US3867811A - Power modulation of a thermal generator - Google Patents

Power modulation of a thermal generator Download PDF

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US3867811A
US3867811A US30655772A US3867811A US 3867811 A US3867811 A US 3867811A US 30655772 A US30655772 A US 30655772A US 3867811 A US3867811 A US 3867811A
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working fluid
liquefied gas
tank
gas
compression
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Raymond Francois Ma Waeselynck
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Compagnie Francaise de Raffinage SA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/14—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/12—Cooling of plants
    • F02C7/14—Cooling of plants of fluids in the plant, e.g. lubricant or fuel
    • F02C7/141—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid
    • F02C7/143—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid before or between the compressor stages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C9/00—Methods or apparatus for discharging liquefied or solidified gases from vessels not under pressure
    • F17C9/02—Methods or apparatus for discharging liquefied or solidified gases from vessels not under pressure with change of state, e.g. vaporisation
    • F17C9/04—Recovery of thermal energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2201/00—Vessel construction, in particular geometry, arrangement or size
    • F17C2201/01—Shape
    • F17C2201/0104—Shape cylindrical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2201/00—Vessel construction, in particular geometry, arrangement or size
    • F17C2201/01—Shape
    • F17C2201/0128—Shape spherical or elliptical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2221/00—Handled fluid, in particular type of fluid
    • F17C2221/03—Mixtures
    • F17C2221/031—Air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2221/00—Handled fluid, in particular type of fluid
    • F17C2221/03—Mixtures
    • F17C2221/032—Hydrocarbons
    • F17C2221/033—Methane, e.g. natural gas, CNG, LNG, GNL, GNC, PLNG
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel
    • F17C2223/01—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by the phase
    • F17C2223/0107—Single phase
    • F17C2223/0123—Single phase gaseous, e.g. CNG, GNC
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel
    • F17C2223/01—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by the phase
    • F17C2223/0146—Two-phase
    • F17C2223/0153—Liquefied gas, e.g. LPG, GPL
    • F17C2223/0161—Liquefied gas, e.g. LPG, GPL cryogenic, e.g. LNG, GNL, PLNG
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
    • F17C2227/01—Propulsion of the fluid
    • F17C2227/0128—Propulsion of the fluid with pumps or compressors
    • F17C2227/0157—Compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
    • F17C2227/03—Heat exchange with the fluid
    • F17C2227/0302—Heat exchange with the fluid by heating
    • F17C2227/0309—Heat exchange with the fluid by heating using another fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
    • F17C2227/03—Heat exchange with the fluid
    • F17C2227/0367—Localisation of heat exchange
    • F17C2227/0388—Localisation of heat exchange separate
    • F17C2227/0393—Localisation of heat exchange separate using a vaporiser

Definitions

  • ABSTRACT A process for modulating the power of a gas turbine by variation of the inlet temperature of the working fluid in a compressor located upstream of a turbine.
  • the compressor and turbine are each staged and the working fluid is cooled at least before the last compressor stage by gasification of a liquefied gas.
  • a portion of the cooling energy produced by expansion of the liquefied gas can be returned to the liquefied gas in storage to cool the latter.
  • the invention is based upon the known fact that lowering the temperature of the cold source of a thermal machine increases its thermodynamic efficiency and increases the power obtained per unit, weight or volume of the working fluid. For instance, when the working fluid is a non condensible gas, by lowering the temperature of the cold source, the density of the gas going through the cycle increases and consequently increases the power produced per unit volume of the working fluid. 5
  • An object of the invention is to provide a process in which the above is utilized in order to increase power production from a given thermal machine and/or to allow utilization of a smaller thermal machine to obtain a given power.
  • the invention seeks to increase the gross power of thermal machines of a given size, as well as to improve their utilization and particularly to increase their efficiency.
  • the invention contemplates a process in which the output power of thermal machines can be modulated by refrigeration.
  • the application of this process permits a more complete and more continuous use of the power of a thermal power generator, as well as a modulation of the power output of a thermal machine without changing, at least within wide limits, the speed of the machine, nor the maximum temperature in the operating cycle.
  • the refrigeration machines may therefore be located in any place. particularly in a place where, due to production. utilization or storage of a product, the cooling effect is transferred to this product.
  • This product may undergo, total or partial, transformation, and be stored near the thermal machine.
  • Liquefied gases are specific substances for storage of refrigeration effect and more particularly liquefied natural gases, liquefied petroleum gases and liquefied gases from the air. Liquefaction of these gases is effected to facilitate their storage and transportation, theymust be re-gasified before use. This re-gasification produces a large quantity of cooling energy hereafter called frigories which may be used in numerous applications, and particularly in power production. Methane is an example of a gas which is liquefied, transported by ship, stored in depots, then re-gasified under pressure and distributed through pipe lines over great distances.
  • An object of the present invention is the specific implementation, giving a maximum efficiency to the utilization of the frigories contained in liquefied gas and permitting continuously or discontinuously to obtain high power and high efficiency in power generation by means of a gas turbine.
  • the thermal machine described above effects compression, then expansion of the working fluid.
  • the Applicant has established that it is advantageous to perform the fluid compression in several stages and to cool the working fluid between stages. Additionally, it is also advantageous to perform the expansion of the working fluid in several stages.
  • a further object of the invention is to provide a process for the modulation of gas turbine power production by variation of the inlet temperature of the working fluid in a compression device located ahead of the gas turbine inlet, said process being characterized in that the working fluid compression and subsequent expansion are performed in several stages, each compression stage following a cooling of the working fluid by means of the cold effect produced during the gasifying of a liquefied gas in a container connected on the one hand to the liquefied gas storage tank and on the other hand to a compressor.
  • the air is first cooled by a coolant consisting of water and anti-freeze.
  • the air later goes through a separator of water droplets; the remaining water in the air will be frozen in the main cooler as very small particles which will be carried along by the air and will not lie in the main cooler as a film.
  • the first compressor preferably operates at a rather low compression ratio to serve the part of a supercharging device fulfilling two functions:
  • FIG. 1 diagrammatically illustrates a circuit for effecting the process according to the invention by means of a utilization device for the cold effect which is producted;
  • FIG. 2 shows another similar circuit according to the invention
  • FIG. 3 shows a device for utilization of the cooling effect by cooling the liquefied gas and this device can be added to the utilization devices shown in FIGS. 1 and 2;
  • FIG. 4 diagrammatically shows another arrangement according to the invention for utilization of the cooling effect by cooling the liquefied gas stock
  • FIG. 5 shows a supplementary refrigeration generation devicr whose cooling effect is used to cool at least a portion of the liquefied gas stock and this device may be added to the utilization devices represented in FIGS. 1 and 2.
  • Air is introduced through line 1 into a scrubber 2 into which a coolant consisting of water with added antifreeze is sprayed by nozzle device 3.
  • the air is thus cooled to a temperature between 2C. and +2C., at which temperature the greatest part of the water present in the air is condensed.
  • the coolant is introduced into the scrubber 2 through a line 4 at a temperature between -5C. and l 0C., this temperature being obtained by passing the coolant, collected by line 5, through an exchanger 6 supplied with a refrigerating fluid through circuit or loop 7 connected to the outlet and of a gasification device of a liquefied gas.
  • a cyclone 8 separates any remaining traces of water droplets from the air.
  • the air from scrubber 2 is introduced, at a temperature between 2C. and +2C, through line 9 into a compressor C1.
  • the compressed air is introduced through a line 10 into a cold water cooler 11 in which water circulates through a line 12.
  • the air is introduced through line 13 into a scrubber 2' which operates similar to the scrubber 2 except that it is fed with air under pressure at a temperature in the neighborhood of 30C.
  • Reference characters 3', 5' and 8in the scrubber 2' designate structure corresponding to 3, 5 and 8 in the scrubber 2.
  • the air is substantially dried.
  • the dried air is discharged from scrubber 2' at a temperature between 2C and +2C and is introduced through lines 14 into a main cooler 15.
  • Liquefied gas enters the main cooler through a line 16 and exits via a line 17 and serves as the refrigeration fluid in cooler 15.
  • the cold energy in the liquefied gas is thus utilized to cool the air fed to compressor C and this increases the efficiency of the compressor and lowers the load on the turbines hence increasing the available output.
  • the air is fed from cooler at very low temperature to compressor C where it is compressed and then is passed to a heat recovery device 18 by opening valve l9 and closing valve 20.
  • the air is heated in recovery device 18 and then passes to a combustion chamber 21 through valve 22 which is opened.
  • a fuel is introduced into the chamber 21 through line 23.
  • the resulting combustion gas from chamber 21 is passed to a turbine T, through line 24.
  • a part of the heat content in the gas is recovered by passing the exhaust gas from T into the heat recovery device 18 (valve 25 being opened and valve 26 being closed).
  • the gas, after having given up heat in device 18 is admitted into turbine T through line 27 (valve 28 being opened) and exhaust is effected through line 30 at atmospheric pressure.
  • the liquefied gas 31, stored in tank 32, is pumped to the main cooler 15 through line 16.
  • the gas discharged from line 17 is supplied either to other gasifiers or to utilization devices or the gas pipelines.
  • FIG. 2 represents another embodiment of the process according to the invention employing a device for the utilization of the refrigeration effect
  • this embodiment as in FIG. I does not include a cooling of the liquefied gas stock.
  • air is introduced through line 1 into scrubber 2 similar to the scrubber described in FIG. 1, and reference characters 2-8 in FIG. 2 designate the same parts as in FIG. 1.
  • the air in line 50 at a temperature which is between 2C and +2C, is introduced into first main cooler 51.
  • the liquefied gas refrigeration fluid is fed from tank 32 through line 16 to cooler 51.
  • the cooled air from cooler 51 is introduced into compressor C1.
  • the compressed air in line 54 passes into second main cooler 55, the refrigerating fluid of which is liquefied gas coming from tank 32 through line 16.
  • the air in discharge line 58 from cooler 55 is fed to compressor C2 where it is further compressed to a maximum value.
  • Turbines T and T are fed, as in FIG. 1, from the air compressed to a maximum coming from compressor C2.
  • the gas coming from the main coolers 51 and 55 is fed through line 17 to other gasifiers or to consumption devices.
  • the implementation of the process of the invention is accompanied by an important cooling of the air admitted into compressor C2 or into compressors C1 and C2, and this enables a high expansion ratio with a high efficiency and consequently allows installation of the heat recovery device 18 between turbines T, and T Nevertheless, the two embodiments which have just been described, need not include heat recovery device 18 in which case the compressed air from compressor C2 is then directly introduced into the combustion chamber 21 (valve 20 being opened, and valves 19 and 22 being closed). Furthermore, the exhaust gas from turbine T is directly admitted into turbine T (valves 26 being opened).
  • recuperating device not between T and T but after T nevertheless, the increase in compression ratio and efficiency which the invention allows to obtain, affords the possibility of placing the heat recovery device after T,, in which case it is less heavy and less bulky than if it were placed after T without loss and even with a slight gain in efficiency.
  • the magnitude of flow of the liquefied gas into the main coolers of FIGS. 1 and 2 depends upon the gas demand, and therefore it is not linked to the operating parameters of the process of the invention. Nevertheless, this may be the case when the liquefied gas is methane and generally, a natural gas whose peaks of consumption correspond to the consumption peaks of the power produced by the thermal machine. Besides, it is usual in gasifyin g centers to maintain the flow of liquefied gas more or less constant independently of the gas consumption by using gas storage means such as natural underground reservoirs, gasholders, very long pipelines under high pressure, etc. The power produced is then that of a basic power plant.
  • FIGS. 3, 4 and 5 Another embodiment of the process according to the present invention, contemplates cooling the liquefied gas stock or a part thereof. Three configurations thereof have been represented in FIGS. 3, 4 and 5.
  • FIG. 3 shows a configuration which can be used instead of tank 32 of FIGS. 1 and 2 and is additive to the utilization arrangements represented in FIGS. 1 and 2.
  • the cooled liquid can be mixed in variable proportions with non-cooled liquid before being introduced into the air coolers.
  • the supplementary refrigeration'effect pro prised by the cooling of the liquefied gas stock is stored in the container used for liquefied gas storage.
  • a flow of liquefied gas coming from the outlet 60 of tank 61 (valve 62 being opened) is expanded in the evaporator 63.
  • the very cold liquefied gas collected in line 64 is introduced into the lower part of tank 61 through line 65 (valve 66 being opened and valve 67 being closed).
  • the cooled liquefied gas introduced through a lower opening 68 is prevented from mixing with non-cooled liquefied gas by the presence of partition means, e.g., cylindrical vertical partition 69 in tank 61.
  • the flow of liquefied gas to be gasified is withdrawn from tank 61 through the outlet 70.
  • Valve 71 is opened and liquefied gas flows through line 72 to a condenser 73 (valve 77 being opened) which condenses the gas compressed in C3 (valves 74 and 75 being opened). After condensing, this gas is introduced into the flow of liquefied gas in line 72 (valve 76 being opened). From the outlet of condenser 73 the liquefied gas is passed through line 16 to the main cooler (FIG. 1) or to the main coolers 51 and 55 (FIG. 2).
  • Compressor C3 does not operate, valves 62, 74, 75, 66, 71, 76 and 77 are closed, valve 67 is opened, so that the flow of liquefied gas to be gasified totally comes from the opening 68 of tank 61 and is therefore very cold. Condenser 73 is by-passed during peak hours by line 78.
  • valve 67 may be partially opened, conversely, during peak hours, valve 71 is generally opened, and additionally, compressor C3 may be operated.
  • FIG. 4 represents a configuration for utilizing refrigeration effect including means for generating supplementary refrigeration effect from the cooling of at least a part of the liquefied gas stock, the cooled liquid first of all, passing through a special cooler before being mixed with the remainder of the liquid introduced into the air coolers.
  • the cooling effect produced by the cooling of the liquefied gas stock is stored in the liquefied gas storage container.
  • This configuration may be used instead of the system constituted by the tank 32 and the main coolers 51 and 55 represented in FIG. 2.
  • Valves 62, 74, 75, 76, 77 and 67 are opened, compressor C3 is in operation, the cooled liquefied gas coming from evaporator 63 is re-introduced into the tank 61 through the lower opening 68. Valves 79 and 80 are closed.
  • the main coolers 55 and 51 are supplied with liquefied gas through line 16.
  • the gas coming out of the main coolers S1 and 55 is supplied through line 17 to other gasifiers or to consumption means.
  • Compressor C3 is not in operation, valves 62, 74, 75, 76, 77 and 67 are closed. Valves 79 and 80 are opened. The cooled liquefied gas is introduced into a special cooler 82 through line 83, and it is discharged through line 84 after heat exchange with the air coming from the main cooler 51. The main coolers 55 and 51 are supplied with liquefied gas through line 16, the condenser 73 is by-passed by line 78.
  • valves 79 and 80 may be partially opened.
  • FIG. 5 represents a configuration for the generation of supplementary cooling effect from the cooling of at least a portion of the liquefied gas stock
  • this configuration may be added to the configuration of the utilization of refrigeration effect represented in' FIGS. 1 and 2.
  • the supplementary refrigerating effect produced by cooling of the liquefied gas stock is stored separately from that used for liquefied gas storage.
  • the cooled liquid may be either mixed in variable proportions with the non-cooled liquid before being introduced into the air coolers, or first introducted into the air cooler.
  • Valves 85, 86, 87, 88 and 89 are opened, compressor C3 is operated.
  • the liquefied gas coming from tank 32 and passing through valve is expanded in the evaporator 90, a large refrigeration effect is generated during this expansion which is stored in the evaporator 90 and is not used.
  • the compressed gas coming from C3 is condensed in the condenser 73, through which passes the flow of liquefied gas coming from tank 32 through lines 91 and 92.
  • the liquefied gas is then fed through line 16 to the main cooler (reference character 15 in FIG. 1) or to the main coolers (reference characters 51 and 55 in FIG. 2).
  • Valves 85, 86, 87, 88 and 89 are closed, compressor C3 is stopped.
  • Distinction must be made as to whether the configuration includes special cooler 82 or not.
  • the configuration includes special cooler 82, it can replace the system in FIG. 4 including the special cooler 82, the tank 61 and the evaporator 63.
  • the line with valve 93 is omitted, valves 94 and 95 are opened.
  • the special cooler 82 is supplied with cooled liquefied gas through line 96 to cool the air coming from the main cooler 51. The resulting very low temperature air is then introduced into compressor C1.
  • the liquefied gas is then introduced into the main cooler 55 through line 16 via lines 97, 92 and 78 (condenser 73 is by-passed by line 78).
  • valve 93 When the configuration is not provided with a special cooler 82, it can replace the system including the tank 61 and the evaporator 63 represented in FIG. 3.
  • the line including valve 93 exists. Lines 96 and 97 as well as valves 94 and 95 are omitted. Valve 93 is opened, the cooled liquefied gas directly joins the liquefied gas coming from tank 32 through line 91.
  • Examples I and II relate to the implementations of the process respectively represented in FIGS. 1 and 2.
  • Example III relates .to the configuration represented in FIG. 3 for the implementation of the process in FIG. 1.
  • the numerical data used in the example are as follows:
  • This example relates to FIG. I.
  • Second body (C2) compression ratio 35/2.5 14
  • recuperator l8 RECUPERATOR Gas temperature before recuperation and before second expansion in T 681K Air temperature after compression: 398K Gas temperature drop in the exchanger:
  • EXAMPLE III The air temperature at the inlet of the first compressor body, which in the case of Example I in the absence of the recuperator 18, was equal to 275K, is lowered by 40C and is equal to 233K during operation in peak hours. Let us assume for the time being that the opening of the gas turbine circuit is not modified, nor is the revolution speed of the two compression devices.
  • the density of the inlet air is increased according to the ratio of the absolute temperatures 275/233.
  • the compression ratio of the first body rises from 2.5 to l lP so that:
  • the peak power is thus increased by 21 percent.
  • Efficiency is itself improved in the ratio 85.9/84 and goes from 0.408 to 0.408 X 85.9/84 0.416.
  • a process for modulating the power of a gas turbine by variation of the inlet temperature of the working fluid in a compressor located upstream of the gas turbine comprising forming the compression and turbine steps each in a plurality of stages, cooling the working fluid before at least the last compression stage by heat exchange with liquified gas stored in a tank, producing a further refrigeration of the liquified gas stored in said tank by supplying at least a part of the liquefied gas during off-peak hours from said tank to an evaporator wherefrom are obtained a gas fraction at the top and a cooled liquefied gas fraction at the bottom, compressing the gas fraction produced in said evaporator, then condensing the thus compressed gas fraction by effecting heat exchange thereof with a flow of liquefied gas coming from said tank and going to cool the working fluid and introducing the now condensed gas fraction into said flow of liquefied gas coming from said tank and going to cool the working fluid, storing the cooled liquefied gas fraction collected in said evapor
  • a process as claimed in claim 4 wherein the working fluid coming out of the first compressor stage is passed through a first cooler, then through a container where it is freed from traces of water vapor by spraying, at a temperature lower than 0C, with a mixture of water and anti-freeze and subsequently separating the condensed water from the working fluid and finally passing the working fluid through a second, main cooler from which it is discharged at a temperature of about l00C before being admitted into the second compressor stage.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Eletrric Generators (AREA)
  • Separation By Low-Temperature Treatments (AREA)
US30655772 1971-11-22 1972-11-14 Power modulation of a thermal generator Expired - Lifetime US3867811A (en)

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FR7141723A FR2164434B1 (xx) 1971-11-22 1971-11-22

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JP (1) JPS4860217A (xx)
FR (1) FR2164434B1 (xx)

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3978663A (en) * 1974-01-11 1976-09-07 Sulzer Brothers Limited Process and apparatus for evaporating and heating liquified natural gas
US4000617A (en) * 1975-01-27 1977-01-04 General Atomic Company Closed cycle gas turbine system
US4036028A (en) * 1974-11-22 1977-07-19 Sulzer Brothers Limited Process and apparatus for evaporating and heating liquified natural gas
US4231226A (en) * 1975-05-28 1980-11-04 Maschinenfabrik Augsburg-Nurnberg Aktiengesellschaft Method and apparatus for vaporizing liquid natural gases
US5419285A (en) * 1994-04-25 1995-05-30 Henry Vogt Machine Co. Boiler economizer and control system
US5622043A (en) * 1993-04-20 1997-04-22 Humphries, Jr.; James J. Gas and steam electrical power generating system
GB2316133A (en) * 1996-08-02 1998-02-18 Gen Electric Gas turbine engine with liquid nitrogen chilling of inlet air, NOx control and power augmentaion.
ES2114773A1 (es) * 1993-07-22 1998-06-01 Otrmat Ind Ltd Metodo y aparato para aumentar la potencia de una turbina de gas.
DE19705215C1 (de) * 1997-02-12 1998-08-06 Frank Dr Ing Triesch Gasturbinenanlage
US6079197A (en) * 1998-01-02 2000-06-27 Siemens Westinghouse Power Corporation High temperature compression and reheat gas turbine cycle and related method
US6119445A (en) * 1993-07-22 2000-09-19 Ormat Industries Ltd. Method of and apparatus for augmenting power produced from gas turbines
WO2002097252A1 (en) * 2001-05-30 2002-12-05 Conoco Inc. Lng regasification process and system
WO2003058047A1 (de) * 2002-01-07 2003-07-17 Alstom Technology Ltd Verfahren zum betrieb einer gasturbogruppe
US20030182944A1 (en) * 2002-04-02 2003-10-02 Hoffman John S. Highly supercharged gas-turbine generating system
US20040194499A1 (en) * 2003-04-01 2004-10-07 Grenfell Conrad Q. Method and apparatus for pressurizing a gas
US20050198957A1 (en) * 2004-03-15 2005-09-15 Kim Bryan H.J. Turbocompound forced induction system for small engines
US20060174627A1 (en) * 2005-02-04 2006-08-10 Siemens Westinghouse Power Corp. Gas turbine cycle
US20070044485A1 (en) * 2005-08-26 2007-03-01 George Mahl Liquid Natural Gas Vaporization Using Warm and Low Temperature Ambient Air
DE102004050182B4 (de) * 2004-10-14 2009-10-22 Triesch, Frank, Dr. Ing. Verfahren zur Luftkonditionierung
US20130074511A1 (en) * 2009-09-07 2013-03-28 Irina Tanaeva Method of operating a gas turbine and gas turbine
EP1828570A4 (en) * 2004-12-20 2015-03-04 Fluor Tech Corp DESIGNS AND METHODS FOR POWER PLANTS POWERED BY LNG
US20160215695A1 (en) * 2012-12-28 2016-07-28 Abengoa Solar New Technologies, S.A. Hybrid plant with a combined solar-gas cycle and operating method

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BE857421A (fr) * 1977-08-03 1978-02-03 Acec Installation de production d'energie electrique comprenant des machines thermiques associees a la revaporisation d'un gaz liquefie
JPS5627034A (en) * 1979-08-14 1981-03-16 Takasago Thermal Eng Co Lts Reducing method for driving force of compressor
US7703272B2 (en) * 2006-09-11 2010-04-27 Gas Turbine Efficiency Sweden Ab System and method for augmenting turbine power output

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US2718753A (en) * 1951-01-02 1955-09-27 Phillips Petroleum Co Improved operation of internal combustion engine operating on liquid petroleum gas fuel
US2988884A (en) * 1958-09-23 1961-06-20 Pouit Robert Improvements in gas turbine power plants
US3154928A (en) * 1962-04-24 1964-11-03 Conch Int Methane Ltd Gasification of a liquid gas with simultaneous production of mechanical energy
US3631673A (en) * 1969-08-08 1972-01-04 Electricite De France Power generating plant
US3720057A (en) * 1971-04-15 1973-03-13 Black Sivalls & Bryson Inc Method of continuously vaporizing and superheating liquefied cryogenic fluid
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Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3978663A (en) * 1974-01-11 1976-09-07 Sulzer Brothers Limited Process and apparatus for evaporating and heating liquified natural gas
US4036028A (en) * 1974-11-22 1977-07-19 Sulzer Brothers Limited Process and apparatus for evaporating and heating liquified natural gas
US4000617A (en) * 1975-01-27 1977-01-04 General Atomic Company Closed cycle gas turbine system
US4231226A (en) * 1975-05-28 1980-11-04 Maschinenfabrik Augsburg-Nurnberg Aktiengesellschaft Method and apparatus for vaporizing liquid natural gases
US5622043A (en) * 1993-04-20 1997-04-22 Humphries, Jr.; James J. Gas and steam electrical power generating system
US6119445A (en) * 1993-07-22 2000-09-19 Ormat Industries Ltd. Method of and apparatus for augmenting power produced from gas turbines
ES2114773A1 (es) * 1993-07-22 1998-06-01 Otrmat Ind Ltd Metodo y aparato para aumentar la potencia de una turbina de gas.
US5419285A (en) * 1994-04-25 1995-05-30 Henry Vogt Machine Co. Boiler economizer and control system
GB2316133A (en) * 1996-08-02 1998-02-18 Gen Electric Gas turbine engine with liquid nitrogen chilling of inlet air, NOx control and power augmentaion.
GB2316133B (en) * 1996-08-02 2000-10-11 Gen Electric Combined gas turbine inlet chiller,NOx control device and power augmentation s ystem and methods of operation
DE19705215C1 (de) * 1997-02-12 1998-08-06 Frank Dr Ing Triesch Gasturbinenanlage
US6079197A (en) * 1998-01-02 2000-06-27 Siemens Westinghouse Power Corporation High temperature compression and reheat gas turbine cycle and related method
WO2002097252A1 (en) * 2001-05-30 2002-12-05 Conoco Inc. Lng regasification process and system
US7104071B2 (en) 2002-01-07 2006-09-12 Alstom Technology Ltd Method for operating a gas turbine group
US20050109033A1 (en) * 2002-01-07 2005-05-26 Jost Braun Method for operating a gas turbine group
WO2003058047A1 (de) * 2002-01-07 2003-07-17 Alstom Technology Ltd Verfahren zum betrieb einer gasturbogruppe
US20030182944A1 (en) * 2002-04-02 2003-10-02 Hoffman John S. Highly supercharged gas-turbine generating system
WO2003100233A1 (en) * 2002-05-22 2003-12-04 Enhanced Turbine Output Holding Llc Highly supercharged gas turbine and power generating system
US20040194499A1 (en) * 2003-04-01 2004-10-07 Grenfell Conrad Q. Method and apparatus for pressurizing a gas
US7065974B2 (en) 2003-04-01 2006-06-27 Grenfell Conrad Q Method and apparatus for pressurizing a gas
US20050198957A1 (en) * 2004-03-15 2005-09-15 Kim Bryan H.J. Turbocompound forced induction system for small engines
DE102004050182B4 (de) * 2004-10-14 2009-10-22 Triesch, Frank, Dr. Ing. Verfahren zur Luftkonditionierung
EP1828570A4 (en) * 2004-12-20 2015-03-04 Fluor Tech Corp DESIGNS AND METHODS FOR POWER PLANTS POWERED BY LNG
US20060174627A1 (en) * 2005-02-04 2006-08-10 Siemens Westinghouse Power Corp. Gas turbine cycle
US7398642B2 (en) * 2005-02-04 2008-07-15 Siemens Power Generation, Inc. Gas turbine system including vaporization of liquefied natural gas
US20070044485A1 (en) * 2005-08-26 2007-03-01 George Mahl Liquid Natural Gas Vaporization Using Warm and Low Temperature Ambient Air
US20130074511A1 (en) * 2009-09-07 2013-03-28 Irina Tanaeva Method of operating a gas turbine and gas turbine
US20160215695A1 (en) * 2012-12-28 2016-07-28 Abengoa Solar New Technologies, S.A. Hybrid plant with a combined solar-gas cycle and operating method

Also Published As

Publication number Publication date
FR2164434B1 (xx) 1974-01-04
JPS4860217A (xx) 1973-08-23
FR2164434A1 (xx) 1973-08-03

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