巴西专利BR112013013387A2 parallel cycle of thermal motors

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SYSTEM AND METHOD TO CONVERTTHERMAL ENERGY AT WORK. Cycles, systems and devices ofResidual thermal energy conversion uses multiple heat exchangers waste arranged in series in a waste heat stream, and multiples thermodynamic cycles develop in parallel with the exchangers ofwaste heat in order to maximize thermal energy extraction from the fluxof waste heat by a working fluid. Parallel cycles operateat different temperature ranges with a working output oflowest temperature used to drive a fluid pumpWork. A working fluid mass management system isintegrated or connected to cycles.
公开号:BR112013013387A2
申请号:R112013013387-2
申请日:2011-11-28
公开日:2021-06-29
发明作者:Timothy James Held；Michael L.
申请人:Echogen Power Systems, Inc；
IPC主号:

专利说明:

[001] [001] This application claims priority to US patent application 13/212,631, filed August 18, 2011 which claims priority to provisional patent application US 61/417,789, filed November 29, 2010, the contents of both are incorporated in their entirety by reference to this application. BACKGROUND
[002] [002] Heat is often created as a by-product of industrial processes where streams of liquids, solids, or gases that contain heat must be exhausted to the environment or otherwise removed from the process in an effort to maintain process equipment operating temperatures industrial. Sometimes the industrial process can use heat exchange devices to capture the heat and recycle it back to the process via other process streams. Other times it is not feasible to capture and recycle this heat because it is too low in temperature or there is no readily available device to use it directly as heat. This type of heat is generally referred to as “waste” heat, and is typically discharged directly to the environment, for example, through a chimney, or indirectly through a cooling medium, such as water. In other configurations, such heat is readily available from renewable sources of thermal energy, such as heat from the sun (which can be concentrated or otherwise manipulated) or geothermal sources. These and other sources of thermal energy are intended to be included in the definition of “waste heat” as that term is used in this document.
[003] [003] Waste heat can be used by turbine generator systems that employ thermodynamic methods, such as the Rankine cycle, to convert heat into work. Typically, this method is steam-based, where waste heat is used to create steam in a boiler to drive a turbine. However, at least one of the disadvantages of a steam-based Rankine cycle is its high temperature requirement, which is not always practical as it generally requires a relatively high temperature (600°F) waste heat stream. (315.55 °C) or more, for example) or a very large total heat content. Also, the complexity of boiling water at multiple pressures/temperatures to capture heat at multiple temperature levels as the heat source stream is cooled is costly in both equipment cost and operating labor. Also, the steam-based Rankine cycle is not a realistic option for low-flow rate and/or low-temperature streams.
[004] [004] The Organic Rankine Cycle (ORC) addresses the disadvantages of steam-based Rankine cycles when replacing water with a lower boiling fluid, such as a light hydrocarbon such as propane or butane, or an HCFC fluid (by example, R245fa). However, boiling heat transfer restrictions remain, and new problems such as thermal instability, toxicity or fluid flammability are added.
[005] [005] To address these disadvantages, supercritical CO2 energy cycles have been used. The supercritical state of CO2 provides improved thermal coupling with multiple heat sources. For example, when using a supercritical fluid, the temperature slips of a process heat exchanger can be more readily matched. However, single-cycle supercritical CO2 power cycles operate at a limited pressure ratio, thus limiting the amount of temperature reduction, i.e., energy extraction, by means of the energy conversion device (typically a turbine or power expander). positive displacement). The pressure ratio is limited primarily because of the fluid's high vapor pressure at typically available condensing temperatures (eg ambient). As a result, the maximum output energy that can be achieved from a single expansion stage is limited, and the expanded fluid retains a significant amount of potentially usable energy. Although a portion of this waste energy can be recovered within the cycle by using a heat exchanger as a recuperator, and thus preheating the fluid between the pump and waste heat exchanger, this approach limits the amount of heat that can be extracted from the heat source. waste heat in a single cycle.
[006] [006] Thus, there is a need in the art for a system that can efficiently and effectively produce energy not only from waste heat, but also from a wide range of thermal sources. SUMMARY
[007] [007] Development modalities can provide a system for converting thermal energy into work. The system may include a pump configured to circulate a working fluid throughout a working fluid circuit, the working fluid being separated into a first mass stream and a second mass stream downstream of the pump, and a first exchanger. heat fluidly coupled to the pump and in thermal communication with a heat source, the first heat exchanger being configured to receive the first mass stream and transfer heat from the heat source to the first mass stream. The system may also include a first turbine fluidly coupled to the first heat exchanger and configured to expand the first mass stream, and a first recuperator fluidly coupled to the first turbine and configured to transfer residual thermal energy from the first mass stream. discharged from the first turbine to the first mass flow directed to the first heat exchanger. The system may further include a second heat exchanger fluidly coupled to the pump and in thermal communication with the heat source, the second heat exchanger being configured to receive the second mass flow and transfer heat from the heat source to the second mass flow, and a second turbine fluidly coupled to the second heat exchanger and configured to expand the second mass flow.
[008] [008] Development modalities can additionally provide another system for converting thermal energy into work. The additional system may include a pump configured to circulate a working fluid throughout a working fluid circuit, the working fluid being separated into a first mass flow and a second mass flow downstream of the pump, a first exchanger. heat fluidly coupled to the pump and in thermal communication with a heat source, the first heat exchanger being configured to receive the first mass stream and transfer heat from the heat source to the first mass stream, and a first coupled turbine fluidly to the first heat exchanger and configured to expand the first mass flow.
[009] [009] Disclosure modalities can additionally provide a method for converting thermal energy into work. The method may include circulating a working fluid with a pump through a working fluid circuit, separating the working fluid in the working fluid circuit into a first mass flow and a second mass flow, and transferring thermal energy into a first heat exchanger from a heat source to the first mass flow, the first heat exchanger being in thermal communication with the heat source. The method may also include expanding the first mass stream in a first turbine fluidly coupled to the first heat exchanger, transferring residual thermal energy in a first recuperator from the first mass stream discharged from the first turbine to the first mass stream directed to the first heat exchanger, the first recuperator being fluidly coupled to the first turbine, and transferring thermal energy in a second heat exchanger from the heat source to the second mass flow, the second heat exchanger being in thermal communication with the heat source. The method may further include expanding the second mass flow in a second turbine fluidly coupled to the second heat exchanger. BRIEF DESCRIPTION OF THE DRAWINGS
[010] [010] The present disclosure is better understood from the following detailed description when read in conjunction with the attached figures. It is emphasized that, as per standard industry practice, many features are not drawn to scale. In fact, the dimensions of the various features can be arbitrarily increased or reduced for clarity of discussion.
[011] [011] Figure 1 schematically illustrates an exemplary mode of a parallel thermal motor cycle, according to one or more disclosed modalities.
[012] [012] Figure 2 schematically illustrates another exemplary mode of a parallel thermal motor cycle, according to one or more disclosed modalities.
[013] [013] Figure 3 schematically illustrates another exemplary mode of a parallel thermal motor cycle, according to one or more disclosed modalities.
[014] [014] Figure 4 schematically illustrates another exemplary mode of a parallel thermal motor cycle, according to one or more disclosed modalities.
[015] [015] Figure 5 schematically illustrates another exemplary mode of a parallel thermal motor cycle, according to one or more disclosed embodiments.
[016] [016] Figure 6 schematically illustrates another exemplary mode of a parallel thermal motor cycle, according to one or more disclosed embodiments.
[017] [017] Figure 7 schematically illustrates an exemplary modality of a mass management system (MMS) that can be implemented with a parallel thermal motor cycle, according to one or more revealed modalities.
[018] [018] Figure 8 schematically illustrates another exemplary modality of an MMS that can be implemented with a parallel thermal motor cycle, according to one or more disclosed modalities.
[019] [019] Figures 9 and 10 schematically illustrate different system arrangements for cooling inlet a separate fluid flow (eg, air) by using the working fluid that can be used in the parallel heat engine cycles disclosed in this document. DETAILED DESCRIPTION
[020] [020] It is to be understood that the following disclosure describes several exemplary embodiments for implementing different features, structures, or functions of the invention. Exemplary embodiments of components, arrangements, and configurations are described below to simplify the present disclosure; however, these exemplary embodiments are provided as examples only and are not intended to limit the scope of the invention. Additionally, the present disclosure may repeat reference numerals and/or letters in the various exemplary embodiments and throughout the figures provided herein. This repetition is for the purpose of simplicity and clarity and does not in itself dictate a relationship between the various exemplary modalities and/or configurations discussed in the various figures. In addition, the formation of a first resource on or a second resource in the description that follows may include modalities in which the first and second resources are formed in direct contact, and may also include modalities in which additional resources can be formed by interposing the first and second resources, such that the first and second resources may not be in direct contact. Finally, the exemplary embodiments presented below may be combined in any combination of modes, that is, any element of an exemplary embodiment can be used in any other exemplary embodiment, without departing from the scope of the disclosure.
[021] [021] Additionally, certain terms are used throughout the following description and claims to refer to particular components. As those skilled in the art will appreciate, multiple entities may refer to the same component by different names and, as such, the naming convention for the elements described in this document is not intended to limit the scope of the invention, unless specifically defined otherwise in this document. Additionally, the naming convention used in this document is not intended to distinguish between components that differ in name but not function. Additionally, in the following discussion and claims, the terms "including" and "comprising" are used in an open-ended manner, and so should be interpreted to mean "including, but not limited to". All numerical values in this disclosure may be exact or approximate values unless specifically noted otherwise. In this way, various modes of disclosure may differ from the numbers, values and ranges disclosed in this document without departing from the intended scope. Furthermore, as used in the claims or descriptive report, the term "or" is intended to encompass both exclusive and inclusive cases, ie, "A or B" is intended to be identical with "at least one of A and B”, unless otherwise expressly specified in this document.
[022] [022] Figure 1 illustrates an exemplary thermodynamic cycle 100, according to one or more embodiments of the disclosure, which can be used to convert thermal energy into work by means of thermal expansion of a working fluid. Cycle 100 is characterized as a Rankine cycle and can be implemented in a heat engine device that includes multiple heat exchangers in fluid communication with a waste heat source, multiple turbines for power generation, and/or power drive power. pump, and multiple recuperators located downstream of the turbine(s).
[023] [023] Specifically, the thermodynamic cycle 100 may include a working fluid circuit 110 in thermal communication with a heat source 106 by means of a first heat exchanger 102 and a second heat exchanger 104 arranged in series. It will be appreciated that any number of heat exchangers can be used in combination with one or more heat sources. In an exemplary embodiment, the first and second heat exchangers 102, 104 may be waste heat exchangers. In other exemplary embodiments, the first and second heat exchangers 102, 104 may include first and second stages, respectively, of a single or combined waste heat exchanger.
[024] [024] Heat source 106 can derive thermal energy from a variety of high temperature sources. For example, heat source 106 may be a waste heat stream such as, but not limited to, gas turbine exhaust, process stream exhaust, or other combustion product exhaust streams such as gas turbine exhaust streams. oven or boiler exhaust. In this way, the thermodynamic cycle 100 can be configured to transform waste heat into electricity for applications ranging from down cycling in gas turbines, stationary diesel engine generator sets, industrial waste heat recovery (eg in refineries and compression stations) , and hybrid alternatives to the internal combustion engine. In other exemplary embodiments, heat source 106 can derive thermal energy from renewable thermal energy sources such as, but not limited to, solar thermal and geothermal sources.
[025] [025] Although the heat source 106 may be a fluid flow from the high temperature source itself, in other exemplary embodiments the heat source 106 may be a thermal fluid in contact with the high temperature source. The thermal fluid can deliver the thermal energy to the waste heat exchangers 102, 104 to transfer the energy to the working fluid in the circuit.
[026] [026] As illustrated, the first heat exchanger 102 may serve as a high temperature or relatively higher temperature heat exchanger adapted to receive an initial or primary flow from the heat source 106. In various exemplary embodiments of disclosure, the initial temperature of heat source 106 entering cycle 100 can range from about 400°F to greater than about 1,200°F (from about 204°C to greater than about 650°C). In the illustrated exemplary embodiment, the initial flow of heat source 106 can have a temperature of about 500°C or more. The second heat exchanger 104 can then receive the heat source 106 via a serial connection 108 downstream of the first heat exchanger
[027] [027] As can be seen, a greater amount of thermal energy is transferred from the heat source 106 through the serial arrangement of the first and second heat exchangers 102, 104, whereby the first heat exchanger 102 transfers heat in a relatively higher temperature spectrum in the waste heat stream 106 than the second heat exchanger 104. Consequently, greater power generation results from the turbines or associated expansion devices, as will be described in more detail below.
[028] [028] The working fluid circulated in the working fluid circuit 110, and in the other exemplary circuits disclosed later in this document, may be carbon dioxide (CO2). Carbon dioxide as a working fluid for power generation cycles has many advantages. It is a neutral, greenhouse-friendly working fluid that offers benefits such as non-toxicity, non-flammability, easy availability, low price and no need for recycling. Due in part to its relatively high working pressure, a CO2 system can be built that is much more compact than systems using other working fluids. The high density and volumetric thermal capacity of CO2 relative to other working fluids makes it more “energy dense” meaning that the size of all system components can be reduced considerably without losing performance. It should be noted that the use of the term "carbon dioxide" as used herein is not intended to be limited to CO2 of any particular type, purity, or degree. For example, in at least one exemplary modality industrial grade CO2 can be used, without departing from the scope of the disclosure.
[029] [029] In other exemplary embodiments, the working fluid in circuit 110 can be a binary, ternary, or other mixture of working fluids. The mixture or combination of working fluids can be selected for the unique attributes possessed by the combination of fluids within a heat recovery system as described in this document. For example, a combination of fluids such as this includes a mixture of absorbent liquid and CO2 enabling the combined fluid to be pumped in a liquid state to high pressure with less energy input than required to compress CO2. In another exemplary embodiment, the working fluid can be a combination of CO2 or supercritical carbon dioxide (ScCO2) and one or more other miscible fluids or chemical compounds. Also in other exemplary modalities, the working fluid can be a combination of
[030] [030] Use of the term "working fluid" is not intended to limit the state or phase of matter in which the working fluid is. In other words, the working fluid can be in a fluid phase, a gas phase, a supercritical phase, a subcritical state, or any other phase or state at any one or more points within the fluid cycle. The working fluid can be in a supercritical state in certain parts of circuit 110 (the “high pressure side”), and in a subcritical state in other parts of circuit 110 (the “low pressure side”). In other exemplary embodiments, the total working fluid circuit 110 may be operated and controlled in such a way that the working fluid is in a supercritical or subcritical state during the total execution of circuit 110.
[031] [031] The heat exchangers 102, 104 are arranged in series in the heat source 106, but arranged in parallel in the working fluid circuit 110. The first heat exchanger 102 can be fluidly coupled to a first turbine 112, and the second heat exchanger 104 can be fluidly coupled to a second turbine
[032] [032] The working fluid circuit 110 may additionally include a first pump 120 and a second pump 122 in fluid communication with the components of the fluid circuit 110 and configured to circulate the working fluid. The first and second pumps 120, 122 can be turbopumps, or independently driven by one or more external machines or devices, such as an engine. In an exemplary embodiment, first pump 120 can be used to circulate working fluid during normal cycle 100 operation, while second pump 122 can be nominally driven and used only to initiate cycle 100. In at least one exemplary embodiment , the second turbine 114 can be used to drive the first pump 120, but in other exemplary embodiments the first turbine 112 can be used to drive the first pump 120, or the first pump 120 can be nominally driven by a motor (not shown) .
[033] [033] The first turbine 112 can operate at a relatively higher temperature (e.g., higher turbine inlet temperature) than that of the second turbine 114, because of the temperature drop of the heat source 106 experienced through the first heat exchanger. heat
[034] [034] In one or more exemplary embodiments, the inlet pressure at the first pump 120 may exceed the vapor pressure of the working fluid by a sufficient margin to prevent vaporization of the working fluid in the local low pressure and/or high velocity regions . This is especially important with high speed pumps such as turbo pumps which can be used in the various exemplary embodiments disclosed in this document. Consequently, a traditional passive pressurization system, such as one employing a surge tank that provides only the incremental pressure of gravity relative to the fluid vapor pressure, may prove insufficient for the exemplary modalities disclosed in this document.
[035] [035] The working fluid circuit 110 may additionally include a capacitor 124 in fluid communication with one or both of the first and second recuperators 116,
[036] [036] In operation, the working fluid is separated at point 126 in the working fluid circuit 110 into a first mass flow m1 and a second mass flow m2. The first mass stream m1 is directed through the first heat exchanger 102 and subsequently expanded in the first turbine 112. Following the first turbine 112, the first mass stream m1 passes through the first recuperator 116 to transfer waste heat back to the first mass flow m1 as it is directed to the first heat exchanger 102. The second mass flow m2 can be directed through the second heat exchanger 104 and subsequently expanded into the second turbine 114. Following the second turbine 114, the second mass stream m2 passes through the second recuperator 118 to transfer waste heat back to the second mass stream m2 as it is directed to the second heat exchanger 104. The second mass stream m2 is then combined again with the first mass flow m1 at point 128 in working fluid circuit 110 to generate a combined mass flow m1+m2. The combined mass flow m1+m2 can be directed through the condenser 124 and back to the pump 120 to start the loop again. In at least one embodiment, the working fluid at pump inlet 120 is supercritical.
[037] [037] As can be seen, each stage of heat exchange with the heat source 106 can be incorporated into the working fluid circuit 110 where it is used most effectively within the complete thermodynamic cycle 100. For example, by splitting the multi-stage heat exchange, with separate heat exchangers (eg first and second heat exchangers 102, 104) or with single or multiple multi-stage heat exchangers, additional heat can be extracted from the heat source 106 for more efficient use in expansion, and primarily to obtain multiple expansions of the heat source 106.
[038] [038] Also, when using multiple turbines 112, 114 at similar or substantially similar pressure ratios, a larger fraction of the available heat source 106 can be efficiently utilized by using the waste heat from each turbine 112, 114 by means of of the recuperators 116, 118 in such a way that the waste heat is not lost or compromised. The arrangement of the recuperators 116, 118 in the working fluid circuit 110 can be optimized with the heat source 106 to maximize energy output from the multiple temperature expansions in the turbines 112, 114. By selectively joining parallel working fluid streams, the two sides of one and the other of the stoves 116, 118 can be balanced, for example, by matching heat capacity ratios; C = m • cp, where C is the heat capacity rate, m is the working fluid mass flow rate, and cp is the specific heat at constant pressure.
[039] [039] Figure 2 illustrates another exemplary embodiment of a thermodynamic cycle 200, according to one or more disclosed embodiments. The cycle 200 may be similar in some respects to the thermodynamic cycle 100 described above with reference to Figure 1. In this way, the thermodynamic cycle 200 may be better understood with reference to Figure 1, where like numbers correspond to like elements and therefore will not be described again in detail. Cycle 200 includes first and second heat exchangers 102, 104, again arranged in series in thermal communication with heat source 106, but in parallel in a working fluid circuit 210. First and second recuperators 116 and 118 they are arranged in series on the low temperature side of circuit 210 and in parallel on the high temperature side of circuit 210.
[040] [040] In circuit 210, the working fluid is separated into a first mass flow m1 and a second mass flow m2 at a point 202. The first mass flow m1 is eventually routed through the first heat exchanger 102 and expanded subsequently in the first turbine
[041] [041] The arrangement of the recuperators 116, 118 provides the combined mass flow m1 + m2 to the second recuperator 118 before reaching the condenser 124. As can be appreciated, this can increase the thermal efficiency of the working fluid circuit 210 by providing better matching of thermal capacity ratios as defined above.
[042] [042] As illustrated, the second turbine 114 can be used to drive the first or main working fluid pump 120. In other exemplary embodiments, however, the first turbine 112 can be used to drive the pump 120, without departing from the scope of the revelation. As will be discussed in more detail below, the first and second turbines 112, 114 can be operated at common turbine inlet pressures or different turbine inlet pressures by managing the respective mass flow rates in the corresponding states. and 42.
[043] [043] Figure 3 illustrates another exemplary embodiment of a thermodynamic cycle 300, according to one or more embodiments of the disclosure. Cycle 300 may be similar in some respects to thermodynamic cycles 100 and/or 200, so cycle 300 may be better understood with reference to Figures 1 and 2, where like numbers correspond to like elements and therefore will not be described from new in detail. Thermodynamic cycle 300 may include a working fluid circuit 310 utilizing a third heat exchanger 302 in thermal communication with heat source 106. Third heat exchanger 302 may be a type of heat exchanger similar to the first and second exchanger of heat 102, 104, as described above.
[044] [044] The heat exchangers 102, 104, 302 can be arranged in series in thermal communication with the heat source flow 106, and arranged in parallel in the working fluid circuit 310. The corresponding first and second recuperators 116, 118 are arranged in series on the low temperature side of circuit 310 with capacitor 124, and in parallel on the high temperature side of circuit 310. After the working fluid is separated into first and second mass streams m1, m2 at point 304, the third heat exchanger 302 may be configured to receive the first mass stream m1 and transfer heat from the heat source 106 to the first mass stream m1 before reaching the first turbine 112 for expansion. Following expansion in the first turbine 112, the first mass stream m1 is directed through the first recuperator 116 to transfer waste heat to the first mass stream m1 discharged from the third heat exchanger 302.
[045] [045] The second mass stream m2 is directed through the second heat exchanger 104 and subsequently expanded into the second turbine 114. Following the second turbine 114, the second mass stream m2 is combined again with the first mass stream m1 at the point 306 to generate the combined mass stream m1 + m2 that supplies waste heat to the second mass stream m2 in the second stove 118.
[046] [046] The second turbine 114 again can be used to drive the first or primary pump 120, or it can be driven by another device as described in this document. Second or initiator pump 122 may be provided on the low temperature side of circuit 310 and may supply circulating working fluid through a parallel heat exchanger path including second and third heat exchangers 104, 302. In an exemplary embodiment , the first and third heat exchangers 102, 302 may have essentially zero flow during the start of cycle 300. The working fluid circuit 310 may also include a butterfly valve 308, such as a pump drive butterfly valve, and a 312 shut-off valve to manage the flow of working fluid.
[047] [047] Figure 4 illustrates another exemplary embodiment of a thermodynamic cycle 400, according to one or more exemplary embodiments disclosed. Cycle 400 may be similar in some respects to thermodynamic cycles 100, 200 and/or 300, and as such cycle 400 can be better understood with reference to figures 1-3, where like numbers correspond to like and non-like elements. will be described again in detail. Thermodynamic cycle 400 may include a working fluid circuit 410 where first and second reclaimers 116, 118 are combined into a single reclaimer 402 or otherwise replaced by it. The stove 402 may be of a similar type to the stoves 116, 118 described herein, or it may be another type of stove or heat exchanger known to those skilled in the art.
[048] [048] As illustrated, the recuperator 402 can be configured to transfer heat to the first mass stream m1 as it enters the first heat exchanger 102 and to receive heat from the first mass stream m1 as it leaves the first turbine 112. Reclaimer 402 can also transfer heat to second mass stream m2 as it enters second heat exchanger 104 and can receive heat from second mass stream m1 as it exits second turbine 114. combined mass flow m1+m2 flows out of the recuperator 402 and into the condenser 124.
[049] [049] In other exemplary embodiments, the stove 402 can be enlarged, as indicated by the dashed extension lines illustrated in Figure 4, or otherwise adapted to receive the first mass flow m1 entering and leaving the third heat exchanger 302 Consequently, additional thermal energy can be extracted from the recuperator 304 and directed to the third heat exchanger 302 to increase the temperature of the first mass stream m1.
[050] [050] Figure 5 illustrates another exemplary embodiment of a thermodynamic cycle 500 according to the disclosure. Cycle 500 may be similar in some respects to thermodynamic cycle 100 and, as such, may be better understood with reference to Figure 1 noted above, where like numbers correspond to like elements that will not be described again. Thermodynamic cycle 500 may have a working fluid circuit 510 substantially similar to the working fluid circuit 110 of Figure 1, but with a different arrangement from the first and second pumps 120,
[051] [051] Figure 6 illustrates another exemplary embodiment of a thermodynamic cycle 600 according to the disclosure. Cycle 600 may be similar in some respects to thermodynamic cycle 300 and, as such, may be better understood with reference to Figure 3 indicated above, where like numbers correspond to like elements and will not be further described in detail. The thermodynamic cycle 600 may have a working fluid circuit 610 substantially similar to the working fluid circuit 310 of Figure 3, but with the addition of a third reclaimer 602 that extracts additional thermal energy from the combined mass flow m1 + m2 discharged from the second recuperator 118. In this way, the temperature of the first mass stream m1 entering the third heat exchanger 302 can be increased before receiving waste heat transferred from the heat source 106.
[052] [052] As illustrated, the recuperators 116, 118, 602 can operate as separate heat exchange devices. In other exemplary embodiments, however, the stoves 116, 118, 602 can be combined into a single stove, similar to the stove 402 described earlier with reference to Figure 4.
[053] [053] As illustrated by each exemplary thermodynamic cycle 100-600 described in this document (meaning cycles 100, 200, 300, 400, 500 and 600), the cycle and parallel heat exchange arrangement incorporated into each fluid circuit 110-610 work (meaning circuits 110, 210, 310, 410, 510 and 610) enables more power generation from a given heat source 106 by raising the power turbine inlet temperature to unattainable levels in a single cycle, thus resulting in greater thermal efficiency for every 100-600 exemplary cycle. The addition of lower temperature heat exchange cycles via the second and third heat exchangers 104, 302 enables recovery of a greater fraction of available energy from the heat source 106. Individual heat exchangers can be optimized for further improvement in thermal efficiency.
[054] [054] Other variations that can be implemented in any of the exemplary embodiments disclosed include, without limitation, the use of two-stage or multi-stage pumps 120, 122 to optimize inlet pressures to turbines 112, 114 at any temperature corresponding input of one or another turbine 112, 114. In other exemplary embodiments, the turbines 112, 114 may be coupled together such as by using additional turbine stages in parallel on a shared turbine power axis. Other variations considered in this document are, but not limited to, the use of additional turbine stages in parallel on a turbine driven pump shaft; coupling turbines by means of a gearbox; the use of different stove arrangements to optimize overall efficiency; and the use of expanders and alternation pumps in place of turbomachinery. It is also possible to connect the output of the second turbine 114 to the generator or electricity production device being driven by the first turbine 112, or even to integrate the first and second turbines 112, 114 into a single piece of turbomachinery, such as a multistage turbine using separate blades/discs on a common shaft, or as separate stages of a radial turbine driving a main gear using separate sprockets for each radial turbine. Other exemplary variations are also considered where the first and/or second turbine 112, 114 are coupled to the main pump 120 and an engine-generator (not shown) that serves as both a starter motor and a generator.
[055] [055] Each of the described cycles 100-600 can be implemented in a variety of physical modalities, including, but not limited to, fixed or integrated installations, or as a stand-alone device such as a motor or portable residual thermal "platform" . The exemplary waste heat engine platform can arrange each working fluid circuit 110-610 and related components such as turbines 112, 114, recuperators 116, 118, condensers 124, pumps 120, 122, valves, supply systems and working fluid and mechanical control and electronic controls are consolidated as a single unit. An exemplary residual heat engine platform is described and illustrated in copending US patent application 12/631,412 entitled "Thermal Energy Conversion Device", filed December 9, 2009, the contents of which are incorporated herein by reference to the non-inconsistent extent. with the present disclosure.
[056] [056] Exemplary modalities disclosed in this document may further include the incorporation and use of a mass management system (MMS) in connection with the thermodynamic cycles 100-600 described or integrated thereto. MMS can be provided to control the inlet pressure to the first pump 120 by adding and removing mass (i.e., working fluid) from the 100-600 working fluid circuit, thus increasing the efficiency of the 100-600 cycles. In an exemplary modality, the MMS operates on the 100-600 cycle semipassively and uses sensors to monitor pressures and temperatures on the high pressure side (from pump 120 output to expander inlet 116, 118) and low pressure side (from expander output 112, 114 to pump input 120) of circuit 110-610. The MMS may also include valves, tank heaters or other equipment to facilitate movement of working fluid in and out of working fluid circuits 110-610 and a mass control tank for storing working fluid. Exemplary modalities of MMS are illustrated and described in co-pending US patent applications 12/631,412, 12/631,400 and 12/631,379, each filed December 4, 2009, in US patent application 12/880,428, filed September 13 2010, and in PCT application US2011/29486, filed March 22, 2011.
[057] [057] Referring now to Figures 7 and 8, exemplary mass management systems 700 and 800, respectively, are illustrated which can be used in combination with the thermodynamic cycles 100-600 described in this document, in one or more exemplary modalities. System connection points A, B and C as shown in figures 7 and 8 (only points A and C are shown in figure 8) correspond to system connection points A, B and C shown in figures 1-6 . In this way, each of the MMS 700 and 800 can be fluidly coupled to the thermodynamic cycles 100-600 of figures 1-6 at the corresponding system connection points A, B and C (if applicable). The exemplary MMS 800 stores a working fluid at a low temperature (subambient) and therefore at low pressure, and the exemplary MMS 700 stores a working fluid at or near ambient temperature. As discussed earlier, the working fluid can be CO2, but it can also be other working fluids without departing from the scope of the disclosure.
[058] [058] In exemplary operation of the MMS 700, a working fluid storage tank 702 is pressurized by bypass working fluid from the working fluid circuit(s) 110-610 through a first valve 704 at connection point A. When required additional working fluid may be added to the working fluid circuit(s) 110-610 by opening a second valve 706 arranged near the bottom of storage tank 702 in order to allow the Additional working fluid flows through connection point C, arranged upstream of pump 120 (figures 1-6). Adding working fluid to circuit(s) 110-610 at connection point C can serve to raise the inlet pressure of the first pump 120. To extract fluid from the working fluid circuit(s) 110- 610, and thereby decrease the inlet pressure of the first pump 120, a third valve 708 can be opened to allow cold pressurized fluid to enter the storage tank via connection point B. Although not necessary in every application, the MMS 700 can also include a transfer pump 710 configured to remove working fluid from tank 702 and inject it into working fluid circuit(s) 110-610.
[059] [059] The MMS 800 of figure 8 uses only the two connection or system interface points A and C. The valve controlled interface A is not used during the control phase (eg normal unit operation), and is provided only to pre-pressurize working fluid circuit(s) 110-610 with steam so that the temperature of circuit(s) 110-610 remains above a minimum threshold during filling. A vaporizer can be included to use ambient heat to convert the working fluid from the liquid phase to approximately an ambient temperature vapor phase of the working fluid. Without the vaporizer the system could drop in temperature significantly during filling. The vaporizer also provides vapor return to storage tank 702 to make up for the lost volume of liquid that has been extracted, thereby acting as a pressure builder. In at least one embodiment, the vaporizer can be electrically heated or heated by a secondary fluid. In operation, when it is desired to increase the suction pressure of the first pump 120 (figures 1-6), working fluid can be selectively added to the working fluid circuit(s) 110-610 by pumping it with a 802 transfer pump provided at or near connection C. When it is desired to reduce the suction pressure of pump 120, working fluid is selectively withdrawn from the system at interface C and expanded through one or more valves 804 and 806 to the relatively low storage pressure of storage tank 702.
[060] [060] Under many conditions, the expanded fluid following valves 804, 806 will be two-phase (ie, vapor + liquid). To prevent the pressure within storage tank 702 from exceeding its normal operating limits, a small vapor compression refrigeration cycle, including a steam compressor 808 and accompanying condenser 810, may be provided. In other embodiments, the condenser can be used as the vaporizer, where condenser water is used as a heat source rather than a heat sink. The refrigeration cycle can be configured to lower the temperature of the working fluid and sufficiently condense the steam to maintain storage tank 702 pressure in its design condition. As will be appreciated, the vapor compression refrigeration cycle can be integrated into the MMS 800, or it can be a standalone vapor compression cycle with an independent refrigerant loop.
[061] [061] The working fluid contained within storage tank 702 will tend to stratify with the higher density working fluid at the bottom of tank 702 and the lower density working fluid at the top of tank 702. work can be in the liquid phase, vapor phase or both, or be supercritical; if the working fluid is in both the vapor and liquid phases, there will be a phase boundary separating one working fluid phase from the other with the denser working fluid at the bottom of storage tank 702. Thus, the MMS 700, 800 may be able to deliver to circuits 110-610 the densest working fluid within storage tank 702.
[062] [062] All various controls or changes described for environment and working fluid status across all 110-610 working fluid circuits, including temperature, pressure, flow direction and rate, and component operation such as pumps 120, 122 and turbines 112, 114 may be monitored and/or controlled by a control system 712, shown generally in Figures 7 and 8. Exemplary control systems compatible with the modalities of this disclosure are described and illustrated in Co-pending US patent application 12/880,428 entitled "Heat Engine and Heat to Electricity Systems and Methods with a Working Fluid Fill System", filed September 13, 2010, and incorporated by reference as indicated above.
[063] [063] In an exemplary embodiment, the control system 712 may include one or more proportional controllers,
[064] [064] Each MMS 700, 800 may be communicably connected to a 712 control system like this in such a way that control of the various valves and other equipment described in this document is automated or semi-automated and reacts to system performance data obtained through the multiple sensors located throughout the 110-610 circuits, and also react to environment and environmental conditions. That is, the control system 712 can be in communication with each of the components of the MMS 700, 800 and be configured to control their operation to perform the function of the thermodynamic cycle(s) 100-600 more efficiently. For example, the 712 control system can be in communication (via wires, RF signal, etc.) with each of the valves, pumps, sensors, etc. in the system and be configured to control the operation of each of the components in accordance with a predetermined control software, algorithm, or other control mechanism. This may prove advantageous for controlling temperature and pressure of the working fluid at the inlet of the first pump 120, to actively increase the suction pressure of the first pump 120 by decreasing the compressibility of the working fluid. Doing so can prevent damage to the first pump 120 as well as increase the total pressure ratio of the thermodynamic cycle(s) 100-600, thus improving efficiency and power output.
[065] [065] In one or more exemplary embodiments, it may be advantageous to maintain the suction pressure of the pump 120 above the boiling pressure of the working fluid at the pump 120 inlet. A method of controlling the working fluid pressure on the temperature side The low of working fluid circuit(s) 110-610 is to control the temperature of the working fluid in storage tank 702 of figure
[066] [066] Referring now to figures 9 and 10, cooling systems 900 and 1000, respectively, can also be employed in connection with any of the cycles described above in order to provide cooling for other areas of an industrial process including, but not limited to this, pre-cooling the inlet air of a gas turbine or other air aspirating engines, thus allowing a greater engine power output. System connection points B and D or C and D in figures 9 and can correspond to system connection points B, C and D in figures 1-6. In this way, each of the cooling systems 900, 1000 can be fluidically coupled to one or more of the 110-610 working fluid circuits of figures 1-6 at corresponding system connection points B, C and/or D (where applicable).
[067] [067] In the cooling system 900 of figure 9, a portion of the working fluid can be drawn from the 110-610 working fluid circuit(s) at system connection C. The pressure of that portion of fluid is reduced by means of an expansion device 902, which may be a valve, orifice, or fluid expander such as a turbine or positive displacement expander. This expansion process lowers the temperature of the working fluid. Heat is then added to the working fluid in an evaporator 904 heat exchanger, which lowers the temperature of an external process fluid (eg, air, water, etc.). The working fluid pressure is then increased again by the use of a compressor 906, after which it is reintroduced into the working fluid circuit(s) 110-610 via system connection D.
[068] [068] Compressor 906 can be engine driven or turbine driven, a dedicated turbine or an additional flywheel added to a primary turbine in the system. In other exemplary embodiments, compressor 906 may be integrated with main working fluid circuit(s) 110-610. Also in other exemplary embodiments, the compressor 906 can take the form of a fluid ejector, with motive fluid supplied by the system connection point A, and discharging to the system connection point D, upstream of the condenser 124 (figures 1 -6).
[069] [069] Cooling system 1000 of figure 10 may also include a compressor 1002, substantially similar to compressor 906 described earlier. Compressor 1002 can take the form of a fluid ejector, with motive fluid supplied by the 110-610 working fluid cycle(s) via connection point A (not shown, but corresponding to point A in figures 1- 6), and discharging to cycle(s) 110-610 via connection point D. In the illustrated exemplary mode, the working fluid is extracted from circuit(s) 110-610 via connection point B and pre-cooled by a heat exchanger 1004 before being expanded in an expansion device 1006, similar to the expansion device 902 described above. In an exemplary embodiment, heat exchanger 1004 may include a water-CO2 or air-CO2 heat exchanger. As can be seen, the addition of heat exchanger 1004 can provide additional cooling capacity above what is possible with the 900 cooling system shown in figure 9.
[070] [070] The expressions "upstream" and "downstream" as used in this document are intended to more clearly describe various exemplary modalities and configurations of disclosure. For example, "upstream" generally means to or against the working fluid flow direction during normal operation, and "downstream" generally means with or in the working fluid flow direction during normal operation. .
[071] [071] The foregoing outlined resources of various modalities so that those skilled in the art could better understand the present disclosure. Those skilled in the art should understand that they can readily use the present disclosure as a basis for designing or modifying other processes and structures to accomplish the same purposes and/or achieve the same advantages of the modalities introduced herein. Those skilled in the art should also appreciate that such equivalent constructions do not depart from the spirit and scope of the present disclosure, and that they may make various changes, substitutions, and alterations to this document without departing from the spirit and scope of the present disclosure.

权利要求:
Claims (15)
[1]
1. System for converting thermal energy into work, characterized in that it comprises: a pump configured to circulate a working fluid throughout a working fluid circuit, the working fluid being separated into a first mass flow and a second mass flow downstream of the pump, wherein the working fluid comprises carbon dioxide and the working fluid is in a supercritical state in at least a portion of the working fluid circuit; a first heat exchanger fluidly coupled to the pump and in thermal communication with a heat source, the first heat exchanger being configured to receive the first mass stream and transfer heat from the heat source to the first mass stream; a first turbine fluidly coupled to the first heat exchanger and configured to expand the first mass flow; a first recuperator fluidly coupled to the first turbine and configured to transfer residual thermal energy from the first mass stream discharged from the first turbine to the first mass stream directed to the first heat exchanger; a second heat exchanger fluidly coupled to the pump and in thermal communication with the heat source, the second heat exchanger being configured to receive the second mass stream and transfer heat from the heat source to the second mass stream; and a second turbine fluidly coupled to the second heat exchanger and configured to expand the second mass flow.
[2]
2. System according to claim 1, characterized in that the working fluid is in a supercritical state within a high pressure side of the working fluid circuit and in a subcritical state within a low pressure side of the working fluid circuit.
[3]
3. System according to claim 1, characterized in that the first and second heat exchangers are arranged in series in the heat source, and the first mass flow circulates in parallel with the second mass flow.
[4]
4. System according to claim 1, characterized in that it further comprises a second recuperator fluidly coupled to the second turbine and configured to transfer residual thermal energy from the second mass stream discharged from the second turbine to the second mass stream directed to the second heat exchanger, and the first and second recuperators are arranged in series on a low temperature side of the working fluid circuit, and the first and second recuperators are arranged in parallel on a high temperature side of the working fluid circuit. working fluid.
[5]
5. System according to claim 1, characterized in that it further comprises a second recuperator fluidly coupled to the second turbine and configured to transfer residual thermal energy from a combined mass flow of the first and second mass flows to the first mass flow directed to the first heat exchanger.
[6]
6. System according to claim 1, characterized in that it further comprises a mass management system operatively connected to the working fluid circuit via at least two connection points, the mass management system being configured to control the amount of working fluid within the working fluid circuit.
[7]
7. System according to claim 1, characterized in that the second mass flow is discharged from the second turbine and recombined with the first mass flow to generate a combined mass flow; and further comprises: a second recuperator fluidly coupled to the second turbine and configured to transfer residual thermal energy from the combined mass stream to the second mass stream directed to the second heat exchanger; and a third heat exchanger in thermal communication with the heat source and arranged between the pump and the first heat exchanger, the third heat exchanger being configured to receive and transfer heat to the first mass stream before passing through the first exchanger of heat.
[8]
8. System according to claim 7, characterized in that the first and second recuperators are arranged in series on a low temperature side of the working fluid circuit, and the first and second recuperators are arranged in parallel on a high temperature side of the working fluid circuit.
[9]
9. System according to claim 7, characterized in that it further comprises a third stove arranged between the pump and the third heat exchanger, wherein the third stove is configured to transfer residual heat from the combined mass flow discharged from the second recuperator for the first mass flow, before the first mass flow is introduced to the third heat exchanger.
[10]
10. System according to claim 7, characterized in that an inlet pressure in the first turbine is substantially equal to an inlet pressure in the second turbine, and that the discharge pressure in the first turbine is different from the discharge pressure in the second turbine.
[11]
11. Method for converting thermal energy into work, characterized in that it comprises: circulating a working fluid with a pump throughout a working fluid circuit, wherein the working fluid comprises carbon dioxide and the working fluid is in a supercritical state in at least a portion of the working fluid circuit; separating the working fluid in the working fluid circuit into a first mass flow and a second mass flow; transferring thermal energy in a first heat exchanger from a heat source to the first mass stream, the first heat exchanger being in thermal communication with the heat source;
expanding the first mass flow in a first turbine fluidly coupled to the first heat exchanger; transferring residual thermal energy in a first reclaimer from the first mass stream discharged from the first turbine to the first mass stream directed to the first heat exchanger, the first reclaimer being fluidically coupled to the first turbine; transferring thermal energy in a second heat exchanger from the heat source to the second mass flow, the second heat exchanger being in thermal communication with the heat source; and expanding the second mass flow in a second turbine fluidly coupled to the second heat exchanger.
[12]
12. Method according to claim 11, characterized in that it further comprises transferring residual thermal energy in a second recuperator from the second mass stream discharged from the second turbine to the second mass stream directed to the second heat exchanger, the second recuperator being fluidly coupled to the second turbine.
[13]
13. The method of claim 12, further comprising transferring thermal energy in a third heat exchanger from the heat source to the first mass stream before passing through the first heat exchanger, the third heat exchanger. heat being in thermal communication with the heat source and arranged between the pump and the first heat exchanger.
[14]
14. Method according to claim 13, characterized in that it further comprises transferring waste heat in a third reclaimer from a combined mass stream of the first and second mass streams discharged from the second reclaimer to the first mass stream before the first mass flow being introduced into the third heat exchanger, the third recuperator being arranged between the pump and the third heat exchanger.
[15]
15. Method according to claim 11, characterized in that it further comprises transferring residual thermal energy in a second recuperator of a combined mass flow of the first and second mass flows to the first mass flow directed to the first exchanger of heat, the second recuperator being fluidly coupled to the second turbine.
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