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WO2011081666A1 - Système de chauffage, de refroidissement et de génération d'énergie - Google Patents

Système de chauffage, de refroidissement et de génération d'énergie Download PDF

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Publication number
WO2011081666A1
WO2011081666A1 PCT/US2010/003255 US2010003255W WO2011081666A1 WO 2011081666 A1 WO2011081666 A1 WO 2011081666A1 US 2010003255 W US2010003255 W US 2010003255W WO 2011081666 A1 WO2011081666 A1 WO 2011081666A1
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WO
WIPO (PCT)
Prior art keywords
fluid
heat exchanger
rankine
cooling
heat
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Ceased
Application number
PCT/US2010/003255
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English (en)
Inventor
Rodney Hugelman
Marc Albertin
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ECOTHERMICS Corp
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ECOTHERMICS Corp
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Filing date
Publication date
Application filed by ECOTHERMICS Corp filed Critical ECOTHERMICS Corp
Priority to US13/515,558 priority Critical patent/US20120255302A1/en
Publication of WO2011081666A1 publication Critical patent/WO2011081666A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/16—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being hot liquid or hot vapour, e.g. waste liquid, waste vapour
    • F22B1/167—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being hot liquid or hot vapour, e.g. waste liquid, waste vapour using an organic fluid
    • 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

Definitions

  • This invention relates to a more efficient and flexible method of providing Combined Cooling, Heating, and Power (CCHP); so-called Tri-generation.
  • the invention embodies a mechanical/electrical power generation system that also produces selectable heating and cooling outputs in an environmentally clean and energy efficient way.
  • a combined thermal separator/power generator uses the thermodynamic properties of natural working fluids to provide supplemental heating, cooling, and power without emitting any additional greenhouse gasses to the environment by use of waste or unused heat energy. This is accomplished through the combined operation of a Rankine cycle, using a refrigerant such as ammonia (NH 3 ) as the working fluid for power production; and a carbon dioxide (C0 2 ) heat pumping cycle. Simultaneous and usable energy output forms from this combined energy efficient cycle are mechanical power and/or electricity, and various options and combinations of usable thermal energy.
  • Cogeneration also called combined heat and power (CHP) is the use of a heat engine or a power station to sequentially generate mechanical and/or electrical power as well as useful heat.
  • Conventional Rankine (i.e., water/steam) and Brayton cycle (i.e. gas turbine) assemblies have been combined in various forms to increase efficiencies advantaging heat recovery principles. Practical temperatures for a steam plant span H 2 0 boiling point to ⁇ 1200°F yielding actual efficiencies well below 50%.
  • a Brayton cycle gas turbine generator utilizes much higher input temperatures and typically yields higher flue gas output temperatures ( ⁇ 840°F to ⁇ 1220 ° F). , , PAGE 2
  • system efficiency may be improved substantially by utilizing recovered heat from the Brayton cycle, typically ⁇ 1000°F, as a heat source for a "bottoming" Rankine steam cycle.
  • These scenarios generally use higher quality (i.e. higher temperature) heat sources for operation.
  • a further conventional use for moderate quality heat ( ⁇ 212 ° F to ⁇ 350°F) that may be recovered from many processes is to drive absorption chillers for cooling.
  • a plant which produces a combination of cooling, heating, and power (CCHP) is sometimes called trigeneration or more generally a polygeneration plant.
  • a stream of medium to high temperature exhaust (waste) heat is utilized to generate a lower temperature cold stream.
  • CHP and CCHP have not lent sufficient consideration to other configurations utilizing natural refrigerants such as ammonia solely in the capacity of the power producing working fluid.
  • Applicant's Thermal Separator/Power Generator (“TSPG”) invention seeks to effectively exploit the thermodynamic properties of natural substances such as carbon dioxide, ammonia, and/or hydrocarbons to provide supplemental heating, cooling and power without emitting additional greenhouse gases to the environment, and to the extent possible, use available waste or unused heat energy.
  • NH 3 ammonia
  • C0 2 carbon dioxide
  • This TG is a network which conveniently facilitates the transportation, amplification, and conversion of waste heat offering nearly limitless opportunities for the recovery and utilization of useful thermal energy that is typically thrown away.
  • the benefits of the invention are made possible by a combination of two specific and sectional natural refrigerant systems.
  • a Rankine cycle power generator (applicant's RPG) section might use synthetic refrigerant fluids or blends.
  • a preferred embodiment would use a natural refrigerant working fluid such as ammonia (NH 3 ), which is heat boosted by a choice of options to a superheated vapor state. Secondary temperatures are also produced in the power generation cycle which are sufficient for uses such as heating domestic hot water or moderate space heating.
  • a C0 2 heat pump section thermally separates a hot and cold thermal stream from ambient or unused low temperature heat sources such as ambient air or geo-bodies.
  • This thermal separation module (applicant's TSM) section when combined in a parallel preheat operation with the RPG section, adds a significant efficiency heat boost to the RPG cycle ultimately and optionally providing power, even for the TSM operation itself, as well as providing simultaneous space or process cooling.
  • Applicant's TSM exploits the thermodynamic properties of carbon dioxide to efficiently provide full-time cooling sufficient for cooling applications and optionally (to electricity production) for off-the-electrical grid supplemental heating.
  • Applicant's invention provides a compact, modular product which is a type of natural refrigerant powered thermal and mechanical/electrical generator capable of supplying options of heating, cooling, refrigeration, hydraulic power, mechanical power, and electrical power in an integrated device serving both mobile and fixed off-the-electric grid applications.
  • Applicant's invention will convert thermal energy from waste sources such as ambient air, geothermal or geoexchange, and solar sources into useable thermodynamic energy for mechanical applications such as power generation or for thermal uses.
  • waste sources such as ambient air, geothermal or geoexchange, and solar sources
  • applicant's unit could operate as a portable platform in harsh and variable conditions and be deployed in both fixed and mobile applications.
  • Applicant's invention embodies a Thermal Separator/Power Generator ("TSPG") for rapid user distribution and deployment as a standalone machine which might efficiently serve multiple simultaneous uses.
  • TSPG Thermal Separator/Power Generator
  • Hydraulic power inputs and/or outputs are options within the scope of mechanical power features. Increased efficiency benefits from boosted thermal gain which may be provided by modular ancillary add-on heat recovery components would directly access available heat sources such as solar, water bodies, and waste heat from vehicles or other processes.
  • An object of the invention is to provide an improved efficiency thermodynamic system which provides all of the following attributes in a singular platform: ⁇ Full time thermal output suitable for heating applications 100 F to 130 F such as domestic hot water
  • Carbon dioxide is present in the soda we drink and the air we breathe and is non- flammable and non-toxic. Despite the high pressures associated with its use, carbon dioxide has been used as a refrigerant since 1862. Its use in an RPG cycle has not been seriously considered given its low critical temperature of ⁇ 85°F.
  • Figs. 1 and 2 show C0 2 and NH 3 as potential candidates for use in a combined heat pump/Rankine cycle.
  • Fig. 1 shows a C0 2 Heat Pump Cycle
  • the carbon dioxide system operates as a trans-critical vapor compression heat pump cycle with the following processes shown on its corresponding Temperature (T) - entropy (s) diagram: Process 1 -2: Compression
  • the ammonia cycle operates as a conventional power producing Rankine cycle with the following processes shown on its corresponding T-s diagram:
  • Process 5-1 Waste heat rejection The cycles are linked to one another because the heat that is rejected in Process 2-3 from the C0 2 cycle is used to provide part (Process 2-3 in the ammonia cycle) of the overall heating that is required for the ammonia Rankine cycle to operate.
  • the benefit is two- fold: 1) The C0 2 heat pump provides useful cooling that may be used to meet air conditioning or refrigeration needs, and 2) the heat that is provided by the C0 2 system to the RPG is provided at a much higher coefficient of performance ("COP") than the simple combustion of a fossil fuel which would normally have met the need.
  • COP coefficient of performance
  • Thermodynamic modeling of the TSPG system indicates that by supplementing a modest heat level input of ⁇ 400 degrees Fahrenheit the full potential of the proposed features described can be attained.
  • waste heat recovered from engine stacks or other on-site sources This would be accomplished by waste heat recovered from engine stacks or other on-site sources.
  • the RPG section of the TSPG will not only produce electrical power, but will also simultaneously produce secondary (water or air) heating ⁇ 100°F to ⁇ 130°F, which otherwise must be rejected, for use in applications such as domestic water heating.
  • the TSM section of the TSPG generates hot liquid such as water at ( ⁇ 130°F to ⁇ 200°F) while simultaneously providing for (water or air) cooling ⁇ 35°F to ⁇ 55°F.
  • TSPG Thermal Separator Power Generator
  • Applicant's TSPG invention results in mechanical/electrical power, heat, and cool at low energy consumed, if any, as additional purchased fuel/electrical energy consumption. This is based on available waste heat resources and priorities selected for the use of the energy reclaimed and used in whatever form.
  • TSM is a modular, lightweight and extremely energy efficient portable packaged platform using environmentally responsible CO, as the refrigerant compound.
  • the TSM provides hot and cold high-pressure C0 2 fluid energy streams from which to transfer thermal temperatures to low pressure, safe, easily handled and low cost hot and cold simultaneously available liquid (such as water) base thermal streams.
  • These low-pressure water- base lines offer unlimited potential for meeting heating, cooling, and refrigeration first responder needs for emergency and disaster relief applications.
  • the TSM utilizes a C0 2 heat pumping cycle, whereby low quality thermal energy is efficiently elevated to significantly higher heat quality than is possible with conventional vapor compression technology using toxic HFC or other refrigerants.
  • the proposed technical departure utilizing the proposed methods would serve many thermal/electrical/mechanical processes simultaneously leaving a cold thermal stream for cooling applications.
  • Heat energy generated with the TSM in this manner can recover more than three times the BTU's compared with electrical kW power equivalent BTU's, yielding aheating Coefficient of Performance efficiency >3, which is three or more times the electrical input to obtain it; a COP of 1. This equates to >300% efficiency compared with electricity assumed as 100%.
  • the method additionally averts a preponderance of the inherent BTU efficiency stack losses resulting in COP efficiencies ⁇ 1 and the inevitable, wasteful fuel consumption and supply logistics.
  • the TSM may integrate an Energy Recovery Module ("ERM") which utilizes the fluid-mechanical expansive properties of high pressure C0 2 gas to increase heat pumping efficiency by as much as one third.
  • ERP Energy Recovery Module
  • the net result would incorporate a C0 2 compressor with an expansion engine or ERM in an efficient TSM system design, which would increase heat pumping efficiency to a COP >3.5 or higher.
  • Combined heating/cooling COP efficiencies may be six (6) or even higher.
  • the outcome is a portable field deployable device, or a fixed heating and cooling unit with myriad applications/utilizations and very high efficiency.
  • FIG. 1 is a graph of a C0 2 heat pump cycle plotting temperature verses entropy.
  • FIG. 2 is a graph of an ammonia Rankine cycle plotting temperatures verses entropy.
  • FIG. 3 is a schematic depiction of the Thermal Separator Module and the Rankine Power Generator illustrating the orientation and applications of the combined two fluid loops.
  • FIG. 4 is a schematic diagram showing the fluid flow of the various fluid loops comprising the Thermal Separator Module and the Rankine Power Generator and the various pumps, compressors, condensers, and other components used in the loops.
  • FIGs. 3 and 4 there is illustrated a schematic diagram of applicant's invention.
  • TSM Thermal Separator Module
  • FIG. 3 There is a Thermal Separator Module (“TSM”) 10 that thermally separates and amplifies low grade or low quality heat sources that are generally less than 100 ° F, into individual, dual hot and cold thermal streams. This is conventionally known and practiced in current heat pump technology.
  • a drive motor 38 and compressor 40 to power a C02 vapor compression cycle in the TSM 10 by any of a number of power sources indicated at 12.
  • These can be various forms of hydraulic power such as hydraulic power packs, wind hydraulics, farm implements, or other hydraulic means.
  • the drive motor can also be conventionally powered by means of electrical energy.
  • the TSM has both a hot loop 14 and a cold loop 16.
  • the hot loop 14 has various applications 18 that it can satisfy a temperature boost up to ⁇ 250 ° F for the RPG working fluid in a thermal exchange between TSM 10 and RPG 22.
  • An alternative use for this thermal energy may include hydronic applications such as hot water ⁇ 130°F to ⁇ 180°F for hydronic distribution, or secondary exchange air delivery/distribution, or secondary heat exchange of other similar singular or combined applications.
  • the cold loop 16 also has various applications that it can satisfy ( ⁇ 25°F to 55°F). These include air conditioning/distribution, air conditioning hydronic delivery, secondary water cooling or chilling and other similar applications illustrated in block 20.
  • the RPG section is illustrated in Fig. 3 at 22.
  • the RPG is arranged combined by heat exchange with the C0 2 heat pumping TSM cycle.
  • low temperature sources ⁇ 100°F
  • ⁇ 200°F for preheat of the working fluid in the RPG This enhances efficiency of the RPG when waste heat sources are insufficient to supply all the thermal capacity requirements of the RPG.
  • One fluid loop at 24 in the RPG is provided to recover waste heat from various heat producing equipment such as vehicles, solar packs, heavy equipment, industrial/commercial processes, etc.
  • the RPG may generate electrical power at 28 and be a feedback source of power for TSM power source 12
  • unused warm/hot fluid such as water i s diverted at valve 32 for undefined thermal regeneration uses or for heat rejection as and if necessary.
  • the warm/hot water may be used at block 34 for warm/hot water applications such as domestic hot water uses, storage, or processes, etc.
  • Fig. 4 illustrates in detail the components and fluid flow circuits of the TSM and RPG.
  • the TSM heat pump high pressure hot loop 14 has the drive motor 38 that drives the compressor 40.
  • the compressor 40 compresses a refrigerant fluid 41 , preferably C0 2 , to high pressures on the order of 1200-2400 psi and temperatures of preferably between 150 ° F and 300 ° F and discharges it at high pressure discharge 42.
  • This fluid 41 from discharge 42 then enters a segmented high pressure to high pressure heat exchanger Rankine cycle refrigerant boiler 44 which cools the fluid 41 from the inlet to the outlet of the boiler 44.
  • the fluid 41 remains at a high pressure on the order of 1200-2400 psi, with a very small pressure drop through the refrigerant boiler 44, whereby heat from the fluid 41 is transferred from the fluid 41 to a second condensed cold Rankine cycle refrigerant fluid 46 (preferably NH 3 ), which is in another fluid flow circuit described later.
  • a second condensed cold Rankine cycle refrigerant fluid 46 preferably NH 3
  • This process is described as high pressure gas of high temperature exchanging thermal energy to a high pressure Rankine refrigerant fluid of lower temperature.
  • the refrigerant boiler 44 is similar to and more fully described in PCT US2008/006827 filed May 30, 2008 which is incorporated herein by reference.
  • both TSM fluid 41 and the Rankine refrigerant fluid circuit are at high pressures; therefore, the entire heat exchanger shell must also be designed to safely handle these pressures.
  • Other types and styles of heat exchangers can also be configured for use as known to those skilled in the art.
  • the high pressure fluid 41 (which is in a gaseous state) passes through a channel tube array in the heat exchanger gas boiler 44 where the fluid 41 is cooled to a warm gas 47 and discharged at the gas boiler 44 discharge 48.
  • the warm gas 47 may then by-pass through a throttle/expansion valve 50 which lowers the pressure and temperature of the gas 47 to a cold gas 52.
  • the throttle/expansion valve 50 controls all or a percentage of warm gas 47 which may be directed to be used by an energy recovery machine i.e., expansion engine 54 which is connected to the compressor 40 and assists in driving the compressor.
  • the expansion engine 54 and compressor 40 may be combined into one machine such as disclosed in PCT/US2006/030759 and PCT/US2008/006845.
  • This compressor/expansion engine has both expansion cylinders and compression cylinders disposed in the same engine. When an expansion engine is used, it will result in a drop in the temperature and pressure of the gas 47 to approximately 300-700 psi at 15 ° F to 50 ° F. For a full description of the compression/expansion engine, see the above referenced applications.
  • the warm gas 47 is then is routed to the expansion engine 54 and throttle/expansion valve 50 exiting either or both as a cold mixed gas/fluid 52 and into a high pressure to low pressure heat exchanger evaporator 56 where it is evaporated back to gas.
  • the cold gas 52 is warmed (as will be explained below) and exits the evaporator 56 as warmed gas 57.
  • the gas remains at close to the inlet pressure which is a pressure of approximately 300- 700 psi, with a very small pressure drop through the evaporator 56.
  • the warmed gas 57 enters the compressor 40 at a low temperature but at pressure and temperature which assures the fluid is in a gaseous state as the cycle repeats.
  • the TSM vapor compression cycle heat extraction function therefore serves to leave a resultant full time supplemental cooling loop exampled and shown, supplied as a water or water/glycol cooling or refrigeration loop but may use other gas or liquid fluids.
  • the cooling loop 16 provides cooled air 60 to a living or temperature cooled environment. It can also serve other low temperature applications such as previously described at block 20.
  • the solution 64 passes through a second stage heat exchanger 66 where ambient warm air forced by a fan 68 is blown over or through the heat exchanger 66.
  • a liquid (i.e., water based) heat exchanger 67 shown supplying block 20 for optional cooling uses.
  • Warmed water/glycol solution 70 leaves the heat exchanger 66 and/or 67 and is pumped to the low pressure section of the evaporator 56.
  • the warmed water glycol solution 70 is cooled in the evaporator 56 and exits at discharge end 72 as a low pressure and low temperature solution 64.
  • the water/glycol solution in the heat exchanger 56 is physically separated from the cold Rankine cycle refrigerant 52 that is passing through the evaporator 56. However, they are in thermal communication with each other so that the heat is removed from the warmed water/glycol solution 70 as it passes through the evaporator 56.
  • the cold water/glycol solution 64 is discharged at 72 and is then recirculated by the pump 62.
  • the RPG 22 is illustrated in the top half of Figs. 3 and 4.
  • the power producing Rankine cycle loop generally uses a relatively high subcritical boiling point refrigerant.
  • a natural refrigerant such as NH 3 is preferable for use in the RPG 22.
  • NH3 boiling point is -28°F and compares favorably with other natural but flammable refrigerants such as Propane (- 44°F) and Butane at (-3 I T).
  • CO, boiling point is very low, - 70T at ⁇ 5X atmospheric which helps explain why C0 2 is not a suitable candidate for the Rankine cycle working refrigerant.
  • a high pressure liquid feed pump 76 pumps liquid NH 3 to one end of the gas boiler 44.
  • the liquid NH 3 is physically segregated from the hot high pressure refrigerant fluid 41 that is passing through the gas boiler 44 from the compressor 40. However, the two fluids are in thermal communication so that heat from the high pressure refrigerant fluid 41 is transferred to the liquid NH 3 causing it to "boil" and transition to a gaseous state.
  • the NH 3 gas leaves the gas boiler 44 as the high pressure warm gas 78.
  • the combined cycle uses the heat exchanged in gas boiler 44 from the C0 2 heat pump refrigerant fluid 41 discharged from the compressor 40 as pre-heat boosting the temperature of the NH 3 before it enters a second pre-heater or waste heat, heat exchanger 80.
  • waste heat exchanger 80 higher temperature heat from the operations described in block 24 is recovered and transferred to the high pressure preheated yet cooler temperature NH 3 This may be accomplished by means of a hot hydronic loop 81 that circulates a fluid from the waste heat recovery source at 24 to the NH 3 waste heat exchanger 80, and then returns it to the source at 24.
  • the NH 3 gas 78 exits the pre heater 80 at 82.
  • the gas 82 is further heated by means of a heat source 84 to assure full capacity temperature and pressure adequate to power a turbine, piston machine, or other prime mover 86.
  • the heat source 84 can be a standby fueled steam boiler, direct fire to the Rankine circuit, or other appropriate heat generating source and means of generating a topping temperature suitable to reach the superheated vapor heat thresholds desired.
  • the fuel source can be an on-board fuel tank which allows the system to be portable.
  • the prime mover 86 is powered by the NH 3 and drives a generator 88. This generates electrical power 90.
  • the prime mover 86 may be any form of electrical or mechanical power generator that can be powered by the high temperature high pressure NH 3 .
  • mechanical, hydraulic or electric power can be produced.
  • Another form of utilization of the gas 78 may be made by the expansion engine as disclosed in both US2006/030759 and PCT/US2008/006845.
  • a warm gas 92 exiting prime mover 86 at a mid pressure enters a high pressure side 94 of a high pressure fluid to low pressure fluid heat exchanger 96 which is a NH 3 condenser or gas cooler providing heat rejection of the power cycle. This cools and liquefies the NH 3 and, in this embodiment, discharges it at 98 as a mixed fluid or liquid to enter liquid storage tank receiver 100 for re-circulation by the pump 76.
  • the last loop to consider is an RPG condenser loop 102.
  • water 104 will be the heat transfer fluid medium.
  • a pump not illustrated, pumps the water 104 through the loop.
  • Cool water 106 enters the heat exchanger 96 at 98. Heat from the warm gas 92 is transferred to the cool water 106 as it passes through the exchanger 96.
  • the water is discharged from the heat exchanger 96 at 108, it is warm/hot water that may be heat rejected as described at block 30 but is also suitable for many domestic warm water applications as described at block 34.

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  • General Engineering & Computer Science (AREA)
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Abstract

L'invention porte sur un séparateur thermique/générateur d'énergie qui utilise les propriétés thermodynamiques de substances frigorigènes pour assurer un chauffage supplémentaire, un refroidissement supplémentaire et fournir de l'énergie sans émettre un quelconque gaz à effet de serre additionnel dans l'environnement, par utilisation d'énergie thermique résiduelle ou non utilisée. Ceci est accompli par le fonctionnement combiné d'un générateur à cycle de Rankine utilisant un fluide frigorigène, de préférence un fluide frigorigène naturel tel que NH3, en tant que fluide de travail, et un cycle de pompe à chaleur à compression de vapeur et de CO2, également appelé module séparateur thermique. Le système combiné est appelé séparateur thermique/générateur d'énergie. Il produit de l'énergie électrique et produit simultanément un chauffage secondaire et un refroidissement secondaire par eau ou air comme sous-produits. Dans la pompe à chaleur à compression de vapeur/cycle générateur d'énergie Rankine combiné, la chaleur résiduelle provenant d'une ou de sources externes est récupérée et utilisée pour le chauffage dans le cycle d'énergie Rankine. La pompe à chaleur à CO2 assure le refroidissement et un chauffage d'espace ou de traitement facultatif à la place du rendement d'augmentation de chaleur pour le cycle générateur d'énergie Rankine.
PCT/US2010/003255 2009-12-28 2010-12-28 Système de chauffage, de refroidissement et de génération d'énergie Ceased WO2011081666A1 (fr)

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US13/515,558 US20120255302A1 (en) 2009-12-28 2010-12-28 Heating, cooling and power generation system

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US28493609P 2009-12-28 2009-12-28
US61/284,936 2009-12-28

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ES2436700R1 (es) * 2012-06-29 2014-02-13 Universidade Da Coruña Planta térmica de ciclos rankine en serie
WO2015005768A1 (fr) * 2013-07-09 2015-01-15 P.T.I. Procédé de mise à niveau et de récupération de chaleur, et compresseur pour la mise en oeuvre dudit procédé
ES2541581A1 (es) * 2015-05-07 2015-07-21 Máximo PUJOL LATRE Sistema de producción de energía eléctrica
WO2014008531A3 (fr) * 2012-07-09 2016-06-23 Just Energy Solutions Pty Ltd Système de moteur thermique
CN108053741A (zh) * 2017-12-10 2018-05-18 北京化工大学 一种过程装备与控制工程综合实验系统
CN112325687A (zh) * 2020-10-28 2021-02-05 广东电网有限责任公司广州供电局 跨季节储热的多能互补分布式能源系统
CN113446656A (zh) * 2021-06-29 2021-09-28 天津滨电电力工程有限公司 功率-负荷匹配的光伏光热pv/t热电冷联供系统调控方法

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US9243520B2 (en) * 2013-03-15 2016-01-26 Electratherm, Inc. Apparatus, systems, and methods for low grade waste heat management
US9512828B2 (en) * 2013-03-15 2016-12-06 Crowder College Bi-field solar geothermal system
US20150000260A1 (en) * 2013-06-26 2015-01-01 Walter F. Burrows Environmentally friendly power generation process
EP3001111B1 (fr) * 2014-02-28 2018-08-08 Tsinghua University Dispositif de récupération de chaleur de production combinée et d'écrêtement des pointes de puissance électrique et son procédé de fonctionnement
WO2016044098A1 (fr) 2014-09-19 2016-03-24 Ortner Charles R Générateur de hvac domestique
US10001025B2 (en) * 2014-10-03 2018-06-19 Monarch Power Corp Combined electricity, heat, and chill generation for a Rankine engine
US10458685B2 (en) * 2016-11-08 2019-10-29 Heatcraft Refrigeration Products Llc Absorption subcooler for a refrigeration system
US11041637B2 (en) * 2017-06-27 2021-06-22 Imby Energy, Inc. Cogeneration systems and methods for generating heating and electricity
CN107060931A (zh) * 2017-06-28 2017-08-18 山西大学 一种工质自冷式烟气余热有机朗肯循环系统
US11466594B2 (en) 2018-03-10 2022-10-11 Gas Technology Institute Combined cooling, heating and power system
CA3097538C (fr) * 2018-11-13 2021-04-27 Lochterra Inc. Systemes et procedes pour la capture de l'energie thermique, le transport a longue distance, le stockage et la distribution de l'energie thermique capturee et de l'energie generee a partir de ceux-ci

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