EP1703201B1 - Procédé de transfert de chaleur - Google Patents

Procédé de transfert de chaleur Download PDF

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Publication number
EP1703201B1
EP1703201B1 EP05005089A EP05005089A EP1703201B1 EP 1703201 B1 EP1703201 B1 EP 1703201B1 EP 05005089 A EP05005089 A EP 05005089A EP 05005089 A EP05005089 A EP 05005089A EP 1703201 B1 EP1703201 B1 EP 1703201B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
medium
plate heat
liquid
gaseous
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.)
Expired - Lifetime
Application number
EP05005089A
Other languages
German (de)
English (en)
Other versions
EP1703201A1 (fr
Inventor
David Hawkins
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.)
Kelvion PHE GmbH
Original Assignee
GEA Ecoflex 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 GEA Ecoflex GmbH filed Critical GEA Ecoflex GmbH
Priority to DK05005089T priority Critical patent/DK1703201T3/da
Priority to AT05005089T priority patent/ATE445812T1/de
Priority to DE502005008317T priority patent/DE502005008317D1/de
Priority to EP05005089A priority patent/EP1703201B1/fr
Priority to US11/146,510 priority patent/US7284380B2/en
Publication of EP1703201A1 publication Critical patent/EP1703201A1/fr
Application granted granted Critical
Publication of EP1703201B1 publication Critical patent/EP1703201B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
    • F22D1/00—Feed-water heaters, i.e. economisers or like preheaters
    • F22D1/003—Feed-water heater systems

Definitions

  • the invention relates to a method for heat energy transfer between a gaseous, warmer medium on the one hand and a liquid, colder medium on the other hand.
  • the object of the invention is therefore to provide an improved method for heat energy transfer.
  • the invention proposes to provide a method for heat energy transfer between a gaseous, warmer medium on the one hand and a liquid, colder medium on the other hand according to the independent claim 1.
  • the quantitative ratio of liquid and gaseous medium is chosen as a function of the temperature difference between liquid and gaseous medium at the beginning of the thermal energy transfer.
  • the flow of the liquid medium can be divided, in which case only part of the liquid medium flow is passed through the plate heat exchanger.
  • the amount of the liquid medium in the partial flow can be determined, wherein it depends on the temperature difference between the liquid and gaseous medium at the beginning of the heat energy transfer.
  • the flow of the gaseous medium before reaching the plate heat exchanger in a main gas flow on the one hand and a side stream on the other hand is divided.
  • the main gas stream is passed through the plate heat exchanger for heat energy transfer whereas the side gas stream is routed around the plate heat exchanger.
  • the secondary gas flow is thus a bypass for the plate heat exchanger.
  • the purpose of the by-pass gas stream is to re-mix the main gas stream after passing through the plate heat exchanger with the secondary gas stream so that the acid dew point can be avoided.
  • the quantity ratio of the main gas flow and the secondary gas flow must be selected accordingly.
  • a mixer connected downstream of the plate heat exchanger in the flow direction is preferably used.
  • a hybrid heat exchanger is used as a plate heat exchanger, which has been found to be particularly suitable for achieving an optimized heat energy transfer between gaseous medium on the one hand and liquid medium on the other.
  • the liquid medium is guided for the purpose of generating electrical energy in a closed flow circuit I.
  • This flow circuit I is formed by a pipeline 10, in which the liquid medium, for example feed water, is circulated by means of pumps 4.
  • the liquid medium is fed into a boiler 1, where it is evaporated.
  • the resulting vapor is then passed through a turbine 2 for electrical power generation.
  • the expanded steam passes to a condenser 3, where the liquid medium condenses out.
  • the resulting condensate is fed back to the boiler 1 via a degasser 5.
  • the turbine 2 and the degasser 5 via a bypass 11 in fluid communication.
  • the exhaust gases leaving the boiler 1 are conducted as gaseous medium through the open flow circuit II to the chimney 8.
  • a suction gas 9 is introduced for this purpose.
  • the liquid medium leaving the condenser 3 is discharged via the feed 13 and the discharge 14 through a plate heat exchanger 6, which is preferably designed as a hybrid heat exchanger.
  • the feed 13 is connected to the pipeline 10 with the interposition of a freely adjustable valve 16.
  • the plate heat exchanger 6 the liquid medium is guided past a part of the gaseous medium leaving the boiler 1 as waste gas. This leads to a cooling of the gaseous medium, wherein the water contained therein condenses out. The heat energy released as a result of the condensation is transferred to the liquid medium, so that the liquid medium leaving the plate heat exchanger 6 is warmer than the liquid medium entering the plate heat exchanger 6.
  • the flow of the gaseous medium is divided into a main gas stream and a secondary gas stream.
  • the main gas stream is passed through the plate heat exchanger 6, whereas the secondary gas stream is bypassed around the plate heat exchanger 6 as a bypass 12.
  • a mixer 7 is provided behind the plate heat exchanger 6, in which the main gas flow leaving the plate heat exchanger 6 is mixed with the side gas flow passing past the plate heat exchanger 6. The ratio of the main gas stream and the secondary gas stream is chosen so that a drop below the acid dew point is avoided.
  • measuring points a-m are shown in the schematic illustration according to FIG. 1, the measured values being reproduced at these measuring points in the following table: measuring point temperature print enthalpy a 109 ° C 60 bar 461 kJ / kg b 300 ° C 60 bar 2,885 kJ / kg c 30 ° C 1.4 bar 126 kJ / kg d 30 ° C 2 bar 126 kJ / kg e 100 ° C 1.4 bar 418 kJ / kg f 79 ° C 1.4 bar 330 kJ / kg G 180 ° C 3 bar 2,824 kJ / kg H 109 ° C 1.4 bar 457 kJ / kg i 199 ° C 218.9 kJ / kg j 199 ° C 229 kJ / kg k 199 ° C 218.9 kJ / kg l 50 ° C 54 kJ / kg m 95 ° C

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Treating Waste Gases (AREA)
  • Furnace Details (AREA)
  • Polymers With Sulfur, Phosphorus Or Metals In The Main Chain (AREA)

Claims (6)

  1. Procédé de transfert d'énergie thermique entre un fluide gazeux plus chaud d'une part et un fluide liquide plus froid d'autre part, lors duquel le fluide liquide et le fluide gazeux sont guidés au voisinage l'un de l'autre au moyen d'un échangeur thermique à plaques (6), le fluide gazeux étant refroidi et l'eau contenue dans ce dernier étant éliminée par condensation, l'énergie thermique libérée du fait de la condensation étant transférée au milieu liquide,
    caractérisé en ce que
    avant d'atteindre l'échangeur thermique à plaques (6), le courant de fluide est divisé en un courant principal et en un courant auxiliaire.
  2. Procédé selon la revendication 1, caractérisé en ce que le rapport quantitatif entre le fluide liquide et gazeux est sélectionné en fonction de la température différentielle entre le fluide liquide et gazeux au début du transfert thermique.
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce que le courant auxiliaire du fluide gazeux est guidé autour de l'échangeur thermique à plaques.
  4. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que, après passage de l'échangeur thermique à plaques (6), le courant principal du fluide gazeux est mélangé au courant gazeux auxiliaire du fluide gazeux guidé au voisinage de l'échangeur thermique à plaques (6).
  5. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que le rapport quantitatif entre le courant principal de gaz et le courant auxiliaire de gaz est sélectionné de sorte à éviter une non atteinte du point de rosée acide.
  6. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce qu'on utilise en tant qu'échangeur thermique à plaques (6) une échangeur thermique hybride.
EP05005089A 2005-03-09 2005-03-09 Procédé de transfert de chaleur Expired - Lifetime EP1703201B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
DK05005089T DK1703201T3 (da) 2005-03-09 2005-03-09 Fremgangsmåde til varmeenergioverförsel
AT05005089T ATE445812T1 (de) 2005-03-09 2005-03-09 Verfahren zur wärmeenergieübertragung
DE502005008317T DE502005008317D1 (de) 2005-03-09 2005-03-09 Verfahren zur Wärmeenergieübertragung
EP05005089A EP1703201B1 (fr) 2005-03-09 2005-03-09 Procédé de transfert de chaleur
US11/146,510 US7284380B2 (en) 2005-03-09 2005-06-07 Method for heat energy transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05005089A EP1703201B1 (fr) 2005-03-09 2005-03-09 Procédé de transfert de chaleur

Publications (2)

Publication Number Publication Date
EP1703201A1 EP1703201A1 (fr) 2006-09-20
EP1703201B1 true EP1703201B1 (fr) 2009-10-14

Family

ID=34934141

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05005089A Expired - Lifetime EP1703201B1 (fr) 2005-03-09 2005-03-09 Procédé de transfert de chaleur

Country Status (5)

Country Link
US (1) US7284380B2 (fr)
EP (1) EP1703201B1 (fr)
AT (1) ATE445812T1 (fr)
DE (1) DE502005008317D1 (fr)
DK (1) DK1703201T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110220111A (zh) * 2019-03-20 2019-09-10 张家港富瑞重型装备有限公司 一种液化船用罐tcs供气方法

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2363455T3 (es) * 2008-07-16 2011-08-04 Abb Research Ltd. Sistema de almacenamiento de nergía termoeléctrica y método de almacenamiento de energía termoeléctrica.

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3282334A (en) * 1963-04-29 1966-11-01 Trane Co Heat exchanger
GB1444235A (en) * 1973-11-27 1976-07-28 Tkach G A Smolyak V D Frumin V Plate heat exchangers
US4969507A (en) * 1977-06-30 1990-11-13 Rosenblad Axel E Integral blow down concentrator with air-cooled surface condenser
US4216002A (en) * 1979-01-11 1980-08-05 Rosenblad Corporation Selective condensation process and condenser apparatus
NL8200384A (nl) * 1982-02-02 1983-09-01 Beondu Ag Condenserende ketel.
SU1273140A1 (ru) * 1985-02-22 1986-11-30 Уфимский Нефтяной Институт Тепломассообменный аппарат
DE4307608C2 (de) * 1993-03-05 1998-02-19 Ver Energiewerke Ag Verfahren und Vorrichtung zur Energienutzung von Rauchgasen in kohlegefeuerten Kraftwerken
DE4343399C2 (de) 1993-12-18 1995-12-14 Balcke Duerr Ag Plattenwärmetauscher
US6357396B1 (en) * 2000-06-15 2002-03-19 Aqua-Chem, Inc. Plate type heat exchanger for exhaust gas heat recovery
US6568466B2 (en) * 2000-06-23 2003-05-27 Andrew Lowenstein Heat exchange assembly
DE10146368A1 (de) * 2000-09-22 2002-06-06 Denso Corp Wärmetauscher
US6360557B1 (en) * 2000-10-03 2002-03-26 Igor Reznik Counter flow air cycle air conditioner with negative air pressure after cooling
SE0201597L (sv) * 2002-05-29 2003-10-21 Alfa Laval Corp Ab Plattvärmeväxlaranordning samt värmeväxlarplatta
IES20040324A2 (en) * 2003-05-08 2004-11-17 Alley Enterprises Ltd A condensing unit
US7134483B2 (en) * 2003-09-26 2006-11-14 Flair Corporation Refrigeration-type dryer apparatus and method

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110220111A (zh) * 2019-03-20 2019-09-10 张家港富瑞重型装备有限公司 一种液化船用罐tcs供气方法

Also Published As

Publication number Publication date
EP1703201A1 (fr) 2006-09-20
DK1703201T3 (da) 2009-11-23
ATE445812T1 (de) 2009-10-15
DE502005008317D1 (de) 2009-11-26
US20060201166A1 (en) 2006-09-14
US7284380B2 (en) 2007-10-23

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