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US3791137A - Fluidized bed powerplant with helium circuit, indirect heat exchange and compressed air bypass control - Google Patents

Fluidized bed powerplant with helium circuit, indirect heat exchange and compressed air bypass control Download PDF

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US3791137A
US3791137A US00253023A US3791137DA US3791137A US 3791137 A US3791137 A US 3791137A US 00253023 A US00253023 A US 00253023A US 3791137D A US3791137D A US 3791137DA US 3791137 A US3791137 A US 3791137A
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fluidised bed
compressor
turbine
heat exchange
bed combustion
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A Jubb
D Williams
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UK Secretary of State for Defence
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Secr Defence
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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
    • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • F02C1/05—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly characterised by the type or source of heat, e.g. using nuclear or solar energy
    • 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
    • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • F02C1/10—Closed cycles
    • 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
    • F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
    • F02C3/20—Gas-turbine plants characterised by the use of combustion products as the working fluid using a special fuel, oxidant, or dilution fluid to generate the combustion products
    • F02C3/205—Gas-turbine plants characterised by the use of combustion products as the working fluid using a special fuel, oxidant, or dilution fluid to generate the combustion products in a fluidised-bed combustor

Definitions

  • ABSTRACT A power unit consists basically of two gas turbine engines.
  • the working fluid helium
  • the exhaust gas is passed through a conventional heat exchanger before being returned to the compressor.
  • the second engine consisting of a compressor and a turbine
  • air from the compressor is passed through the particulate material of the fluidised bed with fuel which maintains combustion in the fluidised bed.
  • the exhaust gas from the turbine of the second engine is passed through a conventional heat exchanger and then to atmosphere.
  • the two engines each drive an alternator.
  • a power plant comprises fluidised bed combustion means connected 1 to receive a working fluid in heat exchange relationship with the fluidised bed, turbine means connected to receive and be driven by the working fluid heated by the fluidised bed combustion means, compressor means connected to supply compressed air to the fluidised bed combustion means to support the combustion therein, further turbine means which is connected to receive and be driven by the combustion products from the fluidised bed combustion means and which is drivingly connected to the compressor means, and control valve means operative to permit at least a part of the compressed air compressed by the compressor means to bypass the fluidised bed combustion means and flow to the inlet of the further turbine means.
  • throttle valve means connected between the outlet of the compressor means and the fluidised bed combustion means so as to control the quantity of compressed air supplied to the latter.
  • the power plant additionally comprises auxiliary combustion means connected between the throttle valve means and the fluidised bed combustion means so as to heat the compressed air supplied to the latter prior to its entry therein.
  • auxiliary combustion means adapted to heat the combustion products from the fluidised bed combustion means prior to their entry into the further turbine means.
  • the power plant may also comprise further control valve means operative to permit at least a part of the compressed air compressed by the compressor means to by-pass the fluidised bed combustion means and flow to the inlet of the further auxiliary combustion means.
  • the fluidised bed combustion means and the firstmentioned turbine means may be arranged to form a closed cycle for the working fluid thereof.
  • condenser means and pump means connected in series between the outlet of the firstmentioned turbine means and thefluidised bed combustion means so as to form a closed steam cycle.
  • compressor means connected in series between the outlet of the firstmentioned turbine means and the fluidised bed combustion means so as to form a closed cycle gas, e.g. helium. cycle.
  • heat exchange means connected to receive exhaust gases from the further turbine means in heat exchange relationship with the working fluid compressed by the further compressor means prior to its heating by the fluidised bed combustion means: additionally or alternatively there may be provided further heat exchange means connected to receive exhaust gases from the further turbine means in heat exchange relationship with the air compressed by the firstmentioned compressor means.
  • the heat exchange means and the further feat exchange means may be connected in flow series or in parallel.
  • recuperator connected to receive the working fluid expanded in the firstmentioned turbine means in heat exchange relationship with the working fluid compressed by the further compressor means prior to its heating by the fluidised bedcombustion means, the recuperator preferably being 0 connected between the compressor means and the firstmentioned heat exchange means.
  • the gas turbine engine power plant shown in the drawing comprises, in flow series, a low pressure compressor 10, a high pressure compressor 12, a fluidised bed combustion apparatus 14, a compressor-driving turbine 16 drivingly connected to the compressors l0 and 12 by a shaft l8-and a free power turbine 20 which is drivingly connected to an alternator 22, the compressors 10, 12, the combustion apparatus 14 and the turbine 16, 20 being connected to form a closed cycle flow path for the working fluid of the power plant.
  • the working fluid is preferably helium.
  • a precooler 24 is provided in flow series with the inlet of the compressor 10 while an intercooler 26 is provided between, and in flow series with, the compressors 10 and 12, the helium being passed in heat exchangerelationship with cooling water in the coolers 24, 26.
  • a recuperator 28-having two flow paths 30, 32 in heat exchange relationship is arranged so that the path 30 is connected in flow series between the outlet of the compressor 12 and the inlet of the fluidised bed combustion apparatus 14, and the path 32 is connected in flow series between the outlet of the turbine 20 and the inlet of the precooler 24.
  • the fluidised bed combustion apparatus 14 com? prises a chamber 34 containing a particulate material 36 constituted by a particulate fuel such as granular coal or coke (about /8 inch diameter), although noncombustible particular material such as sand, soaked in or supplied with a light fuel such as kerosene or a gaseous fuel such as methane, may be used.
  • the chamber 34 has an inlet 37 through-which air compressed by a compressor 38 to a pressure of about six atmospheres enters the chamber and flows upwards through the particulate fuel 36.
  • the particulate fuel 36 is thus fluidised, and burns continuously.
  • Embedded in the particulate fuel 36 are a number of conduits (indicated diagrammatically at 39') through which the helium flows to be heated.
  • the combustionproducts resulting from the combustion of the particulate fuel 36 pass from the chamber 34 into a turbine 40 which is drivingly connected to the compressor 38 and to a further alternator 42. After being expanded in the turbine 40, the combustion products pass to atmosphere through a first flow path 44 of a heat exchanger 46 having a second flow path 48. connected, for the flow of helium, in series between the flow path 30 of the recuperator 28 and the inletto the conduits 39 of the fluidised bed combustion apparatus 14. The considerable waste heat in the exhaust from the turbine 40 is thus injected into the closed helium cycle.
  • the flow path 48 may be arranged upstream of the flow path 30. Additionally, or alternatively, there may be provided a further heat exchanger (shown dotted at 50) having a first flow path 52 connected to receive the combustion products from the turbine 40 in heat exchange relationship with a second flow path 54 connected between the outlet of the compressor 38 and the inlet 37 of the chamber 34. The flow path 52 may be connected in series or in parallel with the flow path 44.
  • a throttle valve 56 and auxiliary combustion equipment 58 which is adapted to be supplied with liquid or gaseous fuel are connected in flow series between the outlet of the compressor 38 and the inlet 37 of the fluidised bed combustion apparatus 14, the throttle valve 56 being upstream of, and the combustion equipment 58 being downstream of, the flow path 54 if the flow path 54 is present.
  • Further auxiliary combustion equipment 62 and a mixing chamber 64 are connected in flow series between the outlet of the chamber 34 of the fluidised bed combustion apparatus 14 and the inlet of the turbine 40, while a by-pass conduit 66 containing a by-pass control valve 68 is connected between the outlet of the compressor 38 and the mixing chamber 64.
  • a further conduit 69 containing a shut-off valve 70 communicates between the outlet of the compressor 38 and the inlet of the combustion equipment 62.
  • the combustion equipment 58, 62 are preferably such that the gas passing therethrough (i.e. the compressed air or combustion products respectively) is indirectly heated, for example by passing through ducts in the combustion equipment 58, 62 which ducts are heated by the combustion of the fuel in the combustion equipment 58, 62.
  • the particulate fuel 36 in the fluidised bed combustion apparatus 14 is cold.
  • the valve 56 is set fully open, the valves 68 and 70 are closed, and fuel is supplied to and burnt in the combustion equipment 58.
  • Hot fluidising gas is thus supplied to the fluidised bed combustion apparatus 14, which hot gas rapidly heats the particulate fuel 36 to a temperature at which self-sustaining combustion can commence.
  • the supply of fuel to the combustion equipment 58 can be gradually reduced to zero.
  • fuel may additionally be supplied to and burnt in the combustion equipment 62.
  • An alternative method of starting the power plant comprises adjusting the valves 56 and 68 so that only about percent of the air compressed by the compressor 38 is supplied to the fluidised bed combustion apparatus 14. Fuel is supplied to the combustion equipment 58 and 62, and the very hot combustion products leaving the combustion equipment 62 are diluted and cooled in the mixing chamber 64 by air passing through the valve 68 to a temperature suitable for driving the turbine 40.
  • by-pass valve 68 is rapidly opened while the throttle valve 56 is closed, thus rapidly reducing the temperature at the inlet of the turbine 40 and within the particulate fuel 36 of the fluidised bed combustion apparatus 14. Fine control of the overall power output of the power plant is exercised by adjusting the valve 68 alone or by simultaneously adjusting the valves 56 and 68 in opposite senses.
  • the power plant can still be used to produce at least some power by closing the valves 56 and 68, opening the valve and supplying fuel to the combustion equipment 62.
  • the compressor 38, combustion equipment 62 and turbine 40 then act as an independently operable gas turbine engine to drive the alternator 42.
  • the invention is applicable to power plants other than gas turbine engine power plants.
  • the closed helium cycle part of the power plant could be replaced by a closed steam cycle.
  • the compressors 10, 12 and their associated equipment would be replaced by a condenser and a water pump
  • the turbines 16, 20 would be replaced by a steam turbine or turbines
  • the fluidised bed combustion apparatus 14 would act as a boiler for the water supplied to the conduits 39.
  • a gas turbine engine power plant comprising:
  • said fluidised bed combustion means being connected to receive working fluid compressed by said compressor means in heat exchange relationship with said fluidised bed
  • said turbine means being connected to receive and be driven by said working fluid heated by said fluidised bed combustion means, said turbine means also being drivingly connected to said compressor means,
  • said further compressor means being adapted to supply said fluidised bed combustion means with compressed air to support combustion therein,
  • said further turbine means being connected to receive and be driven by the combustion products of the fluidised bed combustion means
  • said further compressor means being connected to be driven by said further turbine means
  • control valve means being operative to permit at least a part of the compressed air compressed by said further compressor means to by-pass said fluidised bed combustion means and flow to said further turbine means,
  • auxiliary combustion means connected to receive and heat compressed air from said further compressor before said fluidised bed combustion means
  • a power plant as claimed in claim 1 having throttle valve means connected between the outlet of the further compressor means and the fluidised bed combustion means.
  • a power plant as claimed in claim 2 having further control valve means operable to permit at least a part of the compressed air compressed by the further compressor means to by-pass the fluidised bed combustion bed combustion means and flow to the inlet of the further auxiliary combustion means.
  • a power plant as claimed in claim 1 having condenser means and pump means connected in series between the outlet of the first mentioned turbine means and the fluidised bed combustion means.
  • a power plant as claimed in claim 1 having heat exchange means connected to receive exhaust gases from the further turbine means in heat exchange relationship with the working fluid compressed by the further compressor means prior to its heating by the fluidised bed combustion means.
  • a power plant as claimed in claim 6 having further heat exchange means connected to receive exhaust gases from the further turbine means in heat exchange relationship with the air compressed by the first mentioned compressor means.
  • a power plant as claimed in claim 7 having a recuperator connected to receive the working fluid compressed by the further compressor means prior to its heating by the fluidised bed combustion means, the recuperator being connected between the compressor means and the first mentioned heat exchange means.
  • a power plant as claimed in claim 7 in which the heat exchange means and the further heat exchange means are connected in flow series.
  • a power plant as claimed in claim 7 in which the heat exchange means and the further heat exchange means are connected in parallel.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • High Energy & Nuclear Physics (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

A power unit consists basically of two gas turbine engines. In the first which is a closed cycle the working fluid (helium) is heated by passing it through a duct embedded in a fluidized bed. The exhaust gas is passed through a conventional heat exchanger before being returned to the compressor. In the second engine, consisting of a compressor and a turbine, air from the compressor is passed through the particulate material of the fluidised bed with fuel which maintains combustion in the fluidised bed. The exhaust gas from the turbine of the second engine is passed through a conventional heat exchanger and then to atmosphere. The two engines each drive an alternator.

Description

United States Patent Jubb et a]. Feb. 12, 1974 [5 FLUIDIZED BED POWERPLANT WITH 3,353,360 11/1967 Gorzegno 60/39.l8 13 HELIUM CIRCUIT, INDIRECT HEAT 2,859,954 11/1958 Grey 60/39.]8 C EXCHANGE AND COMPRESSED AIR 3,069,342 12/1962 Flatt 60/39.]8 R
BYPASS CONTROL FOREIGN PATENTS OR APPLICATIONS A22620 6/1956 Germany; 60/39.l8 B
Inventors: Albert Jubb, Kenilworth; David Eyre Williams, Rugby, both of England The Secretary of State for Defense in Her Britannic Majestys Government of the United Kingdom of Great Britain and Northern Ireland, London, England Filed: May 15, 1972 Appl. No.: 253,023
Assignee:
U.S. Cl. 60/39.]8 R, 60/39.46 R, 122/4 D Int. Cl F02c l/04, F02c 3/00 Field of Search. 60/39.18 A, 39.18 B, 39.18 C,
60/39.18 R, 39.46; 122/4 D; 23/288 S [56] References Cited UNITED STATES PATENTS 3,687,115 8/1972 Bell 122/4 D 3,194,015 7/1965 Pacault 60/39.l8 B
Primary ExaminerCarlton R. Croyle Assistant Examiner-Warren Olsen Attorney, Agent, or F irmCushman, Darby &
Cushman [5 7] ABSTRACT A power unit consists basically of two gas turbine engines. In the first which is a closed cycle the working fluid (helium) is heated by passing it through a duct embedded in a fluidized bed. The exhaust gas is passed through a conventional heat exchanger before being returned to the compressor. In the second engine, consisting of a compressor and a turbine, air from the compressor is passed through the particulate material of the fluidised bed with fuel which maintains combustion in the fluidised bed. The exhaust gas from the turbine of the second engine is passed through a conventional heat exchanger and then to atmosphere. The two engines each drive an alternator.
10 Claims, 1 Drawing Figure HELIUM 32- F LUIDIZED BED POWERPLANT WITH I-IELIUM CIRCUIT, INDIRECT HEAT EXCHANGE AND COMPRESSED AIR BYPASS CONTROL This invention relates to power plants, and is particularly but not exclusively concerned with a closed cycle gas turbine engine power plant.
According to the present invention, a power plant comprises fluidised bed combustion means connected 1 to receive a working fluid in heat exchange relationship with the fluidised bed, turbine means connected to receive and be driven by the working fluid heated by the fluidised bed combustion means, compressor means connected to supply compressed air to the fluidised bed combustion means to support the combustion therein, further turbine means which is connected to receive and be driven by the combustion products from the fluidised bed combustion means and which is drivingly connected to the compressor means, and control valve means operative to permit at least a part of the compressed air compressed by the compressor means to bypass the fluidised bed combustion means and flow to the inlet of the further turbine means.
There may be provided throttle valve means connected between the outlet of the compressor means and the fluidised bed combustion means so as to control the quantity of compressed air supplied to the latter.
In a preferred embodiment of the invention, the power plant additionally comprises auxiliary combustion means connected between the throttle valve means and the fluidised bed combustion means so as to heat the compressed air supplied to the latter prior to its entry therein.
There may also be provided further auxiliary combustion means adapted to heat the combustion products from the fluidised bed combustion means prior to their entry into the further turbine means.
The power plant may also comprise further control valve means operative to permit at least a part of the compressed air compressed by the compressor means to by-pass the fluidised bed combustion means and flow to the inlet of the further auxiliary combustion means.
The fluidised bed combustion means and the firstmentioned turbine means may be arranged to form a closed cycle for the working fluid thereof.
, Thus there may be provided condenser means and pump means connected in series between the outlet of the firstmentioned turbine means and thefluidised bed combustion means so as to form a closed steam cycle.
Alternatively, there may be provided further compressor means connected in series between the outlet of the firstmentioned turbine means and the fluidised bed combustion means so as to form a closed cycle gas, e.g. helium. cycle.
Preferably there is provided heat exchange means connected to receive exhaust gases from the further turbine means in heat exchange relationship with the working fluid compressed by the further compressor means prior to its heating by the fluidised bed combustion means: additionally or alternatively there may be provided further heat exchange means connected to receive exhaust gases from the further turbine means in heat exchange relationship with the air compressed by the firstmentioned compressor means.
The heat exchange means and the further feat exchange means may be connected in flow series or in parallel.
There may also be provided a recuperator connected to receive the working fluid expanded in the firstmentioned turbine means in heat exchange relationship with the working fluid compressed by the further compressor means prior to its heating by the fluidised bedcombustion means, the recuperator preferably being 0 connected between the compressor means and the firstmentioned heat exchange means.
The invention will now be described, merely by way of example, with reference to the accompanying drawing, which is a schematic block diagram of a gas turbine engine power plant in accordance with the invention.
The gas turbine engine power plant shown in the drawing comprises, in flow series, a low pressure compressor 10, a high pressure compressor 12, a fluidised bed combustion apparatus 14, a compressor-driving turbine 16 drivingly connected to the compressors l0 and 12 by a shaft l8-and a free power turbine 20 which is drivingly connected to an alternator 22, the compressors 10, 12, the combustion apparatus 14 and the turbine 16, 20 being connected to form a closed cycle flow path for the working fluid of the power plant. The working fluid is preferably helium.
A precooler 24 is provided in flow series with the inlet of the compressor 10 while an intercooler 26 is provided between, and in flow series with, the compressors 10 and 12, the helium being passed in heat exchangerelationship with cooling water in the coolers 24, 26. A recuperator 28-having two flow paths 30, 32 in heat exchange relationship is arranged so that the path 30 is connected in flow series between the outlet of the compressor 12 and the inlet of the fluidised bed combustion apparatus 14, and the path 32 is connected in flow series between the outlet of the turbine 20 and the inlet of the precooler 24.
The fluidised bed combustion apparatus 14 com? prises a chamber 34 containing a particulate material 36 constituted by a particulate fuelsuch as granular coal or coke (about /8 inch diameter), although noncombustible particular material such as sand, soaked in or supplied with a light fuel such as kerosene or a gaseous fuel such as methane, may be used. The chamber 34 has an inlet 37 through-which air compressed by a compressor 38 to a pressure of about six atmospheres enters the chamber and flows upwards through the particulate fuel 36. The particulate fuel 36 is thus fluidised, and burns continuously. The ashrises to the top, and is removed continuously by means not shown, while additional particulate fuel is continuously supplied by means not shown. Embedded in the particulate fuel 36 are a number of conduits (indicated diagrammatically at 39') through which the helium flows to be heated.
The combustionproducts resulting from the combustion of the particulate fuel 36 pass from the chamber 34 into a turbine 40 which is drivingly connected to the compressor 38 and to a further alternator 42. After being expanded in the turbine 40, the combustion products pass to atmosphere through a first flow path 44 of a heat exchanger 46 having a second flow path 48. connected, for the flow of helium, in series between the flow path 30 of the recuperator 28 and the inletto the conduits 39 of the fluidised bed combustion apparatus 14. The considerable waste heat in the exhaust from the turbine 40 is thus injected into the closed helium cycle.
It will be appreciated that the flow path 48 may be arranged upstream of the flow path 30. Additionally, or alternatively, there may be provided a further heat exchanger (shown dotted at 50) having a first flow path 52 connected to receive the combustion products from the turbine 40 in heat exchange relationship with a second flow path 54 connected between the outlet of the compressor 38 and the inlet 37 of the chamber 34. The flow path 52 may be connected in series or in parallel with the flow path 44.
A throttle valve 56 and auxiliary combustion equipment 58 which is adapted to be supplied with liquid or gaseous fuel are connected in flow series between the outlet of the compressor 38 and the inlet 37 of the fluidised bed combustion apparatus 14, the throttle valve 56 being upstream of, and the combustion equipment 58 being downstream of, the flow path 54 if the flow path 54 is present. Further auxiliary combustion equipment 62 and a mixing chamber 64 are connected in flow series between the outlet of the chamber 34 of the fluidised bed combustion apparatus 14 and the inlet of the turbine 40, while a by-pass conduit 66 containing a by-pass control valve 68 is connected between the outlet of the compressor 38 and the mixing chamber 64. A further conduit 69 containing a shut-off valve 70 communicates between the outlet of the compressor 38 and the inlet of the combustion equipment 62.
The combustion equipment 58, 62 are preferably such that the gas passing therethrough (i.e. the compressed air or combustion products respectively) is indirectly heated, for example by passing through ducts in the combustion equipment 58, 62 which ducts are heated by the combustion of the fuel in the combustion equipment 58, 62.
When the power plant is to be started, the particulate fuel 36 in the fluidised bed combustion apparatus 14 is cold. The valve 56 is set fully open, the valves 68 and 70 are closed, and fuel is supplied to and burnt in the combustion equipment 58. Hot fluidising gas is thus supplied to the fluidised bed combustion apparatus 14, which hot gas rapidly heats the particulate fuel 36 to a temperature at which self-sustaining combustion can commence. At this point the supply of fuel to the combustion equipment 58 can be gradually reduced to zero. Before self-sustaining combustion of the particulate fuel 36 has commenced the temperature of the combustion products leaving the chamber 34 may be too low for satisfactorily driving the turbine 40. In this case. fuel may additionally be supplied to and burnt in the combustion equipment 62.
An alternative method of starting the power plant comprises adjusting the valves 56 and 68 so that only about percent of the air compressed by the compressor 38 is supplied to the fluidised bed combustion apparatus 14. Fuel is supplied to the combustion equipment 58 and 62, and the very hot combustion products leaving the combustion equipment 62 are diluted and cooled in the mixing chamber 64 by air passing through the valve 68 to a temperature suitable for driving the turbine 40.
During the normal running of the power plant, no fuel is supplied to the combustion equipment 56 or 62, the valve 56 is fully open and the valves 68 and 70 are closed. Should there be a sudden decrease in the load,
by-pass valve 68 is rapidly opened while the throttle valve 56 is closed, thus rapidly reducing the temperature at the inlet of the turbine 40 and within the particulate fuel 36 of the fluidised bed combustion apparatus 14. Fine control of the overall power output of the power plant is exercised by adjusting the valve 68 alone or by simultaneously adjusting the valves 56 and 68 in opposite senses.
If it is desired to service or repair the main power producing part of the power plant, i.e. the compressors 10, 12 and their associated equipment, the turbines 16, 20, the alternator 22 and the fluidised bed combustion apparatus 14, the power plant can still be used to produce at least some power by closing the valves 56 and 68, opening the valve and supplying fuel to the combustion equipment 62. The compressor 38, combustion equipment 62 and turbine 40 then act as an independently operable gas turbine engine to drive the alternator 42.
It will be appreciated that the invention is applicable to power plants other than gas turbine engine power plants. For example, the closed helium cycle part of the power plant could be replaced by a closed steam cycle. in this case the compressors 10, 12 and their associated equipment would be replaced by a condenser and a water pump, the turbines 16, 20 would be replaced by a steam turbine or turbines, and the fluidised bed combustion apparatus 14 would act as a boiler for the water supplied to the conduits 39.
We claim:
1. A gas turbine engine power plant comprising:
compressor means,
fluidised bed combustion means,
said fluidised bed combustion means being connected to receive working fluid compressed by said compressor means in heat exchange relationship with said fluidised bed,
turbine means,
said turbine means being connected to receive and be driven by said working fluid heated by said fluidised bed combustion means, said turbine means also being drivingly connected to said compressor means,
said turbine means and said compressor means being connected to form a closed cycle,
further compressor means,
said further compressor means being adapted to supply said fluidised bed combustion means with compressed air to support combustion therein,
further turbine means,
said further turbine means being connected to receive and be driven by the combustion products of the fluidised bed combustion means,
said further compressor means being connected to be driven by said further turbine means,
control valve means,
said control valve means being operative to permit at least a part of the compressed air compressed by said further compressor means to by-pass said fluidised bed combustion means and flow to said further turbine means,
auxiliary combustion means connected to receive and heat compressed air from said further compressor before said fluidised bed combustion means, and
further auxiliary combustion means connected to receive and heat combustion products from said fluidised bed combustion means before said further turbine.
2. A power plant as claimed in claim 1 having throttle valve means connected between the outlet of the further compressor means and the fluidised bed combustion means.
3. A power plant as claimed in claim 2 having further control valve means operable to permit at least a part of the compressed air compressed by the further compressor means to by-pass the fluidised bed combustion bed combustion means and flow to the inlet of the further auxiliary combustion means.
4. A power plant as claimed in claim 1 having condenser means and pump means connected in series between the outlet of the first mentioned turbine means and the fluidised bed combustion means.
5. A power plant as claimed in claim 1 in which the gas in the closed cycle is helium.
6. A power plant as claimed in claim 1 having heat exchange means connected to receive exhaust gases from the further turbine means in heat exchange relationship with the working fluid compressed by the further compressor means prior to its heating by the fluidised bed combustion means.
7. A power plant as claimed in claim 6 having further heat exchange means connected to receive exhaust gases from the further turbine means in heat exchange relationship with the air compressed by the first mentioned compressor means.
8. A power plant as claimed in claim 7 having a recuperator connected to receive the working fluid compressed by the further compressor means prior to its heating by the fluidised bed combustion means, the recuperator being connected between the compressor means and the first mentioned heat exchange means.
9. A power plant as claimed in claim 7 in which the heat exchange means and the further heat exchange means are connected in flow series.
10. A power plant as claimed in claim 7 in which the heat exchange means and the further heat exchange means are connected in parallel.

Claims (10)

1. A gas turbine engine power plant comprising: compressor means, fluidised bed combustion means, said fluidised bed combustion means being connected to receive working fluid compressed by said compressor means in heat exchange relationship with said fluidised bed, turbine means, said turbine means being connected to receive and be driven by said working fluid heated by said fluidised bed combustion means, said turbine means also being drivingly connected to said compressor means, said turbine means and said compressor means being connected to form a closed cycle, further compressor means, said further compressor means being adapted to supply said fluidised bed combustion means with compressed air to support combustion therein, further turbine means, said further turbine means being connected to receive and be driven by the combustion products of the fluidised bed combustion means, said further compressor means being connected to be driven by said further turbine means, control valve means, said control valve means being operative to permit at least a part of the compressed air compressed by said further compressor means to by-pass said fluidised bed combustion means and flow to said further turbine means, auxiliary combustion means connected to receive and heat compressed air from said further compressor before said fluidised bed combustion means, and further auxiliary combustion means connected to receive and heat combustion products from said fluidised bed combustion means before said further turbine.
2. A power plant as claimed in claim 1 having throttle valve means connected between the outlet of the further compressor means and the fluidised bed combustion means.
3. A power plant as claimed in claim 2 having further control valve means operable to permit at least a part of the compressed air compressed by the further compressor means to by-pass the fluidised bed combustion bed combustion means and flow to the inlet of the further auxiliary combustion means.
4. A power plant as claimed in claim 1 having condenser means and pump means connected in series between the outlet of the first mentioned turbine means and the fluidised bed combustion means.
5. A power plant as claimed in claim 1 in which the gas in the closed cycle is helium.
6. A power plant as claimed in claim 1 having heat exchange means connected to receive exhaust gases from the further turbine means in heat exchange relationship with the working fluid compressed by the further compressor means prior to its heating by the fluidised bed combustion means.
7. A power plant as claimed in claim 6 having further heat exchange means connected to receive exhaust gases from the further turbine means in heat exchange relationship with the air compressed by the first mentioned compressor means.
8. A power plant as claimed in claim 7 having a recuperator connected to receive the working fluid compressed by the further compressor means prior to its heating by the fluidised bed combustion means, the recuperator being connected between the compressor means and the first mentioNed heat exchange means.
9. A power plant as claimed in claim 7 in which the heat exchange means and the further heat exchange means are connected in flow series.
10. A power plant as claimed in claim 7 in which the heat exchange means and the further heat exchange means are connected in parallel.
US00253023A 1972-05-15 1972-05-15 Fluidized bed powerplant with helium circuit, indirect heat exchange and compressed air bypass control Expired - Lifetime US3791137A (en)

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US3871172A (en) * 1974-01-03 1975-03-18 Chemical Construction Corp Process with fluidized combustor and fluidized heat exchanger for air
US4116005A (en) * 1977-06-06 1978-09-26 General Electric Company Combined cycle power plant with atmospheric fluidized bed combustor
US4164846A (en) * 1977-11-23 1979-08-21 Curtiss-Wright Corporation Gas turbine power plant utilizing a fluidized-bed combustor
US4178754A (en) * 1976-07-19 1979-12-18 The Hydragon Corporation Throttleable turbine engine
US4204401A (en) * 1976-07-19 1980-05-27 The Hydragon Corporation Turbine engine with exhaust gas recirculation
US4223529A (en) * 1979-08-03 1980-09-23 General Electric Company Combined cycle power plant with pressurized fluidized bed combustor
US4228659A (en) * 1978-05-22 1980-10-21 Purification Sciences Inc. Gas turbine system
DE2920069A1 (en) * 1979-05-18 1980-11-20 Curtiss Wright Corp GAS TURBINE ENGINE AND METHOD FOR THE CONTROL THEREOF
US4253300A (en) * 1979-08-03 1981-03-03 General Electric Company Supplementary fired combined cycle power plants
US4274261A (en) * 1978-09-25 1981-06-23 United Technologies Corporation Closed cycle contrarotating gas turbine power plant utilizing helium as the working medium
US4299087A (en) * 1978-04-11 1981-11-10 Stal-Laval Turbin Ab Gas turbine plant with fluidized bed combustor
US4315400A (en) * 1980-02-08 1982-02-16 Curtiss-Wright Corporation Method of and apparatus for preheating pressurized fluidized bed combustor and clean-up subsystem of a gas turbine power plant
US5544479A (en) * 1994-02-10 1996-08-13 Longmark Power International, Inc. Dual brayton-cycle gas turbine power plant utilizing a circulating pressurized fluidized bed combustor
US5617715A (en) * 1994-11-15 1997-04-08 Massachusetts Institute Of Technology Inverse combined steam-gas turbine cycle for the reduction of emissions of nitrogen oxides from combustion processes using fuels having a high nitrogen content
US5704206A (en) * 1994-05-24 1998-01-06 Mitsubishi Jukogyo Kabushiki Kaisha Coal burner combined power plant having a fuel reformer located within the coal furnace
US5813215A (en) * 1995-02-21 1998-09-29 Weisser; Arthur M. Combined cycle waste heat recovery system
WO2010121255A1 (en) * 2009-04-17 2010-10-21 Echogen Power Systems System and method for managing thermal issues in gas turbine engines
US20110185729A1 (en) * 2009-09-17 2011-08-04 Held Timothy J Thermal energy conversion device
EP2420662A1 (en) * 2010-08-12 2012-02-22 Nuovo Pignone S.p.A. Closed cycle brayton cycle system and method
US8613195B2 (en) 2009-09-17 2013-12-24 Echogen Power Systems, Llc Heat engine and heat to electricity systems and methods with working fluid mass management control
US8616001B2 (en) 2010-11-29 2013-12-31 Echogen Power Systems, Llc Driven starter pump and start sequence
US8616323B1 (en) 2009-03-11 2013-12-31 Echogen Power Systems Hybrid power systems
US8783034B2 (en) 2011-11-07 2014-07-22 Echogen Power Systems, Llc Hot day cycle
US8813497B2 (en) 2009-09-17 2014-08-26 Echogen Power Systems, Llc Automated mass management control
US8857186B2 (en) 2010-11-29 2014-10-14 Echogen Power Systems, L.L.C. Heat engine cycles for high ambient conditions
US8869531B2 (en) 2009-09-17 2014-10-28 Echogen Power Systems, Llc Heat engines with cascade cycles
US9062898B2 (en) 2011-10-03 2015-06-23 Echogen Power Systems, Llc Carbon dioxide refrigeration cycle
US9091278B2 (en) 2012-08-20 2015-07-28 Echogen Power Systems, Llc Supercritical working fluid circuit with a turbo pump and a start pump in series configuration
US9118226B2 (en) 2012-10-12 2015-08-25 Echogen Power Systems, Llc Heat engine system with a supercritical working fluid and processes thereof
US20160053638A1 (en) * 2014-08-22 2016-02-25 Peregrine Turbine Technologies, Llc Power generation system including multiple cores
US9316404B2 (en) 2009-08-04 2016-04-19 Echogen Power Systems, Llc Heat pump with integral solar collector
US9341084B2 (en) 2012-10-12 2016-05-17 Echogen Power Systems, Llc Supercritical carbon dioxide power cycle for waste heat recovery
US9441504B2 (en) 2009-06-22 2016-09-13 Echogen Power Systems, Llc System and method for managing thermal issues in one or more industrial processes
EP3109433A1 (en) * 2015-06-19 2016-12-28 Rolls-Royce Corporation Engine driven by sc02 cycle with independent shafts for combustion cycle elements and propulsion elements
DE102015213863A1 (en) * 2015-07-22 2017-01-26 Technische Universität Dresden Method and plant for heat extraction from fluidized beds with heat pipe heat exchangers in combination with the operation of a gas turbine with efficient waste heat recovery
US9638065B2 (en) 2013-01-28 2017-05-02 Echogen Power Systems, Llc Methods for reducing wear on components of a heat engine system at startup
US9752460B2 (en) 2013-01-28 2017-09-05 Echogen Power Systems, Llc Process for controlling a power turbine throttle valve during a supercritical carbon dioxide rankine cycle
IT201800005073A1 (en) * 2018-05-04 2019-11-04 APPARATUS, PROCESS AND THERMODYNAMIC CYCLE FOR THE PRODUCTION OF POWER WITH HEAT RECOVERY
US10934895B2 (en) 2013-03-04 2021-03-02 Echogen Power Systems, Llc Heat engine systems with high net power supercritical carbon dioxide circuits
US11187112B2 (en) 2018-06-27 2021-11-30 Echogen Power Systems Llc Systems and methods for generating electricity via a pumped thermal energy storage system
US11293309B2 (en) 2014-11-03 2022-04-05 Echogen Power Systems, Llc Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system
US11391209B2 (en) * 2018-11-30 2022-07-19 Rolls-Royce Plc Gas turbine engine
US11435120B2 (en) 2020-05-05 2022-09-06 Echogen Power Systems (Delaware), Inc. Split expansion heat pump cycle
US11629638B2 (en) 2020-12-09 2023-04-18 Supercritical Storage Company, Inc. Three reservoir electric thermal energy storage system

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE22620C (en) * A. DICK in London Process for the preparation of copper-tin and copper-zinc alloys with or without the addition of lead, which contain certain amounts of iron or manganese
US2859954A (en) * 1951-06-08 1958-11-11 Power Jets Res & Dev Ltd Gas turbine plant for providing a continuous supply of hot compressed air
US3069342A (en) * 1957-02-05 1962-12-18 Escher Wyss Ag Heat exchange arrangement for nuclear power plant
US3194015A (en) * 1960-11-16 1965-07-13 Babcock & Wilcox Ltd Combined steam and gas turbine power plant
US3353360A (en) * 1966-02-18 1967-11-21 Foster Wheeler Corp Power plant with steam injection
US3687115A (en) * 1969-12-12 1972-08-29 Foster Wheeler Corp Steam boilers

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE22620C (en) * A. DICK in London Process for the preparation of copper-tin and copper-zinc alloys with or without the addition of lead, which contain certain amounts of iron or manganese
US2859954A (en) * 1951-06-08 1958-11-11 Power Jets Res & Dev Ltd Gas turbine plant for providing a continuous supply of hot compressed air
US3069342A (en) * 1957-02-05 1962-12-18 Escher Wyss Ag Heat exchange arrangement for nuclear power plant
US3194015A (en) * 1960-11-16 1965-07-13 Babcock & Wilcox Ltd Combined steam and gas turbine power plant
US3353360A (en) * 1966-02-18 1967-11-21 Foster Wheeler Corp Power plant with steam injection
US3687115A (en) * 1969-12-12 1972-08-29 Foster Wheeler Corp Steam boilers

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* Cited by examiner, † Cited by third party
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US3871172A (en) * 1974-01-03 1975-03-18 Chemical Construction Corp Process with fluidized combustor and fluidized heat exchanger for air
US4178754A (en) * 1976-07-19 1979-12-18 The Hydragon Corporation Throttleable turbine engine
US4204401A (en) * 1976-07-19 1980-05-27 The Hydragon Corporation Turbine engine with exhaust gas recirculation
US4116005A (en) * 1977-06-06 1978-09-26 General Electric Company Combined cycle power plant with atmospheric fluidized bed combustor
US4164846A (en) * 1977-11-23 1979-08-21 Curtiss-Wright Corporation Gas turbine power plant utilizing a fluidized-bed combustor
US4299087A (en) * 1978-04-11 1981-11-10 Stal-Laval Turbin Ab Gas turbine plant with fluidized bed combustor
US4228659A (en) * 1978-05-22 1980-10-21 Purification Sciences Inc. Gas turbine system
US4274261A (en) * 1978-09-25 1981-06-23 United Technologies Corporation Closed cycle contrarotating gas turbine power plant utilizing helium as the working medium
DE2920069A1 (en) * 1979-05-18 1980-11-20 Curtiss Wright Corp GAS TURBINE ENGINE AND METHOD FOR THE CONTROL THEREOF
FR2456847A1 (en) * 1979-05-18 1980-12-12 Curtiss Wright Corp Gas turbine with fluidised bed combustion - has independent controls on air and turbine by=pass to give quick starting performance
US4223529A (en) * 1979-08-03 1980-09-23 General Electric Company Combined cycle power plant with pressurized fluidized bed combustor
US4253300A (en) * 1979-08-03 1981-03-03 General Electric Company Supplementary fired combined cycle power plants
US4315400A (en) * 1980-02-08 1982-02-16 Curtiss-Wright Corporation Method of and apparatus for preheating pressurized fluidized bed combustor and clean-up subsystem of a gas turbine power plant
US5544479A (en) * 1994-02-10 1996-08-13 Longmark Power International, Inc. Dual brayton-cycle gas turbine power plant utilizing a circulating pressurized fluidized bed combustor
US5704206A (en) * 1994-05-24 1998-01-06 Mitsubishi Jukogyo Kabushiki Kaisha Coal burner combined power plant having a fuel reformer located within the coal furnace
US5617715A (en) * 1994-11-15 1997-04-08 Massachusetts Institute Of Technology Inverse combined steam-gas turbine cycle for the reduction of emissions of nitrogen oxides from combustion processes using fuels having a high nitrogen content
US5813215A (en) * 1995-02-21 1998-09-29 Weisser; Arthur M. Combined cycle waste heat recovery system
US8616323B1 (en) 2009-03-11 2013-12-31 Echogen Power Systems Hybrid power systems
WO2010121255A1 (en) * 2009-04-17 2010-10-21 Echogen Power Systems System and method for managing thermal issues in gas turbine engines
US9014791B2 (en) 2009-04-17 2015-04-21 Echogen Power Systems, Llc System and method for managing thermal issues in gas turbine engines
EP2419621A4 (en) * 2009-04-17 2015-03-04 Echogen Power Systems System and method for managing thermal issues in gas turbine engines
US9441504B2 (en) 2009-06-22 2016-09-13 Echogen Power Systems, Llc System and method for managing thermal issues in one or more industrial processes
US9316404B2 (en) 2009-08-04 2016-04-19 Echogen Power Systems, Llc Heat pump with integral solar collector
US8869531B2 (en) 2009-09-17 2014-10-28 Echogen Power Systems, Llc Heat engines with cascade cycles
US9115605B2 (en) 2009-09-17 2015-08-25 Echogen Power Systems, Llc Thermal energy conversion device
US8813497B2 (en) 2009-09-17 2014-08-26 Echogen Power Systems, Llc Automated mass management control
US20110185729A1 (en) * 2009-09-17 2011-08-04 Held Timothy J Thermal energy conversion device
US9458738B2 (en) 2009-09-17 2016-10-04 Echogen Power Systems, Llc Heat engine and heat to electricity systems and methods with working fluid mass management control
US8966901B2 (en) 2009-09-17 2015-03-03 Dresser-Rand Company Heat engine and heat to electricity systems and methods for working fluid fill system
US9863282B2 (en) 2009-09-17 2018-01-09 Echogen Power System, LLC Automated mass management control
US8613195B2 (en) 2009-09-17 2013-12-24 Echogen Power Systems, Llc Heat engine and heat to electricity systems and methods with working fluid mass management control
US8794002B2 (en) 2009-09-17 2014-08-05 Echogen Power Systems Thermal energy conversion method
EP2420662A1 (en) * 2010-08-12 2012-02-22 Nuovo Pignone S.p.A. Closed cycle brayton cycle system and method
US9410449B2 (en) 2010-11-29 2016-08-09 Echogen Power Systems, Llc Driven starter pump and start sequence
US8616001B2 (en) 2010-11-29 2013-12-31 Echogen Power Systems, Llc Driven starter pump and start sequence
US8857186B2 (en) 2010-11-29 2014-10-14 Echogen Power Systems, L.L.C. Heat engine cycles for high ambient conditions
US9062898B2 (en) 2011-10-03 2015-06-23 Echogen Power Systems, Llc Carbon dioxide refrigeration cycle
US8783034B2 (en) 2011-11-07 2014-07-22 Echogen Power Systems, Llc Hot day cycle
US9091278B2 (en) 2012-08-20 2015-07-28 Echogen Power Systems, Llc Supercritical working fluid circuit with a turbo pump and a start pump in series configuration
US9341084B2 (en) 2012-10-12 2016-05-17 Echogen Power Systems, Llc Supercritical carbon dioxide power cycle for waste heat recovery
US9118226B2 (en) 2012-10-12 2015-08-25 Echogen Power Systems, Llc Heat engine system with a supercritical working fluid and processes thereof
US9638065B2 (en) 2013-01-28 2017-05-02 Echogen Power Systems, Llc Methods for reducing wear on components of a heat engine system at startup
US9752460B2 (en) 2013-01-28 2017-09-05 Echogen Power Systems, Llc Process for controlling a power turbine throttle valve during a supercritical carbon dioxide rankine cycle
US10934895B2 (en) 2013-03-04 2021-03-02 Echogen Power Systems, Llc Heat engine systems with high net power supercritical carbon dioxide circuits
US10101092B2 (en) * 2014-08-22 2018-10-16 Peregrine Turbine Technologies, Llc Power generation system including multiple cores
US20160053638A1 (en) * 2014-08-22 2016-02-25 Peregrine Turbine Technologies, Llc Power generation system including multiple cores
US11293309B2 (en) 2014-11-03 2022-04-05 Echogen Power Systems, Llc Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system
US9982629B2 (en) 2015-06-19 2018-05-29 Rolls-Royce Corporation Engine driven by SC02 cycle with independent shafts for combustion cycle elements and propulsion elements
US10677195B2 (en) 2015-06-19 2020-06-09 Rolls-Royce North American Technologies, Inc. Engine driven by Sc02 cycle with independent shafts for combustion cycle elements and propulsion elements
EP3109433A1 (en) * 2015-06-19 2016-12-28 Rolls-Royce Corporation Engine driven by sc02 cycle with independent shafts for combustion cycle elements and propulsion elements
DE102015213863A1 (en) * 2015-07-22 2017-01-26 Technische Universität Dresden Method and plant for heat extraction from fluidized beds with heat pipe heat exchangers in combination with the operation of a gas turbine with efficient waste heat recovery
IT201800005073A1 (en) * 2018-05-04 2019-11-04 APPARATUS, PROCESS AND THERMODYNAMIC CYCLE FOR THE PRODUCTION OF POWER WITH HEAT RECOVERY
WO2019211775A1 (en) * 2018-05-04 2019-11-07 Spada Srl Apparatus, process and thermodynamic cycle for power generation with heat recovery
US11187112B2 (en) 2018-06-27 2021-11-30 Echogen Power Systems Llc Systems and methods for generating electricity via a pumped thermal energy storage system
US11391209B2 (en) * 2018-11-30 2022-07-19 Rolls-Royce Plc Gas turbine engine
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US11629638B2 (en) 2020-12-09 2023-04-18 Supercritical Storage Company, Inc. Three reservoir electric thermal energy storage system

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