EP2557279A2 - Energy generation from low temperature heat - Google Patents

Energy generation from low temperature heat Download PDF

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Publication number
EP2557279A2
EP2557279A2 EP12005615A EP12005615A EP2557279A2 EP 2557279 A2 EP2557279 A2 EP 2557279A2 EP 12005615 A EP12005615 A EP 12005615A EP 12005615 A EP12005615 A EP 12005615A EP 2557279 A2 EP2557279 A2 EP 2557279A2
Authority
EP
European Patent Office
Prior art keywords
working fluid
expander
pressure
relaxed
fluid
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.)
Withdrawn
Application number
EP12005615A
Other languages
German (de)
English (en)
Other versions
EP2557279A3 (fr
Inventor
Heinz Dr. Bauer
Rainer Sapper
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.)
Linde GmbH
Original Assignee
Linde GmbH
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 Linde GmbH filed Critical Linde GmbH
Publication of EP2557279A2 publication Critical patent/EP2557279A2/fr
Publication of EP2557279A3 publication Critical patent/EP2557279A3/fr
Withdrawn legal-status Critical Current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
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • 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

  • the working fluid preferably water or ammonia
  • the working fluid is brought by the pump P10 to a pressure beyond the critical pressure and fed via line 10 to the heat exchanger E10.
  • This in the heat exchanger E10 against the working medium cooled medium is then withdrawn via line B.
  • the heat exchanger E10 and the composition of the working fluid are to be interpreted or selected such that the working fluid 10 is heated in the heat exchanger E10 up to a temperature above the critical temperature.
  • the sensible heat supplied to the heat exchanger E10 by the medium A can be used particularly well. If the temperature of the working fluid 11 after the heat exchanger E10 sufficiently far - typically at least 30 K - is above the critical temperature, the expander X10 can be operated in the gas phase, thus avoiding unwanted partial condensation of the working fluid in the expander X10.
  • the expander X10 is connected to a generator G.
  • the valve V10 serves to keep the pressure of the working fluid in the heat exchanger E10 above the critical pressure.
  • the relaxed working fluid 12 is not only completely condensed in the heat exchanger E20, but also supercooled and then fed to the collection or buffer tank D10. For this it passes via line 13 again to the pump P10.
  • Object of the present invention is to provide a generic method for the conversion of thermal energy into mechanical energy by means of a Rankine cycle, which avoids the aforementioned disadvantages, in particular allows a higher efficiency.
  • a method for the conversion of thermal into mechanical energy by means of a Rankine cycle is proposed, which is characterized in that the regulation of the maximum pressure of the working fluid by means of an adjustable with respect to the flow rate of the working fluid expander and / or with respect to the flow rate of the working fluid controllable pump.
  • the regulation of the maximum pressure of the working fluid is not by means of a valve, but by means of an adjustable with respect to the flow rate of the working fluid expander and / or with respect to the flow rate of the working fluid controllable pump.
  • the controllable with respect to the flow rate of the working fluid expander preferably has an adjustable mecanicsleitapparat, which preferably consists of a nozzle ring at the inlet of the expander.
  • the working fluid is additionally warmed in particular during the start-up procedure and / or the partial-load operation.
  • This embodiment of the method according to the invention requires an additional heat exchanger and an (additional) media flow capable of providing heat at a sufficiently high level.
  • this additional heating of the working fluid ensures that the temperature of the working fluid is at least 30 ° C., preferably 40 ° to 60 ° C., above the critical temperature even during the start-up procedure and / or during partial load operation.
  • the inlet temperature of the expander can also be kept substantially constant during the start-up procedure and / or during partial-load operation.
  • the relaxed working fluid is used to preheat the pumped working fluid before it is subjected to heat exchange with the external fluid.
  • This embodiment of the method according to the invention is particularly useful when the outlet temperature of the working fluid from the expander is higher than the condensation temperature in the expander downstream heat exchanger. In this case, the heat can out the temperature interval between the outlet temperature and the condensation temperature are used for preheating the working fluid.
  • the expanded working fluid be condensed, but not be overcooled.
  • a subcooling of the working fluid can be dispensed with in particular if the collecting container to be provided is set up sufficiently high above the pump in order to prevent undesired cavitation in the pump.
  • the pressure of the working fluid at the inlet of the expander at least 30%, preferably between 40 and 50% above the critical pressure of the working fluid.
  • propane, propylene or any mixture of propane and propylene circulates as the working medium in the Rankine cycle.
  • This embodiment is particularly advantageous when the temperature of the external medium A between 120 and 200 ° C, preferably between 130 and 160 ° C.
  • the circulating in the Rankine cycle working fluid is brought by the pump P1 to the desired working pressure and preheated in the heat exchanger E3 against the relaxed working fluid 5.
  • a pump P1 is provided which can be regulated with respect to the flow rate of the working fluid 1.
  • the working fluid is pumped to a pressure that can be ensured that the pressure of the heated working fluid 4 at the inlet of the expander X1 is at least 30%, preferably between 40 and 50% above the critical pressure of the working fluid.
  • the preheated in the heat exchanger E3 working fluid is supplied via line 2 to the heat exchanger E1, via line A, an external medium, such as hot water, is supplied.
  • This external medium is cooled in the heat exchanger E1 against the working fluid and withdrawn via line B from the heat exchanger E1.
  • the working medium withdrawn from the heat exchanger E1 via line 3 is preferably warmed to a temperature which is at least 30 K above its critical temperature.
  • the heat exchanger E4 is used to heat the working fluid by a suitable (additional) external medium, preferably during the start-up procedure and / or in partial load operation. During normal operation of the Rankine cycle, this heat exchanger is not required.
  • the working fluid is supplied to the expander X1.
  • the expander X1 is a variable expander with respect to the flow rate of the working fluid.
  • the expander X1 preferably has an adjustable devissleitapparat Y, which preferably consists of a nozzle ring at the inlet of the expander.
  • the relaxed working fluid is fed via line 5 to the heat exchanger E3.
  • the preheating of the pumped working fluid 1 realized in the heat exchanger E3 is particularly expedient if the outlet temperature of the working fluid 5 from the expander X1 is higher than the condensation temperature in the heat exchanger E2 downstream of the expander X1. In this case, the heat from the temperature interval between the outlet temperature and the condensation temperature in the heat exchanger E3 for preheating the working fluid 1 can be used.
  • the relaxed working fluid is fed to the heat exchanger E2 and condensed in this against a suitable external medium and undercooled. Subsequently, the supercooled working fluid is fed via line 7 to the collection or buffer tank D1. For this it passes via line 8 again to the pump P1. A subcooling of the working fluid 6 in the heat exchanger E2 can then be dispensed with if the collecting tank D1 is set up sufficiently high above the pump P1 to prevent unwanted cavitation in the pump P1.
  • the working medium used is preferably propane, propylene or any mixture of propane and propylene.
  • the method according to the invention for the conversion of thermal energy into mechanical energy makes it possible to stabilize the drift state of the expander X1, which leads to an improved operation of the Rankine refrigeration cycle.
  • the method according to the invention has a higher efficiency than the method described at the beginning, which belongs to the prior art.

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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)
EP12005615.5A 2011-08-09 2012-08-02 Energy generation from low temperature heat Withdrawn EP2557279A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011109777A DE102011109777A1 (de) 2011-08-09 2011-08-09 Energiegewinnung aus Niedertemperaturwärme

Publications (2)

Publication Number Publication Date
EP2557279A2 true EP2557279A2 (fr) 2013-02-13
EP2557279A3 EP2557279A3 (fr) 2013-11-06

Family

ID=46633988

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12005615.5A Withdrawn EP2557279A3 (fr) 2011-08-09 2012-08-02 Energy generation from low temperature heat

Country Status (4)

Country Link
US (1) US20130036737A1 (fr)
EP (1) EP2557279A3 (fr)
DE (1) DE102011109777A1 (fr)
ZA (1) ZA201205994B (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014017802A1 (de) 2014-12-02 2016-06-02 Linde Aktiengesellschaft Effektivere Arbeitsgewinnung bei der Erwärmung kryogener Flüssigkeiten
EP2604814B1 (fr) * 2011-12-14 2018-08-29 Nuovo Pignone S.p.A. Système à cycle fermé pour récupérer la chaleur perdue

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107905864B (zh) * 2017-11-13 2018-10-30 清华大学 一种储能发电系统及其控制方法

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6751959B1 (en) 2002-12-09 2004-06-22 Tennessee Valley Authority Simple and compact low-temperature power cycle

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4109469A (en) * 1977-02-18 1978-08-29 Uop Inc. Power generation from refinery waste heat streams
US4358930A (en) * 1980-06-23 1982-11-16 The United States Of America As Represented By The United States Department Of Energy Method of optimizing performance of Rankine cycle power plants
FR2928979B1 (fr) * 2008-03-19 2015-05-01 Snecma Dispositif de commande d'aubes a calage variable dans une turbomachine.
JP4935935B2 (ja) * 2008-12-18 2012-05-23 三菱電機株式会社 排熱回生システム
US20100319346A1 (en) * 2009-06-23 2010-12-23 General Electric Company System for recovering waste heat
US8096128B2 (en) * 2009-09-17 2012-01-17 Echogen Power Systems Heat engine and heat to electricity systems and methods

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6751959B1 (en) 2002-12-09 2004-06-22 Tennessee Valley Authority Simple and compact low-temperature power cycle

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2604814B1 (fr) * 2011-12-14 2018-08-29 Nuovo Pignone S.p.A. Système à cycle fermé pour récupérer la chaleur perdue
DE102014017802A1 (de) 2014-12-02 2016-06-02 Linde Aktiengesellschaft Effektivere Arbeitsgewinnung bei der Erwärmung kryogener Flüssigkeiten

Also Published As

Publication number Publication date
DE102011109777A1 (de) 2013-02-14
EP2557279A3 (fr) 2013-11-06
US20130036737A1 (en) 2013-02-14
ZA201205994B (en) 2013-05-29

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