Abstract:
A system and method is disclosed to increase the efficient of internal combustion engines where the system and method converts a portion of thermal energy produced in the combustion process to a usable form of energy. If the engines are used in power generation, then the system and method increases the power output of the engine significantly. If the engines are used in traditional mechanical operations such as ships, then the system and method operates to increase mechanical power output or to increase co-produced electrical energy output.

Description:
BACKGROUND OF THE INVENTION 
   1. Field of the Invention 
   The present invention relates to the utilization of waste heat from diesel or other types of internal combustion engines used in power generation. 
   More particularly, the present invention relates to utilizing waste heat from diesel or similar types internal combustion engines used for power generation, where the fuel is relatively clean permitting the cooling of the exhaust gases from the engine to relatively low temperatures. 
   2. Description of the Related Art 
   A specific characteristic of diesel engines or other similar internal combustion engines used for power generation is that these system have two sources of waste heat: the waste heat from the exhaust gases formed during the combustion process and the waste heat from the water or other coolants used to cool the engine. 
   The utilization of heat from exhaust gas can be done in many different ways, and in general can be done with a conventional type of bottoming cycle. However, the utilization of both heat sources (exhaust gases and coolant—water or water antifreeze mixtures) in the same system has the potential to deliver substantial advantages. 
   Thus, not only is there an need in the art for more efficient and effective means for extracting usable work from waste heat generated by internal combustion engines; there is also a need in the art for solutions that operate within the confines of the heat sources available in such engines. 
   SUMMARY OF THE INVENTION 
   The present invention provides a system including an internal combustion engine, a heat recovery vapor generator (HRVG) connected to the exhaust of the engine and designed to utilized the heat in the exhaust gases to fully vaporize a multi-component working fluid, a turbine connected to the HRVG for converting a portion of thermal energy in the working fluid to a usable form of energy, and a condensation thermal compression subsystem (CTCSS) connected to the turbine and to a coolant system of the engine and designed to fully condense the working fluid and to lower back pressure on the turbine. The system converts a portion of heat from the exhaust gases and from the coolant used to cool the internal combustion engine to a usable form of energy. The system of this invention can be used by one or a plurality of internal combustion engines where the exhausts are combined and forwarded to the HRVG and the hot coolant streams from the engines are combined and sent to the CTCSS to assist in the condensation thermal compression process. 
   The present invention also provides an apparatus including an internal combustion engine having an exhaust system and a cooling system. The apparatus also includes a heat recovery vapor generator (HRVG) connected to the exhaust system and designed to transfer a portion of heat in engine exhaust gases to fully vaporize a fully condensed multi-component working fluid and a turbine connected to the HRVG and designed to convert a portion of heat from the fully vaporized working fluid to a usable form of energy. Preferably, the working fluid is also superheated. The apparatus also includes a condensation thermal compression subsystem (CTCSS) connected to the turbine and to the cooling system and designed to receive a spent working fluid and fully condense the spent working fluid for re-circulation back to the HRVG. The HRVG includes a series of heat exchange stages which successively heat the fully condensed working fluid until it is fully vaporized and preferably superheated. The CTCSS includes a plurality of heat exchangers, at least one separator, at least one throttle valve, at least two pumps, a plurality of dividing and combining valves and sufficient piping to interconnect the components in the CTCSS design of  FIG. 3 . 
   The present invention provides a method for converting a portion of waste thermal energy generated by an internal combustion engine into a usable form of energy such as electrical energy, mechanical energy or electro-mechanical energy—work. The method includes the step of combustion a relatively clean fuel in an internal combustion engine including an exhaust system and a cooling system. The term relatively clean means that the fuel is a fuel approved for use as a fuel in internal combustion engines, such as diesel engines, used in power generation, or a fuel that is cleaner than fuel approved for use in such engines, such as clean diesel or bio-diesel. The method also includes the step of directing the exhaust gas into a heat exchange relationship with a fully condensed, multi-component working fluid in a heat recovery vapor generator (HRVG). The HRVG includes several heat exchange stages resulting in the complete vaporization of the fully condensed, multi-component working fluid and preferably, the superheating of the vaporized working fluid. The method also include the step of converting a portion of thermal energy in the fully vaporized and preferably, superheated working fluid by passing the fluid through a turbine to a usable form of energy. The method also includes the step of passing a spent working fluid through a condensation thermal compression subsystem (CTCSS), where the working fluid is fully condensed using an external coolant and heat from the coolant in the cooling system of the engine. 
   The present invention also provides a method for condensing a spent working fluid including the step of passing the spent fluid stream form the turbine through a first heat exchanger where a portion of its heat is transferred to a first portion of a heated, leaner working fluid stream to form a first partially vaporized leaner working fluid steam and a cooled working fluid stream. The first partially vaporized leaner working fluid stream is combined, with a second partially vaporized leaner working fluid stream to form a combined partially vaporized which is then separated in a separator into a rich vapor stream and a lean liquid stream. The lean liquid stream is passed through a throttle valve where its pressure is adjust to be the same or substantially the same to a pressure of the cooled working fluid stream. The term substantially the same means that the pressure difference is small and does not cause design and operational problems. Generally, the difference should be less tan about 10%, preferably less than about 5% and particularly less than about 2%. The pressure adjusted lean liquid stream is then combined with the cooled working fluid steam to form a leaner working fluid stream. The leaner working fluid stream is then brought into heat exchange relationship with a first portion of a pressurized liquid enriched working fluid stream to form the heated, enriched working fluid stream and a partially condensed leaner working fluid stream. The partially condense leaner working fluid stream is then fully condensed in heat exchange relationship with a coolant in a condenser to form a fully condensed or liquid leaner working fluid stream. The liquid leaner working fluid stream is then pressurized to form a pressurized liquid leaner working fluid stream. The pressurized liquid enriched working fluid stream is then divided into the first portion of the pressurized liquid leaner working fluid stream and a second portion of the pressurized liquid leaner working fluid stream. The second portion of the pressurized liquid leaner working fluid stream is then combined with the rich vapor stream to form a partially condensed working fluid stream. The partially condensed working fluid stream is then fully condensed in heat exchange relationship with a coolant in a high pressure condenser to form a fully condensed working fluid stream. The fully condensed working fluid stream is then sent through a feed pump where its pressure is raised to a desired level and forwarded to the HRVG where it is vaporized by the internal combustion engine exhaust for the conversion of a portion of the exhaust&#39;s thermal energy into electrical work.. 
   Although the systems and methods of this invention are directed primarily to internal combustion engines for power generations, especially diesel engines, the systems and methods of this invention can also be used to extract more energy from internal combustion engines, especially, engines on ships an other vessels or vehicles that are large enough to accommodate the equipment necessary for the implement the HRVG and CTCSS of this invention. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The invention can be better understood with reference to the following detailed description together with the appended illustrative drawings in which like elements are numbered the same: 
       FIG. 1  depicts an expanded view of a preferred embodiment of a secondary energy extraction system for converting a portion of the heat generated by an internal combustion engine into usable work; 
       FIG. 2  depicts a preferred embodiment of a condensation thermal compression subsystem of this invention; and 
       FIG. 3  depicts a preferred system of this invention for extracting additional work from an internal combustion engine. 
   

   DETAILED DESCRIPTION OF THE INVENTION 
   The inventors have found that a secondary energy extraction system can be added onto an existing internal combustion engine to extract an additional amount of work from waste heat produced by the engine in the form of the exhaust gases and in turn of hot water formed in the cooling system. The secondary energy extraction system includes a heat recovery vapor generator designed to vaporize and preferably superheat a multi-component working fluid using heat from the internal combustion engine. The system also includes a turbine for converting a portion of heat from the vaporized working fluid into a usable form of energy and a condensation thermal compression subsystem for condensing the working fluid from the turbine into a fully condensed working fluid. The condensation thermal compression subsystem also uses hot water from the internal combustion engine cooling system to assist in the condensation of the spent working fluid. 
   The system of this invention uses as its working fluid including a mixture of at least two components, where the components have different normal boiling temperatures. That is the working fluid is a multi-component fluid including at least one higher boiling component and at least one lower boiling component. In a two component working fluid, the higher boiling component is often referred to simply as the high boiling component, while the lower boiling component is often referred to simply as the low boiling component. In the CTCSS of this system, the composition of the multi-component working fluid is in the CTCSS to accomplish the condensation of the spent working fluid. The CTCSS utilizes four different working fluid compositions to efficiency condense the spent working fluid. 
   The working fluid used in the systems of this inventions is a multi-component fluid that comprises a lower boiling point material—the low boiling component—and a higher boiling point material—the high boiling component. Preferred working fluids include, without limitation, an ammonia-water mixture, a mixture of two or more hydrocarbons, a mixture of two or more freons, a mixture of hydrocarbons and freons, or the like. In general, the fluid can comprise mixtures of any number of compounds with favorable thermodynamic characteristics and solubilities. In a particularly preferred embodiment, the fluid comprises a mixture of water and ammonia. 
   Suitable fuels for use in this invention include, without limitation, any fuel that can be burned in an internal combustion engine without causing exhaust system clogging or does not produce high levels of solids. Exemplary examples of such fuels include diesel fuels, bio-diesel fuels, clean diesel fuels, jet fuels, heavier or littler hydrocarbon cuts, or mixtures or combinations thereof. 
   Referring now to  FIG. 1 , a preferred embodiment of the heat utilization system of this invention, generally  150 , is shown to include a heat recovery vapor generator HRVG and a condensation thermal compression subsystem CTCSS. In the HRVG, a fully condensed working fluid is vaporized and energy from the vaporized working fluid is passed through an admission valve TV and through a turbine T, where a portion of the thermal energy in the fluid is extracted and converted to a usable from of energy. The spent fluid is then sent to the CTCSS, where it is fully condensed completing the cycle. 
   In particular, a stream  152  fully condensed working fluid having a desired high pressure and other parameters as at a point  129 , which corresponds to a point  29  described below in the CTCSS section, enters the HRVG, where it is heated in counterflow to a stream of exhaust gas  154  having initial parameters as at a point  600 . The working fluid stream  152  is heated to form a heated stream  156  having parameters as at a point  100 , which corresponding to a state of saturated liquid. The stream  156  having the parameters as at the point  100  is thereafter fully vaporized to form a stream  158  having parameters as at a point  101 , which corresponding to a state of saturated vapor. The stream  158  of working fluid having the parameters as at the point  101  is then superheated to form a stream  160  having parameters as at a point  102 . 
   Simultaneously, the exhaust gas stream  154  having the initial parameters as at the point  600 , moving in counterflow to the stream  158  of working fluid having the parameters as at the point  101 , is cooled to form a cooled flue gas stream  162  having parameters as at a point  601 , providing heat for the process of superheating the working fluid stream  158  to the stream  160  in a first heat exchange process  101 - 102 . Thereafter, the cooled flue gas  162  having the parameters as at the point  601  is further cooled to form a further cooled flue gas stream  164  having parameters as at a point  602 , providing heat for the vaporization of the working fluid stream  154  in a second heat exchange process  100 - 101 . Thereafter, the flue gas stream  164  having the parameters as at the point  602  is further cooled to form a spent flue gas stream  166  having parameters as at a point  603 , providing heat for preheating of the working fluid stream  152  in a third heat exchange process  129 - 100 . The spent flue gas stream  166  is then removed from the system  150 . 
   The superheated working fluid stream  160  having the parameters as at the point  102  then passes through the admission valve AV, where its pressure may be reduced to form a stream  168  having parameters as at a point  103 , and thereafter enters into the turbine T. The working fluid stream  168  having the parameters as at the point  103  is expanded in the turbine T converting a portion of its thermal energy into useful work to form a spent working fluid stream  170  having obtains parameters as at a point  104 . The spent working fluid stream  170  having the parameters as at the point  104  is then re-designated as a point  138  becoming the initial feed stream to the CTCSS. 
   The spent working fluid stream  170  exiting the turbine and having the parameters as at the point  138  then enters the CTCSS, where it is again re-designated as an initial CTCSS stream  200  having parameters as at a stream  38 . 
   Referring now to  FIG. 2 , the CTCSS of  FIG. 1  is shown and described in terms of its operation. The stream  200  having the parameters as at the point  38  passes through a first heat exchanger HE 1 , where it is cooled and partially condensed forming a cooled stream  202  having parameters as at a point  15  and releasing heat in a first CTCSS heat exchange process  38 - 15  or  11 - 36 . Then, the stream  202  having the parameters as at the point  15  is mixed with a stream  204  having parameters as at a point  8 . As a result of this mixing, a stream  206  having parameters as at a point  17  is formed. A concentration of a lower boiling component of the multi-component working fluid such as ammonia of a water/ammonia working fluid in the stream  206  having the parameters as at the point  17  is such that it can be fully condensed at ambient temperature. 
   The stream  206  having the parameters as at the point  17  then passes through a second heat exchanger HE 3 , where it is further cooled and condensed to form a partially condensed stream  208  having parameters as at a point  18  releasing heat in a second CTCSS heat exchange process  17 - 18  or  44 - 12 . The stream  208  having the parameters as at the point  18  then passes through a low pressure condenser HE 4 , where it is fully condensed, in counterflow with a stream of coolant  210  in a third CTCSS heat exchange process  18 - 1  or  51 - 52  to form a fully condensed stream  212  having parameters as at a point  1 , which corresponds to a state of saturated liquid. The coolant stream  210  is generally water or air having initial parameters as at a point  51  and final parameters as at a point  52 . 
   The stream  212  having the parameters as at the point  1  then enters into a circulation pump P 5 , where its pressure is raised forming a higher pressure stream  214  having parameters as at a point  2 . The stream  214  having the parameters as at the point  2  is then divided into two substreams  216  and  218  having parameters as at points  44  and  40 , respectively. 
   The substream  216  having the parameters as at the point  44 , which is in a state of subcooled liquid, then passes through the second heat exchanger HE 3 , where it is heated in counterflow with the stream  206  in the second CTCSS heat exchange process  44 - 12  or  17 - 18  as described above to form a heated stream  220  having parameters as at a point  12 , which corresponds or close to a state of saturated liquid. The stream  220  having the parameters as at the point  12  is then divided into two substreams  222  and  224  having parameters as at points  11  and  32 , respectively. 
   The substream  222  having the parameters as at the point  11  then passes through the first heat exchanger HE 1 , where it is heated and partially vaporized in counterflow with stream  200  in the first CTCSS heat exchange process  11 - 36  or  38 - 15  as described above to form a mixed stream  226  having parameters as at a point  36 . 
   Meanwhile, the stream  224  having the parameters as at the point  32  passes through a third heat exchanger HE 7 , where it is heated and partially vaporized, in counterflow with a stream of hot water  228  in fourth CTCSS heat exchange process  32 - 34  or  630 - 631  to obtain a stream  230  having parameters as at a point  34 . The hot water stream  228  has initial parameters as at a point  630  and final parameters as at a point  631 . 
   Thereafter, the streams  226  and  230  having the parameters as at the points  36  and  34 , respectively, are combined forming a combined stream  232  having parameters as at a point  5 . The stream  232  having the parameters as at the point  5  then enters into a separator S 1 , where it is separated into a stream of saturated vapor  234  having with parameters as at a point  6  and a stream of saturated liquid  236  having the parameters as at a point  7 . 
   The liquid stream  236  having the parameters as at point  7  then passes through a throttle valve TV 1 , where its pressure is reduced to a pressure equal to a pressure of the stream  202  having the parameters as at the point  15 , as described above, to form the lower pressure stream  204  having the parameters as at the point  8 . The stream  204  having the parameters as at the point  8  is then mixed with the stream  202  having the parameters as at the point  15  forming the stream  206  having the parameters as at the point  17  as described above. 
   Meanwhile, the stream  234  having the parameters as at the point  6  is then mixed with the stream  218  having the parameters as at the point  40  as described above forming a stream  238  with parameters as at a point  26 . The composition and flow rate of stream  238  having the parameters as at the point  26  are the same as the stream  200  having the parameters at the point  38 . The stream  238  having the parameters as at the point  26  then passes through a high pressure condenser HE 6 , where it fully condensed in counterflow by a stream of coolant  240  in fifth CTCSS heat exchange process  26 - 27  or  53 - 54  to form a stream  242  having parameters as at a point  27 , corresponding to a state of saturated liquid. The coolant stream  240  is generally water or air having initial parameters as at a point  53  and final parameters as at a point  54 . It should be recognized that the coolant streams  210  and  240  can be the same stream or from the same source. 
   Thereafter, the stream  242  of working fluid having the parameters as at the point  27  enters into a feed pump P 3 , where its pressure is raised to a necessary level to form a CTCSS discharge stream  244  having parameters as at a point  29 . The stream  244  having the parameters as at the point  29  is then sent into the HRVG and is renumber as the stream  152  having the parameters as at the point  129  of  FIG. 1 . 
   Generally, the temperatures of the stream  232 ,  234  and  236  having the parameters as at the points  5 ,  6  and  7 , respectively are chosen in such a way that the liquid stream  236  having the parameters as at the point  7 . The stream  236  having the parameters as at the point  7  is then throttled in the throttle valve TV 1 , forming the stream  204  having a temperature, which is equal or very close to the temperature the stream  202  having the parameters as at the point  15 . This is an important feature of the design of this invention, because it allows for increased efficiency of the operation of the CTCSS. 
   In the flow diagram of CTCSS, several additional points  16 ,  19 ,  28 , and  30  are shown, and the parameters of those points are presented in Table 1. These points exist because the computational diagram of the CTCSS required several additional state points; however, these extra points should be disregarded. 
   The performance of the system of this invention has been calculated assuming the exhaust and cooling water flow of a 3 MW diesel engine. 
   The parameters of all key points of the proposed system are presented in Table 1, and a summary of system performance is presented in Table 2. 
   Due to the fact that the system of this invention integrates the utilization of both heat from exhaust gas and from cooling water, it provides a high efficiency of utilization of exhaust gas from diesel engines. 
   
     
       
             
           
             
             
             
             
             
             
             
             
             
             
             
           
             
           
             
             
             
             
             
             
             
             
             
             
             
           
             
           
             
             
             
             
             
             
             
             
             
             
             
           
             
           
             
             
             
             
             
             
             
             
             
             
             
           
         
             
               TABLE 1 
             
           
           
             
                 
             
             
               System Point Summary 
             
             
               Ammonia/Water Working Fluid Simple Boiler, Fixed Inlet Pressure 
             
           
        
         
             
                 
               X 
               T 
               P 
               H 
               S 
               Ex 
               Grel 
               Gabs 
                 
               Wetness/T 
             
             
               Pt. 
               lb/lb 
               F 
               psia 
               Btu/lb 
               Btu/lb−R 
               Btu/lb 
               G/G = 1 
               lb/h 
               Ph. 
               lb/lb/F. 
             
             
                 
             
           
        
         
             
               Working Fluid 
             
           
        
         
             
               1 
               0.5110 
               60.80 
               35.670 
               −77.8236 
               0.0030 
               0.3524 
               3.47220 
               42,206 
               Mix 
               1 
             
             
               2 
               0.5110 
               61.03 
               104.591 
               −77.3966 
               0.0033 
               0.6001 
               3.47220 
               42,206 
               Liq 
                 −59° F. 
             
             
               4 
               0.5110 
               61.03 
               104.591 
               −77.3966 
               0.0033 
               0.6001 
               0.20826 
                2,531 
               Liq 
                 −59° F. 
             
             
               5 
               0.5110 
               162.50 
               97.591 
               182.8350 
               0.4487 
               29.8443 
               3.26394 
               39,674 
               Mix 
               0.7574 
             
             
               6 
               0.9707 
               162.50 
               97.591 
               628.4219 
               1.2068 
               84.2718 
               0.79174 
                9,624 
               Mix 
               0 
             
             
               7 
               0.3638 
               162.50 
               97.591 
               40.1327 
               0.2059 
               12.4136 
               2.47220 
               30,051 
               Mix 
               1 
             
             
               8 
               0.3638 
               121.97 
               38.670 
               40.1327 
               0.2098 
               10.3919 
               2.47220 
               30,051 
               Mix 
               0.9358 
             
             
               11 
               0.5110 
               116.97 
               99.591 
               −15.0197 
               0.1171 
               3.9558 
               1.46129 
               17,762 
               Liq 
                  0° F. 
             
             
               12 
               0.5110 
               116.97 
               99.591 
               −15.0197 
               0.1171 
               3.9558 
               3.26394 
               39,674 
               Mix 
               1 
             
             
               15 
               0.8750 
               121.97 
               38.670 
               520.5509 
               1.1123 
               24.9951 
               1.00000 
               12,155 
               Mix 
               0.1506 
             
             
               16 
               0.5110 
               121.97 
               38.670 
               178.4940 
               0.4697 
               14.5976 
               3.47220 
               42,206 
               Mix 
               0.7096 
             
             
               17 
               0.5110 
               121.97 
               38.670 
               178.4940 
               0.4697 
               14.5976 
               3.47220 
               42,206 
               Mix 
               0.7096 
             
             
               18 
               0.5110 
               104.72 
               37.670 
               119.8584 
               0.3681 
               8.6423 
               3.47220 
               42,206 
               Mix 
               0.7688 
             
             
               19 
               0.5110 
               104.72 
               37.670 
               119.8584 
               0.3681 
               8.6423 
               3.47220 
               42,206 
               Mix 
               0.7688 
             
             
               24 
               0.9707 
               162.50 
               97.591 
               628.4219 
               1.2068 
               84.2718 
               0.79174 
                9,624 
               Mix 
               0 
             
             
               25 
               0.9707 
               162.50 
               97.591 
               628.4219 
               1.2068 
               84.2718 
               0.79174 
                9,624 
               Vap 
                  0° F. 
             
             
               26 
               0.8750 
               136.76 
               97.591 
               481.4280 
               0.9600 
               64.8586 
               1.00000 
               12,155 
               Mix 
               0.2065 
             
             
               27 
               0.8750 
               60.80 
               95.591 
               −9.3244 
               0.0476 
               47.3414 
               1.00000 
               12,155 
               Mix 
               1 
             
             
               28 
               0.8750 
               67.49 
               1,952.000 
               1.8623 
               0.0533 
               55.5466 
               1.00000 
               12,155 
               Liq 
               −255.1° F. 
             
             
               29 
               0.8750 
               67.49 
               1,952.000 
               1.8623 
               0.0533 
               55.5466 
               1.00000 
               12,155 
               Liq 
               −255.1° F. 
             
             
               30 
               0.9707 
               162.50 
               97.591 
               628.4219 
               1.2068 
               84.2718 
               0.79174 
                9,624 
               Mix 
               0 
             
             
               32 
               0.5110 
               116.97 
               99.591 
               −15.0197 
               0.1171 
               3.9558 
               1.80266 
               21,912 
               Liq 
                  0° F. 
             
             
               34 
               0.5110 
               189.00 
               97.591 
               275.4204 
               0.5944 
               46.8462 
               1.80266 
               21,912 
               Mix 
               0.6614 
             
             
               36 
               0.5110 
               132.92 
               97.591 
               68.6217 
               0.2604 
               13.2681 
               1.46129 
               17,762 
               Mix 
               0.8893 
             
             
               38 
               0.8750 
               161.43 
               39.670 
               642.7749 
               1.3123 
               43.4924 
               1.00000 
               12,155 
               Mix 
               0.0422 
             
             
               40 
               0.5110 
               61.03 
               104.591 
               −77.3966 
               0.0033 
               0.6001 
               0.20826 
                2,531 
               Liq 
                 −59° F. 
             
             
               44 
               0.5110 
               61.03 
               104.591 
               −77.3966 
               0.0033 
               0.6001 
               3.26394 
               39,674 
               Liq 
                 −59° F. 
             
             
               100 
               0.8750 
               321.92 
               1,944.000 
               352.4457 
               0.5845 
               130.6245 
               1.00000 
               12,155 
               Mix 
               1 
             
             
               101 
               0.8750 
               389.66 
               1,928.000 
               645.8535 
               0.9471 
               235.9619 
               1.00000 
               12,155 
               Mix 
               0 
             
             
               102 
               0.8750 
               687.00 
               1,920.000 
               933.9828 
               1.2437 
               370.2921 
               1.00000 
               12,155 
               Vap 
                297.4° F. 
             
             
               103 
               0.8750 
               686.22 
               1,900.000 
               933.9828 
               1.2447 
               369.7253 
               1.00000 
               12,155 
               Vap 
                296.9° F. 
             
             
               104 
               0.8750 
               161.43 
               39.670 
               642.7749 
               1.3123 
               43.4924 
               1.00000 
               12,155 
               Mix 
               0.0422 
             
             
               129 
               0.8750 
               67.49 
               1,952.000 
               1.8623 
               0.0533 
               55.5466 
               1.00000 
               12,155 
               Liq 
               −255.1° F. 
             
             
               138 
               0.8750 
               161.43 
               39.670 
               642.7749 
               1.3123 
               43.4924 
               1.00000 
               12,155 
               Mix 
               0.0422 
             
           
        
         
             
               Heat Source 
             
           
        
         
             
               600 
               GAS 
               707.00 
               14.933 
               258.5173 
               0.4143 
               65.3755 
               6.14548 
               74,701 
               Vap 
                 585° F. 
             
             
               601 
               GAS 
               533.88 
               14.919 
               211.6325 
               0.3709 
               41.0108 
               6.14548 
               74,701 
               Vap 
                411.9° F. 
             
             
               602 
               GAS 
               353.19 
               14.664 
               163.8888 
               0.3190 
               20.1445 
               6.14548 
               74,701 
               Vap 
                231.8° F. 
             
             
               603 
               GAS 
               132.17 
               14.650 
               106.8414 
               0.2372 
               5.5190 
               6.14548 
               74,701 
               Vap 
                10.8° F. 
             
             
               630 
               Water 
               194.00 
               24.693 
               162.2393 
               0.2851 
               15.1053 
               9.66880 
               117,528  
               Liq 
               −45.36° F. 
             
             
               631 
               Water 
               140.00 
               14.693 
               108.0895 
               0.1987 
               5.7742 
               9.66880 
               117,528  
               Liq 
               −71.95° F. 
             
           
        
         
             
               Coolant 
             
           
        
         
             
               50 
               Water 
               51.70 
               14.693 
               19.8239 
               0.0394 
               0.0948 
               14.8938  
               181,040  
               Liq 
               −160.25° F.  
             
             
               51 
               Water 
               51.80 
               24.693 
               19.9498 
               0.0396 
               0.1232 
               14.8938  
               181,040  
               Liq 
               −187.56° F.  
             
             
               52 
               Water 
               97.92 
               14.693 
               66.0354 
               0.1260 
               1.4327 
               14.8938  
               181,040  
               Liq 
               −114.04° F.  
             
             
               53 
               Water 
               51.70 
               14.693 
               19.8239 
               0.0394 
               0.0948 
               20.2336  
               245,948  
               Liq 
               −160.25° F.  
             
             
               54 
               Water 
               51.80 
               24.693 
               19.9498 
               0.0396 
               0.1232 
               20.2336  
               245,948  
               Liq 
               −187.56° F.  
             
             
               55 
               Water 
               76.07 
               14.693 
               44.2041 
               0.0860 
               0.3176 
               20.2336  
               245,948  
               Liq 
               −135.89° F.  
             
             
                 
             
           
        
       
     
   
   
     
       
             
           
             
             
             
             
             
           
             
             
             
             
           
             
           
             
           
         
             
               TABLE 2 
             
             
                 
             
             
               Plant Performance Summary 
             
             
               Ammonia/Water Simple Boiler, Fixed Inlet Pressure 
             
             
                 
             
           
           
             
                 
             
           
        
         
             
               Heat in 
               5,182.25 
               kW 
               1,455.68 
               Btu/lb 
             
             
               Heat rejected 
               4,190.64 
               kW 
               1,177.14 
               Btu/lb 
             
             
               Turbine enthalpy Drops 
               1,036.70 
               kW 
               291.21 
               Btu/lb 
             
             
               Gross Generator Power 
               988.55 
               kW 
               277.68 
               Btu/lb 
             
             
               Process Pumps (−12.67) 
               −50.88 
               kW 
               −14.29 
               Btu/lb 
             
             
               Cycle Output 
               937.66 
               kW 
               263.39 
               Btu/lb 
             
             
               Other Pumps and°Fans (−4.42) 
               −17.69 
               kW 
               −4.97 
               Btu/lb 
             
             
               Net Output 
               919.98 
               kW 
               258.42 
               Btu/lb 
             
             
               Gross Generator Power 
               988.55 
               kW 
               277.68 
               Btu/lb 
             
             
               Cycle Output 
               937.66 
               kW 
               263.39 
               Btu/lb 
             
             
               Net Output 
               919.98 
               kW 
               258.42 
               Btu/lb 
             
           
        
         
             
               Net thermal efficiency 
               17.75% 
                 
                 
             
             
               Second Law Limit 
               31.47% 
             
             
               Second Law Efficiency 
               56.42% 
             
           
        
         
             
               Overall Heat Balance (Btu/lb) 
             
           
        
         
             
               Heat In: Source + pumps = 1,455.68 + 12.67 = 1,468.35 
             
             
               Heat Out: Turbines + condenser = 291.21 + 1,177.14 = 1,468.35 
             
             
                 
             
           
        
       
     
   
   Referring now to  FIG. 3 , a preferred embodiment of the heat utilization system of this invention, generally  300 , is shown to include an internal combustion engine  302  having a fuel inlet  304  connected to a fuel reservoir  306  via fuel line  308  and a coolant inlet  310  connected to a coolant outlet  311  of a coolant system  312  via coolant line  314 . The engine  302  also includes an exhaust outlet  316  connected to an exhaust inlet  318  of a heat recovery vapor generator HRVG via an exhaust line  320 . The HRVG also includes an exhaust vent  322  connected to a vent line  323  for venting the cooled exhaust gas to the surroundings. The HRVG also includes a liquid working fluid inlet  324  connected to a liquid working fluid outlet  326  of a condensation thermal compression subsystem CTCSS via a liquid working fluid line  328 . The HRVG also includes a vapor working fluid outlet  330  connected to a turbine inlet  332  of a turbine  334  via a vapor working fluid line  336 . The turbine  334  also includes a turbine outlet  338  connected to a spent working fluid inlet  340  of the CTCSS via a spent working fluid line  342 . The CTCSS also includes a hot coolant inlet  344  connected to a hot coolant outlet  346  of the engine  302  via a hot coolant line  348 . The CTCSS also includes a cooled coolant outlet  350  connected to a coolant inlet  352  of the cooling system  312  via a coolant return line  354 . The system  300  also includes a power output unit  356  having a power inlet  358  connected to a engine power outlet  360  and to a turbine power outlet  362  via power lines  364  and  366 . 
   The system  300  operates by first supplying fuel from the reservoir  306  to the engine  302  via the fuel line  308 . Fuel is combusted in the engine  302  producing exhaust gases which are forwarded to the HRVG via the exhaust line  320 . While the exhaust gases carry away thermal energy, the engine also generated electrical energy which is forwarded to the power output unit  356  via an electric line  364 . The engine  302  is also cooled by a coolant supplied from a cooling system  312  via a coolant line  314 . The HRVG is connected to the CTCSS via liquid line  328  which supplies a stream of a liquid or fully condensed multi-component working fluid to the HRVG. The HRVG places the liquid working fluid stream in heat exchange relationship in multiple stages with the exhaust gases resulting in cooled exhaust gases and a fully vaporized and preferably superheated working fluid vapor stream. The vapor stream is then forwarded to the turbine via the vapor line  336 , where a portion of its thermal energy is converted to electrical energy which is forwarded to the power out unit  356  via the electrical line  366 . The spent working fluid is then forwarded to the CTCSS where it is fully condensed to from the liquid working fluid. The CTCSS utilizes heat from the hot coolant leaving the engine  302  as a source of heat in the condensation process. The arrows in  FIG. 3  show the flow direction of the various streams and energy utilized and produced in the system. It should be noted that the cooling system forms a closed loop and does the working fluid cycle. 
   All references cited herein are incorporated by reference. Although the invention has been disclosed with reference to its preferred embodiments, from reading this description those of skill in the art may appreciate changes and modification that may be made which do not depart from the scope and spirit of the invention as described above and claimed hereafter.