WASTE HEAT RECOVERY AND CONVERSION SYSTEM AND RELATED METHODS

Abstract

Various embodiments of a waste heat recovery and conversion system are disclosed. In one exemplary embodiment, the waste heat recovery system may include a heat exchanger for transferring heat from a first fluid to a second fluid and a power conversion unit configured to convert the energy transferred from the first fluid to the second fluid into usable energy. The heat exchanger may include an outer duct defining an inlet and an outlet through which the first fluid flows in and out, respectively, of the outer duct. The heat exchanger may also include an inner duct disposed inside the outer duct and defining an inner channel inside the inner duct and an outer channel between an outer surface of the inner duct and an inner surface of the outer duct. The inner duct may define an internal flow channel through which the second fluid flows to exchange heat energy with the first fluid.

Description

FIELD OF THE INVENTION

Various embodiments of the present invention generally relate to a waste heat recovery system and related methods. In particular, certain exemplary embodiments relate to a waste heat recovery and/or power conversion system that can be integrated with a waste heat source.

DESCRIPTION OF RELATED ART

A variety of industrial processes and/or thermodynamic engines discharge waste heat into the environment. For example, a typical combustion engine used for propulsion of a moving vessel (e.g., a locomotive, automotive, or marine vessel) or power production (e.g., diesel-electric generators) has the thermodynamic efficiency of generally less than 40%. Lower efficiencies may result when these engines are operated outside of their optimal operational conditions, such as, for example, idling, acceleration transients, and low- and high-power engine operations. The efficiency can be further decreased for engines with purely mechanical or unsophisticated fuel metering controls.

For most combustion engine applications, and under most operating conditions, 22% to 46% of the total energy of fuel used by a combustion engine is normally lost through exhaust gases and engine cooling, which represent waste heat discharged into the environment.

SUMMARY

Thus, there may be a need for developing a heat recovery system and method for recovering and/or converting waste heat into useable energy. Recovering such waste heat and/or converting it into usable energy may increase efficiency, which results in fuel savings as well as reduction in pollutant emission and thermal discharge into the environment.

Accordingly, various exemplary embodiments of the present disclosure may provide an integral waste heat recovery and conversion system and related methods capable of reliably and cost-effectively recovering and converting waste heat energy. For example, certain exemplary embodiments provide modular high-pressure heat exchanger for extracting waste heat energy from various thermodynamic systems and an integral conversion system for ultimately transforming the extracted waste heat energy into electricity and/or other forms of usable energy.

One exemplary aspect may provide a scalable, modular waste heat energy recovery and integral conversion system configured to convert waste heat energy produced by any source that rejects thermal energy into the environment, to heat a working fluid circulating within modular high-pressure heat exchangers thermally and hydraulically coupled and integrated with power conversion unit (PCU) for efficient waste heat conversion into usable energy.

The working fluid can be a suitable fluid with thermal-physical properties that favor phase changes from sub-cooled liquid to superheated vapor when exposed to low-grade heat transfer from any heat source fluid to the working fluid. The working fluid can also be a gas. In this case, the waste heat recovery and conversion system may be simplified as components dedicated to condensation of the working fluid would no longer be required.

The modular heat exchangers, all together with the integrated waste heat conversion system, may be configured to match the ever changing thermodynamic parameters characterizing variable waste heat production sources, especially when these sources are represented by internal combustion engines.

Another aspect may utilize scalable and modular heat exchangers configured to pre-heat and super-heat the working fluid for expansion within the integral waste heat conversion system as non-invasive retrofit for internal combustion engines. In this case, the waste heat recovery and conversion system may be formed by universal pre-heating interfaces coupling the waste heat source thermal-hydraulic system (i.e., pipes, stuck, ducts transporting waste heat fluid) to at least one turbine expander to a fast alternator and to a high-pressure pump dedicated to pressurize the working fluid, for the conversion of waste heat energy into electricity and other usable energy forms. As an example of usable energy forms, a compressor system may be coupled to the fast rotating components forming the integral power conversion system so as to provide compressed intake air to a combustion engine and increase its performance while reducing Particulate Matter formation at idling and intermediate power settings.

Although bottom cycle technologies dedicated to combustion engines generally show low efficiencies, high manufacturing cost, high maintenance costs, and low reliability, the present invention is intended to provide a solution to the low-reliability, and high-costs represented by similar technologies by relatively simple to manufacture high-pressure heat exchangers with geometries and materials that withstand the harsh conditions in which this equipment operates and that can be assembled as clusters of heat exchangers, or multiple modules, to match the waste heat source availability. The scalable, modular, and integral thermal-hydraulic connectivity feature of the waste heat recovery and conversion system characterizing the present invention allows retrofitting schemes that do not require heavy financing. Individual modules can be installed gradually and in a sequence wherein savings attained by the operation of each module over time can result in “self-financing” for the installation of additional modules up to matching the total waste heat source energy availability.

Waste heat energy transported, for example, by the fluid circulating in the cooling system and exhaust gas tubing of an industrial process or a combustion system heats up a suitable working fluid inside a modular heat exchanger in thermal contact with the fluid transporting waste heat energy without mixing with these fluid. By the modular heat exchanger, the working fluid expands by changing thermodynamic state from liquid to superheated vapor (for working fluid characterized by a system of liquid and vapor, or containing two-phases) within fluid-dynamically optimized channels derived internally the high-pressure heat exchanger.

The channels are formed by surfaces within the modular heat exchanger configured so as to increase the working fluid residence time and to enhance the working fluid thermal coupling with the fluid transporting waste heat energy. The residence time is increased by utilizing channel geometries that force the working fluid through pathways that increase turbulence while the working fluid accelerates as a result of its expansion through the channels and as a result of heat energy transfer from the high-pressure heat exchanger internal surfaces.

Furthermore, residence time is enhanced by configuring the working fluid and the fluid transporting waste heat energy so as to essentially swirl or rotate the working fluid and the fluid transporting waste heat energy while wetting and surrounding the surfaces forming the waste heat source system.

The thermal coupling between the working fluid and the fluid transporting waste heat energy occurs without mixing and is enhanced by utilizing suitable high thermal conductivity materials that form the support structures of the channels so as to make them capable of withstanding high-pressure, thermal stresses and mechanical deformation on all axes. As the working fluid travels through the modular heat exchanger, it becomes superheated and, depending on the selected working fluid, it may change phase from liquid to super heated vapor. At this point, the superheated working fluid exiting the modular heat exchanger may enter a series of modular pre-heating and modular heat exchangers so as to increase the waste heat energy transfer to the working fluid, for direct or indirect expansion of the superheated working fluid vapors within at least one set of turbine-alternator systems for the conversion of the working fluid energy into mechanical and electrical energy respectively.

As mentioned, depending on the application, the modular heat exchanger and waste heat conversion system formed by a turbine and alternator may be mechanically or thermal-hydraulically coupled to an air compressor system for the generation of compressed air. When compressed air is provided to the intake manifold of a combustion engine, the results are pollutant emission reductions and engine performance enhancement.

Finally, the working fluid exhausting from the turbine system is either cooled by heat exchangers thermally coupled with environmental fluid (i.e., gaseous single phase working fluid), or made to condense within a sudden-condensation chamber (i.e., liquid-vapor phase working fluid), thereby causing a vacuum at the turbine outlet and resulting in increased waste heat recovery and conversion system efficiency.

Certain exemplary embodiments of the present disclosure focus on bottom cycle applications and make its utilization commercially viable in the context of, for example, internal combustion engine applications. Also, various exemplary embodiments may provide the ability of the waste heat recovery and conversion system to be minimally invasive, with the high-pressure heat exchangers sufficiently rugged to withstand full flame immersion for operation in highly corrosive environments for a high-reliability over prolonged periods of time. Overall, the waste heat recovery and conversion system may efficiently transform low- and high-grade waste heat energy into re-usable energy without significantly interfering with the fluid-dynamic conditions characterizing the fluid transporting waste heat energy from the waste heat sources into the environment as the high-pressure pre-heating heat exchangers, and the superheating high-pressure heat exchangers are designed to reduce back pressure normally generated by drag forming between the heat source fluid and the surfaces of the high-pressure heat exchangers.

Additional objects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. The objects and advantages of the invention will be realized and attained by the elements and combinations particularly pointed out in the appended claims.

It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the invention, as claimed.

BRIEF DESCRIPTION OF THE DRAWINGS

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.

FIG. 1 is a schematic diagram illustrating an application of a heat recovery and conversion system according to one exemplary embodiment.

FIG. 2 is a schematic diagram illustrating exemplary applications of a universal thermal and hydraulic coupler forming an interface between the high-pressure heat exchanger and the heat source while comprising a nozzle to direct waste heat fluid and features allowing the high-pressure heat exchanger to mechanically expand/contract freely while providing hydraulic sealing with the waste heat source.

FIG. 3 is a perspective view of the universal thermal and hydraulic coupler forming a high-pressure heat exchanger of FIG. 2.

FIG. 4 is a perspective view of a retrofittable conduit for transporting fluid that carry waste heat energy from a waste heat source into a modular high-pressure heat exchanger integrally coupled to the conduit and showing the exterior walls of a high-pressure heat exchanger featuring geometries that allow re-directing of the heat source fluid while executing the functions of a nozzle.

FIG. 5 is a perspective view of a retrofittable conduit for transporting fluid that carry waste heat energy from a waste heat source into a modular high-pressure heat exchanger of FIG. 4 showing the coupling of the high-pressure heat exchanger with a sealing flexible member.

FIG. 6 is a schematic diagram illustrating exemplary applications of a high pressure heat exchanger positioned internally a heat source fluid duct.

FIG. 7 is a perspective view of high-pressure heat exchanger for retrofitting configurations in which the high pressure heat exchanger may be positioned within heat source fluid conduits with minimum drag and maximum heat transfer between the waste heat source and the working fluid.

FIG. 8 is a perspective view of a waste heat source conduit or manifold retrofitted with baffles to increase waste heat fluid mixing and turbulence.

FIG. 9 is a perspective view of modular high-pressure heat exchangers grouped to form a thermal-hydraulically coupled cluster of high-pressure heat exchangers submerged within the heat source fluid.

FIG. 10 is a perspective view of multiple modular high-pressure heat exchangers clustered and thermal-hydraulically connected to universal high-pressure heat exchangers with vibrational and structural de-couplers thermal-hydraulically and mechanically coupled to an exemplary waste heat source represented by the exhaust gases of a combustion engine.

FIG. 11 is a schematic diagram illustrating exemplary applications of a power conversion unit (PCU) for the conversion of recovered waste heat energy into electricity and other usable energy forms. The schematic illustrates coupling between the expander, a fast generator/motor, a high-pressure pump wherein the expander provides features for utilization of compressed air.

FIG. 12 is a perspective view of an exemplary compact power conversion unit with features shown in the schematic of FIG. 11 and offering universal thermal-hydraulic and electrical couplings.

DESCRIPTION OF THE EXEMPLARY EMBODIMENTS

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.

Various exemplary embodiments of the present disclosure provide a system and method for recovering waste heat from a heat source and converting it into useable energy. In some exemplary embodiments, the heat recovery system may be formed as a single modular system, where various components of the system are integrated into a single modular unit. For example, as will be described in more detail later, the waste heat recovery and conversion system utilizes a waste heat energy to heat a working fluid circulating within heat exchangers thermally and hydraulically coupled to an integrated power conversion system formed by one or more turbine expanders housed in a power conversion unit and coupled to energy conversion systems (e.g., an electric generator, a high-pressure pump, a clutch or direct mechanical coupler providing torque to drive a compressor or as a torque generator).

The working fluid may be any fluid having thermal-physical properties that favor phase changes from liquid to superheated vapor when exposed to a waste heat source. Alternatively, the waste heat recovery and conversion system may utilize a gaseous working fluid. In this case the integral power conversion unit may be configured to recirculate the gas after expansion in the expander turbine by substituting the high-pressure pump with a compressor/blower and by eliminating the condenser.

The heat exchangers of the present invention may be utilized to pre-heating and superheating the working fluid and as a mechanical and thermal hydraulic interface to decouple the vibrational and structural environment represented by the heat source from the structures of the heat exchangers. The heat exchangers may be formed by compact high-pressure heat exchanging surfaces containing channels for the circulation of the working fluid and provided with universal flanges for thermal-hydraulic coupling with the waste heat source. The heat exchangers may be modular and configured as stand-alone or clusters of heat exchanger systems all together with the power conversion system forming the integrated waste heat conversion system of the present invention and 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 electric generator/motor 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).

As waste heat sources may be represented by different configurations utilizing various fluid 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, with minimally invasively configurations highly adaptable to various waste heat sources requiring minimum maintenance. 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 fluid transporting waste heat energy for final rejection into the environment, the scalable modular heat exchanger and integral conversion system of the present invention may be coupled in parallel, in series, or any hybrid configuration (e.g., series and parallel). Similarly, the modules forming the embodiment of the invention may be scaled to directly match the waste heat source availability rating by employing a large single module, or clusters of smaller modules that all together match the total waste heat energy outputted from the waste heat source.

FIG. 1 is a 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 from a heat source 1 into usable energy may result in a lower heat release 44 into the environment as a portion of the waste heat energy normally discharged to the environment is converted into usable forms of energy. Heat source 1 can be any waste or residual heat from an industrial process, a combustion engine, or any other thermal source. By way of examples only, heat source 1 may comprise exhaust gases from combustion engines, steam or hot gases from various industrial processes, and waste liquids released into the environment or cooled down by closed-loop cooling system prior to being discharged into the environment.

Heat source fluid 2 may be in the form of gas or liquid. Heat source fluid 2, transporting waste heat energy from heat source 1, is made to exchange its thermal energy with 1^st Heat Exchanger 3 configured to pre-heat working fluid 4 prior to entering into the 2^nd Heat exchanger 5 configured to superheat working fluid 4 while transiting within its channels. Working fluid 4 circulates in a closed-loop and does not mix with heat source fluid 2. 1^st heat exchanger 3 and 2^nd heat exchanger 5 may be configured with a flexible thermal-hydraulic and mechanical coupling to attenuate vibrational stressors induced by coupling of the heat exchangers with heat source 1, thereby providing an interface between the heat exchangers and the heat source to mitigate vibrational and thermal stressors. As heat source fluid 2 transfers its thermal energy to working fluid 4, heat source fluid 2 lowers its energy content for final discharge into the environment at lower temperatures.

The heat exchangers in pre-heating interface 3 may have sufficiently large heat transfer surfaces to directly obtain superheating of working fluid 4. If working fluid 4 is a liquid-vapor phase fluid, working fluid 4 may be in a sub-cooled state at the inlet of pre-heating interface 3. Depending on the thermodynamic state of heat source fluid 2, working fluid 4 may exit pre-heating interface 3 in a sub-cooled liquid, a mixed vapor-liquid, or superheated thermodynamic state.

Working fluid 4 exiting 1^st heat exchanger 3 enters the 2^nd heat exchanger 5 configured as a stand alone high pressure heat exchanger or as a cluster of modular heat exchangers, to provide additional thermal energy exchange between heat source fluid 2 and working fluid 4 through its extended heat transfer surfaces. Superheated working fluid 4 exiting 2^nd heat exchanger 5 then enters a power conversion unit (PCU) 6 for expansion within a set of turbines or expander for conversion of heat source 1 into electricity, compressed air, and/or any other usable energy forms while providing pumping power for working fluid 4 to circulate through the closed-loop formed by coupling 1^st heat exchanger, 2^nd heat exchanger and the PCU 6. PCU 6 may be integral as its expander, pump, alternator/motor, torque coupler and condenser may be configured as a single piece within the same housing. This configuration is particularly suitable for applications dedicated to internal combustion engines coupled to electric generators as the waste heat recovery and conversion system of the present disclosure converts a portion of the recovered waste heat energy into electricity for ready electrical voltage and phase coupling with the electrical generators and equipment driven by the internal combustion engine.

The conversion of a portion of the waste heat energy into compressed air may be required to satisfy pollutant reduction features of the waste heat recovery and conversion system. Converting a portion of the recovered heat source 1, when applied to combustion engines, into compressed air 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 combustion engine duty cycle is changed from low-to high-loads.

As a result of thermal energy transfer with working fluid 4, heat source fluid 2, exiting the 2^nd heat exchanger 5, may be characterized by lower temperatures, thereby allowing for Emission Gas Recirculation methodologies and further decrease pollutant emissions.

For waste heat sources characterized by non air-breathing processes (e.g., requiring compressed air to improve their pollutant emissions), the modular heat exchangers forming 1^st and 2^nd heat exchangers 3 and 5 respectively may be configured to increase working fluid 4 energy content for expansion within an expander, for example, formed by a turbine-generator system for electricity production only. For applications requiring conversion of waste heat energy into mechanical torque, working fluid 4 may be expanded through an expander (i.e. turbines) coupled, for example, via gear-box or through a magnetic or hydraulic clutch, to provide shaft work. As working fluid 4 exits the expander system it enters a condenser 7 integrated with the volumes and surfaces formed by the power conversion unit housing so as to provide compact thermal-coupling and a vacuum or a low-pressure state at the exit of the expander. This low-pressure thermodynamic state may be induced by condensation caused by thermal exchange with the compressor fluid (e.g., air). Additionally, auxiliary cooling may be provided by external cooling sources as it will be shown in FIG. 11 and FIG. 12. High-pressure working fluid 4 circulates by means of a pump driven by the torque generated by the expander forming the integral power conversion unit.

To summarize the exemplary embodiments shown in FIG. 1, the waste heat recovery and conversion system may comprise a waste heat source 1 characterizing by thermal-hydraulic systems (i.e., pipes, ducts, venting stuck etc.) transporting waste heat energy from heat source 1 to the environment, one or more high-pressure heat exchangers (e.g. 1^st and 2^nd heat exchangers 3 and 5) wherein a suitable working fluid 4 circulates at high pressure by means of a pump, integrated with and driven by the power conversion unit 6, for the transfer of waste heat energy 1 transported by heat source fluid 2 and transferred into working fluid 4, thereby superheating it, for expansion and conversion into electricity and other suitable energy forms, wherein the working fluid condenses after exiting the expander through a condensing system 7 so as to re-set the closed-loop thermodynamic cycle. 1^st and 2^nd heat exchangers 3 and 5 respectively all together with the components forming the PCU 6 may be made integral and modular as these components may be housed as a single piece.

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. For example, for configurations wherein working fluid is in a gaseous form, condenser 7 may be configured to function as an intercooler while the high-pressure pump integrated with the power conversion unit may be configured to operate as a re-circulator or blower.

With reference to FIG. 2 and FIG. 3, the operational processes occurring within the high-pressure heat exchanger forming a thermal and hydraulic coupler are described in detail. As shown in this figures, flange 13 allows for thermal-hydraulic and mechanical coupling with heat source 1. This provides a thermal-hydraulic and mechanical interface between heat source 1 and 1^st heat exchanger 3 so as to minimize or eliminate thermal and vibrational stressors potentially transferred from the heat source to the heat exchanger and power conversion unit systems. 1^st heat exchanger 3 may be characterized by channels 10 formed by inner jacket walls 18 and outer jacket walls 17. Channels 10 may be configured to form internal pathways by channel fins 11 for working fluid 4 to increase its residence time and enhance heat transfer while transiting within the 1^st heat exchanger. All together, heat channel 10 and fins 11 form a structure allowing high-pressure operation.

As heat source fluid 2 transfers energy to channels 10 by thermal transfer via channel fins 11 and/or via outer and inner jacket walls 17 and 18 respectively, without mixing with working fluid 4, the thermodynamic state of working fluid changes from inlet 8 to outlet 9 as it expands and accelerates within channel 10. Depending on the thermodynamic state and mass-flow-rate of heat source fluid 2, and on the dimensions and materials forming the high-pressure heat exchanger of 1^st heat exchanger 3, working fluid 4 may exit outlet 9 as sub-cooled liquid single phase, as liquid-vapor two-phase, or as superheated vapor single phase. Superheated fluid 21 denotes a single-phase superheated fluid. If working fluid 4 is gaseous, the gas or mixed gases increase their energy content from inlet 8 to outlet 9. As the heat source may be formed by a system inducing vibrational stressors, flexible member flange 14 allows for mechanical coupling with flexible member 12 whose vibrational decoupling of flange 15 allows for mechanical and thermal-hydraulic coupling with modular 2^nd heat exchanger(s) 5 without transferring structural loads and vibrational stresses associated with the system representing heat source 1.

FIGS. 4 and 5 show exemplary geometries of the 1^st heat exchanger 3 wherein heat source fluid 2 may enter through flange 13 configured to thermal-hydraulically and mechanically couple the 1^st heat exchanger 3 to heat source 1. As for the embodiments described in FIGS. 2 and 3, the outer jacket walls 17 and inner jacket walls 18 comprise channels 10 and fins 11 (shown in FIG. 2) not shown in FIGS. 4 and 5 for simplicity. 1^st heat exchanger 3 high-pressure inlet 9 and outlet 8 are interchangeable so as to allow for execution of series, parallel, counter- and parallel-flow configurations according to heat source 1 waste energy availability and PCU 6 ratings. FIG. 4 shows a method to direct heat source fluid 2 flow so as to enable retrofitting with a variety of waste heat sources and configurations. In these exemplary representations, nozzle 16 accelerates waste heat fluid 2 while re-directing the flow. While flange 14 is mechanically directly coupled to flange 13 (e.g., it may be part of the same body), flexible member 12 and flexible member flange 15 allows thermal-hydraulic coupling with 2^nd heat exchanger 5 while providing a vibration damping system to minimize vibrational and thermal stresses.

With reference to FIG. 6 and FIG. 7, the operational processes occurring within the 2^nd heat exchanger 5 are described in detail. As shown in these figures, channels 22 are formed by the jacket-like structure comprising the superheating inner and outer surfaces 26 and 28 respectively, and by internal pathways formed by superheating inner and outer fins 23 and 27.

To minimize drag and reduce backpressure 2^nd heat exchanger 5 may be configured to feature aerodynamically optimized drag reducing entrance 24 and end 25. Additionally, to further reduce aerodynamic drag, 2^nd heat exchanger 5 may be configured to be “floating” within a heat source duct 20 by providing hydraulic and mechanical connections through flexible hydraulic couplers 19. The heat source duct 20 may be provided with the heat source equipment (i.e., exhaust gas manifolds for applications involving waste heat recovery and conversion from combustion engines). Alternatively, a heat source 1 hydraulic conduit may be formed by configuring hydraulic conduit 20 with flanges 29 for modular coupling with clusters of 2^nd heat exchangers 5 thermal-hydraulically connected in series, parallel or mixed series-parallel configurations. As working fluid 4 enters 2^nd heat exchanger 5 at inlet 8, its energy content increases due to thermal exchange with heat source fluid 2 and becomes superheated while transiting through channels 22. Outlet 9 and inlet 8 are interchangeable, thus allowing for various counter-flow, parallel-flow, or hybrid parallel-counter-flow configurations.

FIG. 7 illustrates an exemplary embodiment of the 2^nd heat exchanger 5 without heat source duct 20 for simplicity. In this exemplary representation, fins 23 may be represented by sealed pins extruding through channel 22 and wetted by heat source fluid 2. In FIG. 7 outer fins 27 are not shown for simplicity. In this representation, super heated fluid 21 exits at outlet 9, while working fluid 4 entering at interchangeable inlet/outlet 8 is not shown.

With reference to FIG. 8 the exemplary waste heat source duct 20 may be formed by one or multiple conduit, or manifolds with various shapes, for transport of heat source fluid 2 to the environment. To increase heat source fluid 2 turbulence and heat transfer the heat source duct 20 may be retrofitted with mixing baffles 30. For exemplary purposes the heat source duct 20 may be configured with multiple heat source fluid inlets and outlets that can be coupled to modular heat source ducts via heat source duct coupling flanges 29.

FIG. 9 is an exemplary representation in perspective view of modular 2^nd heat exchangers 5 grouped to form a thermal-hydraulically-coupled and mechanically supported cluster of 2^nd heat exchangers 5 submerged within heat source fluid 2. This figure is not to scale with respect to the heat source duct 20 represented in FIG. 8. As shown in FIG. 9, heat source fluid 2 may wet all surfaces of each individual 2^nd heat exchangers 5, grouped in the cluster formed by supporting 2^nd heat exchangers 5 through cartridge flanges 32. By wetting 2^nd heat exchanger 5 outer surfaces 28 and inner surfaces 26 (shown in FIG. 9 only for one of the multiple superheating heat exchangers forming the cluster) heat transfer from heat source fluid 2 to working fluid 4 may be enhanced. Hydraulic connections among each individual high-pressure heat exchanger and those providing one or multiple inlets 8 to working fluid 4 and outlets 9 to transport superheated fluid 21 may be configured with flexible hydraulic couplers 19 shown in FIG. 6, not shown in FIG. 9.

FIG. 10 shows an exemplary embodiment of thermally-hydraulically and mechanically coupled 1^st and 2^nd heat exchangers 3 and 5 respectively, thermal-hydraulically and mechanically interfaced with the heat source 1, supported within modular heat source ducts 20, and submerged within heat source fluid 2 resulting from operation of a combustion engine representing, as an example, waste heat source 1. As shown in this figure while 1^st heat exchanger 3 is mechanically forming a single piece with the cylinders blocks of the combustion engine, representing as an example waste heat source 1, each heat source duct 20 is mechanically linked to waste heat source 1 through flexible members 12, thereby minimizing the impact of vibrations, and that of expansion and contractions exerted the materials forming the 2^nd heat exchangers 5.

FIG. 11 shows a schematic diagram illustrating exemplary applications of the power conversion unit (PCU) 6 for the conversion of recovered waste heat energy from a heat source 1 into electricity 42 and other usable energy forms. The power conversion unit 6 may include at least one expander 34, mechanically coupled to at least one electric generator/motor 36. The electric generator motor 36 may be configured as a fast and compact electrical machine equipped with a coupling shaft. Alternatively all of the rotary components forming the electrical generator motor 36, the pump 37, the expander 34, the shaft coupler and the compressor 40 may mechanically coupled to a single shaft 35. The expander 36 may be configured to expand superheated fluid 21 by one or multiple turbines or positive displacement components. The fast electric generator/motor 36 may be configured to produce electrical power when driven by expander 34 or deliver torque to shaft 35 when operated as an electric motor. The high-pressure pump may be configured to provide a variable mass-flow-rate (i.e. proportional to shaft 35 revolutions per minute) for example via external control system. The power conversion unit 6 may also be configured to provide mechanical torque resulting from recovered waste heat source 1 energy, for example, to drive an air compressor 40 for combustion engine applications as part of a pollutant reduction system. All of the components comprised in FIGS. 11 and 12 may be integral and housed to form a single unit.

By hydraulically coupling the power conversion unit 6 to the 1^st and 2^nd heat exchangers the thermodynamic loop shown in FIG. 1 is closed. Working fluid 4 may be configured to be stored within a reservoir integrally formed within the housing of condenser 7 wherein it is suctioned by pump 37 and compressed for utilization by the 1^st and/or 2^nd heat exchangers 3 and 5 respectively. Superheated fluid 21 produced by 1^st and 2^nd heat exchangers 3 and 5 respectively may be hydraulically coupled to the power conversion unit 6 by insulated high-pressure tubing (not shown). As superheated fluid 21 expands in expander 34 it exhausts in the condenser 7. Condensing working fluid 33 exiting the expander 34 may undergo condensation by means of active and passive cooling via thermal exchange with the surfaces forming the housing of condenser 7 integrated with power conversion unit 6 and transferring thermal energy to the environment passively via natural convection, and/or actively by forced convection through active recirculation of cooling fluids.

Thermal transfer between the condensing working fluid 33 and the thermodynamic environment represented by condenser 7 may be induced by circulating the working fluid via condenser auxiliary cooling 49 (e.g., radiator system), and/or by thermal transfer with a second fluid 41 (e.g., air) circulating, for example, via compressor 40 in combination or independently of the cooling impact induced by enhancing condenser cooling fins 48. In this configuration, prior to entering compressor 40, secondary fluid 41 provides cooling to condenser 7 through fins 48.

The electric generator/motor 36 may be configured to mechanically couple expander 34 through shaft 35. When the integral power conversion unit 6 is configured to recover and convert waste heat source 1 energy from combustion engines, the compressor 40 may provide features to reduce pollutant emissions while increasing engine efficiency. In this configurations there are combustion engine operating conditions (e.g., low thermal loads) that may reduce waste heat source 1 ability to provide sufficient waste heat energy to drive expander 34. To ensure compressor 40 maintains the function of compressing secondary fluid 41, the electric generator/motor may be actively configured to switch from “generator mode” to “motor mode”, thereby electrically driving compressor 40. Compressor 40 represents a usable form of converted waste heat source. Shaft 35 may be coupled to compressor 40 or any other torque requiring auxiliary system by shaft coupler 39 which may involve various types of clutch systems (e.g., electrical, hydraulic, magnetic, friction and/or centrifugally driven).

Cooling of the electric generator/motor 36 may be accomplished by means comprising the generator/motor cooling system 38. These cooling means may be particularly required for high compact “fast RpM” generator/motors and may independently or jointly include a third cooling fluid 47 to transfer thermal energy with the electric generator/motor 36 and its electric interface 43 by electric interface cooling fins 45, and/or thermal transfer to cooling fluid circulating in the condenser 7 (i.e., via condenser cooling auxiliary 49), and/or thermal transfer with secondary fluid 41 by electric interface cooling fins 46.

FIG. 12 shows a perspective view of an exemplary power conversion unit integrating the features shown in the schematic of FIG. 11. As shown in this Figure, motive and control electric power may be distributed from and provided to the power conversion unit 6 through electric bus inlet/outlet 42. Superheated fluid 21 is provided to the integral power conversion unit 6 through inlet 50, the third cooling fluid 47 may be circulated through inlet/outlet set 51, high-pressure working fluid 4 is provided at pump 37 outlet 52, condenser auxiliary cooling may be circulated via inlet outlet set 53, and secondary fluid 41 enter compressor 40 suction inlet 54 and exits at compressor 40 discharge 55. The power conversion unit 6 external surfaces may be thermally insulated. Thermal-hydraulic and mechanical coupling of the power conversion unit 6 with 1^st and/or 2^nd heat exchangers may be provided through flexible hydraulic couplers 19 and 12 to decouple vibrational and mechanical stresses produced by the heat source 1.

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.

Claims

1. A heat exchanger comprising: an outer duct defining an inlet and an outlet through which a first fluid flows in and out, respectively, of the outer duct; andan inner duct disposed inside the outer duct and defining an inner channel inside the inner duct and an outer channel between an outer surface of the inner duct and an inner surface of the outer duct;wherein the inner duct defines an internal flow channel through which a second fluid flows to exchange heat energy with the first fluid.

2. The heat exchanger of claim 1, wherein the first fluid flows in a first direction inside the outer duct, and the second fluid flows in a second direction substantially opposite to the first direction.

3. The heat exchanger of claim 1, wherein both the outer duct and inner duct are substantially cylindrical.

4. The heat exchanger of claim 1, wherein the outer duct and inner duct are substantially concentric.

5. The heat exchanger of claim 1, wherein the inner duct comprises a plurality of inner ducts disposed inside the outer duct.

6. The heat exchanger of claim 1, further comprising a plurality of fins extending from the internal flow channel to either the inner channel or outer channel to enhance heat transfer between the first fluid and the second fluid.

7. The heat exchanger of claim 1, wherein the second fluid enters the internal flow channel of the inner duct in a subcooled state and exits the internal flow channel in a superheated state.

8. A waste heat recovery system comprising: a heat exchanger comprising:an outer duct defining an inlet and an outlet through which a first fluid flows in and out, respectively, of the outer duct; andan inner duct disposed inside the outer duct and defining an inner channel inside the inner duct and an outer channel between an outer surface of the inner duct and an inner surface of the outer duct;wherein the inner duct defines an internal flow channel through which a second fluid flows to exchange heat energy with the first fluid; anda power conversion unit configured to convert the energy transferred from the first fluid to the second fluid into usable energy.

9. The system of claim 8, further comprising a condenser configured to condense the first fluid.

10. The system of claim 8, further comprising a preheating interface disposed between a heat source and the heat exchanger, wherein the preheating interface is configured to preheat the second fluid prior to entering the heat exchanger.

11. The system of claim 10, wherein the preheating interface comprises a preheating heat exchanger comprising: an inlet through which the first fluid enters to the preheating heat exchanger from the heat source;an outlet through which the first fluid exits the preheating heat exchanger and enters the heat exchanger; anda preheating channel through which the second fluid flows to preheat the second fluid prior to entering the heat exchanger.

12. The system of claim 10, wherein the preheating interface comprises a flange configured to fix the preheating heat exchanger to the heat source.

13. The system of claim 10, wherein the preheating interface comprises a flexible member configured to reduce vibration stress between the heat source and the heat exchanger.