GB1574466A - Creación de Inventos y Patentes con Inteligencia Artificial

GB1574466A – Power generation system
– Google Patents

GB1574466A – Power generation system
– Google Patents
Power generation system

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Publication number
GB1574466A

GB1574466A
GB6749/77A
GB674977A
GB1574466A
GB 1574466 A
GB1574466 A
GB 1574466A
GB 6749/77 A
GB6749/77 A
GB 6749/77A
GB 674977 A
GB674977 A
GB 674977A
GB 1574466 A
GB1574466 A
GB 1574466A
Authority
GB
United Kingdom
Prior art keywords
turbine
pressure section
directly
condenser
transfer means
Prior art date
1976-02-19
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.)

Expired

Application number
GB6749/77A
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

Foster Wheeler Energy Corp

Original Assignee
Foster Wheeler Energy Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
1976-02-19
Filing date
1977-02-17
Publication date
1980-09-10

1977-02-17
Application filed by Foster Wheeler Energy Corp
filed
Critical
Foster Wheeler Energy Corp

1980-09-10
Publication of GB1574466A
publication
Critical
patent/GB1574466A/en

Status
Expired
legal-status
Critical
Current

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Classifications

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES

F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES

F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines

F01K9/04—Plants characterised by condensers arranged or modified to co-operate with the engines with dump valves to by-pass stages

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

F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein

F01K3/18—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters

F01K3/24—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters with heating by separately-fired heaters

F01K3/242—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters with heating by separately-fired heaters delivering steam to a common mains

Description

PATENT SPECIFICATION
( 11) 1 574 466 ( 21) Application No 6749/77 ( 22) Filed 17 Feb 1977 ( 31) Convention Application No.
659 300 ( 32) Filed 19 Feb 1976 in ( 33) United States of America (US) ( 44) Complete Specification published 10 Sept 1980 ( 51) INT CL 3 F Ol K 7/00 ( 52) Index at acceptance F 4 A 3 ( 72) Inventors PAUL V GUIDO ROBERT L CRISWELL ALBERT J ZIPAY ( 54) POWER GENERATION SYSTEM ( 71) We, FOSTER WHEELER ENERGY CORPORATION, a corporation organised and existing under the laws of the State of Delaware, United States of America of 110 South Orange Avenue, Livingston, New Jersey 07039, United States of America, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed to be particularly described in and by the following statement:
This invention relates to a power generation system and, particularly, to such a system in which the condition of the vapor output from one or more vapor generators is precisely controlled before being passed to a turbine for driving same.
In the design of power generation systems, it is often necessary to carefully control the critical parameters, such as temperature and pressure, of steam from a vapor generator before it is passed to a turbine For example, power generation systems may use two vapor generators which operate to drive a single turbine In this manner, the vapor generators can be designed to operate at approximately half the load of the turbine so that, upon failure of one of the generators, the turbine still will be driven by the other generator to avoid a complete stoppage of the turbine However, in systems of this type, when one of the vapor generators is started up after being shut down for any reason, the temperature and pressure conditions of the vapor generated by the starting up vapor generator must be carefully regulated so that it will match the temperature and pressure conditions of the vapor generated by the other vapor generator that is in operation since, otherwise, the turbine may be severely damaged.
We have sought to provide a power generation system of the above type which enables the temperature and pressure conditions of steam generated by a vapour generator to be carefully controlled.
We have also sought to provide a power generating system of the above type in which at least two vapour generators are 50 provided for driving a turbine and in which the temperature and pressure conditions of the steam generated by each generator are precisely controlled to effect optimum matching of the supplies of steam before 55 they are passed to the turbine.
We have further sought to provide a power generation system of the above type in which the steam output from either of the vapour generators is selectively directed 60 to various other stages of the system in order to selectively control its pressure and temperature conditions.
Accordingly the present invention provides a power generating system comprising 65 vapour generating means including at least two boilers connected directly to at least two superheaters, a turbine comprising a relatively high pressure section and a relatively low pressure section, the super 70 heaters being connected directly to the high pressure section of the turbine, the high pressure section of the turbine being connected directly to at least two reheaters which are connected directly to the low 75 pressure section of the turbine which is connected directly to a condensor, a first fluid transfer means connecting each boiler directly to the condenser so as to bypass the superheaters, 80 a second fluid transfer means connecting each superheater directly to the reheater so as to bypass the high pressure section of the turbine and a third fluid transfer means connecting each reheater 85 directly to the condenser so as to bypass the low pressure section of the turbine.
A fluid transfer means may connect the boiler to the high pressure section A fluid transfer means may connect the reheater 90 z z It It r_ tn 1 574466 between the high pressure section and the low pressure section of the turbine.
Preferably each of the boilers has an inlet for receiving liquid and an outlet for discharging vapour, the first fluid transfer means connecting the outlets directly to the condenser.
The present invention is further illustrated in the accompanying drawing which is a schematic representation of the fluid circuit of the power generation system in accordance with the present invention.
Referring specifically to the drawing, reference numeral 10 refers in general to a boiler which is connected via a line 12 to a superheater 14 For the-purposes of this application, it is understood that the term «line» is meant to cover all possible fluid transfer systems, such as tubes, conduits and downcomers which are normally associated with this type of equipment As an example, the line 12 could be in the form of tubes connecting one section of a finned tube wall forming the furnace section of the boiler, with another section thereof.
A line 16 extends from the line 12 and is connected to a condenser 18 for supplying fluid from the boiler 10 directly to the condenser without passing through the superheater 14 A flow control valve 20 and a desuperheating unit 22 are provided in the line 16 for reasons that will be indicated in detail later The outlet of the superheater 14 is connected, via a line 24, to a (Y) junction header 26 with stop-check valve 28 and stop valve 30 being imposed in line 24 Also, a line 32 extends from the line 24 at a point between the stopcheck valve 28 and stop valve 30 for connecting the line 24 to drain, with a flow control valve 34 being disposed in the line 32 for the purpose of checking the tightness of valves 28 and 30.
The outlet of the (Y) junction header 26 is connected, via a line 36, to the high pressure section 38 of a turbine, and a flow control valve 40 is disposed in the line 36 for controlling the flow of fluid to the latter section A line 42 connects the outlet of the high pressure turbine section 38 to a (Y) junction header 44 and a stop; check valve 46 is disposed in the line 42.
The outlet of the (Y) junction header 44 is connected, via a line 48, to a reheater 50.
A flow control valve 52 and a check valve 54 are disposed in the line 48.
A line 56 connects the outlet of the reheater 50 to a (Y) junction header 58 with a stop-check valve 60 being disposed in the line 56 The outlet of the (Y) junction header 58 is connected, via a line 62, to the intermediate pressure section 64 of the above-mentioned turbine and a flow control valve 66 being disposed in the line 62 The intermediate pressure section 64 of the turbine is connected to a low pressure section 68 by a line 70, with the output of the low pressure section being connected to the condenser 8 by a line 72 70 A bypass line 74 connects with the line 24 at a point between the superheater 14 and the valve 28, and with the line 48 at a point between the check valve 54 and the reheater 50 A pressure reducing valve 75 76 and a desuperheating unit 78 are disposed in the line 74.
A bypass line 80 connects with the line 56 at a point between the reheater 50 and the valve 60, and connects the latter line 80 directly to the condenser 18, with a pressure regulating valve 82 and a desuperheating unit 84 being disposed in the line 80.
It should be noted that the basic fluid flow circuit would extend through the 85 appropriate lines just mentioned from the boiler 10 through the superheater 14 and the (Y) junction header 26, and to the high pressure turbine section 38 From the latter turbine section the fluid would 90 flow through the (Y) junction header 44, the reheater 50 and into the (Y) junction header 58, from which it passes to the intermediate pressure turbine section 64.
From the latter turbine section, the fluid 95 would then pass into the low pressure turbine section 68 and to the condenser 18.
It is understood that a line 86 extends from the outlet of the condenser and is connected to the boiler 10 in a conventional 100 manner with feedwater heaters and other associated conventional equipment provided in the line 86.
The boiler 10, the superheater 14 and their corresponding lines, bypass lines and 105 associated equipment are duplicated in any parallel circuit Also, the circuit extending between the (Y) junction headers 44 and 58 and including the reheater 50 and the associated bypass lines, is duplicated 110 in any parallel circuit Since the components of the respective parallel circuits operate in an identical manner, they are given the same reference numeral as their respective corresponding components and 115 with the suffix «a» and will not be discussed in any further detail.
It is apparent from the foregoing that variations in the flow circuit from the above-mentioned standard circuit can be 120 made by operation of the various flow control valves For example, the valves 20 or a can be opened to pass a portion of the fluid from the boiler 10 or 1 Xa to the condenser 18 and thus bypass the superheaters 125 14 and 14 a Also, the pressure reducing valves 76 or 76 a may be opened to pass a portion of the fluid from the outlet of the superheaters 14 and 14 a, respectively, directly to the reheaters 50 and 50 a, respec 130 3 1574466 3 tively and thus bypass the high pressure section 38 of the turbine Further, the valves 82 and 82 a may be opened to permit a portion of the fluid to pass from the outlet of the reheaters 50 and 50 a respectively directly to the condenser 18, and thus bypass the intermediate pressure section 64 and the low pressure section 68 of the turbine.
According to a preferred embodiment of the present invention, the various control valves may be operated in response to temperature and pressure conditions of the fluid at various stages of the circuit For example, the control valves 20 and 20 a may be operated in response to the temperature of the fluid at the outlet of the superheater 14 and the pressure reducing valves 76 and 76 a may be controlled by fluid pressure as measured at the outlet of the superheater 14 and 14 a, respectively, in a manner to control the steam flowing through the line 74 and 74 a.
Similarly, the valves 52 and 52 a may be operated in response to flow from the superheaters 14 and 14 a, respectively, to control the flow through the lines 48 and 48 a, respectively, thereby proportioning the steam applied to the reheaters 50 and 50 a, respectively, from that coming from the high pressure section 38 of the turbine and from the superheaters 14 and 14 a, respectively This also could apply to the valves 60, 60 a, 82 and 82 a to proportion the hot reheat steam flow between the intermediate pressure section 64 of the turbine and direct discharge to the condenser 18 The aforementioned control connections are not shown in the drawings and will not be described in any further detail for the convenience of presentation, since they may be of a conventional design.
It can be appreciated that the provision of the several bypass lines 16, 16 a, 74 74 a, 80 and 80 a, as well as the parallel flow circuit including the additional boiler 10 a, superheater 14 a, enable the fluid flow to be selectively passed to and through the system to precisely control the pressure and temperature conditions of the fluid.
In normal operation, both vapor generators including the boilers 10 and l Oa, their respective superheaters 14 and 14 a, and the associated components are placed in full operation to drive the turbine In this type of system, the turbine could be designed for a load approximately twice that of each individual vapor generator so that both boilers contribute equally in driving the turbine In this normal operation, the fluid flow would be in the main circuit described immediately above with the control valves 20, 20 a, the pressure reducing valves 76 and 76 a, the pressure regulating valves 82, and 82 a being closed to prevent fluid flow through the bypass lines 16, 16 a, 74, 74 a, 80, and 80 a, respectively.
In the event one of the vapor generators is shut down due to its failure, or for other 70 purposes such as cleaning, the remaining vapor generator would be used to drive the turbine at approximately half load The features of the present invention are especially important when the inoperative 75 vapor generator is started up and the following operational description will be predicated on a start-up of the boiler 10 and its associated superheater 14 while the boiler 10 a and the superheater 14 a are in 80 full operation.
In particular, upon initial firing of the boiler 10, the control valve 20 is opened to permit a portion of the vapor generated in the boiler 10 to bypass the superheater 85 14 and pass directly to the condenser 18.
This will enable a relatively larger amount of heat to be transferred to the remaining vapor passing to the superheater 14 and thus bring the temperature of this fluid up 90 to a relatively high value when it passes through the superheater 14 The control valve 76 may also be opened to permit a portion of the vapor from the superheater to be passed directly to the reheater 50 95 and thus bypass the high pressure turbine section 38 Since the remaining vapor flowing in the line 24 is still receiving heat from the furnace section of the boiler, its temperature is raised to the extent it 100 matches the temperature of the vapor from the superheater 14 a As a result, the vapors mixing in the junction header 26 are suitable for passage directly into the high pressure turbine section 38 As the 105 vapor flow to the latter section increases, the flow through the bypass line 74 is reduced accordingly by virtue of the control of the valve 76 in response to flow from the superheater 14, as discussed above 110 The valve 20 and the desuperheating unit 22 reduce the pressure and temperature, respectively, of the fluid passing through the line 16 to the condenser Also, the pressure reducing valve 76 and the desuper 115 heater unit 78 reduce the pressure and temperature, respectively, of the vapor flowing in the line 74 before it mixes with the fluid in the line 48 from the high pressure turbine section 38, before passing into the 120 reheater 50.
The check valves 54 and 54 a function to prevent any back flow of vapor in the lines 48 and 48 a, respectively, towards the (Y) junction header 44 and possibly towards 125 the high pressure turbine section 38.
The stop check valve 60 and the pressure regulating valve 82 may be selectively controlled to permit the flow from the reheater 50 to be proportioned between flow 130 1 574 466 1574466 directly to the condenser 18 and flow to the intermediate pressure turbine section 64, as discussed above This insures that the vapor entering the intermediate turbine section 64 is at the proper condition The desuperheating units 84 and 84 a reduce the temperature of the vapor in the lines 80 and 80 a, respectively before it enters the condenser 18.
As a result, the condition of the fluid from the boiler 10 and the superheater 14, as they are started up, can be carefully matched to that from the operable vapor generator, including the boiler 10 a and the superheater 14 a, to insure that no damage will be made to the various lines and turbine sections.
Although not expressly shown in the drawings, it is understood that the various control valves, such as 20, 20 a, 76, 76 a, 82 and 82 a may, in actual practice, comprise both a flow control valve which is operated as described above and, in addition, a valve which provides a further insurance that during its closing no leakage occurs through the corresponding lines.
It is also understood that the various desuperheating units 22, 22 a, 78, 78 a, 84, and 84 a may also have valves of the above type associated with them.
It is understood that several variations may be made in the foregoing without departing from the scope of the invention.
For example, the present invention is not limited to the application of a power genetation system employing dual vapor generators, but can be easily applied to other designs of power generation systems in which the temperature and pressure conditions of the fluid flowing in one or more circuits must be precisely controlled.

Claims (4)

WHAT WE CLAIM IS:
A power generating system comprising vapour generating means including at least two boilers connected directly to at least two superheaters, a turbine comprising a relatively high pressure section and a relatively low pressure section, the superheaters being connected directly to the high pressure section of the turbine, the high 50 pressure section of the turbine being connected directly to at least two reheaters which are connected directly to the low pressure section of the turbine which is connected directly to a condenser, a first 55 fluid transfer means connecting each boiler directly to the condenser so as to bypass the superheaters, a second fluid transfer means connecting each superheater directly to the reheater so as to bypass the high 60 pressure section of the turbine and a third fluid transfer means connecting each reheater directly to the condenser so as to bypass the low pressure section of the turbine 65

2 A system as claimed in Claim 1, wherein a fluid transfer means connects the boilers to the high pressure section of the turbine.

3 A system as claimed in Claim 2, fur 70 ther comprising a fluid transfer means connecting the reheaters between the high pressure section and the low pressure section of the turbine.

4 A system as claimed in any of claims 75 1 to 3, wherein each of the boilers has an inlet for receiving liquid and an outlet for discharging vapour, the first fluid transfer means connecting the outlets directly to the condenser 80 A power generating system substantially as herein described and with reference to the accompanying Drawing.
For the Applicants:
LLOYD WISE, BOULY & HAIG, Chartered Patent Agents, Norman House, 105-109 Strand, London, WC 2 R OAE.
Printed for Her Majesty’s Stationery Office by The Tweeddale Press Ltd, Berwick-upon-Tweed, 1980.
Published at the Patent Office, 25 Southampton Buildings, London, W C 2 A l AY, from which copies may be obtained.

GB6749/77A
1976-02-19
1977-02-17
Power generation system

Expired

GB1574466A
(en)

Applications Claiming Priority (1)

Application Number
Priority Date
Filing Date
Title

US05/659,300

US4060990A
(en)

1976-02-19
1976-02-19
Power generation system

Publications (1)

Publication Number
Publication Date

GB1574466A
true

GB1574466A
(en)

1980-09-10

Family
ID=24644872
Family Applications (1)

Application Number
Title
Priority Date
Filing Date

GB6749/77A
Expired

GB1574466A
(en)

1976-02-19
1977-02-17
Power generation system

Country Status (7)

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Link

US
(1)

US4060990A
(en)

JP
(1)

JPS52101340A
(en)

AU
(1)

AU513781B2
(en)

CA
(1)

CA1066516A
(en)

ES
(1)

ES456077A1
(en)

GB
(1)

GB1574466A
(en)

MX
(1)

MX143318A
(en)

Families Citing this family (17)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

CH633348A5
(en)

1978-08-10
1982-11-30
Bbc Brown Boveri & Cie

STEAM TURBINE SYSTEM.

US4306417A
(en)

1979-11-28
1981-12-22
Westinghouse Electric Corp.
Multiple boiler steam blending control system for an electric power plant

US4439687A
(en)

1982-07-09
1984-03-27
Uop Inc.
Generator synchronization in power recovery units

SE502492C2
(en)

1991-12-23
1995-10-30
Abb Carbon Ab

Boiler system with common steam system

US5181381A
(en)

1992-07-08
1993-01-26
Ahlstrom Pyropower Corporation
Power plant with dual pressure reheat system for process steam supply flexibility

US6164072A
(en)

1998-10-21
2000-12-26
Battelle Memorial Institute
Method and apparatus for matching a secondary steam supply to a main steam supply of a nuclear or thermal renewable fueled electric generating plant

US7147427B1
(en)

2004-11-18
2006-12-12
Stp Nuclear Operating Company
Utilization of spillover steam from a high pressure steam turbine as sealing steam

US7516620B2
(en)

2005-03-01
2009-04-14
Jupiter Oxygen Corporation
Module-based oxy-fuel boiler

US20060260314A1
(en)

2005-03-25
2006-11-23
Kincaid Ronald F
Method and system integrating combined cycle power plant with a solar rankine power plant

FI120658B
(en)

2005-05-04
2010-01-15
Metso Power Oy

Heat control method for intermediate overheating steam, heat control system and power plant

US20080034757A1
(en)

2005-05-27
2008-02-14
Skowronski Mark J
Method and system integrating solar heat into a regenerative rankine cycle

US7640746B2
(en)

2005-05-27
2010-01-05
Markon Technologies, LLC
Method and system integrating solar heat into a regenerative rankine steam cycle

US8161724B2
(en)

2010-03-31
2012-04-24
Eif Nte Hybrid Intellectual Property Holding Company, Llc
Hybrid biomass process with reheat cycle

US8596034B2
(en)

2010-03-31
2013-12-03
Eif Nte Hybrid Intellectual Property Holding Company, Llc
Hybrid power generation cycle systems and methods

US8783037B2
(en)

2012-01-10
2014-07-22
Ichiroku HAYASHI
Electricity-generating system

US8495878B1
(en)

2012-04-09
2013-07-30
Eif Nte Hybrid Intellectual Property Holding Company, Llc
Feedwater heating hybrid power generation

US9932863B2
(en)

2013-06-28
2018-04-03
Norgren Limited
Vehicle waste heat recovery system

Family Cites Families (8)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

US2676574A
(en)

1948-11-03
1954-04-27
Republic Flow Meters Co
Feedwater control system

FR1253461A
(en)

1960-03-03
1961-02-10
Licentia Gmbh

Control device for reduction valves in injection reduction units and relief valves in steam turbine installations with intermediate superheater

US3140588A
(en)

1960-12-29
1964-07-14
Gen Electric
Reactor-turbine control system

DE1200326B
(en)

1962-01-30
1965-09-09
Buckau Wolf Maschf R

Procedure for starting up a steam power plant

US3359732A
(en)

1966-07-21
1967-12-26
Combustion Eng
Method and apparatus for starting a steam generating power plant

US3358450A
(en)

1965-12-21
1967-12-19
Combustion Eng
Method and apparatus for steam turbine startup

CH470576A
(en)

1967-02-06
1969-03-31
Sulzer Ag

Method for controlling a heating steam power plant

US3882680A
(en)

1972-04-18
1975-05-13
Babcock & Wilcox Co
By-pass system

1976

1976-02-19
US
US05/659,300
patent/US4060990A/en
not_active
Expired – Lifetime

1976-12-13
CA
CA267,759A
patent/CA1066516A/en
not_active
Expired

1976-12-30
AU
AU20958/76A
patent/AU513781B2/en
not_active
Expired

1977

1977-01-04
MX
MX167573A
patent/MX143318A/en
unknown

1977-02-17
GB
GB6749/77A
patent/GB1574466A/en
not_active
Expired

1977-02-18
ES
ES456077A
patent/ES456077A1/en
not_active
Expired

1977-02-19
JP
JP1768777A
patent/JPS52101340A/en
active
Pending

Also Published As

Publication number
Publication date

AU513781B2
(en)

1981-01-08

ES456077A1
(en)

1978-02-01

CA1066516A
(en)

1979-11-20

JPS52101340A
(en)

1977-08-25

US4060990A
(en)

1977-12-06

AU2095876A
(en)

1978-07-06

MX143318A
(en)

1981-04-14

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