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WO2008125827A2 - Appareil et procédé à cycle de rankine organique - Google Patents

Appareil et procédé à cycle de rankine organique Download PDF

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Publication number
WO2008125827A2
WO2008125827A2 PCT/GB2008/001286 GB2008001286W WO2008125827A2 WO 2008125827 A2 WO2008125827 A2 WO 2008125827A2 GB 2008001286 W GB2008001286 W GB 2008001286W WO 2008125827 A2 WO2008125827 A2 WO 2008125827A2
Authority
WO
WIPO (PCT)
Prior art keywords
working fluid
vapour
organic working
evaporator
feed heater
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/GB2008/001286
Other languages
English (en)
Other versions
WO2008125827A3 (fr
Inventor
Ian Kenneth Smith
Nikola Rudi Stosic
Herman Leibowitz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Electratherm Inc
Original Assignee
Electratherm Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Electratherm Inc filed Critical Electratherm Inc
Publication of WO2008125827A2 publication Critical patent/WO2008125827A2/fr
Anticipated expiration legal-status Critical
Priority to GBGB0919961.3A priority Critical patent/GB0919961D0/en
Publication of WO2008125827A3 publication Critical patent/WO2008125827A3/fr
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F01K25/10—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 the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • 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
    • F01K23/06—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 combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—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 combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • 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
    • F01K23/06—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 combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—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 combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/106—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 combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle with water evaporated or preheated at different pressures in exhaust boiler
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2260/00—Recuperating heat from exhaust gases of combustion engines and heat from cooling circuits
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to an organic Rankine cycle apparatus and method for generating mechanical power from two different heat sources operating at different temperatures using a single apparatus.
  • a number of processes which require the combustion of fuel reject heat that can be recovered by an apparatus for generating power may be rejected in two streams at very different temperatures.
  • one source of heat can be directly from the actual combustion products which, after supplying heat to a process, may still be at temperatures of several hundred degrees centigrade.
  • the other source of heat can be from the process for which the original combustion_ofiuel is required. This can be at temperatures of the order of only 100°C, or even less.
  • An example of two such sources is the heat rejected from an internal combustion (IC) engine, where the exhaust gases leave the engine at a temperature of 350-500°C while the cooling jacket surrounding the engine block rejects heat from the jacket coolant to the atmosphere at temperatures of the order of 70-90 ° C.
  • IC internal combustion
  • ORC Organic Rankine cycle
  • ORC is in essence identical to a steam power plant but uses organic fluids such as light hydrocarbons or common refrigerants as the working fluid instead of water. These fluids have unique properties and much of the art of getting the best result from them is based on the choice of the most suitable fluid for each application. Commonly used or considered organic fluids are either refrigerants, such as R124 (Chlorotetrafluorethane), R134a (Tetrafluoroethane) or R245fa (1 ,1,1 ,3,3-Pentafluoropropane), or light hydrocarbons such as isoButane, n- Butane, isoPentane and n-Pentane. Some systems incorporate highly stable thermal fluids, such as the Dowtherms and Therminols but the very high critical temperatures of these fluids create a number of problems in system design which lead to high cost solutions.
  • organic fluids such as light hydrocarbons or common refrigerants as the working fluid instead of water.
  • a feed pump 20 The essential features of an ORC system and the mechanical components needed to implement the cycle are shown in Fig 1.
  • a feed pump 20 There are five main components: a feed pump 20, a feed heater 30, an evaporator 50, an expander 120 and a condenser 150. These are all connected in a closed loop, which must be well sealed in order to prevent any significant loss of the working fluid to the atmosphere, and any inward leakage of air into the circuit.
  • the working fluid is pressurised, heated to its boiling point, evaporated, expanded from the saturated vapour condition, condensed and then repressurised.
  • the critical temperatures of the commonly used fluids are low, being generally in the range of approximately 100 ° C- 200 ° C.
  • the heat source be at a comparatively higher temperature, such as engine exhaust gases (typically 350-500°C)
  • engine exhaust gases typically 350-500°C
  • the vapour entering a boiler is heated in a feed heater 30, evaporated in an evaporator 50 and then superheated in a superheater 160 in order to maximise the working fluid temperature.
  • a feed heater 30 evaporated in an evaporator 50 and then superheated in a superheater 160 in order to maximise the working fluid temperature.
  • Significantly higher cycle efficiencies can thereby be achieved but the system requires a superheater 160 in addition to the feed heater and the evaporator, and a recuperative heat exchanger 200 recaptures heat from the superheated vapour leaving the expander which is then used to preheat the working fluid entering the feed heater. Without this latter feature, gains in efficiency resulting from raising the maximum fluid temperature may only be low.
  • the expander In a large majority of known ORC systems, the expander is a turbine and usually one of the radial inflow type. However for power outputs of up to approximately 1 MW, screw expanders have some advantages.
  • screw expanders can admit wet vapour from the boiler without the risk of incurring mechanical damage or of loss in adiabatic efficiency.
  • This characteristic produces significant advantages in systems where the cycle is of the simple evaporative type, such as that shown in Fig 1.
  • this cycle can operate in the mode shown in Fig 3 where the working fluid entering the expander can be sufficiently wet to eliminate the need to desuperheat it after expansion.
  • This also reduces the proportion of heat transferred in the evaporator at constant temperature and thereby the evaporation temperature using the same heat source can be higher than it would otherwise be if complete evaporation took place.
  • the invention provides an organic Rankine cycle apparatus for generating power from two different sources of heat at different temperatures as defined by independent claim 1 to which reference should now be made.
  • the invention also provides a method of generating power from two different sources of heat at different temperatures using an organic Rankine cycle as defied by independent claim 10 to which reference should now be made.
  • Preferred embodiments of the invention provide an organic Rankine cycle apparatus and a method of generating power based on an organic Rankine cycle system in which power is generated from two different heat sources at different temperatures in a single apparatus. This is achieved with negligible performance penalties compared to a system in which a separate power recovery system is used to recover heat from each of the heat sources.
  • Figure 1 is a schematic illustration of a known type of organic Rankine cycle system in which saturated dry vapour is admitted to an expander, together with an associated temperature-entropy diagram;
  • Figure 2 is a schematic illustration of a known type of superheated recuperative organic Rankine cycle system in which superheated vapour is admitted to an expander, together with an associated temperature-entropy diagram;
  • FIG 3 is a schematic illustration of a known type of organic Rankine cycle system having a screw expander capable of admitting wet vapour (a "wet organic Rankine cycle system"), together with an associated temperature-entropy diagram;
  • Figure 4 is a schematic illustration of a first embodiment of an organic Rankine cycle system of the invention in which dry saturated vapour is delivered to a higher pressure and a lower pressure expander;
  • Figure 5 is a temperature-entropy diagram for the organic Rankine cycle system of Figure 4.
  • Figure 6 is a temperature-entropy diagram of a second embodiment of the invention in which wet vapour is admitted to the lower pressure and higher pressure expanders;
  • Figure 7 is a schematic illustration of an organic Rankine cycle system of a third embodiment of the invention which includes a superheater between the second evaporator and the higher pressure expander for supplying superheated steam to a higher pressure evaporator.
  • Figure 8 is a temperature-entropy diagram for the organic Rankine cycle system of Figure 7;
  • Figure 9 is a temperature-entropy diagram of a fourth embodiment of the invention in which superheated vapour is admitted to the higher pressure expander and wet vapour is admitted to the lower pressure expander;
  • Figure 10 is a schematic illustration of a fifth embodiment of the invention in which the higher pressure expansion is carried out in two expander stages;
  • Figure 11 is a schematic illustration of a sixth embodiment of the invention in which the lower pressure expansion is carried out in two expander stages;
  • Figure 12 is a schematic illustration of the output shafts of the expanders of any of the first to the sixth embodiments being mechanically coupled with a drive belt to drive a generator;
  • Figure 13 is a schematic illustration of a known simple organic Rankine cycle system used to recover heat both from the cooling jacket and exhaust gas stream of an internal combustion engine, in order to provide a comparison with the performance of the Rankine cycle system of embodiments of the invention.
  • FIG. 4 A first embodiment of the invention is shown in Figure 4, and Figure 5 shows the corresponding temperature-entropy diagram.
  • a first organic working fluid circuit 10 an organic working fluid is pressurised to a lower evaporative pressure by a lower pressure pump 20, leaving the lower pressure pump at state 1 and entering a first, lower pressure feed heater 30.
  • the organic working fluid leaves the first feed heater as a saturated liquid at the evaporative temperature (state 2), this being dependent upon the lower pressure feed pump discharge pressure.
  • the flow of the organic working fluid is then divided at a junction 40 so that a portion of the saturated liquid enters a first, lower pressure evaporator 50, in which it is partially evaporated to state 3.
  • the heat required for heating the organic working fluid in the first feed heater 30 and evaporating the organic working fluid into a vapour in the first evaporator is supplied by a lower temperature heat source 60, entering the first evaporator at point C and leaving the first feed heater at state D.
  • the remaining portion of the organic working fluid leaving the first feed heater 30 enters a second organic working fluid circuit 70 under the action of a higher pressure feed pump 80, the working fluid leaving the higher pressure pump at a higher pressure in state 4.
  • This portion of the organic working fluid then passes through a second feed heater 90, the fluid leaving the second feed heater as a saturated liquid at state 5.
  • the saturated liquid then enters a second, higher pressure evaporator 100, where it is evaporated to a dry vapour state (state 6).
  • the heat required for heating the organic working fluid in the second feed heater and evaporating the organic working fluid into a vapour in the second evaporator is supplied by a higher temperature heat source 110 entering the second evaporator 100 at point A and leaving the second feed heater 90 at state B.
  • the higher pressure vapour leaving the second evaporator is expanded in a higher pressure expander 120, leaving as superheated vapour at an intermediate pressure at state 8.
  • This superheated vapour then mixes at a junction 130 with the partially evaporated vapour leaving the first evaporator at state 3, such that the superheated vapour delivers heat to the partially evaporated vapour, thereby having a similar effect to that of a recouperator.
  • the total mass of the organic working fluid then enters a lower pressure expander 140 as dry saturated vapour at state 9.
  • the organic working fluid is expanded to state 10, where it enters a desuperheater-condenser 150 which desuperheats and condenses the working fluid to a saturated liquid at state 11.
  • the working fluid is returned by the lower pressure feed pump to the first feed heater to complete a working fluid cycle.
  • the expanders may be turbines such as those of the radial inflow type.
  • FIG. 6 A second embodiment is shown in Figure 6, in which the expanders 120,140 are of the positive displacement type, more specifically of the twin screw or scroll type.
  • the organic working fluid leaves the higher pressure evaporator 100 as wet vapour (state 6), typically with a dryness fraction of approximately 75%, so that the working fluid leaves the higher pressure expander 120 substantially in the dry saturated vapour phase (state 8).
  • state 6 wet vapour
  • state 8 dry saturated vapour phase
  • the precise state of the working fluid leaving the expansion stage is dependent upon on the range of temperatures and pressures at which the Rankine cycle system operates, hence the dryness fraction may be varied to control the state of the working fluid leaving the higher pressure expander 120.
  • a third embodiment is shown in Figures 7 and 8 in which the higher temperature heat source delivers heat to a superheater 110 which superheats the dry saturated vapour leaving the second evaporator 100, so that the working fluid is delivered to the higher pressure expander 120 as superheated vapour (state 7).
  • the vapour expanded in the higher pressure expander then combines with the partially evaporated vapour leaving the first evaporator 50 so that the organic working fluid is delivered to the lower pressure expander 140 as dry saturated vapour (state 9).
  • a fourth embodiment is shown in Figure 9, this being a modification of the third embodiment.
  • the organic working fluid enters the higher pressure expander as superheated vapour as in the third embodiment however, when the portion of the organic working fluid from the second working fluid circuit combines with that leaving the first evaporator, the total mass of the working fluid enters the lower pressure expander 140 as wet vapour (state 9) which is expanded to dry saturated vapour in the lower pressure expander (state 10).
  • the higher pressure expansion stage takes place in two discrete expander stages 120,121.
  • state 7 denotes an intermediate pressure condition on leaving the first stage higher pressure expander 120, while the higher pressure expansion is completed in a second stage higher pressure expander, leaving that expander in state 8. Because these units are not intended for large power outputs, if this stage of expansion is divided into two, the size of the higher pressure machine is relatively small and the additional cost is not very significant.
  • the expanded fluid at state 8 then mixes with the partially evaporated vapour at state 3 at constant temperature, so that the total mass of the working fluid enters the lower pressure expander as wet vapour at state 9, the vapour being approximately 90% dry.
  • the total flow then expands to condensing conditions at state 10, which, as in state 8, is approximately dry saturated vapour.
  • the three expanders can be mechanically coupled by a drive belt 170, or other suitable equivalent to drive an electrical generator 180 to generate electrical power.
  • the engine considered was a GE Jenbacher J320GS-LL. This engine has a rated electrical power output of 1065kW.
  • the recoverable heat from the exhaust gases in cooling from 450 ° C to 150 ° C is 543kW, while the heat that has to be rejected from the coolant to the surroundings is 604kW to return it at 70 ° C, after leaving the jacket at 90 ° C.
  • the first case considered was one intended to minimise the system cost by using the engine coolant circuit (210) of an engine (220) to recover using a heat exchanger (230) the heat from the exhaust gases (240), in addition to the jacket heat, and then to transfer the entire heat to a single wet organic Rankine cycle system boiler (250) with a single screw expander (120) to recover the power.
  • the disadvantage of this is that the maximum temperature of the coolant would only be raised from 90 ° C to approximately 110 ° C and this would result in a lower cycle efficiency and hence less power recovery than from two separate organic Rankine cycle systems, one for each source of heat.
  • the second case considered was to use a simple wet organic Rankine cycle system, as shown in Fig 3, to recover power from the jacket heat and a separate superheated organic Rankine cycle system, without a recuperative heat exchanger, to recover heat from the exhaust gases.
  • the third case considered was to use a simple wet organic Rankine cycle system, as shown in Fig 3, to recover power from the jacket heat and a separate superheated recuperative cycle, as shown in Fig 2, to recover heat from the exhaust gases.
  • the fourth case considered was a dual pressure cycle system as shown in Figs 4 and 6, where the higher pressure and lower pressure expanders are of the twin screw or scroll type such that they can admit wet vapour.
  • the results of the study are contained in the following table.
  • the most important criterion for the power plant owner is the cost per unit output, since this determines the economic viability of installing a waste heat power recovery system.

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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

L'invention porte sur un appareil et un procédé à cycle de Rankine organique pour générer une puissance à partir de deux sources de chaleur différentes (60, 110) à des températures différentes, comprenant un circuit (10) de fluide de travail organique à pression inférieure et un circuit (20) de fluide de travail organique à pression supérieure en communication de fluide l'un avec l'autre. Une partie du fluide de traitement organique est chauffée par une source de chaleur à température supérieure et est expansée à une pression supérieure dans un dispositif d'expansion (120) à pression supérieure pour générer une puissance mécanique avant qu'elle ne soit combinée avec une partie du fluide de travail qui est partiellement évaporée à une température inférieure par de la chaleur provenant d'une source de chaleur (60) à température inférieure, de telle sorte que la masse totale du fluide de traitement organique est expansée dans un dispositif d'expansion (140) à pression inférieure pour générer une puissance mécanique supplémentaire.
PCT/GB2008/001286 2007-04-13 2008-04-11 Appareil et procédé à cycle de rankine organique Ceased WO2008125827A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GBGB0919961.3A GB0919961D0 (en) 2007-04-13 2009-11-13 Organic rankine cycle apparatus and method

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US92345307P 2007-04-13 2007-04-13
US60/923,453 2007-04-13

Publications (2)

Publication Number Publication Date
WO2008125827A2 true WO2008125827A2 (fr) 2008-10-23
WO2008125827A3 WO2008125827A3 (fr) 2009-12-03

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WO (1) WO2008125827A2 (fr)

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110072818A1 (en) * 2009-09-21 2011-03-31 Clean Rolling Power, LLC Waste heat recovery system
US8006496B2 (en) 2008-09-08 2011-08-30 Secco2 Engines, Inc. Closed loop scroll expander engine
CN102472121A (zh) * 2009-07-23 2012-05-23 康明斯知识产权有限公司 使用有机郎肯循环的能量回收系统
AT510809A1 (de) * 2010-11-16 2012-06-15 Gs Gruber Schmidt Vorrichtung zur abwärmenutzung
WO2011045047A3 (fr) * 2009-10-14 2013-02-21 Conpower Energieanlagen Gmbh & Co Kg Procédé à cycle (o)rc pour la transformation en énergie électrique de la chaleur produite lors de la combustion de biomasse et dispositif correspondant
WO2011066872A3 (fr) * 2009-12-04 2013-02-28 Voith Patent Gmbh Chaîne cinématique, en particulier pour véhicule à moteur
CN103061835A (zh) * 2012-12-28 2013-04-24 东南大学 一种复叠式有机朗肯循环高效热机
WO2013148297A1 (fr) * 2012-03-24 2013-10-03 General Electric Company Système et procédé de récupération de chaleur perdue provenant de deux sources de chaleur
US8561405B2 (en) 2007-06-29 2013-10-22 General Electric Company System and method for recovering waste heat
US8844291B2 (en) 2010-12-10 2014-09-30 Vaporgenics Inc. Universal heat engine
FR3004486A1 (fr) * 2013-04-11 2014-10-17 Aqylon Dispositif permettant de transformer l'energie thermique en energie mecanique au moyen d'un cycle de rankine organique a detente fractionnee par des regenerations
EP2735710A4 (fr) * 2011-07-20 2015-03-25 Mitsubishi Heavy Ind Ltd Système de turbine radiale multipression
WO2015117621A1 (fr) * 2014-02-06 2015-08-13 Talbot New Energy Ag Système de production d'un flux basse pression
WO2015117619A1 (fr) * 2014-02-04 2015-08-13 Talbot New Energy Ag Système de production de courant basse pression
WO2016111976A1 (fr) * 2015-01-05 2016-07-14 General Electric Company Cycle de rankine organique à pression multiple
WO2017151539A1 (fr) * 2016-02-29 2017-09-08 Ethosgen, Llc Génération d'électricité à l'aide d'un moteur thermique et de lits de sorption
AT521050B1 (de) * 2018-05-29 2019-10-15 Fachhochschule Burgenland Gmbh Verfahren zur Steigerung der Energieeffizienz in Clausius-Rankine-Kreisprozessen
CN112594950A (zh) * 2020-12-29 2021-04-02 深圳市海吉源科技有限公司 一种低温冷水制冷机组及控制方法
US11137177B1 (en) 2019-03-16 2021-10-05 Vaporgemics, Inc Internal return pump
US12135016B2 (en) 2021-04-02 2024-11-05 Ice Thermal Harvesting, Llc Systems for generating geothermal power in an organic Rankine cycle operation during hydrocarbon production based on wellhead fluid temperature
US12140124B2 (en) 2021-04-02 2024-11-12 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power at a drilling rig
US12163485B2 (en) 2021-04-02 2024-12-10 Ice Thermal Harvesting, Llc Systems and methods utilizing gas temperature as a power source
US12180861B1 (en) 2022-12-30 2024-12-31 Ice Thermal Harvesting, Llc Systems and methods to utilize heat carriers in conversion of thermal energy
US12305624B2 (en) 2021-04-02 2025-05-20 Ice Thermal Harvesting, Llc Modular mobile heat generation unit for generation of geothermal power in organic rankine cycle operations
US12312981B2 (en) 2021-04-02 2025-05-27 Ice Thermal Harvesting, Llc Systems and methods utilizing gas temperature as a power source
US12454896B2 (en) 2021-04-02 2025-10-28 Ice Thermal Harvesting, Llc Systems and methods utilizing gas temperature as a power source

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3830062A (en) * 1973-10-09 1974-08-20 Thermo Electron Corp Rankine cycle bottoming plant
US4031705A (en) * 1974-11-15 1977-06-28 Berg John W Auxiliary power system and apparatus
CH632051A5 (de) * 1978-10-25 1982-09-15 Sulzer Ag Brennkraftmaschinenanlage.
US4276747A (en) * 1978-11-30 1981-07-07 Fiat Societa Per Azioni Heat recovery system
US5327987A (en) * 1992-04-02 1994-07-12 Abdelmalek Fawzy T High efficiency hybrid car with gasoline engine, and electric battery powered motor

Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8561405B2 (en) 2007-06-29 2013-10-22 General Electric Company System and method for recovering waste heat
US8479516B2 (en) 2008-09-08 2013-07-09 SECCO2 Engines Inc. Closed loop scroll expander
US8006496B2 (en) 2008-09-08 2011-08-30 Secco2 Engines, Inc. Closed loop scroll expander engine
CN102472121A (zh) * 2009-07-23 2012-05-23 康明斯知识产权有限公司 使用有机郎肯循环的能量回收系统
US9243518B2 (en) * 2009-09-21 2016-01-26 Sandra I. Sanchez Waste heat recovery system
US20110072818A1 (en) * 2009-09-21 2011-03-31 Clean Rolling Power, LLC Waste heat recovery system
WO2011045047A3 (fr) * 2009-10-14 2013-02-21 Conpower Energieanlagen Gmbh & Co Kg Procédé à cycle (o)rc pour la transformation en énergie électrique de la chaleur produite lors de la combustion de biomasse et dispositif correspondant
JP2013513052A (ja) * 2009-12-04 2013-04-18 フォイト・パテント・ゲーエムベーハー 特に自動車両用のドライブトレイン
WO2011066872A3 (fr) * 2009-12-04 2013-02-28 Voith Patent Gmbh Chaîne cinématique, en particulier pour véhicule à moteur
US8869503B2 (en) 2009-12-04 2014-10-28 Steamdrive Gmbh Drive train, in particular for a motor vehicle
AT510809A1 (de) * 2010-11-16 2012-06-15 Gs Gruber Schmidt Vorrichtung zur abwärmenutzung
US8844291B2 (en) 2010-12-10 2014-09-30 Vaporgenics Inc. Universal heat engine
US9500205B2 (en) 2011-07-20 2016-11-22 Mitsubishi Heavy Industries, Ltd. Multi-pressure radial turbine system
EP2735710A4 (fr) * 2011-07-20 2015-03-25 Mitsubishi Heavy Ind Ltd Système de turbine radiale multipression
WO2013148297A1 (fr) * 2012-03-24 2013-10-03 General Electric Company Système et procédé de récupération de chaleur perdue provenant de deux sources de chaleur
US9038391B2 (en) 2012-03-24 2015-05-26 General Electric Company System and method for recovery of waste heat from dual heat sources
CN103061835A (zh) * 2012-12-28 2013-04-24 东南大学 一种复叠式有机朗肯循环高效热机
FR3004486A1 (fr) * 2013-04-11 2014-10-17 Aqylon Dispositif permettant de transformer l'energie thermique en energie mecanique au moyen d'un cycle de rankine organique a detente fractionnee par des regenerations
WO2015117619A1 (fr) * 2014-02-04 2015-08-13 Talbot New Energy Ag Système de production de courant basse pression
WO2015117621A1 (fr) * 2014-02-06 2015-08-13 Talbot New Energy Ag Système de production d'un flux basse pression
WO2016111976A1 (fr) * 2015-01-05 2016-07-14 General Electric Company Cycle de rankine organique à pression multiple
CN107407165A (zh) * 2015-01-05 2017-11-28 诺沃皮尼奥内技术股份有限公司 多压力有机兰金循环
US10436075B2 (en) 2015-01-05 2019-10-08 General Electric Company Multi-pressure organic Rankine cycle
WO2017151539A1 (fr) * 2016-02-29 2017-09-08 Ethosgen, Llc Génération d'électricité à l'aide d'un moteur thermique et de lits de sorption
AT521050A4 (de) * 2018-05-29 2019-10-15 Fachhochschule Burgenland Gmbh Verfahren zur Steigerung der Energieeffizienz in Clausius-Rankine-Kreisprozessen
AT521050B1 (de) * 2018-05-29 2019-10-15 Fachhochschule Burgenland Gmbh Verfahren zur Steigerung der Energieeffizienz in Clausius-Rankine-Kreisprozessen
US11137177B1 (en) 2019-03-16 2021-10-05 Vaporgemics, Inc Internal return pump
CN112594950A (zh) * 2020-12-29 2021-04-02 深圳市海吉源科技有限公司 一种低温冷水制冷机组及控制方法
CN112594950B (zh) * 2020-12-29 2024-02-09 深圳市海吉源科技有限公司 一种低温冷水制冷机组及控制方法
US12135016B2 (en) 2021-04-02 2024-11-05 Ice Thermal Harvesting, Llc Systems for generating geothermal power in an organic Rankine cycle operation during hydrocarbon production based on wellhead fluid temperature
US12140124B2 (en) 2021-04-02 2024-11-12 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power at a drilling rig
US12163485B2 (en) 2021-04-02 2024-12-10 Ice Thermal Harvesting, Llc Systems and methods utilizing gas temperature as a power source
US12305624B2 (en) 2021-04-02 2025-05-20 Ice Thermal Harvesting, Llc Modular mobile heat generation unit for generation of geothermal power in organic rankine cycle operations
US12312981B2 (en) 2021-04-02 2025-05-27 Ice Thermal Harvesting, Llc Systems and methods utilizing gas temperature as a power source
US12385474B2 (en) 2021-04-02 2025-08-12 Ice Thermal Harvesting, Llc Systems for generating geothermal power in an organic Rankine cycle operation during hydrocarbon production based on working fluid temperature
US12454896B2 (en) 2021-04-02 2025-10-28 Ice Thermal Harvesting, Llc Systems and methods utilizing gas temperature as a power source
US12180861B1 (en) 2022-12-30 2024-12-31 Ice Thermal Harvesting, Llc Systems and methods to utilize heat carriers in conversion of thermal energy

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