Waste energy recovery system utilizing modular heat exchanger and conversion system

Abstract

Various embodiments of a waste heat recovery and conversion system are disclosed. The system may include a modular heat exchanger whose energy source is provided by waste heat energy transporting fluids transferring their energy to a working fluid. The working fluid may be in a liquid state contained in a reservoir hydraulically connected to a high-pressure heat transfer chamber. The high-pressure heat transfer chamber may be configured to receive thermal energy utilized to convert the working fluid into a superheated vapor.

Claims

1. A waste heat energy recovery system for an internal combustion engine, the system comprising: an exhaust pipe for discharging an exhaust gas from the internal combustion engine, the exhaust pipe comprising: a first conduit having a distal end, a proximal end, and a side wall extending between the distal end and the proximal end, the first conduit having a first internal space; a first exhaust gas port on the side wall of the first conduit for guiding the exhaust gas from the internal combustion engine to the first internal space; a second conduit having a distal end, a proximal end, and a side wall extending between the distal end and the proximal end, the second conduit having a second internal space; a second exhaust gas port on the side wall of the second conduit for guiding the exhaust gas from the internal combustion engine to the second internal space; and a flexible member joining the first conduit and the second conduit; and a heat exchanger for transferring heat from the exhaust gas to a working fluid in the exhaust pipe, the heat exchanger comprising: an inlet disposed on the first conduit for receiving the working fluid; an outlet disposed on the first conduit for discharging the working fluid; a first tube disposed inside the exhaust pipe and having an inner wall defining a first passageway through which the exhaust gas flows; and a second tube disposed concentrically between the exhaust pipe and the first tube, wherein an outer wall of the first tube and an inner wall of the second tube define a fluid channel through which the working fluid flows, the fluid channel being in fluid communication between the inlet and the outlet; and wherein the first tube and the second tube extend from the first internal space of the first conduit to the second internal space of the second conduit.

2. The system of claim 1, wherein: the first exhaust gas port is positioned in a first location along the first conduit, the second exhaust gas port being positioned in a second location along the second conduit, and the first tube and the second tube extend between the first location and the second location.

3. The system of claim 1, wherein an outer wall of the second tube and an inner wall of the first conduit define a second passageway through which the exhaust gas flows.

4. The system of claim 3, wherein the exhaust gas inside the first passageway flows in a first direction, and the exhaust gas inside the second passageway flows in a direction substantially parallel to the first direction.

5. The system of claim 1, further comprising a connector comprising a pipe having a first end connected to either the inlet or the outlet and a second end connected to a port on the inner wall of the first tube that connects to the fluid channel.

6. The system of claim 1, wherein the first and second tubes are structurally supported by the first conduit only and not by the second conduit.

7. The system of claim 1, further comprising: a turbine expander configured to convert energy of the working fluid into shaft energy; an electric generator configured to convert a first portion of the shaft energy into electricity; a vacuum chamber connected to the turbine expander for cooling and collecting the working fluid by heat exchange with a second fluid; a compressor coaxial with the turbine expander and the electric generator, the compressor configured to: convert a second portion of the shaft energy to compress the second fluid; and cool the working fluid after discharge from the turbine expander using the second fluid.

8. The system of claim 1, further comprising one or more fins on the inner wall of the first tube.

9. The system of claim 1, further comprising a second heat exchanger inside the exhaust pipe, the second heat exchanger defining a second fluid channel in fluid communication between a second inlet disposed on the second conduit for receiving the working fluid and a second outlet disposed on the second conduit for discharging the working fluid.

10. The system of claim 9, wherein each of the heat exchanger and the second heat exchanger comprises a turbine expander, an electric generator, and a compressor in a modular housing.

11. The system of claim 1, further comprising a groove in the fluid channel to increase turbulence of the working fluid flowing therethrough.

12. A waste heat energy recovery system for an internal combustion engine, the system comprising: an exhaust pipe for discharging an exhaust gas from the internal combustion engine, the exhaust pipe comprising: a first conduit having a distal end, a proximal end, and a side wall extending between the distal end and the proximal end, the first conduit having a first internal space; a first exhaust gas port on a first location of the side wall of the first conduit for receiving the exhaust gas from the internal combustion engine; a second conduit having a distal end, a proximal end, and a side wall extending between the distal end and the proximal end, the second conduit having a second internal space; a second exhaust gas port on a second location of the side wall of the second conduit for receiving the exhaust gas from the internal combustion engine; and a flexible member joining the first conduit and the second conduit; and a heat exchanger for transferring heat from the exhaust gas to a working fluid in the exhaust pipe, the heat exchanger comprising: an inlet disposed on the first conduit for receiving the working fluid; an outlet disposed on the first conduit for discharging the working fluid; and a fluid channel through which the working fluid flows, the fluid channel being disposed inside the exhaust pipe in fluid communication between the inlet and the outlet, wherein the fluid channel extends from the first internal space of the first conduit to the second internal space of the second conduit.

13. The system of claim 12, wherein the fluid channel extends between the first location of the first conduit and the second location of the second conduit.

14. The system of claim 12, further comprising: a first tube disposed inside the exhaust pipe and having an inner wall defining a first passageway through which the exhaust gas flows; and a second tube disposed concentrically between the exhaust pipe and the first tube, wherein an outer wall of the first tube and an inner wall of the second tube define the fluid channel.

15. The system of claim 14, wherein an outer wall of the second tube and an inner wall of the first conduit define a second passageway through which the exhaust gas flows.

16. The system of claim 14, wherein the exhaust gas inside the first passageway flows in a first direction, and the exhaust gas inside the second passageway flows in a direction substantially parallel to the first direction.

17. The system of claim 12, wherein the fluid channel comprises a plurality of tubes extending from the first internal space of the first conduit to the second internal space of the second conduit.

18. The system of claim 12, further comprising: a turbine expander configured to convert energy of the working fluid into shaft energy; an electric generator configured to convert a first portion of the shaft energy into electricity; a vacuum chamber connected to the turbine expander for cooling and collecting the working fluid by heat exchange with a second fluid; a compressor coaxial with the turbine expander and the electric generator, the compressor configured to: convert a second portion of the shaft energy to compress the second fluid; and cool the working fluid after discharge from the turbine expander using the second fluid.

19. The system of claim 1, wherein each of the first and second conduits comprises an exhaust gas manifold configured to connect to a corresponding engine block of the internal combustion engine.

20. The system of claim 12, wherein each of the first and second conduits comprises an exhaust gas manifold configured to connect to a corresponding engine block of the internal combustion engine.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate several embodiments of the invention and together with the description, serve to explain the principles of the invention.

(2) FIG. 1 is a schematic diagram illustrating exemplary applications of a heat recovery and conversion system according to one exemplary embodiment.

(3) FIG. 2 is a perspective view of a retrofittable conduit for transporting fluids that carry waste heat energy from a waste heat source and a modular heat exchanger integrally coupled to the conduit. The fluids may be directly or indirectly discharged into the environment.

(4) FIG. 3A is a side cross-sectional view of the conduit and the modular heat exchanger of FIG. 2.

(5) FIG. 3B is another perspective view of the conduit and the modular heat exchanger of FIG. 3.

(6) FIG. 4 is an axial cross-sectional view of the modular heat exchanger of FIG. 2, illustrating various components and their structural configurations.

(7) FIG. 5 is a perspective view of a retrofittable conduit and a plurality of modular heat exchangers connected in series, according to another exemplary embodiment of the present disclosure. Alternatively, the plurality of heat exchangers can be connected in parallel.

(8) FIG. 6 is a schematic illustration of a plurality of modular heat exchangers integrally coupled to exhaust gas manifolds of an internal combustion engine, according to another exemplary embodiment.

(9) FIG. 7 is a schematic illustration of a plurality of modular heat exchangers integrally coupled to an exhaustion pipe of an internal combustion engine, according to another exemplary embodiment.

(10) FIG. 8A is a top view of an internal combustion engine, where, in addition to the modular heat exchangers integrated with an exhaustion pipe of a combustion engine, a series of modular heat exchangers are integrated with a closed loop cooling piping system of the internal combustion engine wherein engine fluids transporting waste heat energy may transfer thermal energy to the working fluid circulating within the modular heat exchangers.

(11) FIG. 8B is a side view of the internal combustion engine shown in FIG. 8A.

(12) FIGS. 9A and 9B are schematic illustrations of multiple exemplary configurations of a modular heat exchanger configured to extract waste heat energy from the cooling and exhaust gas systems of an internal combustion engine.

(13) FIG. 10A is a schematic illustration of a single modular integral waste heat recovery and conversion system applied to internal combustion engines, wherein the modular exchangers may be integrated with the waste heat energy conversion system formed by turbine-alternator-compressor systems by scaling the modular heat exchangers so as to serve multiple combustion engine cylinders (or waste heat sources) by coupling each internal combustion engine exhaust gas port with a single integral waste heat conversion system.

(14) FIG. 10B is a schematic illustration of multiple modular integral waste heat recovery and conversion systems applied to internal combustion engines, wherein the modular heat exchangers may be integrated with dedicated waste heat energy conversion systems formed by turbine, alternator, and compressor and configured as a cluster of independent modules serving selected cylinders of the internal combustion engine.

DESCRIPTION OF THE EXEMPLARY EMBODIMENTS

(15) Reference will now be made in detail to the exemplary embodiments of the invention, examples of which are illustrated in the accompanying drawings. Wherever possible, the same reference numbers or letters will be used throughout the drawings to refer to the same or like parts.

(16) Various exemplary embodiments of the present disclosure provide a waste heat recovery and conversion system configured to convert waste heat energy discharged into the environment. In some exemplary embodiments, the heat recovery component (e.g., heat exchanger) and the conversion component (e.g., an expander, electric generator, compressor, and torque generator) may be integrated into a single modular system. For example, as will be described in more detail later, the waste heat recovery and conversion system utilizes waste heat energy to heat a working fluid circulating within an heat exchanger thermally and hydraulically coupled and integrated with a heat conversion system formed by one or more turbine expanders coupled to energy conversion systems (e.g., an electric generator, compressor, and torque generator).

(17) The working fluid may be any fluid having thermal-physical properties that favor phase changes from sub-cooled liquid to superheated vapor when exposed to any waste heat source. The waste heat source may comprise combustion gases from combustion engines, steam or hot gases from various industrial processes, and waste liquids rejected into the environment or cooled down by closed-loop cooling system prior to being discharged into the environment.

(18) The scalable modular heat exchanger all together with the integrated waste heat conversion system of the present invention may be configured to tolerate the stressors generated by ever changing thermodynamic parameters characterizing variable waste heat production sources, especially when these sources are represented by internal combustion engines. To attain the advantages and in accordance with the purpose of the invention, as embodied and broadly described herein, one aspect of the invention provides means to utilize the scalable modular heat exchanger and integral waste heat conversion systems for internal combustion engine applications, wherein the waste heat recovery and conversion system may be formed by coupling at least one turbine expander to an alternator and to an air compressor for the conversion of waste heat energy into electricity and compressed air respectively through a configuration that can be non-invasively retrofitted on existing combustion engine platforms, as well as to new combustion engines utilized for direct propulsion or for hybrid applications (e.g. diesel-electric vehicles, gas-electric vehicles, and stationary combustion-engine driven electric generator platforms).

(19) As waste heat sources may be represented by different configurations utilizing various fluids for the rejection of waste heat energy into the environment, an objective of the present invention is to provide a universal, scalable, modular, waste heat recovery and integral conversion system for the conversion of various forms of waste heat energy into useful energy easily and with minimally invasively configurations highly adaptable to various waste heat sources. Depending on the application, the grade, or temperature, of the waste heat source (e.g. high-, intermediate-, low-grade) and mass-flow-rate of the fluids transporting waste heat energy for final rejection into the environment, the scalable modular heat exchanger and integral conversion system of the present invention can be coupled in parallel, in series, or any hybrid configuration (e.g. series and parallel). Similarly, the modules forming the embodiment of the invention can be scaled to directly match the waste heat source rating by employing a large single module, or clusters of modules that all together match the total waste heat energy outputted from the waste heat source.

(20) FIG. 1 schematic diagram illustrating various industrial applications of a heat recovery and conversion system according to one exemplary embodiment of the present disclosure. As shown in FIG. 1, the conversion of waste heat energy into usable energy results in a lower thermal rejection into the environment as a portion of the waste heat energy normally discharged in the environment is converted into usable forms of energy. Hot fluids 1 (e.g., gases, liquids), transporting waste heat energy from the waste heat source to the final mass and heat transfer discharge into the environment, are made to exchange thermal energy with the modular heat exchangers 5 wherein the working fluid circulates in a closed-loop.

(21) As the waste heat source fluids 1 transfer thermal energy to the working fluid the waste heat source fluids 1 lower their energy content, thereby are discharged into the environment at lower temperatures. The working fluid enters the modular heat exchanger 5 at inlet 3 in a sub-cooled liquid state and exits the high-pressure heat exchangers 5 at the outlet 4 in a superheated vapor state.

(22) Once the working fluid exits outlet 4, it expands within an integral turbine 22, alternator 25, compressor 26 system for the conversion of waste heat energy into electricity and compressed air. This configuration is particularly suitable to waste heat recovery and conversion applications dedicated to internal combustion engines coupled to electric generators as the waste heat recovery and conversion technology of the present invention converts the great majority of the recovered waste heat energy into electricity for ready electrical voltage and phase coupling with the electrical generator and equipment driven by the internal combustion engine.

(23) The conversion of a portion of the waste heat energy into compressed air may be required to satisfy anti-pollution features of the waste heat recovery and conversion invention, as it provides the combustion engine with excess oxygen (air) when the engine operates at low Revolution per Minute (RpM) and/or at high transient loads. Most internal combustion engines operating in these conditions manifest high pollutant emissions. Therefore, providing compressed air as a result of waste heat recovery and conversion results in pollutant emission reductions, while enhancing the combustion engine performance at low RpM and during transients in which the duty cycle is changed from low- to high-loads.

(24) For waste heat sources characterized by non air-breathing processes (e.g. requiring compressed air to improve their pollutant emissions), the modular heat exchanger may be configured to provide working fluid power to an integral turbine-alternator system for electricity production only. Should applications require conversion of waste heat energy into mechanical torque, the working fluid may be expanded through an integral turbine coupled, most likely via gear-box or through a magnetic or hydraulic clutch, so as to provide shaft work. As the working fluid exits the integral turbine system it enters a vacuum chamber 20 cooled by the air entering the compressor (not shown in this Figure), or by a second fluid, to condense the working fluid prior to pumping it at high-pressure within the modular heat exchangers via pump 21.

(25) As shown in FIG. 1, the waste heat recovery and conversion system may comprise a Waste Heat Source containing the fluids 1 that transport waste heat energy from the waste heat source to the environment, one or more high-pressure heat exchangers 5 wherein a suitable working fluid circulates at high pressure through an inlet 3 and an outlet 4, by means of a high-pressure pump 21 and for the transfer of waste heat energy transported by the waste heat source fluids 1 into the working fluid, an integral waste heat conversion system 22 formed by a turbine, an alternator 25, and a compressor 26, a vacuum chamber 20 for the condensation of the working fluid by cooling means represented by the air entering the compressor 26 (see FIG. 9) or by a second fluid.

(26) The working fluid may be represented by water which may be used to describe the exemplary embodiments of the invention. It should be understood, however, that any other fluid having suitable thermodynamic properties may be used alternatively or additionally.

(27) With reference to FIGS. 2, 3A, 3B, and 4, various operational processes occurring within the high-pressure heat exchanger are described in detail.

(28) FIG. 2 is a schematic of a retrofitted basic conduit generally utilized to transport waste heat energy from the waste heat source to the environment through fluids that are directly or indirectly discharged into the environment. In this configuration, thermal and mechanical coupling of fluids 1 with modular heat exchangers may provide a easy to manufacture and install waste heat energy recovery system. In this Figure, the waste heat source fluids 1 enter a generic tubing or conduit system generally utilized to transport high- and low-grade waste heat energy from the waste heat source to a cooling heat exchanger (e.g. cooling tower for industrial processes, radiator for internal combustion engines) or to a discharge outlet venting into the environment (e.g. muffler system for an internal combustion engine, or discharge water or waste stream system for industrial processes).

(29) With reference to FIG. 2, hydraulic conduit 2 may be represented by a cylindrical tube utilized for the displacement of waste heat fluids 1 from the waste heat source origin to the outlet for final discharge of fluids 1 into the environment. Hydraulic conduit 2 may have any geometry. For applications in which fluids 1 are recycled, hydraulic conduit 2 represents the thermal-hydraulic circuit transporting waste heat energy fluids to a cooling heat exchanger. A working fluid circulates through the high-pressure heat exchanger 5 by entering the heat exchanger at high-pressure inlet 3, and exiting it at high-pressure outlet 4.

(30) With reference to FIGS. 3A, 3B, and 4, the high-pressure heat exchanger 5 is formed by an inner cylinder 6 and an outer cylinder 5a. The inner cylinder 6 and outer cylinder 5a are coaxial and form a jacket-like structure enclosing an expansion chamber 10 formed by the annular gap comprised by the inner walls of the outer cylinder 5a and the outer walls of the inner cylinder 6. The inner cylinder 6 and outer cylinder 5a are sealed at the edge, for example, by welding the inner and outer cylinders 6 and 5a through a radial weld at the top and bottom sections of the two cylinders.

(31) The working fluid enters the modular heat exchanger 5 through the system of high-pressure fitting forming inlet 3 and the sealing fitting 12 hydraulically connected to a thermal-hydraulic connection 8. Fitting 12 ensures sealing of the waste heat energy conduit 2 and prevents waste heat energy fluids 1 from exiting conduit 2 at this location. Working fluid and waste heat fluids 1 do not mix.

(32) As working fluid travels into thermal-hydraulic connection 8 it receives a first transfer of waste heat energy as thermal-hydraulic connection 8 is fully immersed in the waste heat fluids pathway. Thermal-hydraulic connection 8 connects the high-pressure inlet 3 with the inner cylinder 6 by means of a sealed port represented by fitting 7. As the working fluid enters chamber 10 formed by the annular gap separating the inner cylinder 6 from the outer cylinder 5a, it continues to expand and accelerate in a counter-flow fashion as it flows in a direction opposite to that of the waste heat fluids 1.

(33) Chamber 10 develops around inner cylinder 6 and forms turbulent channels for the working fluid to increase residence time and enhance heat transfer. While outer cylinder 5a sustains high-pressure exerting forces developing within chamber 10 in the outward radial direction, inner cylinder 6 sustains high-pressures that results in forces directed inward. For these reasons inner cylinder 6 is equipped with structural and fluid-dynamic fins 9 that develop in a manner to form low back-pressure blades along the inner walls of inner cylinder 6. Similar blades can be formed on the outer walls of outer cylinder 5a. Fins 9 have therefore the purpose of increasing structural robustness allowing for high pressure to develop within chamber 10 while the materials of heat exchanger 5 simultaneously withstand high pressures, high temperatures, and heat exchanger expansions and contractions while waste heat energy transporting fluids may be characterized by severe temperature excursions.

(34) As the working fluid expands inside the channels forming chamber 10 it rotates throughout the chamber by grooves etched or machined on the surface of inner cylinder 6 (not shown). By inducing rotation of the working fluid while transiting inside chamber 10 its residence time is increased while enhancing turbulence and heat transfer. As the working fluid expands inside chamber 10 it reaches high-pressure outlet port 11 represented by a fitting sealed to the outer wall of outer cylinder 5a.

(35) As waste heat fluids 1 travel through the modular heat exchanger 5 the rotate due to the effect of fins 9 acting as heat transfer fins as well as fluid dynamic blades to force the waste heat energy transporting fluids 1 to increase their residence time within the heat exchanger and enhance heat transferring from the waste heat source to the working fluid. As the working fluid expands inside chamber 10 under the effect of waste heat energy transfer it becomes superheated by a degree proportional to the dimensions of the modular heat exchanger, the rate of waste heat energy being transported by fluids 1 through conduit 2, the temperature of the waste heat energy transporting fluids 1, the rate of working fluid being pumped through inlet 3, and the thermo-physical properties of the working fluid being utilized.

(36) FIG. 4 provides a cross-sectional view represented by the equipment forming the modular heat exchanger and the back-pressure that may form as a result of the obstruction seen by fluids 1 while transiting through conduit 2. As fluids 1 travel through conduit 2 and the retrofitted modular heat exchanger 5, the actual cross sections seen by these fluids are mainly represented by the obstruction formed by thermal-hydraulic connection 8 and fins 9. However, fins 9 may be shaped and coiled to form minimum fluid dynamic resistance, and fluids 1 temperature decreases while traveling through the heat exchanger as a result of waste heat energy transfer to the cooler working fluid. As fluids 1 temperature decreases the specific volumes characterizing these fluids also decreases, thereby compensating for the potential back-pressure increase within conduit 2.

(37) With reference to FIG. 5, a series of modular heat exchangers 5 may be connected together so as to increase waste heat energy transfer to the working fluid. These configurations allow scalability by simply adding modules and connecting the thermal-hydraulic connections 3 and 4 in series, parallel or hybrid configurations.

(38) FIG. 6 is a schematic illustration of a, according to an exemplary embodiment of the invention, series connection of exhaust gas manifolds as possibly utilized in internal combustion engines for the discharge of waste heat energy transporting fluids into the environment. In this configuration, the modular heat exchangers are integrated and thermally coupled with the exhaust manifolds through minimally invasive retrofitting, wherein waste heat energy transporting fluids 1 are represented by exhaust gases (e.g. produced by internal combustion engines). Conduit 2 is now represented by exhaust gas manifold flanged to the engine block through flange 13 (see also FIG. 7). As shown in this Figure, the high-pressure heat exchangers 5 are positioned/retrofitted inside of conduit 2 for a straight line configuration, however, as flexible members 2a (FIG. 8) seal each repeating conduit 2 by flanging the flexible members 2a to the conduits 2, the modular heat exchangers may be configured to follow curved contours as well.

(39) FIG. 7 is an exemplary embodiment of the invention applied to an internal combustion engine by means of integration of the modular waste heat recovery high-pressure heat exchangers with the internal combustion engine exhaust piping system. In this Figure a 16 cylinder V-configuration on an internal combustion engine block 14 is shown with one cylinder bank equipped with the modular heat exchangers 5 by connecting the retrofitted exhaust gas manifold forming conduit 2 through flange 13 to the exhaust gas port provided by the combustion engine cylinder 15. As it will be described in the discussion that follows additional modular heat exchangers may be thermal-hydraulically coupled with the cooling system fluids utilized in the combustion engine 14.

(40) As shown in FIGS. 7, 8A, and 8B, the internal combustion engine cylinder(s) 15 provide ports for the hydraulic connection of the engine cooling system. The cooling system for most internal combustion engines operates on the principle of circulating coolant (e.g. water) through an internal jacket surrounding cylinder 15, and into a radiator for air cooling. FIGS. 8A and 8B provide a top and side schematic view of an internal combustion engine wherein in addition to the modular heat exchangers integrated with the combustion engine exhaust gas piping system, a series of modular heat exchangers may be integrated with the closed-loop cooling piping system of the internal combustion engine. The engine cooling system represents a piped system in which waste heat energy fluids 1 transport waste heat energy from the internal combustion engine 14 to the environment by means of a cooling heat exchanger (e.g. radiator). In this configuration, modular heat exchangers 5 may be configured as shown in FIGS. 2, 3, 4 and 5, except that the waste heat energy transporting fluids 1 may be represented by the internal combustion engine cooling fluid. As shown in FIG. 8, the modular heat exchangers 5 are represented by heat exchangers 5b with corresponding inlet 3a and 4a. In this configuration the high-pressure heat exchanger is immersed in the engine cooling fluid (representing fluids 1) without the working fluid mixing with the engine cooling fluid. This configuration allows for the working fluid to be increased in temperature while circulating through the high-pressure heat exchanger 5b, prior to expansion and superheating as a result of circulation through the modular heat exchangers 5. As shown in this Figure, the top view of the internal combustion engine 14 illustrates additional waste heat energy conduits represented by the exhaust gas diffuser 17 connected on one side to the exhaust gas piping systems flanged to each cylinder 15, and to the turbo charger 19 on the other side. Under normal operating conditions the exhaust gases (e.g. waste heat transporting fluids 1) expand in the turbo-charger system 18 and vent through the muffler 18. The modular heat exchangers can be configured to operate inside the conduit represented by the muffler 18 as waste heat energy transporting fluids 1 flows through this component prior to final discharge into the environment.

(41) With reference to FIGS. 9A and 9B, a schematic illustration of multiple, according to an exemplary embodiment of the invention, configurations of modular heat exchangers is provided. In this configuration a complete waste heat recovery and conversion system is configured to extract waste heat energy from the cooling and exhaust gas systems of an internal combustion engine 14 wherein waste heat energy is converted into electricity and compressed air by means of an integral waste heat conversion system formed by turbine 22, alternator 25, and air-compressor 26.

(42) In this configuration, the working fluid first receives waste thermal energy by entering the modular heat exchanger 5b at inlet 3a (as the system is symmetric and for easing the illustration only mirrored configurations are represented). As the working fluid exits the modular heat exchanger 5b with high energy content it enters one or multiple high-pressure heat exchangers 5c flanged to the engine exhaust gas port 13.

(43) As waste heat fluids 1 (exhaust gases) transfer waste heat energy to the working fluid inside the modular heat exchangers 5c the working fluid becomes superheated vapor which expands through integral turbine 22. As the working fluid exits integral turbine 22 it may be configured to enter a heat exchanger for the creating of a vacuum in chamber 28.

(44) Vacuum may be generated by the cooling action of air suctioned by the air compressor 26 or by the adoption of a second fluid which drive the working fluid to condense. The condensate is then collected in the condensate reservoir 20 wherein it is pumped back at high pressure into modular heat exchanger 5b and reset the circulatory cycle. In this Figure, the modular heat exchangers 5c are configured to offer a lower cross-sectional area with respect to the exhaust gases (waste heat transporting fluids 1), by employing multiple combinations of inner and outer cylinders 6 and 5a respectively and by eliminating the fins 9 (shown in FIGS. 3 and 4).

(45) FIG. 10A is a schematic illustration of a single modular integral waste heat recovery and conversion system configured, according to an exemplary embodiment of the invention applied to internal combustion engines, wherein a single modular heat exchanger system 5d may be integrated with the waste heat energy conversion system formed by turbine 22, alternator 25, and compressor 26 by scaling the modular heat exchangers 5d so as to serve multiple combustion engine cylinders 15 by coupling each internal combustion engine exhaust gas port with a single integral waste heat conversion system.

(46) FIG. 10B is a schematic illustration of multiple modular integral waste heat recovery and conversion systems configured, according to an exemplary embodiment of the invention applied to internal combustion engines, wherein the modular heat exchangers 5e may be integrated with dedicated waste heat energy conversion systems formed by dedicated turbine 22, alternator 25, and compressor 26 and configured as a cluster of independent modules serving selected cylinders 15 of the internal combustion engine 14.

(47) Other embodiments of the invention will be apparent to those skilled in the art from consideration of the specification and practice of the invention disclosed herein. It is intended that the specification and examples be considered as exemplary only, with a true scope and spirit of the invention being indicated by the following claims.