Abstract:
This invention, a waste heat recycling thermal power plant ( 1000 ), extracts heat from the environment, and concentrates this heat to produce a cfc super-ambient temperature heat source ( 1330 ) having an elevated temperature sufficient to supply a useable heat flow to an incorporated heat engine (e.g., Rankine cycle, Stirling cycle, Seebeck cycle, etc.) flow circuit ( 1400 ). Further, waste heat recycling thermal power plant ( 1000 ) produces an sfc sub-ambient temperature heat sink ( 1250 ), thus increasing the applied temperature differential, thereby permitting the thermal efficiency of ihefc pressure expansion device ( 1460 ) to be increased as well. Lastly, waste heat recycling thermal power plant ( 1000 ) captures for reuse, much of the waste heat that its own operation liberates, thus lowering its net energy utilization per unit of mechanical power produced (a.k.a., heat rate, Btu/kwhr). In the main embodiment of its use, waste heat recycling thermal power plant ( 1000 ) would be used as the driver for a mod driven mechanical device ( 1520 ), specifically an electrical generator. Deriving its source heat by intercepting the heat that would be rejected to the environment by an electrical power generating station&#39;s cooling device, and routing this heat to waste heat recycling thermal power plant ( 1000 ). Then converting this heat to mechanical power, and subsequently to electrical power. This would result in an improvement of the electrical power generating station&#39;s net electrical power generating capacity and fuel efficiency, while simultaneously reducing the quantity of thermal (and potentially chemical) pollution released to the environment.

Description:
BACKGROUND OF THE INVENTION 
   1. Field of the Invention 
   This invention relates to the field of thermal power plants, specifically of the type that recycle a significant portion of the heat that is normally rejected to the environment by “conventional” thermal power plants. 
   2. Description of the Prior Art 
   A search of the prior art reveals numerous inventions that attempt to improve the efficiency of various types (e.g., Rankine cycle, Stirling cycle, Brayton cycle, Otto cycle, Diesel cycle, Seebeck cycle, etc.) of heat engines and the thermal power plants in which they are contained. 
   In 1824, Nicolas Leonard “Sadi” Carnot, a French engineer and founder of the discipline now known as “Thermodynamics,” published his treatise ( Reflexions sur la puissance motrice du feu et sur les machines propres a developper cette puissance ) on the nature of heat engines. The relevant finding of this paper was that all heat engines, in order to function, first receive heat from a “high-temperature” heat source, and then must reject heat (i.e., unused heat, a.k.a. waste heat) to a “low-temperature” heat sink. He also gave us what is now known as the “Carnot Efficiency,” which states that the efficiency of a heat engine is improved as the temperature differential between the heat source and the heat sink is increased. In the decades that followed, others expanded upon and clarified our understanding of the nature of heat, and how best to employ it in heat engines. Most notable among them was an engineering professor from Scotland named William J. M. Rankine, who in 1859, published his treatise ( Manual of the Steam Engine and Other Prime Movers ) relating to heat engines, wherein he described what is now known as the “Rankine cycle.” Later, still others expanded upon the ideas postulated by Prof Rankine, a process that continues to the present day. 
   The Rankine cycle itself is inherently inefficient, yet it has attributes, which have caused it to become one of the leading forms of heat engine cycles employed today. First, the Rankine cycle is well understood by the designers and users of power generation equipment. Second, the Rankine cycle lends itself well to the employment of very large and therefore very cost-effective components. Third, with the exception of “hydro-power” nothing can produce electrical power less expensively than a modern electrical power generating station employing a “modified” Rankine cycle. 
   The latest attempts to improve upon the Rankine cycle employ various forms of “co-generation;” i.e., they attempt to convert a portion of the waste heat rejected by a “host” heat engine into additional electrical power, industrial process heating, and/or air conditioning capacity. The latter two approaches, while beneficial are not very practical, for it is a rare or non-existent industrial process that would require all of the waste heat being liberated by the “host” heat engine. Similarly, the air conditioning capacity approach, while quite ingenious, has two burdens hindering its widespread use, first the “host” heat engine needs to be located near the facility to be cooled, and second, air conditioning is not a “stable” demand (i.e., high demand in the summer, and low demand in the winter). Which leaves the additional electrical power approach as the only economically viable method for improving the efficiency of thermal power plants. 
   There exists a class of heat engines known as “Bottoming Cycle Heat Engines,” many of which include components referred to as “Heat Recovery Steam Generators” or HRSG&#39;s. Essentially, their designers have placed a second Rankine cycle heat engine in the waste heat stream of the “host” heat engine, and while it is the “environmentally friendly” thing to do, financially it is not very attractive. This approach is costly and does not provide the kind of returns that most electric utility shareholders are looking for on the bottom line of their financial statements. 
   One of the principal reasons for the resistance to these devices is that they involve extensive and therefore expensive redesigns of existing facilities; as a result they are not being widely used to rehabilitate older power plants. New facilities, currently under construction, are just now starting to incorporate some of these design elements, yet the larger opportunity is to retrofit the worldwide base of currently operating electrical power generating facilities. To do this, a design approach that accomplishes the following key points must be employed: the design must be environmentally friendly, the design must not require expensive changes to the “host” facility, the design must be reliable, and the design must produce an acceptable financial return. Such a design will meet with success, to date, not a single example of the prior art has satisfied all of these requirements. 
   BRIEF SUMMARY OF THE INVENTION 
   1. Overview 
   In accordance with the present invention a waste heat recycling thermal power plant comprises a multitude of interacting volatile working fluid(s) circuits that generate a thermal potential between itself and an employable external heat source, extracting useable heat from that heat source (to replace the heat converted to mechanical energy or otherwise lost from the system), generating a super-ambient temperature heat source and a sub-ambient temperature heat sink, whose thermal potential is capable of providing a useable heat flow to fuel its incorporated heat engine, recycling collected system thermal losses and much of the useable heat flow that is rejected by its incorporated heat engine to its super-ambient temperature heat source, and the resultant mechanical power output produced by its incorporated heat engine is employed to drive a mechanical load (e.g., gearbox, electrical generator, propeller shaft, etc.). 
   2. Objects &amp; Advantages 
   Accordingly, several objects and advantages of the present invention are:
         (a) to provide a thermal power plant which can capture and reuse much of the waste heat that its own operation liberates;   (b) to provide a thermal power plant which can extract useable heat from the environment;   (c) to provide a thermal power plant which can extract useable heat from a “low-temperature” external heat source;   (d) to provide a thermal power plant which can extract useable heat utilizing a small thermal potential;   (e) to provide a thermal power plant, which can extract useable heat from the waste heat that is rejected by a “host” heat engine;   (f) to provide a thermal power plant which can create a thermal potential between itself and an employable external heat source;   (g) to provide a thermal power plant which having created a thermal potential between itself and an employable external heat source, can utilize the heat extracted from that external heat source to fuel its own operation;   (h) to provide a thermal power plant which can concentrate the extracted heat to generate a super-ambient temperature heat source to supply a useable heat flow to its incorporated heat engine;   (i) to provide a thermal power plant which can generate a sub-ambient pressure region sufficient to evaporate a portion of its liquid working fluid flow at a sub-ambient temperature, thus creating a sub-ambient temperature heat sink for its incorporated heat engine;   (j) to provide a thermal power plant which can supply a useable heat flow between its super-ambient temperature heat source and its sub-ambient temperature heat sink, sufficient to fuel its incorporated heat engine;   (k) to provide a thermal power plant which can produce mechanical power in excess of its own operational requirements, sufficient to drive an electrical generator;   (l) to provide a thermal power plant which can produce electrical power in excess of its own operational requirements, sufficient to provide electrical power to the local electrical power distribution grid;   (m) to provide a thermal power plant which can improve the thermal efficiency of the “host” heat engine by lowering the temperature of the host&#39;s heat sink;   (n) to provide a thermal power plant which can improve the fuel efficiency of the “host” heat engine by allowing the “host” to operate at a lower power level while still meeting the electrical demand;   (o) to provide a thermal power plant which can reduce the amount of chemical pollution released to the environment by allowing the “host” heat engine, or an allied heat engine located elsewhere on the electrical grid, to operate at a lower power level while still meeting the electrical demand; and   (p) to provide a thermal power plant which can increase the output capacity of the “host” engine by adding its electrical output to that of the host&#39;s electrical output.       

   Further objects and advantages are to provide: a thermal power plant that is environmentally friendly, one that will not require expensive modifications to the “host” facility, one that will operate reliably over its operational life-span, and one that will produce an acceptable financial return on its owner&#39;s investment. Still further objects and advantages will become apparent from a consideration of the ensuing description and drawings. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
       FIG. 1A  shows the main embodiment of the waste heat recycling thermal power plant  1000 . 
       FIG. 1B  shows the motive flow circuit  1100  of the main embodiment of the waste heat recycling thermal power plant  1000 . 
       FIG. 1C  shows the suction flow circuit  1200  of the main embodiment of the waste heat recycling thermal power plant  1000 . 
       FIG. 1D  shows the conjoined flow circuit  1300  of the main embodiment of the waste heat recycling thermal power plant  1000 . 
       FIG. 1E  shows the incorporated heat engine flow circuit  1400  of the main embodiment of the waste heat recycling thermal power plant  1000 . 
       FIG. 1F  shows the mechanical output device  1500  of the main embodiment of the waste heat recycling thermal power plant  1000 . 
       FIG. 1G  shows the heat recovery flow circuit  1600  of the main embodiment of the waste heat recycling thermal power plant  1000 . 
       FIG. 1H  shows the heat source flow circuit  1700  of the main embodiment of the waste heat recycling thermal power plant  1000 . 
       FIG. 2A  shows an alternative embodiment of the waste heat recycling thermal power plant  1000  (which details a different arrangement of components within the suction flow circuit). 
       FIG. 2B  shows the suction flow circuit  1200  of an alternative embodiment of the waste heat recycling thermal power plant  1000 . 
   

   DETAILED DESCRIPTION 
   1. Main Embodiment—Physical Layout 
   A waste heat recycling thermal power plant  1000  ( FIG. 1A ) consists primarily of two conjoined circuits, a motive flow circuit  1100  and a suction flow circuit  1200  of a volatile working fluid (the conjoined portions of motive flow circuit  1100  and suction flow circuit  1200  are identified as a conjoined flow circuit  1300 ). Additionally, waste heat recycling thermal power plant  1000  includes an incorporated heat engine flow circuit  1400  connected to a mechanical output device  1500 , a heat recovery flow circuit  1600  (optional, a heat source flow circuit  1700 , and the subcomponents contained therein. These circuits and their subcomponents are described below; the interconnecting piping/ducting is described only where necessary to add clarity to the description. 
   Motive flow circuit  1100  ( FIG. 1B ) which originates at a cfd flow separation chamber  1340 - 30 , and successively flows through: a cfd motive flow discharge  1340 - 40 , an mfc fluid transfer device  1120 , an mfc fluid filtering device  1130  (optional), an mfc fluid flow-regulating device  1140 , and discharges to conjoined flow circuit  1300  via a cfc sub-ambient pressure generating device  1320 , which completes the circuit. 
   Suction flow circuit  1200  ( FIG. 1C ) which originates at a cfd flow separation chamber  1340 - 30 , and successively flows through: a cfd suction flow discharge  1340 - 50 , an sfc fluid flow-regulating device  1220 , an sfc sfc-hsfc heat recycling heat transfer device  1230 , an sfc shrd-ssths fluid transfer device  1240  [which contains: an ssftd sfc working fluid inlet  1240 - 15 , an ssftd shrd excess working fluid inlet  1240 - 20 , an ssftd cssd overpressure relief device working fluid inlet  1240 - 30 , an ssftd suction chamber  1240 - 35 , and an ssftd working fluid discharge  1240 - 40 ], an sfc sub-ambient temperature heat sink  1250  [which contains: an ssths ihefc-sfc evaporative heat transfer device  1250 - 20 , an ssths liquid/vapor separation device  1250 - 30  (optional), and an ssths ihefc-sfc evaporative heat transfer device pressure-regulating device  1250 - 40 ], an shrd hsfc-sfc evaporative heat transfer device ssths vapor supply device  1260 , an shrd hsfc-sfc evaporative heat transfer device liquid supply device  1270 , an sfc heat replenishment device  1280  [which contains: an shrd hsfc-sfc evaporative heat transfer device  1280 - 20 , an shrd liquid/vapor separation device  1280 - 30  (optional), an shrd hsfc-sfc super-heat heat transfer device  1280 - 40  (optional), and an shrd hsfc-sfc evaporative heat transfer device pressure-regulating device  1280 - 50 ], an sfc shrd-cspgd vapor transfer device  1290 , an sfc shrd-ssftd excess tertiary liquid component transfer device  1295 , and discharges to conjoined flow circuit  1300  via cfc sub-ambient pressure generating device  1320 , which completes the circuit. 
   Conjoined flow circuit  1300  ( FIG. 1D ) which originates at a cspgd suction chamber  1320 - 40 , and successively flows through: a cspgd conjoined flow discharge  1320 - 50 , a cfc super-ambient temperature heat source  1330  [which contains: a csths super-heat heat transfer device  1330 - 20 A (optional), a csths boiler heating device  1330 - 20 B, and a csths feed-heat heat transfer device  1330 - 20 C (optional)]], a cfc flow divider  1340  [which contains: a cfd conjoined flow inlet  1340 - 20 , a cfd flow separation chamber  1340 - 30 , a cfd motive flow discharge  1340 - 40 , or a cfd suction flow discharge  1340 - 50 , or a cfd fluid import/export device  1340 - 60 ], a cfc safety/service device  1350  [which contains: a cssd fluid thermal expansion device  1350 - 20 , a cssd overpressure relief device  1350 - 30 , and a cssd venting/servicing device  1350 - 40 ], and discharges to motive flow circuit  1100  and suction flow circuit  1200  via cfc flow divider  1350 , which completes the circuit. 
   Incorporated heat engine flow circuit  1400  ( FIG. 1E ) which originates at the inlet of an ihefc fluid transfer device  1420  (optional, not required if utilizing gravity-induced circulation), and successively flows through: an ihefc fluid transfer device  1420  (optional), an ihefc super-ambient temperature heat source  1430  [which contains: an isths feed-heat heat transfer device  1430 - 20 A (optional), an isths ihefc starting device  1430 - 20 B (optional), an isths boiler  1430 - 20 C, an isths liquid/vapor separation device  1430 - 20 D (optional), and an isths super-heat heat transfer device  1430 - 20 E (optional)]], an ihefc vapor export device  1440  [which contains: an ived ihefc working fluid inlet  1440 - 20 , an ived flow separation chamber  1440 - 30 , an ived overpressure relief device working fluid discharge  1440 - 40 , and an ived ipedlc working fluid discharge  1440 - 50 ], an ihefc fluid flow-regulating device  1450 , an ihefe pressure expansion device  1460  (e.g., Rankine cycle vapor turbine), an ihefc sub-ambient temperature heat sink  1470  [which contains: an isths ihefc-sfc condensing heat transfer device  1470 - 20 , and an isths venting/servicing device  1470 - 30 ], and an ihefc fluid storage device  1415 , which completes the circuit. 
   An ihefc pressure expansion device lubrication circuit  1480  (optional) augments the incorporated heat engine flow circuit  1400 . Ihefc pressure expansion device lubrication circuit  1480  [optional, which contains: an ipedlc pressure-regulating device  1480 - 20 , an ipedlc vapor bearing device  1480 - 30 , and an ipedlc vapor flow-regulating device  1480 - 40 ], bypasses around the ihefc fluid flow-regulating device  1450  and the ihefc pressure expansion device  1460 , via an ihefc vapor export device  1440  and an ihefc fluid return device  1490  [which contains: an ifrd ihefc overpressure relief device working fluid inlet  1490 - 20 , an ifrd ipedlc working fluid inlet  1490 - 30 , an ifrd flow collecting chamber  1490 - 40 , and an ifrd isths ihefc-sfc condensing heat transfer device working fluid discharge  1490 - 50 ]. In addition, an ihefc overpressure relief device  1485  is interposed between the ihefc vapor export device  1440  and the ihefc fluid return device  1490 . 
   Mechanical output device  1500  ( FIG. 1F ) is connected to incorporated heat engine flow circuit  1400 . Specifically, a mod driven mechanical device  1520  (e.g., gearbox, generator, propeller shaft, etc.) is connected to incorporated heat engine flow circuit  1400 &#39;s ihefc pressure expansion device  1460  via a mod hermetic power coupling device  1510 A (omit if  1510 B is utilized) or a mod intermediate drive shaft with shaft sealing device  1510 B (omit if  1510 A is utilized), which completes the device. 
   Heat recovery flow circuit  1600  (optional,  FIG. 1G ) originates at the inlet of an hrfc ventilation motive device  1620 , and successively flows through: an hrfc ventilation motive device  1620 , an hrfc machinery space  1630  [which contains: an hms exposed surfaces  1630 - 20  (i.e., floor, walls, ceiling, equipment, piping, etc.), and an hms overpressure relief device  1630 - 30  (discharges to the environment)], an hms cooling distribution device  1640  [optional which includes: an hcdd working fluid inlet  1640 - 20 , an hcdd distribution device  1640 - 30 (x) (one channel for each unit that requires cooling, “x”—the designation changes for each unit), an hcdd cooled machinery unit  1640 - 40 (x) (“x”—the designation changes for each unit), and an hcdd cooling exhaust collection device  164650 (x) (“x”—designation changes for each unit)], an hrfc heat recycling heat transfer device  1650  [which contains: an hhrhtd hrfc-hsfc heat recycling evaporative heat transfer device  1650 - 20 , and an hhrhtd hrfc-sfc heat recycling condensing heat transfer device  1650 - 30 , and an hhrhtd working fluid storage device  1650 - 40 ], which completes the circuit. 
   Heat source flow circuit  1700  ( FIG. 1H ) originates at the inlet of an hsfc fluid transfer device  1720  (optional, not required if utilizing gravity-induced circulation), and successively flows through: an hsfc fluid transfer device  1720  (optional), an hsfc fluid filtering device  1730  (optional), an hsfc fluid import/export device  1740 , an hsfc safety/service device  1750  [which contains: an hssm fluid thermal expansion device  1750 - 20 , an hssm overpressure relief device  1750 - 30 , and an hssm venting/servicing device  1750 - 40 ], an hsfc heat source heat transfer device  1760 , an hsfc sfc-hsfc heat recycling heat transfer device  1770 , an hsfc hrfc-hsfc heat recycling heat transfer device  1780 , an hsfc hsfc-sfc super-heat heat transfer device  1785  (optional), an hsfc hsfc-sfc evaporative heat transfer device  1790 , an hsfc hsfc-sfc heat transfer device working fluid discharge temperature-regulating device  1795 , and an hsfc fluid return device  1715 , which completes the circuit. 
   In additions the circuits are constructed of materials suitable for containing the working fluid in each circuit (i.e., chemically compatible, and capable of withstanding the operating conditions imposed by the operation of waste heat recycling thermal power plant  1000 ). 
   Note: Other types of heat engines may be utilized in lieu of the example Rankine cycle vapor turbine unit described above (e.g., Stirling cycle engine, Seebeck cycle thermoelectric generator, etc.). Any heat engine, which is capable of employing the developed temperature differential, may be interposed between cfc super-ambient temperature heat source  1330  and sfc sub-ambient temperature heat sink  1250 . Depending upon the characteristics of the alternative heat engine, and the working fluid(s) utilized, configuration changes may be required (i.e., the routing of conjoined flow circuit  1300  through cfc super-ambient temperature heat source  1330  and suction flow circuit  1200  through sfc sub-ambient heat sink  1250  may need to be altered). In the forgoing, “ambient” refers to the conditions (in terms of absolute pressure and absolute temperature) at cfd flow separation chamber  1340 - 30 , this reference point (a.k.a., an ambient conditions datum), depending upon the characteristics of the working fluid utilized in conjoined flow circuit  1300 , could differ substantially from standard atmospheric conditions (i.e., 14.696 psia and 536.67 deg-R). 
   2. Main Embodiment—Operation 
   Every heat engine requires a source of heat to operate, typically it is a hydrocarbon-based fuel that is burned in order to release the energy stored in the substance&#39;s inter-atomic chemical bonds. Depending upon the type of heat engine in question, it is normal for a large portion of the heat provided to such engines to be rejected to the environment (i.e., wasted, having performed no useful work). This has been the state of the art since the first recorded example of a heat engine (in the first century AD, Hero of Alexandria, Egypt is said to have described his Aeolipile, a rudimentary steam turbine). To be sure, the state of the art has improved much over the intervening centuries, yet it remains an unbreakable rule (i.e., the Second Law of Thermodynamics) that all heat engines must reject heat in order to function, and waste heat recycling thermal power plant  1000  is no different in this regard. What is different is the proportion of heat rejected, and the methodology employed to conserve and reuse much of the heat that is rejected in a typical heat engine. 
   Waste heat recycling thermal power plant  1000  ( FIG. 1A ) utilizes the interaction of motive flow circuit  1100 , suction flow circuit  1200 , conjoined flow circuit  1300 , incorporated heat engine flow circuit  1400 , mechanical output device  1500 , heat recovery flow circuit  1600  (optional), and heat source flow circuit  1700  to capture and reuse much of the waste heat that its own operation liberates. What follows is an examination of those interactions. 
   Heat source flow circuit  1700  ( FIG. 1H ) performs four essential functions in the operation of waste heat recycling thermal power plant  1000 . First, it acquires replenishment heat (i.e., replacing the heat that is converted to mechanical energy or lost from the system) from the external heat source(s) (e.g., geothermal pool, solar collector, river, industrial process cooling water, etc.) via hsfc heat source heat transfer device  1760 . Second, it receives recyclable heat (i.e., heat that is wasted in a typical heat engine) from suction flow circuit  1200  via hsfc sfc-hsfc heat recycling heat transfer device  1770 , and the heat recovery flow circuit  1600  (optional) via hfsc hrfc-hsfc heat recycling heat transfer device  1780  (optional). Third, it transports this heat (replenishment and recycled) to hsfc hfsc-sfc super-heat heat transfer device  1785  (optional) and hsfc hfsc-sfc evaporative heat transfer device  1790 . Fourth, it provides “chilled” working fluid to hsfc heat source heat transfer device  1760 . 
   The working fluid in heat source flow circuit  1700  is motivated by hsfc fluid transfer device  1720  (optional, not required if utilizing gravity-induced circulation), filtered by hsfc fluid filtering device  1730  (optional), and its flow is controlled by hsfc hsfc-sfc evaporative heat transfer device working fluid discharge temperature-regulating device  1795 . This last element acts to increase the flow of hsfc working fluid  1710  in heat source flow circuit  1700  when hsfc hsfc-sfc evaporative heat transfer device  1790  discharge temperature decreases below the desired operating point, conversely it acts to decrease hsfc working fluid  1710  flow when the discharge temperature rises above the desired operating point (the desired operating point is user adjustable). 
   The remaining enumerated subcomponents of heat source flow circuit  1700  serve to protect the circuit itself from the hydraulic hazards associated with fluids in confined spaces (i.e., thermal expansion, and over-pressurization), as well as providing a way to add/remove working fluid to/from the circuit. 
   Heat recovery flow circuit  1600  (optional,  FIG. 1G , omit if  1780  is not utilized) performs four essential functions in the operation of waste heat recycling thermal power plant  1000 . First, it receives recyclable heat from the heat liberating machinery units (e.g., gearbox, electric generator, electric motor(s), etc.) in hrfc machinery space  1630 . Second, it receives recyclable heat lost from hotter portions of the system [i.e., system heat lost to the surrounding environment by hms exposed surfaces  1630 - 20  (i.e., floor, walls, ceiling, equipment, piping, etc.), in this case the heat is “lost” to hrfc machinery space  1630 ]. Note: heat lost by hrfc machinery space  1630  to the environment is non-recoverable; however, this loss may be minimized and/or partially offset by passive solar gain during the warmest portions of the year. Third, it transports this recycled heat to hsfc hrfc-hsfc heat recycling heat transfer device  1780  (optional) via hrfc heat recycling heat transfer device  1650 . Fourth, it provides “chilled” working fluid to hcdd working fluid inlet  1640 - 20 . 
   The working fluid in heat recovery flow circuit  1600  is motivated by gravity-induced circulation; further, this circulation is augmented with hrfc ventilation motive device  1620 , and the flow of hrfc working fluid  1610  is controlled by the operation of the previous element. Hrfc ventilation device  1620  is operated at maximum output to increase the flow of hrfc working fluid  1610  in order to reduce the temperature in hrfc machinery space  1630 , minimum output is utilized to decrease the flow and increase the temperature to the desired level, intermediate output levels are utilized to maintain the temperature at the desired level, once that temperature is attained (the desired operating point is user adjustable). 
   As heated gas tends to rise, hcdd working fluid inlet  1640 - 20  is located near the ceiling of hrfc machinery space  1630  from there hms working fluid  1640 - 10  is conducted via hms cooling distribution device  1640  [optional, which contains: an hcdd working fluid inlet  1640 - 20 , hcdd distribution device  1640 - 30 (x) (one channel for each heat generating device, “x”—designation changes for each unit) conducts hms working fluid  1640 - 10  to hcdd cooled machinery unit  1640 - 40 (x) (“x”—designation changes for each unit) where it receives recyclable heat liberated by the operation of the cooled machinery unit, next hcdd machinery cooling exhaust collection device  1640 - 50 (x) (“x” designation changes for each unit) conducts the heated hms working fluid  1640 - 10  via chimney effect to hrfc heat recycling heat transfer device  1650 ]. The collected heat conducted to hrfc heat recycling device  1650  is transported to hsfc hrfc-hsfc heat recycling heat transfer device  1780  (optional) via hhrhtd hrfc-hsfc heat recycling evaporative heat transfer device  1650 - 20 , and an hhrhtd hrfc-hsfc heat recycling condensing heat transfer device  1650 - 30 . Note: were a single operating point possible, this interconnection could be achieved more efficiently with a liquid-to-liquid heat transfer device; however, that type of operating environment is unlikely, and this evaporative/condensing interface provides a self-adjusting heat transfer device (i.e., the evaporative temperature will rise/fall on its own until the rate of evaporation is equal to the rate of condensation, and a new heat transfer equilibrium is established). 
   In addition, hrfc machinery space  1630  is protected from over-pressurization damage by hms overpressure relief device  1630 - 30  (discharges to the environment), such damage is possible in the event of a catastrophic loss of working fluid containment and the resultant flashing of the working fluid to vapor, although the working fluid temperatures and pressures envisioned make this an extremely remote possibility. 
   Suction flow circuit  1200  ( FIG. 1C ) performs seven essential functions in the operation of waste heat recycling thermal power plant  1000 . First, it provides recyclable heat to heat source flow circuit  1700  via sfc sfc-hsfc heat recycling heat transfer device  1230 . Second, it utilizes residual sfc working fluid  1210  pressure to operate sfc shrd-ssths fluid transfer device  1240 , this element draws excess working fluid from shrd hsfc-sfc evaporative heat transfer device  1280 - 20  and along with sfc working fluid  1210  supplied via sfc sfc-hsfc heat recycling heat transfer device  1230  combines to provide vigorous circulation within the heat transfer passages of sfc sub-ambient temperature heat sink  1250 , and sfc heat replenishment device  1280 . Third, it receives recyclable heat (i.e., waste heat in a typical heat engine) from sfc sub-ambient temperature heat sink  1250 , this occurs specifically in ssths ihefc-sfc evaporative heat transfer device  1250 - 20 , where much of ssths working fluid  1250 - 10  admitted is converted to vapor. The portion of ssths working fluid  1250 - 10  that remains in liquid form is transported to sfc heat replenishment device  1280  via shrd hsfc-sfc evaporative heat transfer device ssths liquid supply device  1270 . The portion of ssths working fluid  1250 - 10  that is converted to vapor is transported to sfc heat replenishment device  1280  via shrd hsfc-sfc evaporative heat transfer device ssths vapor supply device  1260 , where it combines with the vapor formed in shrd hsfc-sfc evaporative heat transfer device  1280 - 20 , then through ssths liquid/vapor separation device  1250 - 30  (optional), ssths ihefc-sfc evaporative heat transfer device pressure-regulating device  1250 - 40 . Fourth, it receives replenishment heat (i.e., replacing the heat converted to mechanical energy or lost from the system) from heat source flow circuit  1700  via shrd hsfc-sfc evaporative heat transfer device  1280 - 20  and shrd hsfc-sfc super-heat heat transfer device  1280 - 40  (optional). Fifth, it transports super-heated vapor to cfc sub-ambient pressure generating device  1320  via shrd liquid/vapor separation device  1280 - 30  (optional), shrd hsfc-sfc super-heat heat transfer device  1280 - 40  (optional), shrd hsfc-sfc evaporative heat transfer device pressure-regulating device  1280 - 50 , and sfc shrd-cspgd vapor transfer device  1290 . Sixth, it provides the heat (i.e., latent heat of vaporization and super-heat contained within the super-heated vapor) required to increase the temperature of mfc working fluid  1110  to that observed at the discharge of cfc sub-ambient pressure generating device  1320 . Seventh, it provides working fluid to conjoined flow circuit  1300 . 
   Sfc working fluid  1210  flow is motivated by the pressure differential between cfd flow separation chamber  1340 - 30  and cspgd suction chamber  1320 - 40 , and its flow is controlled by sfc fluid flow-regulating device  1220 . Note: by producing a region of sub-ambient pressure, cfc sub-ambient pressure generating device  1320  enables the pressure-regulating devices ( 1250 - 40  &amp;  1280 - 50 ) to regulate the pressure of their respective evaporative heat transfer devices ( 1250 - 20  &amp;  1280 - 20 ) by controlling the flow of working fluid vapor flow that exits their respective evaporative heat transfer device. This has an added benefit to the operation of waste heat recycling thermal power plant  1000 ; precision regulation of these evaporating pressures also produces precise control of the temperatures within the respective evaporative heat transfer device ( 1250 - 20  &amp;  1280 - 20 ). 
   Motive flow circuit  1100  ( FIG. 1B ) performs four essential functions in the operation of waste heat recycling thermal power plant  1000 . First, it produces the pressure differential that is responsible for motivating all working fluid flow in motive flow circuit  1100 , suction flow circuit  1200 , and conjoined flow circuit  1300 . Second, it filters (if so configured) all the working fluids in those same circuits. Third, it provides the high-pressure working fluid to cfc sub-ambient pressure generating device  1320  that is required to generate a region of sub-ambient pressure in cspgd suction chamber  1320 - 40 . Fourth, it provides working fluid to conjoined flow circuit  1300 . 
   Mfc working fluid  1110  is motivated by mfc fluid transfer device  1120 , is filtered by mfc fluid filtering device  1130  (optional), and its flow is controlled by mfc fluid flow-regulating device  1140 . The previous element acts to decrease mfc working fluid  1110  flow, when the flow exceeds the desired operating point, and conversely it acts to increase the flow, when the flow is below the desired operating point (the desired operating point is user adjustable). 
   Conjoined flow circuit  1300  ( FIG. 1D ) performs four essential functions in the operation of waste heat recycling thermal power plant  1000 . First, it receives high-pressure liquid from motive flow circuit  1100  and super-heated vapor from suction flow circuit  1200 , and combines these flows to produce the high temperature liquid working fluid flow discharged from cfc sub-ambient pressure generating device  1320 . Second, it transports this thermal energy-rich liquid working fluid flow to cfc super-ambient temperature heat source  1330  where it supplies heat to ihefc super-ambient temperature heat source  1430 . Third, it provides working fluid to motive flow circuit  1100  and suction flow circuit  1200 . Fourth, via cssd thermal expansion device  1350 - 20  it is possible to adjust the “ambient” pressure experienced at cfd flow separation chamber  1340 - 30 . 
   Cfc working fluid  1310  flow is motivated by the pressure differential between cspgd conjoined flow discharge  1320 - 50  and cfd flow separation chamber  1340 - 30 , and is controlled by the resistance to flow inherent in the same circuit (i.e., depending upon configuration, multiple indirect heat transfer devices impede the flow of the working fluid). Note: the pressure differential generated between  1320 - 50  &amp;  1340 - 30  will rise/fall on its own until the rate at which working fluid leaves the conjoined flow circuit  1300  is equal to the rate at which working fluid enters the same circuit, thus establishing a new mass transfer equilibrium. 
   Cssd overpressure relief device  1350 - 30  is interposed between cfd flow separation chamber  1340 - 30  and ssftd cssd overpressure relief device working fluid inlet  1240 - 30 , in the event of an overpressure condition this element would allow excess working fluid to be routed to ssths ihefc-sfc evaporative heat transfer device  1250 - 20 , which has a surge capacity. Cssd venting/servicing device  1350 - 40  allows for adding/removing working fluid to/from conjoined flow circuit  1300 . 
   Incorporated heat engine flow circuit  1400  ( FIG. 1E ) performs six essential functions in the operation of waste heat recycling thermal power plant  1000 . First, it receives heat from conjoined flow circuit  1300  via ihefc super-ambient temperature heat source  1430 . Second, it transports this heat to ihefc pressure expansion device  1460  via ihefc fluid flow-regulating device  1450 . Third, it produces mechanical power by pressure expanding ihefc working fluid  1410  in ihefc pressure expansion device  1460  (e.g., Rankine cycle vapor turbine). Fourth, it rejects recyclable heat to suction flow circuit  1200  via ihefc sub-ambient temperature heat sink  1470 . Fifth, it provides a hermetic circuit to lubricate ihefc pressure expansion device  1460  via ihefc pressure expansion device lubricating circuit  1480  (optional). Sixth, it provides working fluid to ihefc super-ambient heat source  1430  [this function can be accomplished utilizing gravity-induced circulation, augmented with or supplanted by, ihefc fluid transfer device  1420  (optional)]. 
   The remaining enumerated subcomponents of incorporated heat engine flow circuit  1400  serve to protect the circuit itself from the hydraulic hazards associated with fluids in confined spaces (i.e., thermal expansion, and over-pressurization), as well as providing a device to add/remove working fluid to/from the circuit. 
   Mechanical output device  1500  ( FIG. 1F ) performs four essential functions in the operation of waste heat recycling thermal power plant  1000 . First, it receives the mechanical power produced by ihefc pressure expansion device  1460 . Second, it transmits this mechanical power to hrfc machinery space  1630  via mod hermetic power coupling  1510 A or mod intermediate drive shaft with shaft sealing device  1510 B. Third, it provides mechanical power to mod driven mechanical device  1520  (e.g., gearbox, generator, propeller shaft, etc.). Fourth, it provides recyclable heat to heat recovery flow circuit  1600  via hrfc heat recycling heat transfer device  1650 . 
   To review, the operation of waste heat recycling thermal power plant  1000  (FIG.  1 A), requires heat source flow circuit  1700  to acquire and transport replenishment heat in sufficient quantity to replace all of the heat that is converted to mechanical energy or lost from the system. This heat is then transferred to suction flow circuit  1200  where it completes the evaporation of sfc working fluid  1210  flow, and super-heats the entire shrd hsfc-sfc evaporative heat transfer device pressure-regulating device  1280 - 50  inlet flow (i.e., all of the liquid working fluid provided to suction flow circuit  1200  from conjoined flow circuit  1300  is returned to conjoined flow circuit  1300  from suction flow circuit  1200  in the form of super-heated vapor). This super-heated vapor then combines with liquid from motive flow circuit  1100  in cfc sub-ambient pressure generating device  1320  to produce a thermal energy-rich liquid working fluid flow which is provided to cfc super-ambient temperature heat source  1330 . This heat is then supplied to ihefc flow circuit  1400  where a portion of it is converted to mechanical power by ihefc pressure expansion device  1460 . This mechanical power is then transmitted via mechanical output device  1500  to mod driven mechanical device  1520  (e.g., gearbox, generator, propeller shaft, etc.) to drive a mechanical load. Wherever feasible, waste heat recycling thermal power plant  1000 , captures and reuses substantial portions of the waste heat that its own operation liberates, in particular the heat rejected to sfc sub-ambient temperature heat sink  1250  by incorporated heat engine flow circuit  1400 , thus lowering its net energy utilization per unit of mechanical power produced. 
   3. Alternative Embodiments—Physical Layout &amp; Operation 
   The basic embodiment of the waste heat recycling thermal power plant  1000  is similar to the main embodiment, the differences being that none of the optional components installed in the main embodiment are utilized in the basic embodiment. The operation of the basic embodiment is also similar to that of the main embodiment; however, the functions performed by the optional components installed in the main embodiment are not performed at all, or not performed as well in the basic embodiment. 
   One alternative embodiment of the waste heat recycling thermal power plant  1000  utilizes a reconfigured suction flow circuit (FIG.  2 A). This approach combines most of the functions that are performed by sfc sub-ambient temperature heat sink  1250  and sfc heat replenishment device  1280  of the main embodiment ( FIG. 1C ) into a single device (FIG.  2 B). Further, it eliminates one evaporation process and the need for a device to control that process&#39; evaporation pressure. The operation of the alternative embodiment is also similar to that of the main embodiment; however, its reconfigured suction flow circuit  1200  can produce a colder heat sink temperature than that of the main embodiment. This alternative embodiment has much to recommend its adoption over that of the main embodiment. 
   Other alternative embodiments involve: rerouting the flow of the ihefc fluid flow-regulating device  1450  discharge to acquire additional super-heat by cooling the mod driven mechanical device  1520 , or rerouting the mfc fluid flow-regulating device  1140  discharge to acquire additional sensible heat by cooling the mod driven mechanical device  1520 , and still others involve various methods for evaporating the working fluid and/or the use of various combinations of working fluids. 
   4. Conclusion, Ramifications, and Scope 
   Accordingly, the reader will see that the waste heat recycling thermal power plant of this invention can be used to convert the heat contained in a thermal reservoir or a thermal stream to mechanical power, and thereby drive a mechanical load. In addition, the waste heat recycling that occurs within the invention itself enables the waste heat recycling thermal power plant to produce useable mechanical power at “high” net operating efficiencies, even while extracting replenishment heat from “low-temperature” external heat sources. Furthermore, the waste heat recycling thermal power plant has these additional advantages in that 
   it permits the production of mechanical power without burning hydrocarbon-based fuel, thus eliminating the attendant release of “greenhouse” gases; 
   it permits the production of mechanical power with minimal modifications and/or adaptation expenses to a “host” facility; 
   it permits the production of mechanical power reliably, through its utilization of robust sub-components; 
   it permits the production of mechanical power without the need to purchase additional fuel, thus improving the fuel efficiency of the “host” facility; 
   it permits the production of mechanical power by extracting replenishment heat directly from the environment. 
   Although the description above contains many specificities, these should not be construed as limiting the scope of the invention but merely providing illustrations of some of the presently preferred embodiments of this invention. For example, the external heat source can take many forms, such as: an industrial process&#39; cooling fluid, a geothermal pool, a solar collector, an internal combustion engine&#39;s coolant and/or its exhaust, a sufficiently large body of liquid water (e.g., a lake, or an ocean), etc. 
   Thus the scope of the invention should be determined by the appended claims and their legal equivalents, rather than by the examples given.