EP1936129A2 - Procédé et appareil de conversion de la chaleur en énergie utile - Google Patents

Procédé et appareil de conversion de la chaleur en énergie utile Download PDF

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Publication number
EP1936129A2
EP1936129A2 EP07110803A EP07110803A EP1936129A2 EP 1936129 A2 EP1936129 A2 EP 1936129A2 EP 07110803 A EP07110803 A EP 07110803A EP 07110803 A EP07110803 A EP 07110803A EP 1936129 A2 EP1936129 A2 EP 1936129A2
Authority
EP
European Patent Office
Prior art keywords
stream
working
heat
heat exchanger
lean
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.)
Granted
Application number
EP07110803A
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German (de)
English (en)
Other versions
EP1936129B1 (fr
EP1936129A3 (fr
Inventor
Alexander I. Kalina
Richard I. Pelletier
Lawrence B. Rhodes
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.)
KCT POWER LIMITED
Original Assignee
Exergy 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
Priority claimed from US09/019,476 external-priority patent/US5953918A/en
Application filed by Exergy Inc filed Critical Exergy Inc
Priority to EP07110803.9A priority Critical patent/EP1936129B1/fr
Priority to DK07110803.9T priority patent/DK1936129T3/en
Publication of EP1936129A2 publication Critical patent/EP1936129A2/fr
Publication of EP1936129A3 publication Critical patent/EP1936129A3/fr
Application granted granted Critical
Publication of EP1936129B1 publication Critical patent/EP1936129B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F01K25/06—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 mixtures of different fluids
    • F01K25/065—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 mixtures of different fluids with an absorption fluid remaining at least partly in the liquid state, e.g. water for ammonia

Definitions

  • the invention relates to implementing a thermodynamic cycle to convert heat to useful form.
  • Thermal energy can be usefully converted into mechanical and then electrical form. Methods of converting the thermal energy of low temperature heat sources into electric power present an important area of energy generation. There is a need for increasing the efficiency of the conversion of such low temperature heat to electric power.
  • Thermal energy from a heat source can be transformed into mechanical and then electrical form using a working fluid that is expanded and regenerated in a closed system operating on a thermodynamic cycle.
  • the working fluid can include components of different boiling temperatures, and the composition of the working fluid can be modified at different places within the system to improve the efficiency of operation.
  • Systems that convert low temperature heat into electric power are described in Alexander I. Kalina's U.S. Pat. Nos. 4,346,561 ; 4,489,563 ; 4,982,568 ; and 5,029,444 .
  • systems with multicomponent working fluids are described in Alexander I. Kalina's U.S. Pat. Nos.
  • the invention features, in general a method and system for implementing a thermodynamic cycle.
  • a working stream including a low boiling point component and a higher boiling point component is heated with a source of external heat (e.g., a low temperature source) to provide a heated gaseous working stream.
  • the heated gaseous working stream is separated at a first separator to provide a heated gaseous rich stream having relatively more of the low boiling point component and a lean stream having relatively less of the low boiling point component.
  • the heated gaseous rich stream is expanded to transform the energy of the stream into useable form and to provide an expanded, spent rich stream.
  • the lean stream and the expanded, spent rich stream are then combined to provide the working stream.
  • the working stream is condensed by transferring heat to a low temperature source at a first heat exchanger and thereafter pumped to a higher pressure.
  • the expanding takes place in a first expansion stage and a second expansion stage, and a stream of partially expanded fluid is extracted between the stages and combined with the lean stream.
  • a separator between the expander stages separates a partially expanded fluid into vapor and liquid portions, and some or all of the vapor portion is fed to the second stage, and some of the vapor portion can be combined with the liquid portion and then combined with the lean stream.
  • a second heat exchanger recuperatively transfers heat from the reconstituted multicomponent working stream (prior to condensing) to the condensed multicomponent working stream at a higher pressure.
  • a third heat exchanger transfers heat from the lean stream to the working stream after the second heat exchanger.
  • the working stream is split into two substreams, one of which is heated with the external heat, the other of which is heated at a fourth heat exchanger with heat from the lean stream; the two streams are then combined to provide the heated gaseous working stream that is separated at the separator.
  • Embodiments of the invention may include one or more of the following advantages.
  • Embodiments of the invention can achieve efficiency of conversion of low temperature heat to electric power that exceeds the efficiency of standard Rankine cycles.
  • a system for implementing a thermodynamic cycle to obtain useful energy (e.g., mechanical and then electrical energy) from an external heat source is shown.
  • the external heat source is a stream of low temperature waste-heat water that flows in the path represented by points 25-26 through heat exchanger HE-5 and heats working stream 117-17 of the closed thermodynamic cycle.
  • Table 1 presents the conditions at the numbered points indicated on Fig. 1.
  • a typical output from the system is presented in Table 5.
  • the working stream of the Fig. 1 system is a multicomponent working stream that includes a low boiling component and a high boiling component.
  • a preferred working stream may be an ammonia-water mixture, two or more hydrocarbons, two or more freons, mixtures of hydrocarbons and freons, or the like.
  • the working stream may be mixtures of any number of compounds with favorable thermodynamic characteristics and solubility.
  • a mixture of water and ammonia is used.
  • the working stream has the same composition from point 13 to point 19.
  • the stream at point 34 is referred to as the expanded, spent rich stream.
  • This stream is considered “rich” in lower boiling point component. It is at a low pressure and will be mixed with a leaner, absorbing stream having parameters as at point 12 to produce the working stream of intermediate composition having parameters as at point 13.
  • the stream at point 12 is considered “lean” in lower boiling point component.
  • the working stream (of intermediate composition) at point 13 can be condensed at a lower pressure than the richer stream at point 34. This permits more power to be extracted from the turbine T, and increases the efficiency of the process.
  • the working stream at point 13 is partially condensed. This stream enters heat exchanger HE-2, where it is cooled and exits the heat exchanger HE-2 having parameters as at point 29. It is still partially, not completely, condensed. The stream now enters heat exchanger HE-1 where it is cooled by stream 23-24 of cooling water, and is thereby completely condensed, obtaining parameters as at point 14. The working stream having parameters as at point 14 is then pumped to a higher pressure obtaining parameters as at point 21. The working stream at point 21 then enters heat exchanger HE-2 where it is recuperatively heated by the working stream at points 13-29 (see above) to a point having parameters as at point 15.
  • the working stream having parameters as at point 15 enters heat exchanger HE-3 where it is heated and obtains parameters as at point 16.
  • point 16 may be precisely at the boiling point but it need not be.
  • the working stream at point 16 is split into two substreams; first working substream 117 and second working substream 118.
  • the first working substream having parameters as at point 117 is sent into heat exchanger HE-5, leaving with parameters as at point 17. It is heated by the external heat source, stream 25-26.
  • the other substream, second working substream 118 enters heat exchanger HE-4 in which it is heated recuperatively, obtaining parameters as at point 18.
  • This stream is in a state of partial, or possibly complete, vaporization.
  • point 19 is only partially vaporized.
  • the working stream at point 19 has the same intermediate composition which was produced at point 13, completely condensed at point 14, pumped to a high pressure at point 21, and preheated to point 15 and to point 16. It enters the separator S. There, it is separated into a rich saturated vapor, termed the "heated gaseous rich stream" and having parameters as at point 30, and a lean saturated liquid, termed the "lean stream” and having parameters as at point 7.
  • the lean stream (saturated liquid) at point 7 enters heat exchanger HE-4 where it is cooled while heating working stream 118-18 (see above).
  • the lean stream at point 9 exits heat exchanger HE-4 having parameters as at point 8. It is throttled to a suitably chosen pressure, obtaining parameters as at point 9.
  • the heated gaseous rich stream exits separator S.
  • This stream enters turbine T where it is expanded to lower pressures, providing useful mechanical energy to turbine T used to generate electricity.
  • a partially expanded stream having parameters as at point 32 is extracted from the turbine T at an intermediate pressure (approximately the pressure as at point 9) and this extracted stream 32 (also referred to as a "second portion" of a partially expanded rich stream, the "first portion” being expanded further) is mixed with the lean stream at point 9 to produce a combined stream having parameters as at point 10.
  • the lean stream having parameters as at point 9 serves as an absorbing stream for the extracted stream 32.
  • the resulting stream (lean stream and second portion) having parameters as at point 10 enters heat exchanger HE-3 where it is cooled, while heating working stream 15-16, to a point having parameters as at point 11.
  • the stream having parameters as at point 11 is then throttled to the pressure of point 34, obtaining parameters as at point 12.
  • the extraction at point 32 has the same composition as the streams at points 30 and 34.
  • the turbine is shown as first turbine stage T-1 and second turbine stage T-2, with the partially expanded rich stream leaving the higher pressure stage T-1 of the turbine at point 31.
  • Conditions at the numbered points shown on Fig. 2 are presented in Table 2.
  • a typical output from the Fig. 2 system is presented in Table 6.
  • the partially expanded rich stream from first turbine stage T-1 is divided into a first portion at 33 that is expanded further at lower pressure turbine stage T-2, and a second portion at 32 that is combined with the lean stream at 9.
  • the partially expanded rich stream enters separator S-2. where it is separated into a vapor portion and a liquid portion.
  • the composition of the second portion at 32 may be chosen in order to optimize its effectiveness when it is mixed with the stream at point 9.
  • Separator S-2 permits stream 32 to be as lean as the saturated liquid at the pressure and temperature obtained in the separator S-2; in that case, stream 33 would be a saturated vapor at the conditions obtained in the separator S-2.
  • the amount of mixing at stream 133 the amount of saturated liquid and the saturated vapor in stream 32 can be varied.
  • this embodiment differs from the embodiment of Fig. 1, in that the heat exchanger HE-4 has been omitted, and there is no extraction of a partially expanded stream from the turbine stage.
  • the hot stream exiting the separator S is admitted directly into heat exchanger HE-3.
  • Conditions at the numbered points shown on Fig. 3 are presented in Table 3.
  • a typical output from the system is presented in Table 7.
  • this embodiment differs from the Fig. 3 embodiment in omitting heat exchanger HE-2.
  • Conditions at the numbered points shown on Fig. 4 are presented in Table 4.
  • a typical output from the system is presented in Table 8. While omitting heat exchanger HE-2 reduces the efficiency of the process, it may be economically advisable in circumstances where the increased power given up will not pay for the cost of the heat exchanger.
  • the working fluid is expanded to drive a turbine of conventional type.
  • the expansion of the working fluid from a charged high pressure level to a spent low pressure level to release energy may be effected by any suitable conventional means known to those skilled in the art.
  • the energy so released may be stored or utilized in accordance with any of a number of conventional methods known to those skilled in the art.
  • the separators of the described embodiments can be conventionally used gravity separators, such as conventional flash tanks. Any conventional apparatus used to form two or more streams having different compositions from a single stream may be used to form the lean stream and the enriched stream from the fluid working stream.
  • the condenser may be any type of known heat rejection device.
  • the condenser may take the form of a heat exchanger, such as a water cooled system, or another type of condensing device.

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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)
EP07110803.9A 1998-02-05 1999-07-23 Procédé et appareil de conversion de la chaleur en énergie utile Expired - Lifetime EP1936129B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP07110803.9A EP1936129B1 (fr) 1998-02-05 1999-07-23 Procédé et appareil de conversion de la chaleur en énergie utile
DK07110803.9T DK1936129T3 (en) 1999-07-23 1999-07-23 Method and apparatus for converting heat into usable energy

Applications Claiming Priority (12)

Application Number Priority Date Filing Date Title
US09/019,476 US5953918A (en) 1998-02-05 1998-02-05 Method and apparatus of converting heat to useful energy
CA002278393A CA2278393C (fr) 1998-02-05 1999-07-22 Methode et appareil pour convertir de la chaleur en energie utile
HU9902503A HUP9902503A2 (hu) 1998-02-05 1999-07-23 Eljárás és berendezés hő hasznos energiává történő átalakítására szolgáló termodinamikai ciklus gyakorlati megvalósítására
ZA9904752A ZA994752B (en) 1998-02-05 1999-07-23 Method and apparatus of converting heat to useful energy.
AU41108/99A AU728647B1 (en) 1998-02-05 1999-07-23 Method and apparatus of converting heat to useful energy
EP99305850A EP1070830B1 (fr) 1998-02-05 1999-07-23 Méthode et appareil de conversion de la chaleur en énergie utile
NO993596A NO993596L (no) 1998-02-05 1999-07-23 Fremgangsmåte og anordning for å konvertere varme til nyttig energi
EP07110803.9A EP1936129B1 (fr) 1998-02-05 1999-07-23 Procédé et appareil de conversion de la chaleur en énergie utile
CZ19992631A CZ289119B6 (cs) 1998-02-05 1999-07-26 Způsob převádění tepla na vyuľitelnou energii a zařízení k provádění tohoto způsobu
CNB991109910A CN100347417C (zh) 1998-02-05 1999-07-27 用于实现热循环的方法和装置
BR9903020-9A BR9903020A (pt) 1998-02-05 1999-07-28 Método e aparelho para converter o calor em energia útil.
JP22380299A JP3785590B2 (ja) 1998-02-05 1999-08-06 熱を有用なエネルギーに変換する方法および装置

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP99305850A Division EP1070830B1 (fr) 1998-02-05 1999-07-23 Méthode et appareil de conversion de la chaleur en énergie utile

Publications (3)

Publication Number Publication Date
EP1936129A2 true EP1936129A2 (fr) 2008-06-25
EP1936129A3 EP1936129A3 (fr) 2008-07-02
EP1936129B1 EP1936129B1 (fr) 2019-01-02

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EP07110803.9A Expired - Lifetime EP1936129B1 (fr) 1998-02-05 1999-07-23 Procédé et appareil de conversion de la chaleur en énergie utile

Country Status (6)

Country Link
EP (1) EP1936129B1 (fr)
DE (1) DE69938039T2 (fr)
DK (1) DK1936129T3 (fr)
ES (1) ES2301229T3 (fr)
PT (1) PT1070830E (fr)
SI (1) SI1070830T1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1998013A3 (fr) * 2007-04-16 2009-05-06 Turboden S.r.l. Appareil pour la production d'énergie électrique à l'aide de fumées à haute température
WO2011035273A2 (fr) * 2009-09-18 2011-03-24 Kalex, Llc Systèmes et procédés pour la production combinée d'énergie et de chaleur
US8087248B2 (en) 2008-10-06 2012-01-03 Kalex, Llc Method and apparatus for the utilization of waste heat from gaseous heat sources carrying substantial quantities of dust
US8176738B2 (en) 2008-11-20 2012-05-15 Kalex Llc Method and system for converting waste heat from cement plant into a usable form of energy
US8474263B2 (en) 2010-04-21 2013-07-02 Kalex, Llc Heat conversion system simultaneously utilizing two separate heat source stream and method for making and using same
US8695344B2 (en) 2008-10-27 2014-04-15 Kalex, Llc Systems, methods and apparatuses for converting thermal energy into mechanical and electrical power
IT201900023364A1 (it) * 2019-12-10 2021-06-10 Turboden Spa Ciclo rankine organico ad alta efficienza con disaccoppiamento flessibile del calore

Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4346561A (en) 1979-11-08 1982-08-31 Kalina Alexander Ifaevich Generation of energy by means of a working fluid, and regeneration of a working fluid
US4489563A (en) 1982-08-06 1984-12-25 Kalina Alexander Ifaevich Generation of energy
US4548043A (en) 1984-10-26 1985-10-22 Kalina Alexander Ifaevich Method of generating energy
US4573321A (en) 1984-11-06 1986-03-04 Ecoenergy I, Ltd. Power generating cycle
US4586340A (en) 1985-01-22 1986-05-06 Kalina Alexander Ifaevich Method and apparatus for implementing a thermodynamic cycle using a fluid of changing concentration
US4604867A (en) 1985-02-26 1986-08-12 Kalina Alexander Ifaevich Method and apparatus for implementing a thermodynamic cycle with intercooling
US4732005A (en) 1987-02-17 1988-03-22 Kalina Alexander Ifaevich Direct fired power cycle
US4756162A (en) 1987-04-09 1988-07-12 Abraham Dayan Method of utilizing thermal energy
US4763480A (en) 1986-10-17 1988-08-16 Kalina Alexander Ifaevich Method and apparatus for implementing a thermodynamic cycle with recuperative preheating
US4899545A (en) 1989-01-11 1990-02-13 Kalina Alexander Ifaevich Method and apparatus for thermodynamic cycle
US4982568A (en) 1989-01-11 1991-01-08 Kalina Alexander Ifaevich Method and apparatus for converting heat from geothermal fluid to electric power
US5029444A (en) 1990-08-15 1991-07-09 Kalina Alexander Ifaevich Method and apparatus for converting low temperature heat to electric power
US5095708A (en) 1991-03-28 1992-03-17 Kalina Alexander Ifaevich Method and apparatus for converting thermal energy into electric power
EP0649985A1 (fr) 1993-09-22 1995-04-26 Saga University Générateur d'énergie thermique
US5440882A (en) 1993-11-03 1995-08-15 Exergy, Inc. Method and apparatus for converting heat from geothermal liquid and geothermal steam to electric power
US5572871A (en) 1994-07-29 1996-11-12 Exergy, Inc. System and apparatus for conversion of thermal energy into mechanical and electrical power
US5649426A (en) 1995-04-27 1997-07-22 Exergy, Inc. Method and apparatus for implementing a thermodynamic cycle

Patent Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4346561A (en) 1979-11-08 1982-08-31 Kalina Alexander Ifaevich Generation of energy by means of a working fluid, and regeneration of a working fluid
US4489563A (en) 1982-08-06 1984-12-25 Kalina Alexander Ifaevich Generation of energy
US4548043A (en) 1984-10-26 1985-10-22 Kalina Alexander Ifaevich Method of generating energy
US4573321A (en) 1984-11-06 1986-03-04 Ecoenergy I, Ltd. Power generating cycle
US4586340A (en) 1985-01-22 1986-05-06 Kalina Alexander Ifaevich Method and apparatus for implementing a thermodynamic cycle using a fluid of changing concentration
US4604867A (en) 1985-02-26 1986-08-12 Kalina Alexander Ifaevich Method and apparatus for implementing a thermodynamic cycle with intercooling
US4763480A (en) 1986-10-17 1988-08-16 Kalina Alexander Ifaevich Method and apparatus for implementing a thermodynamic cycle with recuperative preheating
US4732005A (en) 1987-02-17 1988-03-22 Kalina Alexander Ifaevich Direct fired power cycle
US4756162A (en) 1987-04-09 1988-07-12 Abraham Dayan Method of utilizing thermal energy
US4899545A (en) 1989-01-11 1990-02-13 Kalina Alexander Ifaevich Method and apparatus for thermodynamic cycle
US4982568A (en) 1989-01-11 1991-01-08 Kalina Alexander Ifaevich Method and apparatus for converting heat from geothermal fluid to electric power
US5029444A (en) 1990-08-15 1991-07-09 Kalina Alexander Ifaevich Method and apparatus for converting low temperature heat to electric power
US5095708A (en) 1991-03-28 1992-03-17 Kalina Alexander Ifaevich Method and apparatus for converting thermal energy into electric power
EP0649985A1 (fr) 1993-09-22 1995-04-26 Saga University Générateur d'énergie thermique
US5440882A (en) 1993-11-03 1995-08-15 Exergy, Inc. Method and apparatus for converting heat from geothermal liquid and geothermal steam to electric power
US5572871A (en) 1994-07-29 1996-11-12 Exergy, Inc. System and apparatus for conversion of thermal energy into mechanical and electrical power
US5649426A (en) 1995-04-27 1997-07-22 Exergy, Inc. Method and apparatus for implementing a thermodynamic cycle

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1998013A3 (fr) * 2007-04-16 2009-05-06 Turboden S.r.l. Appareil pour la production d'énergie électrique à l'aide de fumées à haute température
US8087248B2 (en) 2008-10-06 2012-01-03 Kalex, Llc Method and apparatus for the utilization of waste heat from gaseous heat sources carrying substantial quantities of dust
US8695344B2 (en) 2008-10-27 2014-04-15 Kalex, Llc Systems, methods and apparatuses for converting thermal energy into mechanical and electrical power
US8176738B2 (en) 2008-11-20 2012-05-15 Kalex Llc Method and system for converting waste heat from cement plant into a usable form of energy
WO2011035273A2 (fr) * 2009-09-18 2011-03-24 Kalex, Llc Systèmes et procédés pour la production combinée d'énergie et de chaleur
WO2011035273A3 (fr) * 2009-09-18 2011-07-14 Kalex, Llc Systèmes et procédés pour la production combinée d'énergie et de chaleur
US8474263B2 (en) 2010-04-21 2013-07-02 Kalex, Llc Heat conversion system simultaneously utilizing two separate heat source stream and method for making and using same
IT201900023364A1 (it) * 2019-12-10 2021-06-10 Turboden Spa Ciclo rankine organico ad alta efficienza con disaccoppiamento flessibile del calore
EP3835556A1 (fr) * 2019-12-10 2021-06-16 Turboden S.p.A. Cycle de rankine organique hautement efficace avec décharge de chaleur flexible

Also Published As

Publication number Publication date
SI1070830T1 (sl) 2008-06-30
EP1936129B1 (fr) 2019-01-02
DE69938039D1 (de) 2008-03-13
ES2301229T3 (es) 2008-06-16
DE69938039T2 (de) 2009-01-22
EP1936129A3 (fr) 2008-07-02
DK1936129T3 (en) 2019-03-04
PT1070830E (pt) 2008-04-28

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