CN103195524A - Non-azeotropic working fluid mixtures for rankine cycle systems - Google Patents
Non-azeotropic working fluid mixtures for rankine cycle systems Download PDFInfo
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Images
Classifications
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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
-
- 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
Abstract
A power generation system includes a non-azeotropic working fluid mixture and a Rankine cycle system. The Rankine cycle system includes a turbine generator that is driven by vapor of the first working fluid mixture, and a condenser that exchanges thermal energy between the vapor received from the turbine generator and a cooling medium. The working fluid mixture is characterized by a condenser temperature glide during phase change between approximately five degrees and thirty degrees Kelvin, a condensing pressure between approximately one tenth of one percent and eleven percent of a critical pressure of the working fluid mixture, and a condenser bubble point temperature between approximately one degree and nine degrees Kelvin greater than a temperature at which the cooling medium is received by the condenser.
Description
The present invention makes under government supports according to the contract number No.DE-EE0002770 that U.S. Department of Energy authorizes.Government can enjoy certain right in the present invention.
Technical field
The present invention relates to Rankine cycle system, and especially, the present invention relates to cycle through organic rankine cycle system with energy-producing non-azeotropic working fluid mixture.
Background technique
Organic Rankine circulation (ORC) system can be used for producing electric energy at for example system for geothermal production of electricity.Typical organic rankine cycle system can comprise the organic working fluids that cycles through pump, vaporizer, turbogenerator and condenser.If technical and economic requirements allows, also can use recuperator.During operation, vaporizer is delivered to heat energy the working fluid in order to form working fluid steam, along with this steam driven turbogenerator of steam expansion from warm relatively heat source fluid.Condenser is delivered to cold relatively low-temperature receiver (heat sink) fluid in order to made its condensation before working fluid steam is fed to vaporizer again by pump with heat energy (for example heat) from expanded working fluid steam.
Typical organic working fluids can comprise single (pure) chemical composition, or the azeotropic mixture of different chemical component.But the folder point that accompanies with the organic working fluids of single component in heat exchanger has reduced usually and adopts them to carry out the total efficiency of the organic rankine cycle system of work.The point at minimum (minimum) temperature gap place that exists in the temperature working fluid curve can be described in term " folder point " between temperature working fluid and heat source fluid temperature or low-temperature receiver fluid temperature (F.T.).
Summary of the invention
According to a first aspect of the invention, power generation system comprises non-azeotropic working fluid mixture and Rankine cycle system.This Rankine cycle system comprises the steam-powered turbogenerator by the working fluid mixture, and the condenser that exchanges heat energy between the steam that is received from turbogenerator and cooling medium.The working fluid mixture show about 5 degree Kelvins to the condenser temperature slippage between 30 degree Kelvins, working fluid mixture critical pressure about 0.1% to 11% between condensing pressure and high about 1 degree Kelvin of temperature of the cooling medium when receiving than condenser to the condenser bubble point temperature of about 9 degree Kelvins.
According to a second aspect of the invention, power generation system comprises Intermediate Heat Exchanger, first Rankine cycle system and second Rankine cycle system.This heat exchanger comprises the condenser passes that receives first working fluid and receives the vaporizer path of the second working fluid mixture of organic non-azeotropic.This heat exchanger is delivered to the second working fluid mixture with heat energy from first working fluid.First Rankine cycle system comprises that guiding first working fluid is by first pump of vaporizer and condenser passes.Second Rankine cycle system comprises second pump that guides the second working fluid mixture to pass through the vaporizer path, the steam-powered turbogenerator that passes through the second working fluid mixture, and the condenser that exchanges heat energy between the steam that is received from turbogenerator and cooling medium.The second working fluid mixture be characterised in that the condenser temperature slippage about 5 degree Kelvins between 30 degree Kelvins, condensing pressure the second working fluid mixture critical pressure about 0.1% to 11% between and high about 1 degree Kelvin of temperature of the cooling medium of condenser bubble point temperature when receiving than condenser to 9 degree Kelvins.
With reference to following description and appended accompanying drawing, aforementioned feature of the present invention and operation will become more apparent.
Description of drawings
Fig. 1 is the schematic representation that comprises the power generation system of Rankine cycle system;
Fig. 2 is the warm entropy phasor that cycles through the organic non-azeotropic working fluid mixture of Rankine cycle system shown in Figure 1; And
Fig. 3 is the schematic representation that comprises the alternative embodiment of power generation system of a plurality of Rankine cycle systems;
Fig. 4 is the warm entropy phasor of power generation system operation period working fluid mixture.
Fig. 5 is another warm entropy phasor of power generation system operation period working fluid.
Embodiment
Fig. 1 is the schematic representation that comprises the power generation system 10 of the working fluid mixture (for example organic non-azeotropic working fluid mixture) that cycles through Rankine cycle system 12 (for example organic rankine cycle system).Rankine cycle system 12 can comprise turbogenerator 14, condenser 16 (for example contra-flow heat exchanger), pump 18 and vaporizer 20 (for example contra-flow heat exchanger).Condenser 16 can comprise the first heat exchange path 22 and the second heat exchange path 24.Vaporizer 20 can comprise the first heat exchange path 26 and the second heat exchange path 28.
Operation period, the working fluid mixture can cycle through the second heat exchange path 28 of the first heat exchange path 22, pump 18 and the vaporizer of turbogenerator 14, condenser sequentially, and the cyclic loop that they can seal links together.In some embodiments, power generation system 10 can also comprise and being connected, for example, and the liquid receiver/hydraulic accumulator between the first heat exchange path 22 and the pump 18.Cooling medium (for example water, seawater, air) can guide the second heat exchange path 24 by condenser.Heat source fluid can guide the first heat exchange path 26 by vaporizer.
Fig. 2 is the warm entropy phasor of Rankine cycle system 12 operation period working fluid mixture.This phasor shown first curve 30 corresponding to organic non-azeotropic working fluid mixture, corresponding to second curve 32 of cooling medium with corresponding to the 3rd curve 34 of heat source fluid.With reference to Fig. 1 and 2, the superheated vapor guiding at point 200 places with the working fluid mixture enters turbogenerator 14.At point 200 and put between 204, steam expansion and mechanically drive turbogenerator 14, but produce power (for example electric energy) thus.Locate steam is entered the first heat exchange path 22 from turbogenerator 14 guiding at 204.Between 204 and 206, heat energy enters the cooling medium from the transmission of working fluid mixture by condenser 16, and this can cause the phase transformation of working fluid mixture generation from steam to liquid.Steam can, for example, the point 204 and put 208 between in the first heat exchange path 22, remove overheated (de-superheated), and the point 208 and put 210 between be condensed into liquid.This liquid is cold excessively in the first heat exchange path 22 between can also and putting 206 at point 210.At point 206 and put between 212, this liquid enters pump 18 from 22 guiding of the first heat exchange path.At point 212 and put between 214, this liquid pressurize in pump 18, and guides at point 216 places and to enter the second heat exchange path 28.At point 216 and put between 200, heat energy enters the working fluid mixture by vaporizer 20 from the heat source fluid transmission, and this may cause the working fluid mixture that another phase transformation from liquid to steam takes place.This liquid can, for example, at point 216 with preheating in the second heat exchange path 28 between putting 220, and evaporation becomes steam between point 220 and 218.This steam is all right, and for example, the overheated point 218 that surpasses is to putting 200 to minimize the risk of mixture steam condensation in turbogenerator 14.At point 200 places steam is entered turbogenerator 14 from 28 guiding of the second heat exchange path then.
The working fluid mixture can show some character, for example at the temperature glide during the phase transformation, pressure, bubble point temperature in condenser passes 22 and vaporizer path 28, and make the thermal efficiency of cycle during generating potential and the aforementioned Rankine cycle increase the mixture critical pressure of (for example maximization).The saturated-steam temperature of working fluid mixture and the temperature contrast between the saturated liquid temperature described in term " temperature glide ".What term " saturated-steam temperature " was described is the dew point temperature of working fluid mixture; For example during the condensation the point 208 places temperature, and the evaporation during the point 218 places temperature.What term " saturated liquid temperature " was described is the bubble point temperature of working fluid mixture; For example during the condensation the point 210 places temperature, and the evaporation during the point 220 places temperature.The condenser temperature slippage can be, for example, in about 5 degree Kelvins to (for example between about 6-8 ° of K and 20-25 ° of K) between 30 degree Kelvins.Condenser pressure can, for example, the critical pressure of working fluid mixture 1% about 1/10th (0.1%) to 11% between (for example at about 1-2.5% of critical pressure between the 7.5-8%).The condenser bubble point temperature at point 210 places can, for example, the temperature T of the cooling medium when receiving than the second heat exchange path 24
5(T for example
5Between about 280 ° of K to 308 ° of K) high about 1 degree Kelvin is to 9 degree Kelvins (for example high about 1 ° of K to 5 ° of K).Critical pressure can for example approximately 2MPa between the 6.5MPa.
The working fluid mixture can also show other features during Rankine cycle, for example low global warming potentiality (GWP), low flammability, low ozone depletion potentiality, low toxicity etc.Term " global warming potentiality " is that certain greenhouse gases contains in the atmosphere during their atmospheric lifetime heat is with respect to the relative measurement of carbon dioxide.The global warming potentiality of carbon dioxide is standardized as 1.The global warming potentiality of described working fluid mixture can be for example less than about 675 (for example less than about 150-250), and the working fluid mixture can be for example nonflammable.
The mixture of some non-azeotropic may show lower condensation coefficient, and this is because the interface temperature between the liquid and gas that reduce.The interface temperature of this reduction causes heat transfer and resistance to mass tranfer.For fear of this problem, the working fluid mixture can be chosen as (for example minimum) condensation coefficient that makes the condensation coefficient of this mixture be higher than each component.The component of minimum volatilization refers to the minimum component of boiling point under the fixed temperature.
Described working fluid mixture can be by mixing manufacturing with multiple different chemical component (for example multiple organic chemistry component).This working fluid mixture can comprise, for example, and the chemical component of listing in the multiple following table 1.
Aforementioned chemical component can for example, design and use so that the heat exchange temperature slippage of working fluid mixture, heat exchanger pressure, bubble point temperature and/or other characteristics (for example GWP, flammability etc.) adapt to concrete Rankine cycle system through selecting.Chemical component can also be through selection, and for example, thereby so that the folder point moves the temperature T when reducing heat source fluid outflow vaporizer heat exchange path 26
6, can improve the efficient of Rankine cycle by the generating quantity that increases per unit resource flow thus.Be included in the working fluid mixture in the power generation system 10 of Fig. 1, for example, can comprise first chemical component and second chemical component.The example of first and second chemical components combinations is listed in the table below in 2.
The thermodynamic property of the refrigerant mixture that provides in the table 2 and transport properties use REFPROP 8.0 databases of NBS and Institute for Research and Technology to generate.The equation of state of these refrigerant mixtures uses the empirical estimating figure (for example mixing rule) that is included in this database to generate.Yet the present invention is not limited to above-mentioned mixing rule.
Described working fluid mixture can also comprise chemical component and/or the compound that one or more are extra, and its selection is used for for example strengthening systematic function, strengthen heat transfer between the Rankine cycle fluid, strengthen diagnostic (diagnostics), refractory nature is provided, lubricity is provided, fluid stability is provided, corrosion resistance etc. is provided.This working fluid mixture can also comprise for example fire retardant, oil, oiling agent, heat transfer strengthening agent, tracer etc.
Cooling medium can be water, air or their combination.Water can obtain from underground water reservoir, lake, streams or ocean.Cooling medium can also be the process stream that can make the condensation of working fluid mixture.Cooling medium can be received from the low-temperature receiver place, and this low-temperature receiver has in for example sink temperature between about 280 ° of K to 308 ° of K.In other embodiment, this cooling medium can be the working fluid mixture that is received from another Rankine cycle system, and this will be discussed in greater detail following.
Heat source fluid can be liquid and/or the gas that for example is received from geothermal reservoir, burning machine (for example gas turbine, internal-combustion engine etc.), solar thermal system, incinerator or other waste-energy conversion devices or industrial system or process.This heat source fluid can be received from thermal source, and this thermal source has at for example heat source temperature between about 360 ° of K to 623 ° of K.In other embodiment, this heat source fluid can be the working fluid mixture that is received from another Rankine cycle system, and this will discuss in more detail following.Selectively, this heat source fluid can omit from power generation system 10, and for example vaporizer 20 is configured to solar heat heating system (for example passing through the system of the direct heated working fluid mixture of solar energy) in this system.
In some embodiments, turbogenerator 14 can be in a plurality of turbogenerators, and these turbogenerators for example serial or parallel connection is together in Rankine cycle system.In other embodiment, vaporizer 20 can be in a plurality of vaporizers, and these vaporizers for example serial or parallel connection is together in Rankine cycle system.Also in other embodiment, condenser 16 can be in a plurality of condensers, and these condensers for example serial or parallel connection is together in Rankine cycle system.
According to another aspect of the present invention, power generation system can comprise Intermediate Heat Exchanger, top circulation (topping cycle) (for example first Rankine cycle system of operating under the high relatively temperature) and the end circulate (bottoming cycle) (for example second Rankine system of operating) under relative low temperature.Intermediate Heat Exchanger can comprise from pushing up the vaporizer path that circulation receives the condenser passes of the first organic working fluids mixture and receives second working fluid from end circulation.Intermediate Heat Exchanger is sent to second working fluid with heat energy from first working fluid.In the ORC of this cascade (cascaded) arranges, top circulation (for example high temperature ORC system) can be drawn heat, or sensible heat is for example from hot gas or hot liquid, or latent heat is for example from the fluid that condensation takes place such as the steam in refrigerant boiler/vaporizer, and produces high temperature and high pressure steam.End circulation (for example low cost/low temperature ORC system) can be efficiently and cost make effectively low temperature heat energy is converted into electric energy.
Fig. 3 is the schematic representation of power generation system 36.Power generation system 36 comprises Intermediate Heat Exchanger 38 (for example contra-flow heat exchanger), cycles through first working fluid (for example organic non-azeotropic working fluid mixture) of top circulation 40 (for example organic Rankine systems), and second working fluid (for example organic non-azeotropic working fluid mixture) that cycles through end circulation 42 (for example organic rankine cycle systems).Intermediate Heat Exchanger 38 comprises the first heat exchange path 44 and the second heat exchange path 46.The first heat exchange path 44 forms for first working fluid and carries out condenser condensing path 48.The vaporizer path 50 that the second heat exchange path 46 forms for the evaporation of second working fluid.Top circulation 40 can comprise first turbogenerator 52, condenser passes 48, first pump 56, vaporizer 58 (for example countercurrent evaporation device), and liquid receiver/hydraulic accumulator 54.Vaporizer 58 can comprise the first heat exchange path 60 and the second heat exchange path 62.End circulation 42 can comprise second turbogenerator 64, condenser 68 (for example contraflow condenser), second liquid receiver/hydraulic accumulator 66, second pump 70 and vaporizer path 50.Condenser 68 can comprise the first heat exchange path 72 and the second heat exchange path 74.
Operation period, first working fluid can cycle through first turbogenerator 52, the first heat exchange path 44 (being the condenser passes 84 of heat exchanger 38), first liquid receiver/hydraulic accumulator 54, first pump 56 and the second heat exchange path 62 sequentially, and the cyclic loop that they can seal links together.Second working fluid can cycle through second turbogenerator 64, the first heat exchange path 72 (being condenser 68), second liquid receiver/hydraulic accumulator 66, second pump 70 and the second heat exchange path 46 (being the vaporizer path 50 of heat exchanger 38) sequentially, and the cyclic loop that they can seal links together.Heat source fluid can be received from thermal source 76 places and guide by the first heat exchange path 60 (being vaporizer 58).Cooling medium can be received from low-temperature receiver 78 places and guide by the second heat exchange path 74 (being condenser 68).
In some embodiments, be used for the working fluid (for example non-azeotropic working fluid mixture) that circulating in the top and circulates in the end and can be chosen as the evaporation that makes first condensing temperature that circulates of higher temperature can be used for second circulation of lower temperature.In this way, the raising of the utilization ratio that the thermal efficiency of organic Rankine circulation can be by available thermal energy is improved.
In some embodiments, the zeotrope of relatively-high temperature can guide by the top circulation, and the zeotrope of low temperature can guide by circulating at the end relatively.The use of zeotrope in the circulation of top can make the utilization ratio of heat source fluid improve by the slippage coupling.The use of zeotrope in end circulation can reduce the nonreversibility that presents in (for example minimizing) Intermediate Heat Exchanger, and the evaporation slippage of this fluid equals to push up the condensation slippage of the working fluid mixture of circulation in this Intermediate Heat Exchanger.Fig. 4 illustrates warm entropy (T-s) phasor at aforementioned working fluid mixture of the operation period of this power generation system.This phasor has shown first curve 400 that guides the zeotrope that circulates by the top and second curve 402 that guides the zeotrope that circulates the end of by.
It is big that operating temperature difference between each component of working fluid mixture can become along with the increase of temperature glide.This species diversity can increase the efficiency of cycle of system.But the working fluid mixture of high-temperature slippage may need to comprise the condenser of relatively large surface area, is condensed into the necessary heat transfer of liquid with the steam that makes that expectation is provided.Therefore in some embodiments, one or more plate and frame contra-flow heat exchanger, the single-passes of can being configured in the heat exchanger (for example condenser and vaporizer) directly evaporate the shell pipe type contra-flow heat exchanger, perhaps the shell-and-plate contra-flow heat exchanger.
In some embodiments, the non-azeotropic first working fluid mixture can guide by the top circulation, can guide by circulating at the end and show second working fluid that does not have temperature glide relatively.Working fluid in the end circulation can comprise the azeotropic mixture of pure substance or one or more known substances (being chemical component).Zeotrope in the circulation of top can make the utilization ratio of heat source fluid improve by the slippage coupling.Though use azeotropic fluid or pure substance may increase the nonreversibility in the Intermediate Heat Exchanger in end circulation, the negative effect that slippage is followed in the condenser of end circulation has also reduced (for example minimizing).Fig. 5 illustrates warm entropy (T-s) phasor at the aforementioned working fluid of run duration of this power generation system.This phasor has shown first curve 500 that guides the non-azeotropic first working fluid mixture that circulates by the top and second curve 502 that guides second working fluid that circulates the end of by.Selectively, in other embodiment, first working fluid that shows relative no temperature glide can guide by the top circulation, but not the azeotropic second working fluid mixture can guide by circulating at the end.
Though herein disclosed is different embodiments of the present invention, those of ordinary skills be it is evident that more embodiment also may be arranged within the scope of the invention and carry into execution a plan.For example be included in the chemical component in organic non-azeotropic working fluid mixture and be not intended to and be limited to chemical product group and the component of listing in table 1 and 2.Therefore, except claims and equivalent thereof, the present invention is not limited by other.
Claims (20)
1. power generation system, it comprises
Non-azeotropic working fluid mixture; With
Rankine cycle system, it comprises the steam-powered turbogenerator by this working fluid mixture, and the condenser that exchanges heat energy between the steam that is received from turbogenerator and cooling medium,
Wherein this working fluid mixture show the condenser temperature slippage during the phase transformation of about 5 degree Kelvins between about 30 degree Kelvins, this working fluid mixture critical pressure about 0.1% to 11% between condensing pressure and high about 1 degree Kelvin of temperature of the cooling medium when receiving than the condenser condenser bubble point temperature that arrives about 9 degree Kelvins.
2. the system of claim 1, wherein said working fluid mixture comprises first chemical component and second chemical component, and first chemical component and second chemical component each is self-contained following at least a: hydrocarbon, fluorocarbon, ether, HCFC, hydrogen fluorohydrocarbon, fluorinated ketone, hydrogen fluorine ether, hydrogen chlorine fluoroolefins, bromine fluoroolefins, fluorinated olefins, HF hydrocarbon, annular siloxane and linear siloxane.
3. the system of claim 2, wherein first chemical component comprises following at least a: R134a, R245fa, R236ea, 1,1,1,2,2,4,5,5,5-, nine fluoro-4-(trifluoromethyl)-propiones, HFE-7000, R1234ze, R1234yf, R1233zd and R1243zf.
4. the system of claim 3, wherein second chemical component comprises following at least a: pentane, hexane, isohexane, cyclopentane, cyclohexane, R245fa, R1234ze, isopentane, R161, R30, R134a, R1233zd, C7FK, isobutylene, 1,1,1,2,2,4,5,5,5-, nine fluoro-4-(trifluoromethyl)-propiones, R236ea, HFE-7000, CF3I and R1243zf.
5. the system of claim 1, wherein said condenser temperature slippage in about 6 degree Kelvins between 25 degree Kelvins.
6. the system of claim 5, wherein said condenser temperature slippage in about 8 degree Kelvins between 20 degree Kelvins.
7. the system of claim 1, wherein said condensing pressure working fluid mixture critical pressure about 1% to 8% between.
8. the system of claim 7, wherein said condensing pressure working fluid mixture critical pressure about 2.5% to 7.5% between.
9. the system of claim 1, high about 1 degree Kelvin of the temperature of the cooling medium when wherein said condenser bubble point temperature receives than condenser is to 5 degree Kelvins.
10. the system of claim 1, wherein said working fluid mixture shows and is lower than about 675 global warming potentiality.
11. the system of claim 10, wherein said global warming potentiality is lower than about 150.
12. the system of claim 1, it is one of following that wherein said condenser comprises: plate and frame contra-flow heat exchanger, single-pass directly evaporate shell pipe type contra-flow heat exchanger and shell-and-plate contra-flow heat exchanger.
13. power generation system, it comprises:
Intermediate Heat Exchanger, the vaporizer path that this heat exchanger comprises the condenser passes that receives first working fluid and receives the second working fluid mixture of organic non-azeotropic, wherein this heat exchanger is delivered to the second working fluid mixture with heat energy from first working fluid;
First Rankine cycle system, it comprises first pump of first working fluid guiding by vaporizer and described condenser passes; With
Second Rankine cycle system, it comprise with second pump by described vaporizer path of second working fluid mixture guiding, by steam-powered second turbogenerator of the second working fluid mixture and between the steam that is received from second turbogenerator and cooling medium the condenser of exchange heat energy;
Wherein the second working fluid mixture be characterised in that the condenser temperature slippage about 5 degree Kelvins between 30 degree Kelvins, condensing pressure the second working fluid mixture critical pressure about 0.1% to 11% between and high about 1 degree Kelvin of temperature of the cooling medium of condenser bubble point temperature when receiving than condenser to 9 degree Kelvins.
14. the system of claim 13, wherein the second working fluid mixture comprises first chemical component and second chemical component, and first chemical component and second chemical component each is self-contained following at least a: hydrocarbon, fluorocarbon, ether, HCFC, hydrogen fluorohydrocarbon, fluorinated ketone, hydrogen fluorine ether, hydrogen chlorine fluoroolefins, bromine fluoroolefins, fluorinated olefins, HF hydrocarbon, annular siloxane and linear siloxane.
15. the system of claim 14, wherein first chemical component comprises following at least a: R134a, R245fa, R236ea, 1,1,1,2,2,4,5,5,5-, nine fluoro-4-(trifluoromethyl)-propiones, HFE-7000, R1234ze, R1234yf, R1233zd and R1243zf.
16. the system of claim 15, wherein second chemical component comprises following at least a: pentane, hexane, isohexane, cyclopentane, cyclohexane, R245fa, R1234ze, isopentane, R161, R30, R134a, R1233zd, C7FK, isobutylene, 1,1,1,2,2,4,5,5,5-, nine fluoro-4-(trifluoromethyl)-propiones, R236ea, HFE-7000, CF3I and R1243zf.
17. the system of claim 13, wherein said vaporizer is delivered to heat energy in first working fluid by heat source fluid, this heat source fluid is received from geothermal reservoir, burning machine, solar thermal system, incinerator and the industrial system, and described cooling medium comprises at least a in the liquids and gases.
18. the system of claim 13, wherein said vaporizer comprises solar thermal system.
19. the system of claim 13, wherein first working fluid comprises first chemical component and second chemical component, and first chemical component and second chemical component each is self-contained following at least a: hydrocarbon, fluorocarbon, ether, HCFC, hydrogen fluorohydrocarbon, fluorinated ketone, hydrogen fluorine ether, hydrogen chlorine fluoroolefins, bromine fluoroolefins, fluorinated olefins, HF hydrocarbon, annular siloxane and linear siloxane.
20. the system of claim 19, wherein
First chemical component comprises following at least a: R134a, R245fa, R236ea, 1,1,1,2,2,4,5,5,5-nine fluoro-4-(trifluoromethyl)-propiones, HFE-7000, R1234ze, R1234yf, R1233zd and R1243zf; And
Second chemical component comprises following at least a: pentane, hexane, isohexane, cyclopentane, cyclohexane, R245fa, R1234ze, isopentane, R161, R30, R134a, R1233zd, C7FK, isobutylene, 1,1,1,2,2,4,5,5,5-, nine fluoro-4-(trifluoromethyl)-propiones, R236ea, HF-7000, CF3I and R1243zf.
Applications Claiming Priority (2)
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| US13/345,330 | 2012-01-06 | ||
| US13/345,330 US20130174552A1 (en) | 2012-01-06 | 2012-01-06 | Non-azeotropic working fluid mixtures for rankine cycle systems |
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| CN103195524A true CN103195524A (en) | 2013-07-10 |
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| CN2012105586621A Pending CN103195524A (en) | 2012-01-06 | 2012-11-06 | Non-azeotropic working fluid mixtures for rankine cycle systems |
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| US (1) | US20130174552A1 (en) |
| EP (1) | EP2613026A3 (en) |
| CN (1) | CN103195524A (en) |
| CA (1) | CA2794061C (en) |
| PH (1) | PH12012000341A1 (en) |
| SG (1) | SG192327A1 (en) |
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Also Published As
| Publication number | Publication date |
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| US20130174552A1 (en) | 2013-07-11 |
| EP2613026A2 (en) | 2013-07-10 |
| PH12012000341A1 (en) | 2016-01-18 |
| CA2794061A1 (en) | 2013-07-06 |
| EP2613026A3 (en) | 2017-04-19 |
| CA2794061C (en) | 2015-05-12 |
| SG192327A1 (en) | 2013-08-30 |
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