GB2076062A - Turbine power plant - Google Patents
Turbine power plant Download PDFInfo
- Publication number
- GB2076062A GB2076062A GB8114917A GB8114917A GB2076062A GB 2076062 A GB2076062 A GB 2076062A GB 8114917 A GB8114917 A GB 8114917A GB 8114917 A GB8114917 A GB 8114917A GB 2076062 A GB2076062 A GB 2076062A
- Authority
- GB
- United Kingdom
- Prior art keywords
- power plant
- fluidised bed
- combustor
- turbine
- turbine power
- 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.)
- Granted
Links
Classifications
-
- 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
-
- 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
- F01K23/061—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 combustion in a fluidised bed
-
- 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
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)
Abstract
In the plant the exhaust air from a power turbine 2 supplies a fluidised bed combustor 1 and a waste heat boiler 7 in parallel. The proportion of exhaust air supplied to the fluidised bed combustor is controlled by means of a valve B in the primary airflow path of the combustor. The throughput of the power turbine can therefore exceed the primary air throughput of the combustor allowing an extended reduction of power whilst maintaining the temperature of the bed within its operational range. The input air of the power turbine 2 is heated by being passed through a secondary air flow path 17 of the combustor, the path 17 being isolated from, but in thermal contact with, the combustor bed. The waste heat boiler 7 drives a steam turbine 8 coupled by differential gearing to the power turbine 2 to produce a common output drive. <IMAGE>
Description
SPECIFICATION
Turbine power plant
The present invention relates to a turbine power plant employing a fluidised bed combustor for external heating of a gas turbine cycle using the gas turbine exhaust air. This concept is in itself well known. However, a fluidised bed combustor has a limited operational temperature range which in turn, severely limits the minimum power output to about 70% maximum. An object of the present invention is therefore to provide a more flexible and economic power plant.
According to the present invention in a turbine power plant exhaust air from a gas turbine is applied to the primary air flow path of a fluidised bed combustorforfluidisation and combustion, working air for the turbine is supplied by a secondary path which secondary path is isolated from the primary air flow path but arranged to derive heat from the fluidised bed to preheat the working air, and a parallel path from the turbine exhaust feeds auxiliary heating means, the throughput of the turbine being thereby permitted to exceed the primary air throughput of the fluidised bed combustor.
The steam turbine may have an output shaft coupled to the output shaft of the gas turbine to provide a common drive.
The relative proportions of exhaust air supplied to the fluidised bed combustor and the auxiliary heating means may be controlled by a valve included in the primary path through-the fluidised bed combustor. In addition, a valve may be included in the air flow path through the auxiliary heating means.
A controlled shunt path is preferably provided around the auxiliary heating means.
The auxiliary heating means is preferably a water boiler which is arranged to feed a steam turbine.
The feed path to the steam turbine may lie partly in the exhaust outlet of the fluidised bed combustor to extract heat therefrom. In particular it may include parallel portions in the boiler and the combustor exhaust outlet and a series portion in the boiler.
A control valve may be connected in parallel with the secondary air path through the combustor.
A clean fuel combustor may be connected in series with the secondary air path either before or after the fluidised bed combustor.
In addition to the fluidised bed combustor of the turbine power plant, there may be provided fluidised bed heating means which incorporate heat exchanger means in direct thermal contact with the fluidised bed, the secondary path extending through the heat exchanger means, and the power plant may further comprise separator means arranged to receive exhaust gas and elutriated particles from the fluidised bed combustor and to pass the particles into the fluidised bed heating means to contribute to or constitute the fluidised bed thereof. In particular
the heat exchanger means may include heating
tubes in and above the fluidised bed, the upper
heating tubes being arranged to engage particles
separated by the separator means as they fall
towards the fluidised bed.
At least one of the fluidised bed combustor and
the fluidised bed heating means may have a fluid
heating casing. The casing or casings may be
connected in parallel with the secondary path, and
also may be connected in parallel with the upper
heating tubes. Additionally the casing or casings
may be connected to provide heat to the auxiliary
heating means.
An embodiment of a turbine power plant in
accordance with the invention, and a modification
thereof, will now be described, by way of example,
with reference to the accompanying drawings, of
which:
Figure 1 shows a schematic drawing of a
turbine power plant incorporating a fluidised bed
combustor and,
Figure 2 shows diagrammatically, a
modification of the combustor portion of Figure 1.
Referring to Figure 1, a gas turbine 11 has its
air exhaust outlet 32 connected to the primary air
flow path 13 of an atmospheric fluidised bed
combustor 1 to fluidise the bed by way of a
distributor 3 of the combustor. The latter
eventually vents to atmosphere by way of a
stack 15.
The combustor 1 has an isolated secondary air
flow path in thermal contact with the bed. This
secondary air flow path comprises heat exchanger
piping 1 7 within the combustor 1 , the output path
33 of an air compressor 5 and the input path 57 of
a compressor turbine 4, the turbine air thereby
being preheated by the combustor 1.
In addition the secondary air path may include a
combustion chamber CC1 or CC2 before and/or
after the combustor 1, as shown in Figure 1. These
combustion chambers are supplied with clean fuel
to raise the gas turbine firing temperature to the
highest levels permitted by cooled blading. The
working fluid of the turbine although referred to as
'air' in this specification in accordance with
common practice, does in fact contain a small
proportion of oxidised fuel gases.
The plant so far described is known and suffers
from the disadvantages already referred to. In this
embodiment the invention is concerned with
overcoming these disadvantages by combining
the above gas turbine cycle with a steam turbine
cycle. Accordingly, the exhaust air of the gas
turbine is partially diverted to fire a steam turbine
cycle.
The working fluid path of the turbine 4/2,
passing through air exhaust outlet 32, is split at
junction A, one branch, in which a valve B is
included, leading to the primary air flow path 1 3 of
the combustor 1 and the other branch 34 to a 5 waste heat boiler 7. A third combustion chamber
CC3 may be included in the primary air flow path
13 to heat the primary air entering the
combustor 1.
After passing through the boiler 7 and a throttle valve C, the exhaust air is vented to atmosphere or employed in process heating.
The heat exchanger pipes of the boiler 7 comprise two portions 19 and 21 in series, these supplying steam to a steam turbine 8 by way of a turbine stop valve 23. The steam turbine output shaft 25 and the gas turbine output shaft 27 may be coupled together by differential gearing to produce a common output drive on shaft 29.
Alternatively, the two turbine outputs may be employed separately.
A further heat exchanger 9 is mounted in the combustor 1 and connected in parallel with the portion 21 of the boiler heat exchangerthus providing additional heat to the steam path.
The valve C in the boiler 7 provides and controls the pressure drop across the boiler.
Operation of either or both valves B and C will therefore control the proportions of exhaust air supplied to the combustor 1 and the boiler 7.
The-relatively higher pressure drop that inherently exists across the combustor 1, compared with the boiler 7, means that a wide range of variation of air split can be achieved by simple regulation of the valves B and/or C.
Increased air velocities past the heat exchangers 9, 19 and 21 can be used to improve heat transfer.
In addition a shunt path 31, controlled by a valve D, bypasses the boiler 7 and provides an additional control on the air split at junction A.
A further valve E is incorporated between the compressor 5 and the compressor turbine 4 to short circuit the secondary air flow path to a controlled extent.
The disadvantage, mentioned above, of the limited operating temperature range of a conventional fluidised bed combustor, is overcome in the present arrangement, which permits a greatly extended reduction of power by reducing the air flow to the bed (opening valves C and/or D, or closing valve B) whilst maintaining the temperature of the bed within its operational range.
Alternatively, using the valve 'E the turbine inlet temperature can be varied while maintaining constant fluidised bed flow by closing valve 'C', thus providing a simple bed operating method. A wide range of steam outputs can be achieved by different choices of flow split at design point with appropriate choice of boilers and steam turbine, ranging from 2 to 3 times the gas turbine power.
The air flow through the combustor is normally limited to 20 to 50% excess air (i.e. 1.2 to 1.5 times that required to combust the fuel) which can include the lowest quality coals, refinery "bottoms", wood chippings and municipal waste.
Limiting the air flow through the combustor in this way correspondingly limits its size and cost and thus the size of the contained air heater and boiler tubes and the air clean up system to meet emission regulations.
The minimisation of this air flow, which has to be exhausted to atmosphere at 1 700C or more to avoid dewpoint corrosion problems from sulphur oxides etc., thus aids the combined cycle efficiency. In general the bulk of steam raised in this combined cycle can be raised in the clean air waste heat recovery boiler 7, which can exhaust at temperature 500C or less, since there are no corrosion or emission considerations. This again aids the cycle efficiency compared to currently known cycles. This clean gas boiler is moreover very compact and economic with extended surface tubing, due to the available high velocities of clean gas.
As suggested above, the cycle is capable of substantial improvement in efficiency by adding the combustor CC1 or CC2 fired by clean fuel to raise the gas turbine firing temperature. This "topping" fuel would ideally be 'volatiles' driven from coal or refinery bottoms, in a thermal reactor, leaving the ashy, corrosive residues or chars to be passed to the fluidised bed combustor. The topping fuel could be any 'clean' fuel.
The combustor arrangement shown within the broken line of Figure 1 may be replaced by the arrangement shown in Figure 2, where the combustion process and the heating of the air being circulated from the compressor to the compressor turbine are now largely separated. The combustion process is performed in a fluidised bed combustor 35 which is of the 'fast type', in which the bed is violently agitated and massive elutration of the bed material,takes place:This fluidised bed combustor 35 has no heating tubes such as those in the combustor 1 of Figure 1. It does however have a distributor 3 as before, supplied with exhaust air from the power turbine 2. At the upper end of the combustor 35 is a large vent 59 which allows the particles of the bed which are carried up with the exhaust gases to be carried over into a cyclone separator 40.This separator is mounted over an air tube heating bed 37 which collects the particles separated out. It is in this bed that the main heating process of the turbine input air takes place. The heating bed incorporates upper heating tubes 38 through which the particles fall, and lower heating tubes 39 which become immersed in a bed of the fallen particles. The two sets of heating tubes are connected in series with each other between the compressor (5) output and the turbine (4) input.
The heating bed has an air intake distributor in similar manner to a fluidised bed combustor the air so supplied causing fluidisation, completing any combustion that is required, and extracting most of the heat from the particles. This air may be obtained in parallel with the primary air for the fluidised bed combustor, from the turbine exhaust.
This air is boosted by a boost fan 60, or alternatively a throttle (not shown) can be employed for control of this exhaust air, or the fan 60 can introduce fresh atmospheric air which is heated by the combustion chamber CC3.
An exit duct 45 for surplus bed particles, connects the heating bed 37 and the fluidised bed combustor 35, the air pressure through the heating bed carrying the surplus particles back through duct 45.
Mounted above the cyclone separator 40 is a heat exchanger having tubes 9 connected to the waste heat boiler as in Figure 1.
Supplementary heating of the turbine input air is provided by fluid heating jackets 46 and 47 surrounding the fluidised bed combustor and the heating bed 37. These jackets are connected in parallel between the output of the air compressor 5 and the junction between the upper and lower heating tubes of the heating bed 37. The air for these fluid heating casings 46 and 47 comes from the compressor 5 along pipe 33 to junction H. At this junction part of the air goes to the casings, the rest to the air tubes 38 and 39. From junction H the air travels along pipe 54 and is further split at junction G. Here part of the air travels along pipe 51, through casing 46, along pipe 49 to junction
F. The rest of the air travels along pipe 52, through casing 47, and along pipe 50 to the junction F.
The air then travels along pipe 56 to join the air in the air tube heater 38. Alternatively water cooled casing for water heating and/or steam raising can be employed as fluid heating casings.
Whereas in the embodiment of Figure 1, the secondary path, constituted by the heating tubes
17, is in direct thermal contact with the fluidised bed, in the modification of Figure 2, the secondary path, constituted by the heating pipes 38 and 39 are in indirect thermal contact with the fluidised bed combustor, being heated only by hot particles carried over from the fluidised bed combustor.
Claims (19)
1: A turbine power plant wherein exhaust air from a gas turbine is applied to the primary air flow path of a fluidised bed combustor for fluidisation and combustion, working air for the turbine is supplied by a second path which secondary path is isolated from said primary aiP flow path but arranged to derive heat from the fluidised bed to pre-heat the working air, and wherein a parallel path from the turbine exhaust feeds auxiliary heating means, the throughput of the turbine being thereby permitted to exceed the primary air throughput of the fluidised bed combustor.
2. A turbine power plant according to Claim 1, 'wherein said steam turbine has an output shaft coupled to the output shaft of the gas turbine to provide a common drive.
3. A turbine power plant according to any preceding claim, including valve means arranged to control the relative proportions of exhaust air supplied to the fluidised bed combustor and the auxiliary heating means.
4. A turbine power plant according to Claim 3, wherein said valve means comprises a valve in the primary path through the fluidised bed combustor.
5. A turbine power plant according to Claim 3 or Claim 4, wherein said valve means further comprises a valve included in the exhaust air flow
path through said auxiliary heating means.
6. A turbine power plant according to any of
Claims 3, 4 and 5, wherein a controlled shunt path is provided around said auxiliary heating means.
7. A turbine power plant according to any preceding claim, wherein said auxiliary heating means is a water boiler which is arranged to feed a steam turbine.
8. A turbine power plant according to Claim 7, wherein the feed path to said steam turbine lies partly in the exhaust outlet of the fluidised bed combustor to extract heat therefrom.
9. A turbine power plant according to Claim 8, wherein the feed path to the steam turbine includes parallel portions in the boiler and the combustor exhaust outlet and a series portion in the boiler.
10. A turbine power plant according to any preceding claim, including a control valve connected in parallel with the secondary air path through the combustor.
11. A turbine power plant according to
Claim 10, including a clean fuel combustor connected in series with said secondary air path.
12. A turbine power plant according to any of
Claims 1 to 11, and comprising in addition to said fluidised bed combustor, fluidised bed heating means incorporating heat exchanger means in direct thermal contact with the fluidised bed, said secondary path extending through said heat exchanger means, and said power plant further comprising separator means arranged to receive exhaust gas and elutriated particles from the fluidised bed combustor and to pass said particles into said fluidised bed heating means to contribute to or constitute the fluidised bed thereof.
13. A turbine power plant according to
Claim 12, wherein said heat exchanger means includes heating tubes in and above the fluidised bed, the upper heating tubes being arranged to engage particles separated by said separator means as they fall towards the fluidised bed.
14. A turbine power plant according to
Claim 12 or Claim 13, wherein at least one of the fluidised bed combustor and the fluidised bed heating means has a fluid heating casing.
1 5. A turbine power plant according to
Claim 14, wherein said fluid heating casing or casings are connected in parallel with said secondary path.
16. A turbine power plant according to
Claim 14 as appendent to Claim 13 wherein said fluid heating casing or casings are connected in parallel with said upper heating tubes.
17. A turbine power plant according to
Claim 14 as appended to Claim 13, wherein said fluid heating casing or casings are connected to provide heat to said auxiliary heating means.
1 8. A turbine power plant substantially as
hereinbefore described, with reference to Figure 1 of the accompanying drawings.
19. A turbine power plant substantially as
hereinbefore described with reference to Figure 2
of the accompanying drawings.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB8114917A GB2076062B (en) | 1980-05-16 | 1981-05-15 | Turbine power plant |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB8016335 | 1980-05-16 | ||
| GB8114917A GB2076062B (en) | 1980-05-16 | 1981-05-15 | Turbine power plant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB2076062A true GB2076062A (en) | 1981-11-25 |
| GB2076062B GB2076062B (en) | 1984-04-26 |
Family
ID=26275545
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB8114917A Expired GB2076062B (en) | 1980-05-16 | 1981-05-15 | Turbine power plant |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2076062B (en) |
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0061262A1 (en) * | 1981-03-23 | 1982-09-29 | Cpc International Inc. | Power generating system |
| FR2528493A1 (en) * | 1982-06-10 | 1983-12-16 | Westinghouse Electric Corp | COMBUSTION CHAMBER ASSEMBLY WITH A PRESSURIZED FLUIDIFIED BED WITH HEATER FOR A POWER PLANT |
| DE3225140A1 (en) * | 1982-07-06 | 1984-01-12 | Brown, Boveri & Cie Ag, 6800 Mannheim | METHOD FOR THE OPERATION OF A STEAM POWER PLANT EQUIPPED WITH A FLUIDIZED LIFE BURNER, IN PARTICULAR HEATING POWER PLANT |
| US4462206A (en) * | 1981-06-10 | 1984-07-31 | Sulzer Brothers Limited | Gas turbine-steam power plant |
| GB2133839A (en) * | 1982-09-27 | 1984-08-01 | English Electric Co Ltd | Power plant comprising a pressurised fluidised bed combustor |
| FR2540975A1 (en) * | 1983-02-14 | 1984-08-17 | Inst Francais Du Petrole | Method of recovering energy from a high-temperature fluid using heat exchange with a compressed gas |
| US4519207A (en) * | 1981-12-29 | 1985-05-28 | Hitachi, Ltd. | Combined plant having steam turbine and gas turbine connected by single shaft |
| GB2148734A (en) * | 1983-10-10 | 1985-06-05 | English Electric Co Ltd | Divided fluidised bed |
| EP0199902A1 (en) * | 1985-04-29 | 1986-11-05 | GebràDer Sulzer Aktiengesellschaft | Combined hot air and steam plant |
| US4660375A (en) * | 1982-09-27 | 1987-04-28 | The English Electric Company Limited | Power-generation plant and method |
| US4845942A (en) * | 1986-04-19 | 1989-07-11 | Brown, Boveri & Cie | Combined gas turbine and steam power plant having a fluidized bed furnace for generating electrical energy |
| EP0329155A1 (en) * | 1988-02-18 | 1989-08-23 | A. Ahlstrom Corporation | Integrated gas turbine power generation system and process |
| US5713195A (en) * | 1994-09-19 | 1998-02-03 | Ormat Industries Ltd. | Multi-fuel, combined cycle power plant method and apparatus |
| US6014856A (en) * | 1994-09-19 | 2000-01-18 | Ormat Industries Ltd. | Multi-fuel, combined cycle power plant |
| NL1011133C2 (en) * | 1999-01-26 | 2000-07-27 | Stork Energy Services B V | Wall for boiler, particularly in rubbish burning installation, involves first wall of flat plate and second wall at distance from it, with inner space formed between them |
| WO2008039095A1 (en) * | 2006-09-29 | 2008-04-03 | Lev Nikolaevich Smirnov | Method for converting heat energy into mechanical energy by heat regeneration and closed gas turbine for carrying out said method |
| EP2295736A3 (en) * | 2009-08-26 | 2011-04-27 | Schutter Rotterdam B.V. | An apparatus for converting waste heat from a production process into electrical energy |
| US8424280B2 (en) | 2008-03-20 | 2013-04-23 | Rolls-Royce, Plc | Gas turbine engine arrangement |
-
1981
- 1981-05-15 GB GB8114917A patent/GB2076062B/en not_active Expired
Cited By (23)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0061262A1 (en) * | 1981-03-23 | 1982-09-29 | Cpc International Inc. | Power generating system |
| US4462206A (en) * | 1981-06-10 | 1984-07-31 | Sulzer Brothers Limited | Gas turbine-steam power plant |
| US4519207A (en) * | 1981-12-29 | 1985-05-28 | Hitachi, Ltd. | Combined plant having steam turbine and gas turbine connected by single shaft |
| FR2528493A1 (en) * | 1982-06-10 | 1983-12-16 | Westinghouse Electric Corp | COMBUSTION CHAMBER ASSEMBLY WITH A PRESSURIZED FLUIDIFIED BED WITH HEATER FOR A POWER PLANT |
| US4476674A (en) * | 1982-06-10 | 1984-10-16 | Westinghouse Electric Corp. | Power generating plant employing a reheat pressurized fluidized bed combustor system |
| DE3225140A1 (en) * | 1982-07-06 | 1984-01-12 | Brown, Boveri & Cie Ag, 6800 Mannheim | METHOD FOR THE OPERATION OF A STEAM POWER PLANT EQUIPPED WITH A FLUIDIZED LIFE BURNER, IN PARTICULAR HEATING POWER PLANT |
| EP0098481A2 (en) * | 1982-07-06 | 1984-01-18 | BROWN, BOVERI & CIE Aktiengesellschaft | Method for generating electric power in a combined power plant with fluidised bed combustion |
| EP0098481A3 (en) * | 1982-07-06 | 1985-10-09 | Brown, Boveri & Cie Aktiengesellschaft | Method of operating a power plant with a fluidised bed combustion, particularly a heating power plant |
| GB2133839A (en) * | 1982-09-27 | 1984-08-01 | English Electric Co Ltd | Power plant comprising a pressurised fluidised bed combustor |
| US4660375A (en) * | 1982-09-27 | 1987-04-28 | The English Electric Company Limited | Power-generation plant and method |
| FR2540975A1 (en) * | 1983-02-14 | 1984-08-17 | Inst Francais Du Petrole | Method of recovering energy from a high-temperature fluid using heat exchange with a compressed gas |
| GB2148734A (en) * | 1983-10-10 | 1985-06-05 | English Electric Co Ltd | Divided fluidised bed |
| EP0199902A1 (en) * | 1985-04-29 | 1986-11-05 | GebràDer Sulzer Aktiengesellschaft | Combined hot air and steam plant |
| US4901521A (en) * | 1986-04-19 | 1990-02-20 | Brown Boveri & Cie | Combined gas turbine and steam power plant having a fluidized bed furnace for generating electrical energy |
| US4845942A (en) * | 1986-04-19 | 1989-07-11 | Brown, Boveri & Cie | Combined gas turbine and steam power plant having a fluidized bed furnace for generating electrical energy |
| EP0329155A1 (en) * | 1988-02-18 | 1989-08-23 | A. Ahlstrom Corporation | Integrated gas turbine power generation system and process |
| US5713195A (en) * | 1994-09-19 | 1998-02-03 | Ormat Industries Ltd. | Multi-fuel, combined cycle power plant method and apparatus |
| US6014856A (en) * | 1994-09-19 | 2000-01-18 | Ormat Industries Ltd. | Multi-fuel, combined cycle power plant |
| NL1011133C2 (en) * | 1999-01-26 | 2000-07-27 | Stork Energy Services B V | Wall for boiler, particularly in rubbish burning installation, involves first wall of flat plate and second wall at distance from it, with inner space formed between them |
| WO2008039095A1 (en) * | 2006-09-29 | 2008-04-03 | Lev Nikolaevich Smirnov | Method for converting heat energy into mechanical energy by heat regeneration and closed gas turbine for carrying out said method |
| US8424280B2 (en) | 2008-03-20 | 2013-04-23 | Rolls-Royce, Plc | Gas turbine engine arrangement |
| EP2295736A3 (en) * | 2009-08-26 | 2011-04-27 | Schutter Rotterdam B.V. | An apparatus for converting waste heat from a production process into electrical energy |
| BE1018868A3 (en) * | 2009-08-26 | 2011-10-04 | Schutter Rotterdam B V | DEVICE FOR CONVERSION OF WASTE HEAT FROM A PRODUCTION PROCESS TO ELECTRIC ENERGY. |
Also Published As
| Publication number | Publication date |
|---|---|
| GB2076062B (en) | 1984-04-26 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| 732 | Registration of transactions, instruments or events in the register (sect. 32/1977) | ||
| PE20 | Patent expired after termination of 20 years |
Effective date: 20010514 |