    4   c  and  4   d.  The energy density increasing means cylinder container  68  on top is not depicted. The circular structure  83  houses the infrared radiation emitter members  3   a  and enables air inflow through grids  3   c  below and it has air inflow channels  3   d  to cool radiation emitter members  3   a  and the radiation  74  throughput volume  4   a.  Air in and outflow into volume  4   a  is shown with arrows. Radiant energy  74  entering volume  3  through openings  87  is absorbed by the interior walls-surfaces  4   c,    4   b  and  4   d  of the closed container  4 . Also seen is the double surface circular pipe  89  in cross sectional view within the TES  69 , containing the flat and wide working gas pipe  70 . Arrows in the internal volume  3  indicate the radiant energy that gets absorbed by surfaces  4   c,    4   b,  and  4   d.    
     With reference to  FIG. 14 , it is the front cross sectional and three dimensional perspective partially hatched view combination of the double surface circular pipe  89  showing how the small inlet channels  90  reach the middle molten salt volume  91 , and the relative location of the flat and wide working gas pipe  70  circulating within volume  92  of the double surface circular pipe  89 . Within volume  92  are also the internal structural supports  93 , between the external  92   b  and inner  92   a  walls of the circular pipe  89 . 
     With reference to  FIG. 15 , it is the cross sectional view of how infrared radiation emitter members  3   a,  the secondary backup radiation emitters  78  and the infrared radiation application volume  4   a  are made tamper proof and inaccessible to unauthorized people by containing these in an enclosure  94 , which has tamper proof closures of  94  and  95  and the fast energy density increasing means cylindrical container  68  also has a tamper proof closure  80  and is made inaccessible to unauthorized people. 
     The system would be monitored and controlled by a direct digital control (DDC) computer. Operation parameters are based on volumes, pressure, temperature and working gas flow controls. 
     Monitoring Devices 
     For the various volumes and components, voltage regulators for the generator turbines, power output and mechanic switches and electronic controls have to be used. System operation conditions are based on two main phases: 1. Before base load: This is before reaching the temperature range of 400-500 degrees Centigrade within the TES molten salt volume  69 . (500-600 degrees Centigrade, 2nd embodiment). 2. Post base load: After the temperature of the TES molten salt volume  69  reaches a range of 400-500 degrees Centigrade stabilized, sustained. (500-600 degrees Centigrade 2nd embodiment). 
     The data coming from these sensors would be monitored continuously by the computer and direct digital control (DDC). Before the base load and peak load operation conditions are reached, the computer would do the initialization with the following initialization fourth algorithm, based on the pre-radiation temperature of the upper surface  4   b  of the double surface container  4  that closely approximates an ideal blackbody radiator and infrared radiation temperature readouts. 
     The radiated state  75  of the upper surface  4   b  of the blackbody container  4  results in increasing the thermo-dynamic energy of the TES  69  and the non-radiation state wait periods  77 ; where radiation frequencies can be adjusted and all wait periods  77  are in terms of post-radiation  74  applied state upper surface  4   b,  container  4  temperature: (Power on-Initialization): 
       Do   (4);
     If (infrared emitters operate initially on reduced energy input phase from renewable source  1  and have completed reduced energy input phase).   

     Then; raise operational energy input to normal radiation level; 
     Else if (source is to be utility  2 ; get input energy from the utility grid  2 , then; raise operational energy input to radiation level);
     Frequency of radiation=Get frequency pre-radiation temperature  74  (To) of TES  69 ;   

     Activate infrared radiation Start (to);
     Stop infrared radiation when sensor  82  reads; (TES  69  temperature=500 C) End (t 1 );   (At the end of every radiated state  75 ; apply to+t 1  non-radiation wait state  77 );   

     Wait (frequency to+t 1 =radiated wait state  77 ); 
     While do 
     If (radiated temperature  75  of surfaces  4   c  or  4   b  of container  4 &lt;350 C);
     Frequency of radiation=A; (set to long period timer and high frequency), or;   Else if (working gas  33  temperature pre-container  68  volume spiral section  8  entry&lt;350 C);   Activate infrared radiation in container  68  volume until 40 percent working gas  33 =550 C;   

     Else if (radiated temperature  75  of surfaces  4   c  or  4   b  of the container  4 &lt;500 C);
     Frequency of radiation=C; (set to middle duration and middle frequency.) or;   

     Else if (TES  69  temperature&lt;300 C for a period exceeding preset time limit);
     Activate secondary infrared emitters  78  on TES  69  bottom concentric ring  67 ;   

     Else if (radiated temperature  75  of surfaces  4   c,    4   b  of container  4 &lt;550 C);
     Frequency of radiation=E (set to base load; optimal duration low frequency) and;   Activation frequency of infrared emitters  71  in cylindrical volume  68  for working gas  33 =Set to minimum frequency;   (Only activated for 30 percent, and for 100 percent if at peak load, of the working gas  33  in spiral section&lt;or equal to 350 C);   (For second embodiment: If radiated temperature  75  of surface  4   c  of container  4 =600 C);   Frequency of radiation=E; (set to base load; low frequency). (Repeat cycle).   

     The initialization and then gradually reaching the desired base load temperature of the TES  69  as a function of the radiated state  75  of upper surface  4   b  of container  4  stands at a temperature range of 350-550 degrees Centigrade, heated by radiation  75  temperature range of 450-650 degrees Centigrade and therefore the TES molten salt volume  69  long term temperature range of 400-550 degrees Centigrade gets stabilized due to specified time interval repeated radiant energy supply that would be provided by the infrared radiation members  3   a.    
     The maximum 550 degrees Centigrade of the TES and maximum 550 degrees Centigrade of surface of  4   b  periodically becomes equal for certain periods, hence this enables radiation  74 , a long term balanced pattern of energy input, which is for short intervals and with high energy efficiency. 
     Every time the two are equated; which can remain so for certain periods or are within the range of 500-550 degrees Centigrade for example, there is no need for radiation  74  input. Therefore, fast thermo-dynamic energy flow occurs when the average of the TES  69  is 400 degrees Centigrade or equal to 500 degrees Centigrade and surface  4   b  is 500-650 degrees Centigrade, 650 degrees Centigrade being a short term maximum, and periodic radiation  74  temperature is 650 degrees Centigrade for example. Wherein, this contributes thermo-dynamic energy input into at least one TES volume  69  by the double surface container  4 . 
     A lower range radiant energy within 400-500 degrees Centigrade with shorter duration radiation in the radiation closed container  4   a  is to be provided along with strong insulation of the TES  69 , once the TES  69  temperature gets stabilized at about 500 degrees Centigrade; thereby less energy is needed to keep TES  69  temperature stable. 
     Purified molten salt or combined molten salt or oil; both have a higher average density (kg/m), higher heat capacity (cal/C), higher average heat conductivity (W/m K), higher average heat capacity (kJ/kg K) and higher volume specific heat capacity (kWh/m) values than water, if once-one of these materials reach a high threshold temperature. Hence, one of these choices would establish a thermo-dynamic energy storage stability volume, once the threshold temperature is stabilized. 
     What is meant by “thermo-dynamic stability” as related to specific heat capacity defined by the following fifth formula: 
         c=Q /Delta  T/m    (5);
 
     where Q is expressed in calories, it is the fact that it would take considerably less energy for example, the (kcal) of heat-once a threshold of high temperature range gets stabilized, to raise or keep the temperature at a certain range of a said fluid mentioned above, while having minimized losses by strong insulation, as compared to heat input needed to raise the temperature by one Celsius degrees of another reservoir, of another element of equal mass. 
     After base load conditions are reached, the computer would start operational and monitoring functions with the sixth algorithm that is based on the TES  69  molten salt temperature instead of the pre-radiation molten salt TES  69 , and the radiated wait periods  78  and volume temperature readings thereafter, as follows: 
       While not stopped   (6);
     Temperature=TES ( 69 ) Temperature-T 1  (to);   Frequency of radiation=Get frequency (TES  69  Temperature);   

     Activate infrared radiation ( 74 ) Start (to); 
     Stop infrared radiation ( 74 ) End (t 1 ); 
     Wait (frequency to+t 1 =First period radiated state  75 ); 
     Temperature=TES ( 69 ) Temperature-T 2  (t 1 );
     Frequency of radiation=Get frequency (TES  69  Temperature);   

     Repeat Cycle for next radiation:
         Activate infrared radiation ( 74 ) Start (t 1 );   Stop infrared radiation ( 74 ) End (t 2 );   Wait (frequency to+t 1 =Second period radiated state  75 );   Power Generation=Get Power Output (e);   If (Power Output&gt;Optimal (e));       Frequency of radiation=E; (set to base load; low frequency).   

     If (Power Output&lt;Optimal (e));
     Frequency of radiation=C; (set to middle duration, middle frequency);   

     If (Heat generation for central heating&lt;Optimal; Temperature T);
     Frequency of radiation=C; (set to middle duration, middle frequency);   

     Else if (TES Temperature&gt;500 degrees Centigrade;
     (Second embodiment: Else if TES Temperature&gt;600 C);   Set frequency of radiation=G; (Overheated; Set to low frequency   

     until TES temperature=500 degrees Centigrade); or (optional); 
     Set frequency=I; (System overheats—second option: Full stop). 
     This system offers very important advantages as compared to combustion systems for example. The invention enables a fully secure control method against overheating accidents, as indicated in the last line of above algorithm. There is no risk of a disaster, no waste products; no exhaust heat loss. 
     Central Chilled-Water Air Conditioner Unit 
     The molten salt in the TES  69  has to be kept at a temperature range of 400-550 degrees Centigrade. Sodium freezes at 208 F (97.68 C, and remains liquid at 288 degrees Centigrade). Therefore, the TES volume  69  temperature must never decline below 350 degrees Centigrade. The hot TES volume  69  central air conditioner refrigerant  19  hot spiral coil  21  to be heated to 70 degrees Centigrade within the waste heat utilizing oil volume  20 , which surrounds ½ of the external cylindrical surface area  15  of the TES  69 . 
     In order to increase the pressure of the refrigerant  19 , mostly the waste heat of the TES  69  is utilized to increase temperature and thereby also the pressure of refrigerant gas  19  to 70 degrees Centigrade. to enable much shorter total compressor time, or absorption cooling is utilized. 
     Demand for service hot water is about the same in summer; energy is needed for service hot-water tank  13  throughout all seasons. Utilization of the waste heat from the TES volume  69  for both central air conditioning chilled-water unit  36  and to provide heat for the service hot-water tank  13 , and provide power with the steam turbines  27  and  30 , or of more units of turbines based on capacity, this combination makes the system to be utilized all year long efficiently. In summer; all of the working gas-steam  33  is available for power generation. 
     Return on investment would occur sooner, electricity can be sold on a contract basis to users outside of host facility, while satisfying air conditioning needs. 
     Investment Feasibility 
     Due to the feature of the complete independence from all types of combustion-fossil fuels and the ability to utilize both renewable and utility power as operational energy input, the system is very efficient and flexible. Thereby, the long term operational energy input cost becomes negligible. The organizer company would have the option to have a modular design and production method where the components can be made by one or several different expert companies with established economies of scale and these could be modularly assembled. The organizing company can have a relatively low capital intensive investment. Return on investment can be realized in a substantially shorter time, as the system could become efficiently operational with optimal system capacity utilization conditions much sooner as compared to comparable capacity combustion plants and due to high profit margins on system sales or on high profit rate leases. The system is suitable to provide onsite-decentralized customized solutions, enables diversification and provides high modularity and flexibility. Since there is no central heating demand in summer; power generation level would be maximized. This enhances faster return on investment, as electricity can be sold on contract basis to outside of host facility, while satisfying even peak load air conditioning. 
     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, and for the more than two combined system TES units, within the legitimate and valid scope of the amended claims, to be appropriately interpreted in accordance with the doctrine of equivalents. 
     The device and the methods mentioned heretofore have novel features resulting in a new device, method for high efficiency, and a second embodiment system of which the capacity can be increased modularly, that are not anticipated, rendered obvious, suggested, implied by prior art systems, alone or in any combination thereof.