EP0664377A1 - Verfahren zur verbesserung einer dampfturbine und dampfkreislauf kombiniertensystems mit einer fosilen primärenergiequelle - Google Patents

Verfahren zur verbesserung einer dampfturbine und dampfkreislauf kombiniertensystems mit einer fosilen primärenergiequelle Download PDF

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Publication number
EP0664377A1
EP0664377A1 EP94907572A EP94907572A EP0664377A1 EP 0664377 A1 EP0664377 A1 EP 0664377A1 EP 94907572 A EP94907572 A EP 94907572A EP 94907572 A EP94907572 A EP 94907572A EP 0664377 A1 EP0664377 A1 EP 0664377A1
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EP
European Patent Office
Prior art keywords
vapor
reheating
cycle
pressure
steam
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Withdrawn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
EP94907572A
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English (en)
French (fr)
Inventor
Serafin Mendoza Rosado
Luis E. Diez Vallejo
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.)
SEVILLANA DE ELECTRICIDAD SA
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SEVILLANA DE ELECTRICIDAD SA
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 SEVILLANA DE ELECTRICIDAD SA filed Critical SEVILLANA DE ELECTRICIDAD SA
Publication of EP0664377A1 publication Critical patent/EP0664377A1/de
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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
    • 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
    • F01K23/06—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 combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—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 combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle

Definitions

  • the invention relates to a process for improving the combination between a gas turbine and a steam cycle that uses an additional non-fossil fuel as primary energy, applicable to electric power plants or electricity and thermal energy cogeneration plants employing at least two primary energy sources: an appropriated fuel for the gas turbine and an additional non-fossil fuel (refuse, geothermal, biomass, solar energy, etc.) for the steam cycle.
  • the invention proposed herein applicable to all those cases in which the practice of intermediate reheating using the primary non-fossil energy source is not techno-economically feasible, gives a limited cost effectiveness or presents appreciable technical risks, consists in applying an intermediate reheating of the steam cycle by means of the waste heat of gas turbine exhaust gases in their high-temperature range.
  • the proposed schematic offers a number of advantages which, in general, considerably improve the conditions under which the reheating could be carried out using non-fossil primary energy, provided that this would be feasible, as here the steam reheating at relatively low pressure and temperature may be carried out near the steam turbine, in a typical heat recovery boiler, with clean gases, allowing the option of using finned tubes in the gas area and notably improving the thermal transfer, with or without intermediary fluid.
  • the regulation is much simpler as the steam cycle can operate even when the gas turbine is out of service with an admissible temporary increase in the wetness in turbine and, if necessary, regulation of the steam turbine load. With all this, the techno-economical balance is much more favorable as compared with that of existing solutions.
  • the first schematic is the simplest and corresponds to a layout in which the rest of the low-temperature energy contained in exhaust gases is used exclusively for heating condensate and feedwater up to the inlet temperature to economizer of non-fossil fuel boiler.
  • This schematic requires that the total energy contained in the gas turbine exhaust gases, in their cooling until their release to atmosphere, coincides with that required for the aforementioned heatings and for the characteristic reheating.
  • This schematic conditions and limits the gas turbine output for a given thermal output of the non-fossil fuel boiler, because of which it may be in general more convenient to use part of the gas turbine exhaust gases, after the steam reheating and before the feedwater heating, for carrying out at the maximum cycle pressure a vaporization of a part of water flow, which may be superheated either in the recovery boiler or together with the rest of the steam generated in the non-fossil boiler.
  • An important variant of this schematic consists in not limiting the operation to the intermediate reheating of steam, as described, but in generating a reheated mixture of vapors, of water and another substance having a higher boiling point than water, mixed in liquid phase with the vapor to be reheated in such a manner that, in this case, the intermediate reheating process is a combined process of vaporization-reheating wherein the less volatile substance vaporizes at variable temperature at the same time as the vapor mixture, gradually becoming richer in the less volatile substance, is reheated until all the less volatile substance has been vaporized, from which point the vapor mixture with the final composition continues being reheated, until reaching the maximum temperature of the intermediate reheating.
  • the reheated vapor mixture thereby generated once it has been expanded in the low-pressure turbine to the minimum cycle pressure, is still at a sufficiently high temperature as to deliver heat for various uses in the cycle itself ( condensate heating, vaporizations at low pressure, etc.), or external uses (water heating for domestic or industrial purposes, air heating, etc.) at variable temperature.
  • this heat yielding process there takes place the non-isothermal condensation of the less volatile substance which can thus be separated almost totally from the steam.
  • the case of a municipal solid waste (MSW) incineration plant with 1000 t/day capacity has been selected.
  • the first example shows the application with a pure steam cycle and the second, the system working with a mixture of water and a thermal fluid which is a eutectic mixture of biphenyl and biphenyl oxide and will be called hereinafter TF.
  • example 1 is the application of the process to a MSW incinerating plant working with a pure steam cycle.
  • the parameters of the steam cycle are typical values for this type of plants, except the maximum pressure in the furnace-boiler (1) which in this case is not limited by the final wetness in the expansion and, therefore, has been raised to an optimum value of 105 bar abs.
  • feedwater is heated until saturation, vaporized and superheated at the maximum process pressure.
  • the additional saturated steam obtained is mixed with that exhausted from the high-pressure body of steam turbine (6), which in this case is at a very similar temperature, and is reheated by the energy corresponding to the heat yield of higher temperature of gas turbine (5) exhaust gases before it is admitted to the low-pressure body of turbine (6).
  • the combustion gases of gas turbine (5) after the aforementioned reheating and vaporization, are used for heating the liquid from the temperature of preheating (carried out by means of an extraction from low-pressure steam turbine (6)) to the inlet temperature to incineration furnace-boiler (1).
  • Example 2 shows an application of the process to a MSW incinerating plant working with a vapor mixture of water and TF.
  • This option has all the advantages of the vapor reheating using the exhaust waste heat of a gas turbine (16) plus those offered by the use of a vapor mixture of thermal fluid (TF) and water.
  • the schematic includes the partial heating of feedwater until saturation at the maximum pressure, the vaporization at this pressure and the superheating of the vapor to the temperature of 400°C in furnace-boiler (13), in exactly the same way and under identical conditions as in example 1, except the small percentage of TF (4%) that accompanies the water, without hardly any practical incidence, which therefore has been neglected for the sake of simplicity of calculation, and the vapor is considered pure steam.
  • the heat recovery from the exhaust gases of turbine (16) is carried out in the following way:
  • the waste heat corresponding to the non-isothermal condensation of TF is used with very little exergy loss for the primary heating of combustion air and the primary heating of condensates (TF plus water).
  • the energy of higher thermal level of this recovery is used for vaporizing a part of water at low pressure which is introduced into the expanding flow in turbine (19) through a partial admission.
  • Tables 1 and 2 show the basic results of the thermal balances for application examples 1 and 2, respectively.
  • Figures 1 and 2 are the basic thermal schematics of the plant for application examples 1 and 2, respectively, which include the following elements:

Landscapes

  • 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)
EP94907572A 1993-05-03 1994-02-18 Verfahren zur verbesserung einer dampfturbine und dampfkreislauf kombiniertensystems mit einer fosilen primärenergiequelle Withdrawn EP0664377A1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
ES9300930A ES2116136B1 (es) 1993-05-03 1993-05-03 Procedimiento de mejora de la combinacion entre una turbina de gas y un ciclo de vapor con otra fuente no fosil de energia primaria.
ES9300093 1993-05-03
PCT/ES1994/000017 WO1994025739A1 (es) 1993-05-03 1994-02-18 Procedimiento de mejora de la combinacion entre une turbina de gas y un ciclo de vapor con otra fuente no fosil de energia primaria

Publications (1)

Publication Number Publication Date
EP0664377A1 true EP0664377A1 (de) 1995-07-26

Family

ID=8281672

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94907572A Withdrawn EP0664377A1 (de) 1993-05-03 1994-02-18 Verfahren zur verbesserung einer dampfturbine und dampfkreislauf kombiniertensystems mit einer fosilen primärenergiequelle

Country Status (3)

Country Link
EP (1) EP0664377A1 (de)
ES (1) ES2116136B1 (de)
WO (1) WO1994025739A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997014887A1 (de) * 1995-10-17 1997-04-24 Siemens Aktiengesellschaft Verfahren zur erzeugung von energie und kraftwerksanlage zur durchführung des verfahrens
WO2010057279A1 (en) * 2008-11-24 2010-05-27 Ribeiro Sergio Vieira Guerreir High efficiency waste to energy power plants combining municipal solid waste and natural gas

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2005135A6 (es) * 1987-04-08 1989-03-01 Carnot Sa Ciclo termico con fluido de trabajo mezcla
NL8701573A (nl) * 1987-07-03 1989-02-01 Prometheus Energy Systems Werkwijze en inrichting voor het opwekken van elektrische en/of mechanische energie uit tenminste een laagwaardige brandstof.
ES2006059A6 (es) * 1988-01-21 1989-04-01 Sener Ing & Sist Sistemas para la produccion de vapor de agua a alta presion y temperatura.
DE4101064A1 (de) * 1991-01-16 1992-07-23 Radebeul Energie Umwelt Verfahren zum betreiben eines kraftwerkes
DE4103228A1 (de) * 1991-02-02 1992-08-06 Radebeul Energie Umwelt Verfahren zum betreiben von kraftwerken
DE4117191C2 (de) * 1991-05-25 1994-11-24 Saarbergwerke Ag Kombinierte Gas-Dampfkraftanlage zur Erzeugung von Energie

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9425739A1 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997014887A1 (de) * 1995-10-17 1997-04-24 Siemens Aktiengesellschaft Verfahren zur erzeugung von energie und kraftwerksanlage zur durchführung des verfahrens
WO2010057279A1 (en) * 2008-11-24 2010-05-27 Ribeiro Sergio Vieira Guerreir High efficiency waste to energy power plants combining municipal solid waste and natural gas

Also Published As

Publication number Publication date
ES2116136B1 (es) 1998-12-16
ES2116136A1 (es) 1998-07-01
WO1994025739A1 (es) 1994-11-10

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