AU639437B2 - System and method for reheat steam temperature control in circulating fluidized bed boilers - Google Patents
System and method for reheat steam temperature control in circulating fluidized bed boilers Download PDFInfo
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- AU639437B2 AU639437B2 AU49419/90A AU4941990A AU639437B2 AU 639437 B2 AU639437 B2 AU 639437B2 AU 49419/90 A AU49419/90 A AU 49419/90A AU 4941990 A AU4941990 A AU 4941990A AU 639437 B2 AU639437 B2 AU 639437B2
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- reheater
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D5/00—Devices using endothermic chemical reactions, e.g. using frigorific mixtures
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- 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
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
- F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
- Fluidized-Bed Combustion And Resonant Combustion (AREA)
- Control Of Steam Boilers And Waste-Gas Boilers (AREA)
- Control Of Turbines (AREA)
Description
OPI DATE 24/08/90 AOJP DATE 27/09/90 APPLN- ID 49419 PCe PCT NUMBER PCT/FI90/00026 INTERNATIONAL APFLILA llUN PUBLIsHI-U UNDER 1 H PATENT COOPERATION TREATY (PCT) (51) International Patent Classification 5 International Publication Number: WO 90/08917 F22D 5/00, F22B 31/00 Al (43) International Publication Date: 9 August 1990 (09.08.90) (21) International Application Number: PCT/F190/00026 (81) Designated States: AT (European patent), AU, BE (European patent), CA, CH (European patent), DE (Euro- (22) International Filing Date: 23 January 1990 (23.01.90) pean patent), DK (European patent), ES (European patent). FI, FR (European patent), GB (European patent), IT (European patent), JP, KR, LU (European patent), Priority data: NL (European patent), SE (European patent), SU.
301,621 24 January 1989 (24.01.89) US Published (71)Applicant: A. AHLSTROM CORPORATION [FI/Fl]; With international search report.
SF-29600 Noormarkku (FI).
(72) Inventors: GOUNDER, Ponnusami, K. 10669 Glendover Lane, San Diego, CA 92126 KAURANEN, Timo, M. 6068 Zenako Court, San Diego, CA 92122 (US).
RASKIN, Neil, R. 7322 Muslo Lane, Carlsbad, CA 92009 6 3 (74) Agent: BLOMQUISTM, Tuula: A. Ahlstrom Corporation, P.O. Box 18, SF-48601 Karhula (FI).
(54)Title: SYSTEM AND METHOD FOR REHEAT STEAM TEMPERATURE CONTROL IN CIRCULATING FLUID- IZED BED BOILERS (57) Abstract A steam generator having a fluidized bed combustion system that includes a fluidized bed combustor and at least one hot separator, includes a superheater and a reheater. A first stage of reheater and a second stage or final stage of reheater are sequentially disposed in a common gas flue. Cold steam from a turbine is divided into selective first and second portions, the first portion being directed through the first stage of reheater and thereafter recombined with the second portion of cold steam. The recombined first and second portions of steam are directed through the second stage of reheater.
WO 90/08917 PCr/F190/00026 1 SYSTEM AND METHOD FOR REHEAT STEAM TEMPERATURE CONTROL IN CIRCULATING FLUIDIZED BED BOILERS BACKGROUND OF THE INVENTION The present invention relates to a power plant including a two-stage steam turbine and a steam generator plant having a fluidized bed combustion system that includes a fluidized bed combustor, at least one separator, and a gas flue comprising a reheater and superheater.
The present invention relates also to a method of controlling reheater temperatures in a steam generator having a fluidized bed combustion system that includes a fluidized bed combustor, at least one hot separator, and a reheater in a gas flue.
Several methods are presently known for controlling reheat steam temperatures.
One method of reheater temperature control is the use of a system for gas bypass over the reheater. Two separate flue gas passes are provided in the convection pass of the boiler (one for superheater and one for reheater), with means such as dampers downstream of each to vary the amount of flue gas flow over each section. The outlet steam temperature of the reheater can be controlled by varying the amount of flue gas flow between the convection pass sections. The main disadvantage of this system is that the dampers are located in a higher temperature (260-371C) dust laden flue gas path making them susceptible to erosion and mechanical failure. Also, the steam temperature control range is limited with this type of system.
Another method of reheater outlet steam temperature control is by the use of external heat exchangers. With this approach, a portion of the recirculated solids within the circulating fluidized bed system is diverted to an SUr.3TITUTE SKEET externally mounted fluidized bed heat exchanger, i.e.
external heater exchanger (EHE), in which a section of or complete. reheater is located. By varying the amount of solids flow to the EHE, the quantity of heat transfer to the reheater and the reheater outlet steam temperature is controlled. The main disadvantages of this system are that the solids flow control valve is a high maintenance item and the reheat tube surface within the EHE is subject to erosion. This effects the availability of the unit.
It has also been suggested in US 4,748,940 to arrange first reheater heating surfaces in a flue gas passage of a circulating fluidized bed combustor and to connect to this first reheater a second reheater disposed in an external heat exchanger (EHE). An adjustable by-pass line is connected in parallell to the reheater heating surfaces. The outlet temperature of the reheater is controlled by controlling the solids flow in the external heat exchanger and by controlling the steam flow in the two reheaters by means of the by-pass line.
SUBST1'TUT ;*EEt 2 a A further different arrangement of first and final stages of reheaters has been suggested in EP-A- 0 274 637. EP-A- 0 274 637 shows a power plant including a two-stage turbine and a steam generator plant having a fluidized bed combustor, particle separators, first and second or final stages of reheaters and a superheater.
The first and final stages of reheaters are according to EP-A- 0 274 637 sequentially disposed. Two stages of reheaters are disposed in separate external heat exchangers for cooling discharged ash. The final stage of reheater is disposed in a gas flue connected to the gas outlet of the fluidized bed combustor. The quantity of heat transferred to the first stages of reheaters and the reheater outlet temperature is controlled by varying the amount of solids flow to the external heat exchangers. This arrangement is not favored due to solids flow control valve maintenance problems as already mentioned earlier.
A further approach to the control of the reheater outlet steam temperature is by the use of spray desuperheater.
This approach utilizes spraying water for desuperheating and thereby controlling reheater outlet steam temperature.
This is a simple approach, but not generally accepted because it degrades the cycle efficiency.
Still another approach is by the use of excess air. Excess air supplied to the boiler can be used for reheat steam temperature control. This approach, however, is not favored because of its negative affect on boiler efficiency.
A still further approach is by the use of gas recirculation.
By this approach, large quantities of flue gases are recirculated to achieve the rated reheater outlet steam temperature. This approach, however, requires the use of a gas recirculation fan for handling a hot dust laden gas SUBSTITUTE
SHEE+
^T and requires additional power consumption, which makes this approach disadvantageous.
Accordingly, the present invention is directed to an improved method and system for reheat steam temperature control.
In accordance with a primary aspect of the present invention there is provided a power plant comprising a twostage steam turbine and a steam generator plant having a fluidized bed combustion system that includes a fluidised bed combustor, at least one separator, at least a first and a second or final stage of a reheater for reheating steam from a first stage of the two-stage steam turbine sequentially disposed in which the first stage of the reheater and the second or final stage of the reheater are sequentially disposed in a common gas flue, and there is dividing means for dividing cold steam from the first stage of the two-stage stem turbine into selective first and second portions and directing said first portion through the first stage of the reheater, and recombining means for recombining the first and second portions and directing same through said second or final stage of the reheater.
Preferably the steam generator includes means for controlling the temperature of the second or final stage of the re7eater and comprises means for by-passing a selected portion of cold steam around said first stage reheater directly to said second or final stage reheater.
According to the present invention there is provided a method of controlling reheater temperatures in a steam generator having a fluidized bed combustion system that includes a fluidized bed combustor, at least one hot separator, and a reheater for reheating cold steam comprising dividing the reheater into a first and second or final stage reheater and sequentially disposing the first and second or final stages of the reheater in a common gas flue, dividing the cold steam returning to the reheater into selective first and second portions and directing the first portion through the first stage of the reheater and recombining the first portion and the second portion to form a recombined portion and directing the recombined portion through the second or final stage of reheater.
WO 90/08917 PCT/F190/00026 4 di2vdig WId 271= reuiingy L the reheater U selective first and second portions and ing the first portion through the first reheater and recombining the fir ion and the second portion and directin ame through the second or final stage of BRIEF DESCRIPTION OF THE DRAWING The above and other objects and advantages of the present invention will become apparent from the following description when read in conjuntion with the accompanying drawings wherein: Fig. 1 is a schematic diagram illustrating a typical circulating fluidized bed boiler system embodying the present invention; Fig. 2 is a schematic diagram illustrating another embodiment of the present invention; and Fig. 3 is a schematic diagram illustrating an arrangement of two typical boilers connected to a single turbine.
DETAILED DESCRIPTION OF A PREFERRED EMBODIMENT Referring to Fig. 1, a power plant embodying a typical circulating fluidized bed boiler with superheater and reheater is illustrated with the system incorporating a preferred embodiment of the present invention. The boiler system, designated generally by the numeral 10, comprises a fluid bed combustor 12 having a combustion chamber 14 into which combustible material, non-combustible material, possibly additives or recirculated material, primary air and secondary air are fed. In the combustion chamber, the bed is maintained in fluidized state by having the correct inventory of bed material and flow of air. The combustion ry, chamber is provided with a bottom 16 having a grid-like STeTUTE SE-I ET WO 90/08917 PCT/F19000026 construction through which fluidizing air is introduced.
The combustion chamber walls are preferably constructed with membrane type tube walls, with or without a refractory covering.
First and second stages of superheaters 18 and 20 are located within the combustion chamber. The combustioh chamber materials are carried from the combustion chamber by way of flues 22 to a hot separator 24 wherein the solids are separated from the flue gases for return by way of particle recycling system 26, 28 and 30 to the bottom of the combustion chamber for recirculation. These may be passed through fluidized bed coolers or the like prior to return to the combustion chamber.
The details of circulation circuit for the feed water and the primary superheaters are not illustrated as they do not form an essential part of the present invention.
Flue gases from the hot separator pass along by way of flue 32 to a convection pass 34. A single stage superheater 38 is placed or located in the convection pass with reheaters 40 and 42 located downstream of the superheater 38 and upstream of an economizer surface 44. The reheater is illustrated as two stages with 42 being a first stage and being a second or final stage. The reheater may have more than two stages, with the final stage just down stream from superheater 38 such as 40 is located. These are arranged as counter flow heat exchangers with the gas flow direction down and the reheat steam flow direction up. The placement of the superheater 38 within this pass helps keep the temperature of the gas flow to reheater 40 below the critical temperature. This arrangement together with the bypass feature as will be explained enables a unique and effective control of the temperatures within the reheater sections.
S U C7T7Z7 Si-: E T WO 90/08917 PCT/F190/00026 6 When the steam temperature leaving the particular section (in a counter flow heat exchanger arrangement) is close to the gas temperature entering that section, reducing the steam flow to that section will result in a considerable reduction in heat absorption. As the steam temperature approaches the gas temperature, the effective thermal heat available for heat transfer is reduced. This provides the basis for the principle used for the reheat temperature control system in accordance with the present invention.
The generating system as illustrated in Fig. 1 is supplying steam to a two-stage turbine. In the illustrated arrangement, steam from superheater 38 flows via an outlet header 46 and supply line 48 by way of valve 50 to the inlet side of the high pressure turbine (HPT) 52. Cold steam leaving the turbine 52 returns by way of return line 53 to the reheaters 42 and 40. At the reheater, a bypass line 54 joins the return line 53 at 55 and bypasses a portion of the cold steam with the remaining portion of the steam going by way of differential control valve 56 to the inlet header 58 of the first stage reheater 42.
The steam passing through the reheater 42 exists by way of a header 60 and rejoins or combines with the bypass portion of the cold steam at 62. A flow control valve 64 is provided in the bypass line 54 for control of the flow between the inlet manifold of the first stage reheater 42 and the bypass line. The recombined steam at 62 flows into inlet header 66 of the second or final stage reheater 40 where it is further heated and flows by way of outlet headey 68, supply line 70 and valve 72 to the second stage or lower stage of the turbine 74. The selective proportioning of the cold steam between the bypass line 54 and the second stage of the reheater 42 provides an effective and efficient means of controlling the temperature in the reheater stages.
The location of the first stage reheater 42 along the flue gas path is so chosen that bypassing the required portion SU3%IZuIT SfHEET WO 90/08917 PC/F190/00026 7 of the cold reheat steam directly to the second stage reheater 40 cannot increase the steam temperature leaving the first stage reheater to more than the allowed metal temperature for the reheater tube material. A limit will be set to protect the first stage reheater materials from exceeding their allowable metal temperature. The value of 566°C is a typical limit and may vary depending upon the actual design conditions. The purpose of the system is such that the maximum tube outside surface temperature will not exceed the allowable metal temperature limit for the material selected.
The arrangement of the control valves 56 and 64 is so chosen that controlability is achieved throughout the steam temperature control range and permits all reheater surfaces to be placed in the convection pass of the boiler, eliminating the need for in furnace reheater surfaces.
This also makes feasible a simplified start-up scheme when more than one boiler for example is connected to a common turbine system. In this arrangement, the set of valves provide a means .Eor reheat steam flow balancing under various operating conditions.
In the circulating fluidized bed boiler, the combustion takes place in a fluidized bed of inert material. The fluidized bed material leaving the combustor is returned by means of a hot collector (such ae a hot cyclone) through suitable sealing device. In operation, air and fuel are delivered to the combustion chamber 14 wherein the bed material is maintained in a fluidized state by having the correct flow of air and bed material. The fluidizing air is introduced through a grid-like grating or construction at 16 in the bottom of the chamber. The flue gas and combustion products, along with the carry over solids, first convey heat to the superheaters 18 and 20 and are conveyed by way of flue 22 into the hot separator 24 wherein the solids are separated and returned to the combustion chamber through the recycling arrangement 26, 28 and SL.. :7:U7Z S EZ T WO %/1t08917 IPCTF190/00076 8 The hot flue gases are then conveyed from the hot separator(s) by way of flue 32 to the convection pass section 34 wherein the final stage superheater 38 and the reheater stages 40 and 42 are located.
Three superheater stages are disposed in the described system, these being 18 and 20 and 38, with 38 being in the flue gas convection pass. Desuperheaters may be positioned between the superheater stages for steam temperature control if necessary. The two stages 40 and 42 of the reheater are positioned in the convection pass 34 and in conjunction with the control valves and interconnecting piping so that precise control of the reheater outlet steam temperature is possible. The piping system is such that cold steam reentering this system at pipe 53 is selectively divided into two streams at the juncture 55 thereof with the bypass line 54. One stream passes to the first stage reheater and is distributed through inlet header 58. The other steam goes to the second stage reheater by way of valve 64 and inlet header 66. The selective division of the stream will be in proportion to the temperature control necessary, which is accomplished by the valves 56 and 64.
The hot steam leaving the first stage reheater from the outlet header 60 is mixed with the cold steam via the bypass line 54 after or down stream of the flow control valve 64 and the blended stream enters the second stage reheater by way of the inlet header 66. The flow through the first stage reheater is controlled by proper manipulation of the two control valves 56 and 64, which in turn control the steam temperature leaving the second stage reheater 40. Hot steam from the second or final stage reheater is directed back to the turbine by way of the hot reheat steam line A differential pressure responsive control unit 80 controls the setting of valve 56 for controlling the pressure differential available for the control valve 64. The control SUW25T1 UTESHE WO 90/08917 PCr/F190/00026 9 unit 80 is responsive to the pressure differential between the cold steam return line 53 and the outlet pressure at juncture 62 of the outlet of reheater 42 and the bypass line 54. This is indicated by phantom line 84 in Fig. 1.
The control unit 80 is set to control the valve 56 as a function of load on the boiler.
The valve 64 in the bypass line 54 is controlled by temperature responsive control unit 82 which responds to the temperature of the outlet steam from the second or final stage reheater 40. This is indicated by phantom line 86 in Fig. 1. In the illustrated embodiment, as an example the temperature of reheater 40 is maintained within the limit of about 538*C, plus or minus 10 As the temperature of the steam leaving reheater 40 begins to increase above 543 0 C, the valve 64 is opened to bypass additional cold steam directly to reheater 40. As the temperature begins to fall below 532 0 C, the valve 64 is closed to reduce the flow of bypass cold steam to the second stage In Fig. 2, a system identical to Fig. 1, but with superheater 38 located between the reheaters 40 and 42, is disclosed. A single staged iiuperheater 38 is placed in the convection pass, with second stage reheater 40 located upstreams and first stage reheater 42 downstream of the superheater. An economizer 44 is located downstream of the superheater 38. This is in contrast to what was shown in Fig. 1. The placement of the second stage reheater upstream of the superheater 38 allows it to pick up more heat at lower loads. This gives it the potential to extend its steam temperature control range, while having little if any effect on the superheater control range. This potential extersion of the reheat steam temperature control range will enhance the coupling of two units to one turbine easier as to temperature matching capabilities.
The present arrangement, with second stage reheater upstream of superheater 38, gives even greater control SU"ZT TU OE-:rE-T WoO 90/0991 PCT/F190/00026 over the temperature in the reheater stages. As the gas now passes reheater 40 before it passes superheater 38, it may not be below the critical temperature for reheater up to some load of the bctler. Thus, with superheater 38 in the pass behind the reheater 40, the gas temperature will be below the critical temperature for reheater only until after about 25% to 30% load is reached. At this time cold steam is available for control of the temperature in accordance with this invention. If a higher load point is required, the tube metal materials could be upgraded to allow a maximum load of about 35% to 40%. This point of not requiring flow through the reheater until the unit is at 25% to about 40% load is another advantage of this invention.
Referring to Fig. 3, a system identical to Fig. 1, but with a duplicate boiler, is disclosed. In this system, the components of the first boiler arrangement are identified by the same reference numerals as in Fig. 1, with the second boiler arrangement being identified with the same numbers primed. Therefore, in this arrangement, a boiler turbine system is disclosed wherein two boilers are supplying steam to a single turbine. One essential feature required for this type of system is that means be provided for controlling the amount of reheat steam flow to each boiler, so that the steam temperature at reheat outlet is within limits at all possible operating conditions. In the illustrated system, duplicate controls and piping are provided for the two boilers.
The control valves 56 and 64 for the reheat steam temperature control can be used for flow balancing and maintaining the reheater outlet temperature within limits under both normal and abnormal operating conditions. In this arrangement, pressure reducing valves 80 and 82, along with desuperheaters 76 and 78, provide for flexibility during cold start-up, hot start-up and also when starting the second unit while the first one is on line. This simple sys- SU a TU T C' S i-T WO 90/08917 PCT/F190/00026 11 tem eliminates the need for a sophisticated steam blending system. It provides a simple and effective system and method for reheat outlet steam temperature control under varying load conditions.
In operation, from a cold start, combustion is initiated in the combustion chamber 14 with the introduction of fuel and combustion air. As heat is generated as a result of the combustion, the hot gases of combustion move upward in the combustion chamber transferring heat to the water in the combustion chamber walls and to superheaters 18 and The hot gas, combustion products, and solids pass from the combustion chamber along flue 22 into the hot separatox 24 where the solids are separated for return to the combustion chamber. The hot flue gas passes along flue 32 into the convection pass 34 where the heat is transferred in sequence to the superheater 38, the second or final stage reheater 40, and the first stage reheater 42. The flow of hot gas through the system begins before the flow of cold steam. Tie boiler is fired and fuel burns for a period of time providing hot gas before steam is generated and starts the turbine. Cold reheat steam does not start flowing until after the turbine starts.
As the hot gas give up their heat to the water and steam in the water walls, in superheaters and reheaters, the temperature drops so that it is less at each successive stage. It should be noted that the gas temperature leaving the combustion chamber outlet at full load will be in the range of 843 to 927°C. The greater the temperature differential between the gas and the water, the greater the heat transfer will be, and the cooler the gas will be as it passes from the respective heater.
Therefore, as the gas passes superheater 38, it will be below the critical temperature for reheater 40 up to some load of the boiler. Thus, with superheater 38 in the gas pass ahead of the reheater 40, the gas temperature will be SUBSTTUTE SifT WO 90/08917 PCT/F10/00026 12 below the critical temperature for reheater 40 until after about 40% to 50% load is reached. At this time cold steam is available for control of the temperature in accordance with this invention. This point of not requiring flow through the reheater until the unit is at 50% load is another advantage of this invention. Most standard systems require flow through the reheater during the earlier stages of start-up (hot or cold), to protect some from burn out.
Thus, an expensive by-pass system must be utilized. However, with this system's physical layout, a bypass is not required and system start-up periods can be shortened.
Other modifications and changes are possible in the foregoing disclosure and in some instances, some .eatures may be employed without the corresponding use of other features.
Accordingly, while the present invention has been illustrated and described with respect to a specific embodiment, it is to be understood that numerous changes and modifications may be made therein without departing from the spirit and scope of the invention as defined in the appended claims.
SUS ST;I-ir TH MET
Claims (12)
1. A power plant comprising a two-stage steam turbine and a steam generator plant having a fluidized bed combustion system that includes a fluidized bed combustor, at least one separator, at least a first and a second or final stage of a reheater for reheating steam from a first stage of the two-stage steam turbine sequentially disposed in which the first stage of the reheater and the second or final stage of the reheater are sequentially disposed in a common gas flue, and there is dividing means for dividing cold steam from the first stage of the two-stage stem turbine into selective first and second portions and directing said first portion through the first stage of the reheater, and reconnecting means for recombining the first and second portions and directing same through said second or final stage of the reheater.
2. A power plant according to claim 1, further comprising a superheater in which the superheater is arranged downstream of said second stage of reheater.
3. A power plant according to claim 1 or 2, in which the dividing means for dividing the cold steam comprises a by-pass line provided with at least one flow control valve, for by-passing a selected portion of cold steam from the turbine around the first stage of the reheater directly to the second or final stage of the reheater.
4. A power plant according to any preceding claim, further comprising at least one pressure control valve located at the inlet to the first stage of the reheater, the pressure control valve being responsive to the difference between the return steam pressure and the outlet steam pressure of the first stage of the reheater.
5. A power plant according to any preceding claim in which the dividing means for dividing the cold 9team is responsive to outlet temperature of the second stage of the reheater.
6. A method of controlling reheater temperatures in a steam generator having a fluidized bed combustion system that includes a fluidized bed combustor, at least one hot separator, and a reheater for reheating cold steam comprising dividing the reheater into a first and Pecond or final stage reheater and sequentially disposing the first and second or final stages of the reheater in a common gas flue, dividing the cold steam returning to the reheater into selective first and second portions and directing the first portion through the first stage of the reheater and recombining the first portion and the second portion to form a recombined portion and directing the recombined portion through the second or final stage of reheater.
7. A method according to claim 6, further comprising maintaining the temperature of the second stage of the reheater at about 538 0 C, plus or minus 10 0 C.
8. A method according to claim 6 or 7 in which, the second portion of the divided cold steam is directed through a by-pass line extending between an inlet and an outlet of the first stage of the reheater.
9. A method according to any one of claims 6 to 8, further comprising controlling the steam temperature of the second or final stage of the reheater, temperature responsively for dividing the cold steam into the first and the second portions.
A method according to any one of claims 6 to 9 further comprising controlling the pressure difference between the return steam pressure and the outlet steam pressure of the first stage reheater, for dividing the cold steam into the first and the second portions.
11. A power plant substantially as hereinbefore described with reference to any one of the accompanying drawings.
12. A method of controlling reheater temperatures in a steam generator substantially as hereinbefore described with reference to any one of the accompanying drawings. Dated this 24th day of May 1993 A AHLSTROM CORPORATION By its Patent Attorneys: GRIFFITH HACK CO Fellows Institute of Patent Attorneys of Australia 4I
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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US30162189A | 1989-01-24 | 1989-01-24 | |
US301621 | 1989-01-24 |
Publications (2)
Publication Number | Publication Date |
---|---|
AU4941990A AU4941990A (en) | 1990-08-24 |
AU639437B2 true AU639437B2 (en) | 1993-07-29 |
Family
ID=23164149
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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AU49419/90A Ceased AU639437B2 (en) | 1989-01-24 | 1990-01-23 | System and method for reheat steam temperature control in circulating fluidized bed boilers |
Country Status (15)
Country | Link |
---|---|
EP (1) | EP0455660B1 (en) |
JP (1) | JP2532750B2 (en) |
KR (1) | KR0147059B1 (en) |
CN (1) | CN1020951C (en) |
AU (1) | AU639437B2 (en) |
CA (1) | CA2045571C (en) |
CZ (1) | CZ284932B6 (en) |
DD (1) | DD291803A5 (en) |
DE (1) | DE69002758T2 (en) |
ES (1) | ES2045903T3 (en) |
LT (1) | LT3379B (en) |
LV (1) | LV11061B (en) |
PL (1) | PL166038B1 (en) |
UA (1) | UA24009C2 (en) |
WO (1) | WO1990008917A1 (en) |
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CN101893232B (en) * | 2010-06-24 | 2012-02-01 | 东南大学 | Improved generalized predictive control method for reheat steam temperature of thermal power units |
WO2014048089A1 (en) * | 2012-09-26 | 2014-04-03 | 上海伏波环保设备有限公司 | Natural circulation indirect type flue gas reheater |
KR102051101B1 (en) * | 2013-07-19 | 2019-12-02 | 한국전력공사 | Variable heat exchanger of circulating fluid bed boiler |
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CN106545833B (en) * | 2016-10-28 | 2018-07-17 | 杭州红山热电有限公司 | Boiler steam and water circuit |
HUE056813T2 (en) * | 2017-07-27 | 2022-03-28 | Sumitomo SHI FW Energia Oy | A fluidized bed boiler plant and a method of preheating combustion gas in a fluidized bed boiler plant |
KR102093302B1 (en) * | 2018-07-19 | 2020-04-23 | 한국생산기술연구원 | Sand falling type circulating fluidized bed boiler having a plurality of riser and its operation method |
KR20210063369A (en) * | 2018-10-10 | 2021-06-01 | 베이징 싸이너텍 씨오., 엘티디. | How to improve the efficiency of the Rankine cycle |
CN113753237B (en) * | 2021-09-21 | 2023-04-07 | 中国航空工业集团公司西安飞机设计研究所 | Temperature control decoupling method for refrigeration assembly |
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- 1990-01-23 EP EP90901818A patent/EP0455660B1/en not_active Expired - Lifetime
- 1990-01-23 JP JP2502023A patent/JP2532750B2/en not_active Expired - Lifetime
- 1990-01-23 KR KR1019900702150A patent/KR0147059B1/en not_active IP Right Cessation
- 1990-01-23 CA CA002045571A patent/CA2045571C/en not_active Expired - Fee Related
- 1990-01-23 UA UA93002096A patent/UA24009C2/en unknown
- 1990-01-23 AU AU49419/90A patent/AU639437B2/en not_active Ceased
- 1990-01-23 DD DD90337276A patent/DD291803A5/en not_active IP Right Cessation
- 1990-01-23 DE DE90901818T patent/DE69002758T2/en not_active Expired - Lifetime
- 1990-01-23 ES ES90901818T patent/ES2045903T3/en not_active Expired - Lifetime
- 1990-01-23 WO PCT/FI1990/000026 patent/WO1990008917A1/en active IP Right Grant
- 1990-01-23 CN CN90100421A patent/CN1020951C/en not_active Expired - Lifetime
- 1990-01-24 PL PL90283427A patent/PL166038B1/en unknown
- 1990-01-24 CZ CS90330A patent/CZ284932B6/en not_active IP Right Cessation
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1993
- 1993-06-28 LV LVP-93-662A patent/LV11061B/en unknown
- 1993-08-10 LT LTIP842A patent/LT3379B/en not_active IP Right Cessation
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AU477834B2 (en) * | 1972-01-27 | 1974-07-25 | Westinghouse Electric Corporation | Improvements in or relating to electric power plant system and method for operating a steam turbine especially of the nuclear tupe with electronic reheat control of a cycle steam reheater |
EP0257254A1 (en) * | 1986-07-31 | 1988-03-02 | L. & C. Steinmüller GmbH | Process for the combustion of carbon-containing materials in a circulating fluidised bed, and fluidised bed combustion plant for carrying out the process |
EP0274637A1 (en) * | 1986-12-11 | 1988-07-20 | Siemens Aktiengesellschaft | Steam generator with a circulating fluidised bed |
Also Published As
Publication number | Publication date |
---|---|
KR0147059B1 (en) | 1998-08-17 |
DE69002758D1 (en) | 1993-09-16 |
KR910700434A (en) | 1991-03-15 |
CA2045571C (en) | 1995-09-12 |
LV11061B (en) | 1996-06-20 |
CZ284932B6 (en) | 1999-04-14 |
UA24009C2 (en) | 1998-08-31 |
CN1020951C (en) | 1993-05-26 |
CS33090A3 (en) | 1992-03-18 |
JP2532750B2 (en) | 1996-09-11 |
LV11061A (en) | 1996-02-20 |
JPH04503095A (en) | 1992-06-04 |
CN1045168A (en) | 1990-09-05 |
DE69002758T2 (en) | 1993-12-16 |
EP0455660A1 (en) | 1991-11-13 |
LTIP842A (en) | 1995-02-27 |
EP0455660B1 (en) | 1993-08-11 |
WO1990008917A1 (en) | 1990-08-09 |
DD291803A5 (en) | 1991-07-11 |
LT3379B (en) | 1995-08-25 |
CA2045571A1 (en) | 1990-07-25 |
PL166038B1 (en) | 1995-03-31 |
AU4941990A (en) | 1990-08-24 |
ES2045903T3 (en) | 1994-01-16 |
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MK14 | Patent ceased section 143(a) (annual fees not paid) or expired |