CN111699302A - Method, apparatus and thermodynamic cycle for generating power from a variable temperature heat source - Google Patents
Method, apparatus and thermodynamic cycle for generating power from a variable temperature heat source Download PDFInfo
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- CN111699302A CN111699302A CN201880088116.1A CN201880088116A CN111699302A CN 111699302 A CN111699302 A CN 111699302A CN 201880088116 A CN201880088116 A CN 201880088116A CN 111699302 A CN111699302 A CN 111699302A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/04—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled condensation heat from one cycle heating the fluid in another cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/32—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines using steam of critical or overcritical pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/02—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of multiple-expansion type
- F01K7/025—Consecutive expansion in a turbine or a positive displacement engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
- F01K9/003—Plants characterised by condensers arranged or modified to co-operate with the engines condenser cooling circuits
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The invention relates to a cascade method for generating power from a variable temperature heat source, comprising: circulating a primary working fluid selected from perfluorinated compounds (such as perfluoro-2-methylpentane/perfluorohexane) in the primary loop (2) according to a supercritical organic Rankine cycle, operatively coupling a variable temperature heat source (9) with the primary working fluid of the primary loop (2) in a boiler (4) to heat and evaporate the primary working fluid; circulating an auxiliary working fluid in an auxiliary circuit (3) according to an auxiliary Rankine cycle; thermally coupling the expanded primary working fluid of the primary rankine cycle in cascade with a secondary working fluid of the secondary rankine cycle to cool the primary working fluid and heat and evaporate the secondary working fluid by heat transfer from the primary rankine cycle to the secondary rankine cycle before the secondary working fluid is expanded in an auxiliary expander (12).
Description
Technical Field
The present invention relates to a method, apparatus and cascaded thermodynamic cycle for generating mechanical and/or electrical power from a variable temperature heat source. This type of process/apparatus/cycle utilizes a variable temperature heat source to heat one or more working fluids, which transfers heat to the working fluid, which is power transferred and expanded in one or more expanders. As non-limiting examples, these variable temperature heat sources may be: flue gas from gas turbines, flue gas and heat from endothermic engines, CSP applications for solar collectors with oil collectors or salts (liquid-carrying, non-vapour), compressor interactive heating and cooling, intercooler cooling, engine oil and jackets for endothermic engines, industrial waste heat (steel works, cement works, glass works, petrochemical process heat, etc.), combustion flue gas from biomass and waste, etc.
Background
Publication US7942001 shows a system for generating power from waste heat of an internal combustion engine (e.g. a microturbine or a reciprocating engine) using a cascaded organic rankine cycle. The pair of ORC systems are combined and their respective organic fluids are selected such that the organic fluid (toluene) of the first organic rankine cycle condenses at a condensation temperature significantly higher than the boiling point of the organic fluid (R245fa) of the second organic rankine cycle. A single heat exchanger serves as a condenser for the first rankine organic cycle and an evaporator for the second organic rankine cycle.
Publication US8869531 shows a cascade system and method for recovering energy from waste heat. The system comprises: an exchanger coupled with a waste heat source to heat a working fluid (CO)2Propane, ammonia); a first expansion device that receives the first stream from the exchanger to expand it and rotate the shaft; a first heat exchanger coupled to the first expansion device to receive the first stream from the first expansion device and transfer heat from the first stream to a second stream of the working fluid; a second expansion device that receives the second stream from the first heat exchanger; and a second heat exchanger fluidly coupled to the second expansion device to receive the second stream from the second expansion device and to transfer heat from the second streamTo a combined stream of the first and second streams.
Publication US6857268 is a cascaded closed loop cycle for recovering power from a thermal energy source having a temperature high enough to vaporize light hydrocarbons such as propane or propylene. The light hydrocarbons are vaporized in a plurality of indirect exchangers, expanded in a plurality of cascaded turbines, and condensed in a cooling system. The light hydrocarbons are then pressurized with a pump and returned to the indirect heat exchanger.
Publication EP2607635 shows a cascaded organic rankine cycle provided with a top cycle and a bottom cycle in thermal communication with the top cycle through a condenser/evaporator in which the working fluid of the bottom cycle (R245fa) is subsequently evaporated and then heated, the working fluid of the top cycle (siloxane MM) being first cooled and then condensed. In this way, the percentage of total heat transferred from the working fluid of the top cycle during condensation is equal to or lower than the percentage of total heat transferred to the bottom cycle during evaporation.
Disclosure of Invention
Definition of
The term "high temperature" means that the maximum temperature of the variable temperature heat source is between 300 and 600 ℃.
The term "stable and non-flammable" with reference to the working fluid means that the fluid is stable, i.e., it does have a significant kinetic reaction, and is non-flammable under operating conditions at the operating temperature, i.e., its auto-ignition temperature is above the maximum temperature of the variable temperature heat source from which it receives heat.
The term "reduced temperature" of a fluid refers to the ratio between the temperature of the fluid in degrees kelvin and the critical temperature of the fluid in degrees kelvin.
The term "reduced pressure" refers to the ratio between the pressure of a fluid and the critical pressure of the fluid.
SUMMARY
In this context, the applicant has realised that there is a need to improve the efficiency of a method/apparatus/cycle for generating mechanical and/or electrical power from a variable temperature heat source, for example to generate more power for the same available source.
The applicant has in particular perceived the need to propose an even more efficient cycle that allows a better utilization of the waste heat contained in a variable temperature heat source, such as the one described above.
In particular, the applicant defines the following objectives:
more efficient cascading methods, apparatus and cycles are designed to take advantage of variable temperature resources, preferably at high temperatures;
cascading methods, devices and cycles are designed which allow more heat to be extracted from the resources to cool them to lower temperatures than in the prior art.
Processes, devices and cycles designed to be less irreversible and therefore have better conversion performance;
designing intrinsically safe methods, plants and cycles, especially taking into account the fire risks posed by the working fluids used up to now;
relatively economical methods, apparatus and circuits are devised, particularly but not exclusively with reference to the art for expanders.
The applicant has found that the above and other objects can be achieved by performing a plurality of cascade cycles, the top cycle of which, i.e. preferably in direct heat exchange with a high temperature source, is an organic supercritical rankine cycle, the organic working fluid of which is selected from the cycle of perfluorinated compounds.
In particular, the objects described and other objects among others are substantially achieved by a method, a device and a cycle of the type claimed in the appended claims and/or described in the following aspects.
In a separate aspect, the present invention relates to a cascade method for generating power from a variable temperature heat source.
Preferably, the method comprises: according to a main organic supercritical rankine cycle, a main working fluid selected from perfluorinated compounds is circulated in a main circuit, wherein said main working fluid is heated and evaporated, expanded in a main expander, preferably belonging to a generator or to a mechanical user, cooled, condensed and heated and evaporated again. The term "supercritical" cycle in this specification and claims means that supercritical is the state of the working fluid flowing into the turbine (whereas condensation is subcritical).
Preferably, the method comprises: a variable temperature heat source, preferably flue gas, is operatively coupled to the primary working fluid of the primary circuit in the boiler to perform said heating and evaporation of the primary working fluid.
Preferably, the variable temperature heat source is directly coupled to the primary working fluid, i.e. without the intervention of an intermediate fluid.
Preferably, the method comprises: according to an auxiliary rankine cycle, an auxiliary working fluid is circulated in an auxiliary circuit, wherein the auxiliary working fluid is heated and evaporated, expanded in an auxiliary expander, preferably belonging to an auxiliary generator or to an auxiliary mechanical user, cooled, condensed and heated and evaporated again.
Preferably, the method comprises: thermally coupling the expanded primary working fluid of the primary rankine cycle to the secondary working fluid of the secondary rankine cycle to cool the primary working fluid and heat and evaporate the secondary working fluid by heat transfer from the primary rankine cycle to the secondary rankine cycle before the secondary working fluid is expanded at the secondary expander.
In one aspect, the primary working fluid is preheated in a primary heat exchanger or a first heat exchanger.
In a separate aspect, the present invention relates to a cascade device for generating power from a variable temperature heat source.
Preferably, the apparatus comprises: a primary loop, comprising: a boiler operatively coupled to a variable temperature heat source (preferably flue gas); a main expander; a primary or first heat exchanger; a main condenser; a main pump; a main pipe connecting the boiler, the main expander, the main heat exchanger, the main condenser, and the main pump to each other; a primary working fluid selected from perfluorinated compounds and flowing in the primary loop to effect a supercritical organic rankine cycle.
Preferably, the apparatus comprises: at least one auxiliary circuit thermally coupled to the main circuit and including an auxiliary expander; wherein the secondary working fluid enters the secondary expander after exchanging heat with the primary working fluid exiting the primary expander.
In another independent aspect, the invention relates to the combination of a cascade device for generating power from a variable temperature heat source as claimed and described with a primary working fluid selected from perfluorinated compounds.
In another independent aspect, the present invention relates to a cascade thermodynamic cycle for generating power from a variable temperature heat source.
Preferably, the cascade cycle comprises: a supercritical primary rankine cycle having an organic primary working fluid selected from perfluorinated compounds; wherein the primary rankine cycle receives heat from a variable temperature heat source, preferably flue gas.
Preferably, the cascade cycle comprises: an auxiliary Rankine cycle having an auxiliary working fluid; wherein the secondary cycle is thermally coupled to the primary cycle to receive heat from the primary cycle after expansion of the primary working fluid and before expansion of the secondary working fluid.
Preferably, in the main cycle: the reduced temperature of the primary working fluid immediately prior to the primary expansion is between 1.1 and 1.7.
Preferably, in the main cycle: the reduced pressure of the primary working fluid immediately prior to the primary expansion is between 1 and 2.5.
Preferably, in the main cycle: the reduced condensation temperature of the primary working fluid is between 0.6 and 0.9.
Preferably, in the main cycle: the reduced condensing pressure of the primary working fluid is between 0.005 and 0.3.
The applicant has verified that the present invention allows the efficient and effective utilization of high temperature waste heat sources with relatively economical and intrinsically stable and safe equipment.
In particular, the applicant has verified that the cascade configuration of cycles and circuits allows to use the heat source in series, to cool the flue gases sufficiently, and to obtain a lower irreversibility and therefore better conversion performance.
The applicant has verified that the working fluid reaching the highest temperature, i.e. directly in heat exchange with the high-temperature and variable-temperature source, is a fluid chosen from perfluorinated compounds and that it is thermally stable and non-combustible at high operating temperatures.
The applicant has verified that the cascade configuration of cycles and circuits and the use of a working fluid chosen from perfluorinated compounds allows to use the same technology on all cycles and circuits, in particular the technology of expanders, also the technology of main expanders directly coupled with high temperature variable temperature heat sources.
In at least one of the above aspects, the invention may have one or more of the other preferred aspects described below.
In one aspect, a plurality of auxiliary working fluids are circulated in respective auxiliary circuits arranged in a cascade according to respective auxiliary rankine cycles.
In one aspect, the apparatus comprises: a plurality of auxiliary circuits arranged in cascade and thermally coupled to each other.
Below the main circulation/circuit there may be a plurality of circulation/circuits arranged in series or one after the other in cascade, which exchange heat between them. Each cycle/loop receives heat from the top cycle/loop and transfers heat to the bottom cycle/loop.
In one aspect, the method comprises: circulating an additional auxiliary working fluid in an additional auxiliary circuit according to an additional auxiliary rankine cycle, wherein the additional auxiliary working fluid is heated and evaporated, expanded in an additional auxiliary expander preferably belonging to an additional auxiliary generator or an auxiliary mechanical user, cooled, condensed, and reheated and evaporated; thermally coupling the expanded auxiliary working fluid of the auxiliary Rankine cycle with an additional auxiliary working fluid of an additional auxiliary Rankine cycle to cool the auxiliary working fluid and heat and evaporate the additional auxiliary working fluid by heat transfer from the auxiliary Rankine cycle to the additional auxiliary Rankine cycle before the additional auxiliary working fluid is expanded in an additional auxiliary expander.
In one aspect, the apparatus comprises: at least one additional auxiliary circuit thermally coupled to the auxiliary circuit and including an additional auxiliary expander; wherein additional auxiliary working fluid enters the additional auxiliary expander after heat exchange with the auxiliary working fluid exiting the auxiliary expander.
In one aspect, a cascade cycle comprises: an additional auxiliary Rankine cycle with an additional auxiliary working fluid; wherein the additional auxiliary cycle is thermally coupled to the auxiliary cycle to receive heat from the auxiliary cycle after the expansion of the auxiliary working fluid and before the expansion of the additional auxiliary working fluid.
In one aspect, the primary working fluid selected from perfluorinated compounds is selected from: perfluoro-2-methylpentane/perfluoro-hexane (Flutec)tmPP1), perfluoromethylcyclohexane (PP2), perfluoro-1, 3-dimethylcyclohexane (PP3), hexafluorobenzene.
In one aspect, the primary working fluid and the secondary working fluid are the same fluid.
In one aspect, the pressure of the same fluid entering the main expander and the auxiliary expander is substantially the same.
In one aspect, the secondary working fluid is different from the primary working fluid.
In one aspect, the secondary working fluid is an organic fluid.
In one aspect, the secondary working fluid is selected from: cyclopentane, isopentane, isohexane, hexane, pentane, R245fa, R1234 yf.
In one aspect, the maximum temperature of the variable temperature heat source is between 900 and 300 ℃.
In one aspect, the reduced temperature of the secondary working fluid immediately prior to the secondary expansion is between 0.8 and 1.2.
In one aspect, the reduced pressure of the secondary working fluid immediately prior to the secondary expansion is between 0.3 and 1.2.
In one aspect, the reduced condensation temperature of the secondary working fluid is between 0.5 and 0.75.
In one aspect, the reduced condensing pressure of the secondary working fluid is between 0.001 and 0.1.
In one aspect, the temperature of the primary working fluid immediately prior to the primary expansion is between 250 ℃ and 400 ℃.
In one aspect, the pressure of the main working fluid immediately prior to the main expansion is between 25 bar and 50 bar.
In one aspect, the condensation temperature of the primary working fluid is between 10 ℃ and 50 ℃.
In one aspect, the condensation pressure of the primary working fluid is between 0.1 bar and 1 bar.
In one aspect, the temperature of the secondary working fluid immediately prior to the secondary expansion is between 150 ℃ and 300 ℃.
In one aspect, the pressure of the secondary working fluid immediately prior to the secondary expansion is between 20 bar and 50 bar.
In one aspect, the condensation temperature of the secondary working fluid is between 10 ℃ and 50 ℃.
In one aspect, the condensing pressure of the secondary working fluid is between 0.1 bar and 2 bar.
The condensing pressure at the condensing temperature makes it possible to use an air condenser, since the condensing pressure does not differ much from the atmospheric pressure.
In one aspect, the condensation temperature of the primary working fluid is substantially equal to the condensation temperature of the secondary working fluid.
In one aspect, the secondary loop is a branch of the primary loop.
In one aspect, the thermal coupling of the primary working fluid to the secondary working fluid is performed in a second heat exchanger located downstream of the primary expander and upstream of the secondary expander. The second heat exchanger is a high temperature heat exchanger and the main heat exchanger is a low temperature heat exchanger.
In one aspect, the secondary working fluid is separated from the primary working fluid upstream of the primary expander and the secondary working fluid and the primary working fluid are reconnected downstream of the primary expander and the secondary expander.
In one aspect, the secondary working fluid reconnects the primary working fluid in the primary heat exchanger.
In one aspect, the secondary working fluid is a primary working fluid.
In one aspect, the plant further comprises a second heat exchanger located on the primary circuit downstream of the primary expander and placed on the secondary circuit upstream of the secondary expander; the working fluid of the primary circuit exchanges heat with the working fluid of the secondary circuit in a second heat exchanger.
In one aspect, the auxiliary circuit branches from the primary circuit at a point located between the primary heat exchanger and the boiler and reconnects the primary circuit in the primary heat exchanger.
In one aspect, an apparatus having a single working fluid includes a single pump, i.e., a main pump.
In one aspect, the apparatus having a single working fluid comprises a single cryogenic heat exchanger, i.e., a main heat exchanger.
In one aspect, an apparatus having a single working fluid includes a single condenser.
In one aspect, an apparatus having a single working fluid comprises a single set of: condenser, heat exchanger, pump.
In one aspect, the primary working fluid and the secondary working fluid are fluidly separate; wherein the apparatus comprises a heat exchanger; wherein the primary working fluid and the secondary working fluid are thermally coupled in the heat exchanger.
In one aspect, the secondary circuit is fluidly separate from the primary circuit; wherein the apparatus comprises a heat exchanger; wherein the primary circuit and the secondary circuit are thermally coupled in the heat exchanger.
In one aspect, an auxiliary circuit comprises: an auxiliary heat exchanger; an auxiliary condenser; an auxiliary pump; and an auxiliary pipeline connecting the auxiliary expander, the auxiliary heat exchanger, the auxiliary condenser and the auxiliary pump to each other.
In one aspect, a heat exchanger is positioned on the primary circuit between the primary expander and the primary heat exchanger, and on the secondary circuit between the secondary heat exchanger and the secondary expander.
In one aspect, the expansion ratio of the main expander is between 30 and 200.
In one aspect, the main expander and/or auxiliary expander and/or additional auxiliary expander is selected from: axial turbine, radial outflow/inflow turbine, radial/axial turbine. Preferably, the main expander and/or the auxiliary expander and/or the additional auxiliary expander are radial outflow turbines.
Preferably, the radial outflow turbine comprises: a housing; a rotor disc provided with a front surface and rotatably housed in the casing; an annular array of rotor blades concentrically located on the front surface; an annular array of stator blades mounted on the casing and interposed between the annular array of rotor blades to define a first radial path for a working fluid.
Preferably, the casing has an inlet in fluid communication with said first radial path and preferably located near the centre of the rotor disc.
Preferably, the casing has an outlet located near a radially peripheral portion of the rotor disc.
Preferably, the rotor disk is provided with an aft surface opposite the forward surface, wherein the annular array of rotor blades is positioned concentrically on the aft surface, wherein the annular array of stator blades is mounted on the casing and interposed between the annular array of rotor blades of the aft surface to define a second radial path for the working fluid.
Preferably, the housing has an additional inlet located forward of the rear surface and in fluid communication with said second radial path.
In one aspect, the first radial path is part of a primary circuit and the second radial path is part of a secondary circuit.
When the primary and secondary working fluids are the same fluid, a radial outflow turbine having two blade faces defines a primary expander (through a first radial path) and a secondary expander (through a second radial path). In one aspect, a boiler includes a vessel and a plurality of tubes contained in the vessel, wherein a main working fluid flows in the tubes.
In one aspect, the vessel has an inlet and an outlet for flue gas defining a variable temperature heat source.
In one aspect, the flue gas directly covers the tubes to transfer heat to the primary working fluid.
In one aspect, the pipe is a curved conduit, preferably without joints/welds.
In one aspect, the tube comprises a plurality of coiled tubes.
Further features and advantages will become more apparent from the detailed description of a preferred but not exclusive embodiment of a cascaded thermodynamic method/apparatus/cycle for generating power from a variable temperature heat source according to the present invention.
Drawings
This description is made with reference to the accompanying drawings, which are for illustrative purposes only and are not limiting of the invention, and in which:
FIG. 1 schematically illustrates a cascade apparatus for generating power from a variable temperature heat source in accordance with the present invention;
FIG. 2 shows a T-S diagram of a cascade thermodynamic cycle implemented by the apparatus of FIG. 1;
FIG. 3 shows a T-Q diagram relating to the heat exchange between the two circuits of the plant of FIG. 1 under subcritical conditions;
FIG. 4 shows a T-Q diagram relating to the heat exchange between the two circuits of the plant of FIG. 1 under supercritical conditions;
fig. 5 shows a different embodiment of the device according to the invention;
FIG. 6 shows a T-S diagram of a cascade thermodynamic cycle implemented by the apparatus of FIG. 5;
figure 7 shows a variant of the device of figure 5;
FIG. 8 shows a T-S diagram of a cascade thermodynamic cycle implemented by the apparatus of FIG. 7;
FIG. 9 shows a variant of the cascade device of FIG. 1;
figure 10 schematically illustrates a turbine that may be used in the apparatus of figure 5 or 7.
Detailed Description
With reference to the preceding figures, numeral 1 generally indicates a cascade device for generating mechanical and/or electrical power from a variable temperature heat source according to the invention.
With particular reference to fig. 1, the apparatus 1 comprises a closed main circuit 2 and a closed auxiliary circuit 3 thermally coupled to each other but fluidly separated from each other.
The main circuit 2 comprises a boiler 4, a main expander 5, a main heat exchanger 6, a main condenser 7, a main pump 8. A main conduit interconnects the boiler 4, the main expander 5, the main heat exchanger 6, the main condenser 7 and the main pump 8 for effecting a heat exchange supercritical organic rankine cycle by means of a working fluid circulating through the main conduit and the above elements.
Specifically, with respect to the flow direction of the working fluid, the main expander 5 is located immediately downstream of the boiler 4, the main condenser 7 is located immediately downstream of the main expander 5, the main pump 8 is located immediately downstream of the main condenser 7, and the boiler 4 is located downstream of the pump 8.
The main heat exchanger 6 is operatively positioned on a first section of the main conduit extending from the pump 8 towards the boiler 4 and on a second section of the same main conduit extending from the main expander 5 towards the main condenser 7. The main heat exchanger 6 has the function of preheating the main working fluid by means of the heat transferred by the same main working fluid exiting from the main expander 5 before it enters the boiler 4.
The primary working fluid is selected from perfluorinated compounds, and it is preferably perfluoro-2-methylpentane/perfluorohexane (e.g. under the trade name Flutec)tmPP1 is known).
The boiler 4 is operatively coupled to a variable temperature heat source of high temperature, for example, a maximum temperature of 600 ℃, such as a turbine gas or flue gas 9 of an industrial process.
As schematically shown in fig. 1, the boiler 4 comprises a vessel 10 having an inlet and an outlet for flue gas 9 and a plurality of tubes accommodated in the vessel 10. These tubes are part of the main conduit described above and are defined by bent/curved tubes arranged in coils. The flue gas 9 directly covers the tubes to transfer heat to the primary working fluid. The bent/buckled tubing is preferably made of stainless steel and made without joints/welds.
The main expander 5 is slaved to a generator 11 which generates energy by the rotation imparted to the main expander 5 by the working fluid expanded in said main expander 5. The main expander 5 is preferably, but not exclusively, a radial outflow turbine known per se, comprising: a housing; a rotor disc provided with a front surface and rotatably housed in the casing; an annular array of rotor blades concentrically located on the front surface; an annular array of stator vanes mounted on the casing and interposed between the annular array of rotor vanes to define a first radial path for the working fluid, wherein the casing has an inlet located near the center of the rotor disk and an outlet located near a radially peripheral portion of the rotor disk. For example, the radial outflow turbine is similar to the radial outflow turbine described in patent EP2699767 in the name of the same applicant. In other embodiment variants, the main expander may be an axial turbine, a radial inflow turbine, a radial/axial turbine, for example similar to those described in patent EP2743463 in the name of the same applicant.
The auxiliary circuit comprises: auxiliary expanders 12 belonging to respective auxiliary generators 13; an auxiliary heat exchanger 14; an auxiliary condenser 15; an auxiliary pump 16; and an auxiliary conduit connecting the auxiliary expander 12, the auxiliary heat exchanger 14, the auxiliary condenser 15 and the auxiliary pump 16 to each other so as to allow a heat exchange organic rankine cycle to be realized by means of an auxiliary working fluid circulating through the auxiliary conduit and the above-mentioned elements.
The auxiliary expander 12 may be an axial turbine, a radial outflow/inflow turbine, a radial/axial turbine.
The secondary working fluid is an organic fluid such as cyclopentane.
The plant 1 comprises a heat exchanger 17 which thermally couples the primary circuit 2 and the secondary circuit 3.
The primary working fluid of the primary circuit 2 transfers heat to the secondary working fluid of the secondary circuit 3 through said heat exchanger 17.
Specifically, with respect to the flow direction of the auxiliary working fluid, the main expander 12 is located immediately downstream of the heat exchanger 17, the auxiliary condenser 15 is located immediately downstream of the auxiliary expander 12, the auxiliary pump 16 is located immediately downstream of the auxiliary condenser 15, and the heat exchanger 17 is located downstream of the auxiliary pump 16.
The auxiliary heat exchanger 14 is operatively positioned on a first section of the auxiliary conduit extending from the auxiliary pump 16 towards the heat exchanger 17 and on a second section of the same auxiliary conduit extending from the auxiliary expander 12 towards the auxiliary condenser 15. The auxiliary heat exchanger 14 has the function of preheating the auxiliary working fluid by means of the heat transferred by the same auxiliary working fluid exiting from the auxiliary expander 12 before it enters the heat exchanger 17.
In use and according to the cascade method and thermodynamic cycle of the invention, and with reference to the T-S diagram of fig. 2, a primary working fluid (Flutec) circulates in the primary circuit 2tmPP1) is pumped by the main pump 8 and slightly increases its own temperature from point a to point B. The primary working fluid is heated through the primary heat exchanger 6 to point C and then enters the boiler 4 where it absorbs heat from the flue gas 9 (e.g., the flue gas has a maximum temperature of 600℃) to heat and evaporate to point D (at about 400℃). The evaporated main working fluid is then expanded in the main expander 5 to cool to point E and cause rotation of the expander 5 and the respective generator 11.
Primary working fluid (Flutec) immediately before primary expansion (point D)tmPP1) has the following parameters:
temperature: 400 deg.C
Reduced temperature: 1.5
Pressure: 40 bar
Reduced pressure: 2.1
The primary working fluid is further cooled in heat exchanger 17, transferring heat to the secondary working fluid of the secondary circuit 3, and then cooled in the primary heat exchanger 6 (points F and G). The subsequent passage in the main condenser 7 determines the condensation of the main working fluid and then returns to point a, ready for the start of a new main rankine cycle.
Main working fluid (Flutec)tmPP1) has the following parameters:
condensation temperature: 25 deg.C
Reduced condensation temperature: 0.65
Condensing pressure: 0.25 bar
Reduced condensing pressure: 0.01
The auxiliary working fluid (cyclopentane) circulating in the auxiliary circuit 3 is pumped by the auxiliary pump 16 and increases its own temperature slightly from point H to point I. The secondary working fluid passes through the secondary heat exchanger 14 to be heated to point L and then enters the heat exchanger 17 where it absorbs heat from the primary working fluid to be heated and evaporated to point M (at about 250 c). The evaporated secondary working fluid is then expanded in the secondary expander 12 to cool to point N and cause rotation of the expander 12 and the respective generator 13.
The secondary working fluid (cyclopentane) immediately before the secondary expansion (point M) has the following parameters:
temperature: 250 deg.C
Reduced temperature: 1.02
Pressure: 30 bar
Reduced pressure: 0.7
The secondary working fluid is further cooled in the secondary heat exchanger 14 (point O) and then cooled in the secondary condenser 15. The passage in the auxiliary condenser 15 determines the condensation of the auxiliary working fluid and then returns to point H, ready for the start of a new auxiliary rankine cycle.
The secondary working fluid (cyclopentane) had the following parameters:
condensation temperature: 25 deg.C
Reduced condensation temperature: 0.6
Condensing pressure: 0.32 bar
Reduced condensing pressure: 0.007
Figure 3 shows a T-Q diagram (points E-F and L-M) relating to the heat exchange that takes place between the two circuits of the plant of figure 1 at the heat exchanger 17 under subcritical conditions. Figure 4 shows the T-Q diagram associated with the same heat exchange under supercritical conditions.
Fig. 5 shows a different embodiment of the apparatus 1 according to the invention, in which the auxiliary circuit 3 is a branch of the main circuit 2, so that the working fluid in both circuits 2, 3 is the same.
The main circuit 2 includes: boiler 4, main expander 5 (subordinate to generator 11), main heat exchanger 6, main condenser 7, main pump 8. Specifically, with respect to the flow direction of the working fluid, the main expander 5 is located immediately downstream of the boiler 4, the main condenser 7 is located immediately downstream of the main expander 5, the main pump 8 is located immediately downstream of the main condenser 7, and the boiler 4 is located downstream of the pump 8. The main heat exchanger 6 is operatively positioned on a first section of the main conduit extending from the pump 8 towards the boiler 4 and on a second section of the same main conduit extending from the main expander 5 towards the main condenser 7.
The auxiliary circuit 3 also comprises an auxiliary expander 12, which in this particular embodiment is subordinate to the same generator 11 of the main expander 5. The auxiliary circuit 3 branches off from the main circuit 2 at a branch point 18 between the main heat exchanger 6 and the boiler 4 and reconnects the main circuit 2 in the main heat exchanger 6. Thus, the main expander 5 and the auxiliary expander 12 are fluidly placed in parallel, and the working fluid entering the two expanders 5 and 12 has substantially the same pressure. The working fluid of the primary circuit and the working fluid of the secondary circuit exchange heat in the second heat exchanger 19. A second heat exchanger 19 is placed on the main circuit downstream of the main expander 5 and on the auxiliary circuit upstream of the auxiliary expander 12. The second heat exchanger 19 is a high temperature heat exchanger. The main heat exchanger 6 is a cryogenic heat exchanger.
The single working fluid is chosen from perfluorinated compounds and it is preferably perfluoro-2-methylpentane/perfluorohexane (for example, under the trade name Flutec)tmPP1 is known).
In use and in accordance with the cascading method and thermodynamic cycle of the present invention, and with reference to the T-S diagram of fig. 6, the primary working fluid (Flutec)tmPP1) is pumped by the main pump 8 and slightly increases its own temperature from point a to point B.
The working fluid passes through the primary heat exchanger 6 to be heated to point C and then is split into a primary stream which enters the boiler 4 where it absorbs heat from the flue gases to be heated and evaporated to point E (at about 350 ℃) and a secondary stream which enters the secondary heat exchanger 19 to be heated to point D.
The evaporated main flow is then expanded in the main expander 5 to cool to point F and cause rotation of the expander 5 and the respective generator 11, and then enters the second heat exchanger 19 where it transfers heat to the auxiliary flow (which heats to point D) and cools to point G.
The auxiliary stream is then expanded in the auxiliary expander 12 to cool to point G and induce rotation of the expander 12 and the generator 11. The main and auxiliary flows merge into the main heat exchanger 6 and transfer heat in the main heat exchanger to cool to point H. At this point, the single flow of working fluid passes through the condenser 7, condenses (at about 30 ℃) and returns to the pump 8, i.e. to point a.
Fig. 7 shows a variant of the device 1 of fig. 5. With respect to the plant of fig. 5, the variant of fig. 7 comprises an additional auxiliary circuit 20 thermally coupled to the auxiliary circuit 3. The additional auxiliary circuit 20 comprises an additional auxiliary expander 21. The additional auxiliary circuit 20 branches from the branch point 18 or from an additional branch point 22 of the auxiliary circuit 3 located between the branch point 18 and the second heat exchanger 19. The working fluid of the auxiliary circuit and the working fluid of the additional auxiliary circuit exchange heat in the third heat exchanger 23.
The third heat exchanger 23 is placed on the auxiliary circuit downstream of the auxiliary expander 12 and on the additional auxiliary circuit upstream of the additional auxiliary expander 21. The third heat exchanger 21 is a high temperature heat exchanger. The second heat exchanger 19 is a medium temperature heat exchanger and the main heat exchanger 6 is a low temperature heat exchanger.
The additional auxiliary circuit 20, the auxiliary circuit 3 and the main circuit 2 are connected in the main heat exchanger 6. Thus, the main expander 5, the auxiliary expander 12 and the additional auxiliary expander 21 are fluidly placed in parallel, and the working fluid entering the three expanders 5, 12 and 21 has substantially the same pressure.
In use and in accordance with the cascading method and thermodynamic cycle of the present invention, and with reference to the T-S diagram of fig. 7, the working fluid is pumped by the main pump 8 and slightly increases its own temperature from point a to point B. The working fluid passes through the main heat exchanger 6 to be heated to point C and is then divided into a main flow, which enters the boiler 4 where it absorbs heat from the flue gases to be heated and evaporated to point F (at about 400 ℃), an auxiliary flow, which enters the second heat exchanger 19 to be heated to point E, and an additional auxiliary flow, which enters the third heat exchanger 23 to be heated to point D.
The main flow is then expanded in the main expander 5 to cool to point G and cause rotation of the expander 5 and the respective generator 11, and then enters the second heat exchanger 19 where it transfers heat to the auxiliary flow (which heats to point E) and cools to point I.
The auxiliary stream is expanded in auxiliary expander 12 to cool to point H and cause expander 12 and generator 11 to rotate and then enter third heat exchanger 23 where it transfers heat to the additional auxiliary stream (which heats to point D) and then cools to point I.
The additional auxiliary stream is expanded in the additional auxiliary expander 21 to cool to point I and induce rotation of the expander 21 and the generator 11.
The main flow, the auxiliary flow and the additional auxiliary flow are connected in the main heat exchanger 6 and transfer heat in the main heat exchanger for cooling to point L. At this point, the single flow of working fluid passes through the condenser 7, condenses (at about 30 ℃) and returns to the pump 8, i.e. to point a.
Other variants of fig. 5 and 7 (not shown) include additional auxiliary circuits/cycles in cascade, all operating with the same working fluid. Other variants of the apparatus of fig. 1 comprise a plurality of circulations/circuits arranged in series, i.e. cascaded one after the other, wherein the fluids between which heat is exchanged are different.
For example, fig. 9 shows an additional auxiliary circuit 20 arranged in cascade with respect to the auxiliary circuit 3 of fig. 1. The additional auxiliary circuit 20 is similar in structure to the auxiliary circuit 3. The additional auxiliary circuit 20 is operatively coupled with the auxiliary circuit 3 at an additional heat exchanger 24. The additional auxiliary circuit 20 comprises an additional auxiliary expander 21 with a corresponding additional auxiliary generator 25, an additional auxiliary heat exchanger 26, an additional auxiliary condenser 27 and an additional auxiliary pump 28.
In other embodiments, the main expander 5 and the auxiliary expander 12 of the plant of fig. 5 and/or 7 are incorporated into a single radial outflow turbine 100 of the type shown in fig. 10.
An annular array of rotor blades 105 is concentrically arranged on the front surface 103 as well as the rear surface 104. An annular array of stator vanes 106 is mounted on the inner surface of the casing 101 forward of the forward surface 103 of the rotor disk 102 and interposed between the annular array of rotor vanes 105 of the forward surface 103 to define a first radial path for the working fluid. An annular array of stator vanes 106 is also mounted on the inner surface of the casing 101 forward of the rear surface 104 of the rotor disk 102 and interposed between the annular array of rotor vanes 105 of the rear surface 104 to define a second radial path for the working fluid.
The housing 101 has: an inlet 107 forward of forward surface 103, near the center of rotor disk 102, and in fluid communication with the first radial path; an additional inlet 108 located forward of the rear surface 104 and in fluid communication with the second radial path; and an outlet 109 positioned proximate to a radially peripheral portion of the rotor disk 102.
In the embodiment shown, the additional inlet 108 is defined by an opening obtained through the wall of the casing 101, which is positioned around a supporting sleeve 110 of a shaft 111 of the turbine 100, which is mounted in said sleeve 110 by means of bearings. Shaft 111 supports and supports rotor disk 102 in a cantilevered manner.
The first radial path defined on the front surface 103 is part of the primary circuit of fig. 5 or 7, and the second radial path defined on the rear surface 104 is part of the secondary circuit of fig. 5 or 7.
Thus, the radial outflow turbine 100 with two blade faces defines the main expander 5 (through the first radial path) and the auxiliary expander 12 (through the second radial path) of fig. 5 or 7. In other words, the entrance 107 corresponds to point E of fig. 5 or 7, and the additional entrance 108 corresponds to point D of fig. 5 or 7. These points E and D are at substantially the same pressure, and thus the rotor disk 102 is essentially balanced.
Component list
1 Cascade device
2 main loop
3 auxiliary circuit
4 boiler
5 Main expander
6 main heat exchanger
7 main condenser
8 main pump
9 flue gas
10 container body
11 electric generator
12 auxiliary expander
13 auxiliary generator
14 auxiliary heat exchanger
15 auxiliary condenser
16 auxiliary pump
17 heat exchanger
18 branch point
19 second heat exchanger
20 additional auxiliary circuit
21 additional auxiliary expander
22 additional branch point
23 third heat exchanger
24 additional heat exchanger
25 additional auxiliary generator
26 additional auxiliary heat exchanger
27 additional auxiliary condenser
28 additional auxiliary pump
100 radial outflow turbine
101 outer casing
102 rotor disk
103 front surface
104 rear surface
105 rotor blade
106 stator blade
107 inlet
108 additional entry
109 outlet port
110 sleeve
111 axle
Claims (19)
1. A cascading method of generating power from a variable temperature heat source, comprising:
circulating a primary working fluid selected from perfluorinated compounds in a primary circuit (2) according to a primary organic supercritical rankine cycle, wherein said primary working fluid is heated and evaporated, expanded in a primary expander (5) belonging to a generator (11) or to a mechanical user, cooled, condensed and heated and evaporated again;
operatively coupling a variable temperature heat source (9) to the main working fluid of the main circuit (2) in the boiler (4) to perform said heating and evaporation of the main working fluid;
circulating an auxiliary working fluid in an auxiliary circuit (3) according to an auxiliary Rankine cycle, wherein the auxiliary working fluid is heated and evaporated, expanded in an auxiliary expander (12) belonging to an auxiliary generator (11; 13) or to an auxiliary mechanical user, cooled, condensed and heated and evaporated again;
thermally coupling the expanded primary working fluid of the primary rankine cycle to a secondary working fluid of the secondary rankine cycle to cool the primary working fluid and heat and evaporate the secondary working fluid by heat transfer from the primary rankine cycle to the secondary rankine cycle before the secondary working fluid is expanded in an secondary expander (12).
2. The method according to claim 1, wherein the primary working fluid is preheated in a primary heat exchanger (6).
3. A method according to claim 1 or 2, wherein the primary and secondary working fluids are the same fluid, and the secondary circuit (3) is a branch of the primary circuit (2); wherein the thermal coupling of the primary working fluid to the secondary working fluid is carried out in a second heat exchanger (19) located downstream of the primary expander (5) and upstream of the secondary expander (12).
4. A method according to claim 3, wherein the secondary working fluid is separated from the primary working fluid upstream of the primary expander (5) and the secondary expander (12), and the secondary working fluid and the primary working fluid are reconnected downstream of the primary expander (5) and the secondary expander (12).
5. A method according to claim 3 or 4 when dependent on claim 2, wherein the secondary working fluid reconnects the primary working fluid in the primary heat exchanger (6).
6. The method of claim 1 or 2, wherein the primary working fluid and the secondary working fluid are fluidly separated; wherein the apparatus (1) comprises a heat exchanger (17); wherein the primary and secondary working fluids are thermally coupled in a heat exchanger (17).
7. The method of claim 6, wherein the secondary working fluid is different from the primary working fluid.
8. The method according to claim 7, wherein the secondary working fluid is an organic fluid, preferably selected from: cyclopentane, isopentane, isohexane, hexane, pentane, R245fa, R1234 yf.
9. The method of any one of claims 1 to 8, wherein the primary working fluid selected from perfluorinated compounds comprises: perfluoro-2-methylpentane/perfluoro-hexane (Flutec)tmPP1), perfluoromethylcyclohexane (PP2), perfluoro-1, 3-dimethylcyclohexane (PP3), hexafluorobenzene.
10. A cascade apparatus for generating power from a variable temperature heat source, comprising:
a main circuit (2) comprising:
a boiler (4) operatively coupled to a variable temperature heat source (9);
a main expander (5);
a main heat exchanger (6);
a main condenser (7);
a main pump (8);
a main pipe connecting the boiler (4), the main expander (5), the main heat exchanger (6), the main condenser (7) and the main pump (8) to each other;
a primary working fluid selected from perfluorinated compounds and flowing in the primary circuit (2) to realize a supercritical organic rankine cycle;
at least one auxiliary circuit (3) thermally coupled to the main circuit (2) and comprising an auxiliary expander (12); wherein the secondary working fluid enters the secondary expander (12) after heat exchange with the primary working fluid exiting the primary expander (5).
11. The apparatus of claim 10, wherein the secondary circuit (3) is a branch of the primary circuit (2) and the secondary working fluid is the primary working fluid; wherein the plant (1) further comprises a second heat exchanger (19) located on the main circuit (2) downstream of the main expander (5) and placed on the auxiliary circuit (3) upstream of the auxiliary expander (12); heat is exchanged between the primary working fluid and the secondary working fluid in a second heat exchanger (19).
12. Plant according to claim 11, wherein the auxiliary circuit (3) branches from the main circuit (2) at a point (18) located between the main heat exchanger (6) and the boiler (4), and the main circuit (2) is reconnected in the main heat exchanger (6).
13. Plant according to claim 11 or 12, wherein the main expander (5) and the auxiliary expander (12) are combined in a single radial outflow turbine (100) comprising a single rotor disc (102) provided with a front surface (103) and a rear surface (104); wherein the annular array of blades (105) is arranged concentrically on the front surface (103) to define a first radial path for the working fluid, and the annular array of blades (105) is arranged concentrically on the rear surface (104) to define a second radial path for the working fluid; wherein the main expander (5) is defined by a first radial path and the auxiliary expander (12) is defined by a second radial path.
14. The apparatus of claim 10, wherein the secondary circuit (3) is fluidly separated from the primary circuit (2); wherein the apparatus (1) comprises a heat exchanger (17); wherein the primary circuit (2) and the secondary circuit (3) are thermally coupled in a heat exchanger (17).
15. The apparatus according to claim 14, wherein the auxiliary loop (3) comprises:
an auxiliary heat exchanger (14);
an auxiliary condenser (15);
an auxiliary pump (16);
an auxiliary pipe connecting the auxiliary expander (12), the auxiliary heat exchanger (14), the auxiliary condenser (15), and the auxiliary pump (16) to each other;
wherein the heat exchanger (17) is placed on the main circuit (2) between the main expander (5) and the main heat exchanger (6) and on the auxiliary circuit (3) between the auxiliary heat exchanger (14) and the auxiliary expander (12).
16. A cascaded thermodynamic cycle for generating power from a variable temperature heat source, comprising:
a supercritical primary rankine cycle having an organic primary working fluid selected from perfluorinated compounds; wherein the primary Rankine cycle receives heat from a variable temperature heat source;
an auxiliary Rankine cycle having an auxiliary working fluid; wherein the auxiliary cycle is thermally coupled to the main cycle to receive heat from the main cycle after expansion of the main working fluid and before expansion of the auxiliary working fluid;
wherein in the main cycle:
the reduced temperature of the primary working fluid immediately prior to the primary expansion is between 1.1 and 1.7;
wherein the reduced pressure of the primary working fluid immediately prior to the primary expansion is between 1 and 2.5;
wherein the reduced condensation temperature of the primary working fluid is between 0.6 and 0.9;
wherein the reduced condensing pressure of the primary working fluid is between 0.005 and 0.3.
17. The cycle of claim 16, wherein in the auxiliary cycle:
the reduced temperature of the secondary working fluid immediately prior to the secondary expansion is between 0.8 and 1.2;
wherein the reduced pressure of the secondary working fluid immediately prior to the secondary expansion is between 0.3 and 1.2;
wherein the reduced condensation temperature of the secondary working fluid is between 0.5 and 0.75;
wherein the reduced condensing pressure of the secondary working fluid is between 0.001 and 0.1.
18. A cycle according to claim 16 or 17, wherein in the main cycle:
the temperature of the primary working fluid immediately prior to the primary expansion is between 250 ℃ and 400 ℃;
wherein the pressure of the main working fluid immediately prior to the main expansion is between 25 bar and 50 bar;
wherein the condensation temperature of the primary working fluid is between 10 ℃ and 50 ℃;
wherein the condensation pressure of the main working fluid is between 0.1 bar and 1 bar.
19. A cycle according to any one of claims 16 to 18, wherein in the auxiliary cycle:
the temperature of the secondary working fluid immediately prior to the secondary expansion is between 150 ℃ and 300 ℃;
wherein the pressure of the secondary working fluid immediately prior to the secondary expansion is between 20 bar and 50 bar;
the condensation temperature of the secondary working fluid is between 10 ℃ and 50 ℃;
wherein the condensing pressure of the secondary working fluid is between 0.1 bar and 2 bar.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| IT201700145913 | 2017-12-18 | ||
| IT102017000145913 | 2017-12-18 | ||
| PCT/IB2018/060245 WO2019123243A1 (en) | 2017-12-18 | 2018-12-18 | Process, plant and thermodynamic cycle for production of power from variable temperature heat sources |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN111699302A true CN111699302A (en) | 2020-09-22 |
Family
ID=61868702
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201880088116.1A Pending CN111699302A (en) | 2017-12-18 | 2018-12-18 | Method, apparatus and thermodynamic cycle for generating power from a variable temperature heat source |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20210017883A1 (en) |
| EP (1) | EP3728802A1 (en) |
| CN (1) | CN111699302A (en) |
| AU (1) | AU2018392903A1 (en) |
| CA (1) | CA3085850A1 (en) |
| WO (1) | WO2019123243A1 (en) |
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| US5071312A (en) * | 1988-07-30 | 1991-12-10 | John Kirby | Turbines |
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| US7942001B2 (en) * | 2005-03-29 | 2011-05-17 | Utc Power, Llc | Cascaded organic rankine cycles for waste heat utilization |
| US20100326076A1 (en) * | 2009-06-30 | 2010-12-30 | General Electric Company | Optimized system for recovering waste heat |
| US20110083437A1 (en) * | 2009-10-13 | 2011-04-14 | General Electric Company | Rankine cycle system |
| BR112012024146B1 (en) * | 2010-03-23 | 2020-12-22 | Echogen Power Systems, Inc. | working fluid circuit for lost heat recovery and method of recovering lost heat in a working fluid circuit |
| BE1019372A3 (en) * | 2010-06-11 | 2012-06-05 | Schutter Rotterdam B V | COOLING SYSTEM WITH LOW ENERGY CONSUMPTION. |
| US8857186B2 (en) * | 2010-11-29 | 2014-10-14 | Echogen Power Systems, L.L.C. | Heat engine cycles for high ambient conditions |
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2018
- 2018-12-18 CA CA3085850A patent/CA3085850A1/en not_active Abandoned
- 2018-12-18 AU AU2018392903A patent/AU2018392903A1/en not_active Abandoned
- 2018-12-18 EP EP18836405.3A patent/EP3728802A1/en not_active Withdrawn
- 2018-12-18 CN CN201880088116.1A patent/CN111699302A/en active Pending
- 2018-12-18 US US16/955,354 patent/US20210017883A1/en not_active Abandoned
- 2018-12-18 WO PCT/IB2018/060245 patent/WO2019123243A1/en unknown
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5071312A (en) * | 1988-07-30 | 1991-12-10 | John Kirby | Turbines |
| US7827791B2 (en) * | 2005-10-05 | 2010-11-09 | Tas, Ltd. | Advanced power recovery and energy conversion systems and methods of using same |
| US20100319346A1 (en) * | 2009-06-23 | 2010-12-23 | General Electric Company | System for recovering waste heat |
| CN102536363A (en) * | 2010-11-19 | 2012-07-04 | 通用电气公司 | Rankine cycle integrated with organic rankine cycle and absorption chiller cycle |
| US20120131919A1 (en) * | 2010-11-29 | 2012-05-31 | Echogen Power Systems, Llc | Driven starter pump and start sequence |
| CN104487662A (en) * | 2012-06-29 | 2015-04-01 | 通用电气公司 | Triple expansion waste heat recovery system and method |
| CN105765178A (en) * | 2013-09-05 | 2016-07-13 | 艾克竣电力系统股份有限责任公司 | Heat Engine System Having a Selectively Configurable Working Fluid Circuit |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2019123243A1 (en) | 2019-06-27 |
| CA3085850A1 (en) | 2019-06-27 |
| EP3728802A1 (en) | 2020-10-28 |
| AU2018392903A1 (en) | 2020-07-30 |
| US20210017883A1 (en) | 2021-01-21 |
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