GB2099558A - Heat recovery steam generator - Google Patents
Heat recovery steam generator Download PDFInfo
- Publication number
- GB2099558A GB2099558A GB8208645A GB8208645A GB2099558A GB 2099558 A GB2099558 A GB 2099558A GB 8208645 A GB8208645 A GB 8208645A GB 8208645 A GB8208645 A GB 8208645A GB 2099558 A GB2099558 A GB 2099558A
- Authority
- GB
- United Kingdom
- Prior art keywords
- economizer
- section
- heat
- flow
- bypass
- 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.)
- Withdrawn
Links
- 238000011084 recovery Methods 0.000 title claims abstract description 17
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 26
- 238000010025 steaming Methods 0.000 claims abstract description 20
- 239000007789 gas Substances 0.000 claims description 43
- 239000012530 fluid Substances 0.000 claims description 16
- 238000011144 upstream manufacturing Methods 0.000 claims description 14
- 238000012546 transfer Methods 0.000 claims description 6
- 238000000034 method Methods 0.000 claims description 4
- 230000003292 diminished effect Effects 0.000 claims description 2
- 239000002918 waste heat Substances 0.000 claims description 2
- 230000001174 ascending effect Effects 0.000 claims 1
- 238000013461 design Methods 0.000 abstract description 6
- 238000005260 corrosion Methods 0.000 abstract description 2
- 230000007797 corrosion Effects 0.000 abstract description 2
- 238000010438 heat treatment Methods 0.000 abstract description 2
- 230000007704 transition Effects 0.000 abstract 1
- 230000000153 supplemental effect Effects 0.000 description 4
- 230000007423 decrease Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 230000003466 anti-cipated effect Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000009429 distress Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 238000005215 recombination Methods 0.000 description 1
- 230000006798 recombination Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
- F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
- F22D1/00—Feed-water heaters, i.e. economisers or like preheaters
- F22D1/02—Feed-water heaters, i.e. economisers or like preheaters with water tubes arranged in the boiler furnace, fire tubes or flue ways
- F22D1/12—Control devices, e.g. for regulating steam temperature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
- F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
- F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
- F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
- F22B1/1815—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines using the exhaust gases of gas-turbines
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- Combustion & Propulsion (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Chemical & Material Sciences (AREA)
- Control Of Steam Boilers And Waste-Gas Boilers (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
- Control Of Turbines (AREA)
Abstract
In a combined cycle power plant, otherwise wasted gas turbine exhaust gas is used to heat water into steam in a heat recovery steam generator (HRSG). The HRSG may include three general heating sections in descending order; i.e., the economizer (42), the evaporator (44) and the superheater. One initiative of economizer design is to prevent the transition of water into steam while the water is in the economizer. Otherwise, deposits of corrosion could occur to the detriment of HRSG performance and longevity. Since the heat input from the gas turbine exhaust may vary with load on the gas turbine, it is possible that a design which is satisfactory under normal conditions could lead to 'steaming' in the economizer tubes under low load conditions. One solution to this problem is a multi-section (A, B) economizer (42) which utilizes its full surface length for normal operation and which has a by-pass line 58 for bypassing a portion (A) of its surface length for off-normal operating conditions. <IMAGE>
Description
SPECIFICATION
Heat recovery steam generator
BACKGROUND OF THE INVENTION
This invention is directed in general to combined cycle power piants and in particular to that portion of a combined cycle power plant indentified as a heat recovery steam generator.
A combined cycle power plant includes both a gas turbine and a steam turbine which are thermally connected through a heat recovery steam generator (HRSG). The heat recovery steam generator is a noncontact heat exchanger which utilizes otherwise wasted gas turbine exhaust gases to heat feedwater into steam which becomes the driving fluid in the steam turbine. The
HRSG may be divided into several distinct heating sections which include, in descending order, an economizer, an evaporator and a superheater. The coolest section of the HRSG relatively speaking is the economizer, whereas the hottest section is the superheater. The heat energy of the gas turbine exhaust may vary in accordance with ambient conditions and, further, in accordance with the electrical load on the gas turbine.
It is desirable from an operating point of view to always maintain the water temperature in the ecomomizer at a level below saturation to avoid "steaming" or the production of steam in the ecomomizer tubes. Steaming is undesirable because it may cause flow instability and/or tube dryout that could result in deposits or corrosion which may lead to premature tube distress. If the water flow/gas flow/heat transfer relationship were constant, the HRSG designer could provide an economizer design wherein the phenomenon of steaming would never occur. However, because the gas turbine exhaust heat capacity varies with load, the designer can only optimize a design such that steaming under adverse part load points is within certain empirical guidelines.This results in a water temperature leaving the ecomomizer at a guarantee point somewhat below saturation temperature with a corresponding diminition in
HRSG thermodynamic efficiency.
One prior art solution to the steaming phenomenon is to monitor a current operating condition of the gas turbine or HRSG, such as load or gas exhaust temperature respectively, to compute an ideal inlet temperature setpoint at the economizer tube inlet. Thereafter, an actual temperature reading is made at the entrance to the economizer tube inlet and a supplemental water flow to the economizer is increased or decreased in accordance with the temperature difference between the desired setpoint and the actual water temperature. This supplemental water may be taken downstream from the circulation pump used in combination with the steam drum. This solution is adequate for small changes in operating parameters for the HRSG.
However, acknowledging such factors as the availability of supplemental water and pipe flow capacity, it is apparent than under a wide range of operating conditions this prior art arrangement would be self-limiting.
OBJECT OF THE INVENTION
It is an object of the invention to provide an
HRSG tube bundle with a means to prevent steaming within the tube bundle during various changes in operating conditions.
It is another object of the invention to provide an HRSG tube bundle with a means to prevent steaming within the tube bundle without the addition of supplemental water into the system.
The novel features believed characteristic of the present invention are set forth in the appended claims. The invention itself, however, together with further objects and advantages thereof may be best understood with reference to the following description taken in connection with the included drawings.
SUMMARY OF THE INVENTION
The invention is a tube bundle that is divided into two separate heat transfer sections which are connected in series. A bypass line with a control valve apportions the inlet water flow between an upper (downstream) economizer section and a lower (upstream) economizer section in accordance with the water temperature at the outlet of the lower economizer section. The upper economizer section is designed so that under all flow conditions, steaming will not occur in that section. In the lower economizer section, as the heat energy content of the gas exhaust increases, water may be diverted directly into the lower section so as to avoid steaming. In addition, the control valve may be automatically set by a controller which positions the control valve in accordance with a desired temperature setpoint based on steam drum conditions.
BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 is a simplified sketch of a combined cycle power plant used to illustrate the application of the present invention.
Fig. 2 is a schematic of the HRSG economizer and evaporator sections and the steam drum.
Fig. 3 is a schematic of the economizer piping in a preferred embodiment of the invention which further shows automatic means for adjusting the bypass valve.
DETAILED DESCRIPTION OF THE INVENTION
A basic combined cycle power plant 10 shown in Fig. 1 may include a gas turbine power plant 12 and a steam turbine power plant 14. A heat recovery steam generator 16, hereinafter HRSG, provides a thermal link between the gas turbine power plant and the steam turbine power plant in that the gas turbine exhaust gas waste heat is used to heat feedwater delivered from pipe 1 8 into the HRSG in order to produce superheated steam delivered to the steam power plant through pipe 20 and inlet valve 21. The gas turbine power plant 12 includes a gas turbine 22 and a driven compressor 24 which are connected by a ring of combustors 26, only one of which is shown. The
gas turbine power plant may also include an
electrical generator 28 which is also driven by the
gas turbine to produce electricity.
The steam turbine power plant includes a
steam turbine 32 which drives an electrical
generator 34. Steam which is exhausted from the
steam turbine is input into a condenser 36 to
become feedwater which is then returned to the
HRSG through the pipe 18 and condensate pump
38.
The HRSG comprises three main sections
which include top to bottom (as viewed), an
economizer 42, an evaporator 44, and a
superheater 46. The HRSG is generally a
noncontact counterflow heat exchanger in that the watertemperature profile increases as it flows downwardiy through the heat exchange box and
the gas temperature profile decreases as it rises in
the box.
All three HRSG sections are connected to a
steam drum 48 such that the economizer delivers
heated water into the steam drum which is then
pumped into the evaporator by pump 50 and
subsequently returned to the steam drum where it
is fed to the superheater through line 54. This
entire representation is for background
information only and is neither part of, nor limits,
the scope of the present invention.
In the event that the HRSG is oriented in the
horizontal direction, the upper sections are
considered downstream with respect to the gas
flow direction, whereas the lower sections are
considered upstream with respect to the gas flow
direction.
Referring to Fig. 2, the details of the present
invention will now be described. Similiar parts of
the HRSG main sections and drum are identified
as described for Fig. 1. The dashed lines 56
represent the hot gas flow path within the HRSG.
The fluid contained within the HRSG generally
increases in temperature as it progresses down
the HRSG. The gas temperature in the hot gas
duct will decrease as the gas rises and heat
exchange through the tubes takes place. The
overall heat energy of the gas flow is dependent
upon the load placed on the gas turbine. During
low load periods, the gas exiting from the
evaporator section 44 contains more heat energy
than is required in the economizer section. This
phenomenon has been a limiting factor in the
design of economizer sections since the desirable
goal is maximum heat recovery during high load
periods. An undesirable result is the occurrence of
"steaming" or the production of steam in the
economizer tubes.The design practice has been a
compromise between heat recovery efficiency and
the avoidance of "steaming" for particular
ambients and other conditions.
The present invention contemplates providing
two economizer sections; namely, an upper or
downstream economizer section A and a lower or
upstream economizer section B. A bypass line 58
is provided for conducting feedwater directly into
the lower economizer section, thus bypassing the
upper economizer section and consequent heat transfer during low load and other high heat gas conditions. The amount of fluid which is bypassed is controlled by the position of a mixing valve 60.
The upper economizer section A is designed so that under the worst anticipated condition no steaming will occur in that section. The water which bypasses the upper economizer section A will not have heated and so will avoid the occurence of steaming in the lower economizer section B. The lower economizer section B terminates at the steam drum.
Fig. 3 is a more detailed representation of a preferred embodiment of the present invention which shows one means for controlling the valve position of the mixing valve 60. Economizer sections A and B represent the same sections as shown in Fig. 2. The water flow into the upper economizer section A is divided between the upper economizer inlet header 62 and the bypass line 58 in accordance with the position of the valve plug 61 of mixing valve 60. Inlet header 62 distributes the incoming feedwater to other parallel tubes (not shown) which form part of the upper economizer section.
The outflow of the mixing valve 60 is the recombination of the upper economizer flow and the bypass flow. The intent of this invention during periods where steaming is likely to occur is to minimize flow through the upper economizer section while increasing flow through the bypass.
The intent is not to add flow to the overall system so that the steam drum water level remains unaffected, thereby simplifying the level control for the drum. The outflow of the mixing valve is then input into the lower economizer section B which includes inlet header 64. The flow from the upper economizer section is collected in an outlet header 66 upstream from the mixing valve whereas the flow from the lower economizer section is collected in an outlet header 68 upstream from the steam drum as shown in Fig. 2.
There is a control system for distributing the water flow between the upper economizer section and the bypass. The control system includes the mixing valve 60 and a valve position controller 70.
Referring now to Figs. 2 and 3 together, a temperature signal on line 72 is derived from thermocouple 74 at the outlet end of the lower economizer section B. The temperature signal in line 72 is a signal representation of the water temperature at the outlet end of the lower economizer section B and represents a feedback signal to the controller 70. The setpoint signal indicated by arrow 78 is based on steam drum pressure from pressure transmitter 75 which is used according to the steam tables to derive a setpoint in function generator 77 according to saturation temperature plus an offset of several degrees to ensure that flashing or steaming does not occur at the outlet of the lower economizer tube bundle B. The controller will maintain the outlet temperature in line 72 at the setpoint temperature 78 by adjusting the position of the mixing valve plug in accordance with any error signal or valve adjustment signal appearing on line 79. Indicator 80 may be a temperature indicator which displays the water temperature at the lower economizer outlet as sensed by thermocouple 84 and sent to the indicator through line 82.
The operation of the invention is as follows.
Under normal operating conditions the upper and lower economizer sections may be operative to carry a full flow of water the entire length of the economizer while bypass mixing valve 6.0 remains closed on the bypass side. In this manner maximum heat is absorbed from the exhaust gas flow under conditions which would obviate the occurence of a steaming condition in the economizer section. As the heat energy in the exhaust gas entering the economizer rises, the water temperature at the outlet of the economizer rises until it approaches the saturation temperature of the steam drum. At this point, if nothing were done, steaming would begin to occur in lower economizer section.However, thermocouple 74 will provide a warning of such a condition when compared with the saturation temperature of the drum and cause mixing valve 60 to open thereby passing feedwater directly into the lower economizer section, bypassing the upper economizer section so that the waterexhaust gas heat transfer surface is diminished for that quantity of water which will allow the desired setpoint temperature to be maintained. In this manner the water temperature in the economizer is maintained at a level below saturation temperature so that steaming is avoided under all conditions and wherein maximum efficiency of the heat exchange process is obtained.
While there has been shown what is considered to be a preferred embodiment of the invention, other modifications may occur to those skilled in the art. It is intended to claim all such modifications as fall within the true spirit and scope of the invention.
Claims (15)
1. A noncontact, counterflow heat exchanger comprising a duct for channeliing hot gases past a plurality of fluid-carrying tubes whereby heat transfer occurs between the hot gas and fluid, said heat exchanger comprising:
an inlet heat exchange section located in the downstream direction with respect to the gas flow;
an outlet heat exchange section located in the upstream direction with respect to the gas flow; and,
means for adjusting the fluid flow between the downstream heat exchange section and the upstream heat exchange section whereby as the hot gas heat energy increases, more fluid is bypassed around the downstream heat exchange section directly into the upstream heat exchange section.
2. The heat exchanger recited in claim 1 wherein the flow adjusting means comprises:
a bypass conduit connected to the inlet end of the downstream heat exchange section; and
a valve for diverting fluid flow from the downstream heat exchange section to the upstream heat exchange section.
3. The heat exchanger recited in claim 2 further comprising a valve controller for automatically setting the flow diverting valve in accordance with the fluid temperature at the outlet of the heat exchanger.
4. The heat exchanger recited in claim 3 further comprising:
a steam drum at the outlet end of the upstream heat exchange section;
means for sensing steam drum pressure;
means for calculating a saturation temperature in accordance with the steam drum pressure;
means for sensing fluid temperature at the outlet of the heat exchanger, said valve controller providing a valve adjustment signal whereby the fluid temperature at the outlet of the heat exchanger is maintained not greater than the saturation temperature.
5. The heat exchanger recited in claim 4 further comprising an offset incorporated into the saturation temperature calculation whereby the outlet fluid temperature is less than the saturation temperature.
6. An improved heat recovery steam generator which includes a superheater, an evaporator and an economizer arranged in the direction of gas flow from upstream to downstream; wherein:
the economizer includes at least two separate but connected sections, namely a downstream economizer section, with respect to the gas flow direction, and an upstream economizer section;
a bypass connected at the inlet of the economizer for bypassing the downstream or upstream economizer; and
valve means for controlling water flow through the bypass, whereby flow is increased through the bypass as the gas flow heat content rises in the economizer.
7. The improved heat recovery steam generator as claimed in claim 6, further including a steam drum connected to said superheater, the evaporator and the economizer, and wherein
a valve controller is provided for positioning said valve means in response to the difference between the upstream economizer outlet temperature and at least the steam drum saturation temperature.
8. The improved heat recovery steam generator recited in claim 7, further comprising:
means for sensing steam drum pressure; and,
means for converting steam drum pressure into a saturation temperature.
9. The improved heat recovery steam generator as claimed in claim 6, for a combined cycle power plant comprising at least one gas turbine, one steam turbine and the heat recovery steam generator, wherein the waste heat exhaust gas in use heats feedwater into steam for driving the steam turbine, and wherein means are provided for bypassing the upper economizer section and including a bypass conduit and valve whereby feedwater may be selectively diverted from the economizer inlet to the lower economizer section; and
means for adjusting the feedwater flow through the bypass to avoid the occurence of steaming in the economizer.
10. The improved heat recovery steam generator recited in claim 9, wherein the means for adjusting the feedwater flow through the bypass include a valve connecting the bypass outlet with the junction of the two connected economizer sections.
11. The improved heat recovery steam generator recited in claim 9 further including a steam drum connected at the outlet end of the lower economizer section wherein the means for adjusting the feedwater flow through the bypass includes:
a valve connected to the bypass, the outlet end of the upper economizer and the inlet end of the lower economizer; and
means for adjusting the valve plug position in accordance with the saturation temperature of the steam drum.
12. A method of operating a noncontact counterflow heat exchanger containing watercarrying tube bundles whereby a descending fluid is heated by a duct enclosed ascending gas and wherein at least one section comprises a divided economizer section including a bypass around an upper economizer section directly into a lower economizer section whereby the heat transfer surface of the economizer may be substantially diminished; valve means for controlling fluid flow past the upper economizer section, said method comprising the steps of:
measuring the fluid temperature at the discharge end of the economizer;
determining a saturation temperature for said fluid; and
controlling the bypass flow around the upper economizer section so that the fluid temperature remains not greater than the saturation temperature.
13. A heat-exchanger according to claim 1 substantially as herein described with reference to and as shown in the accompanying drawings.
14. A heat recovery steam generator according to claim 6 or 9 substantially as herein described with reference to and as shown in the accompanying drawings.
15. A method of operating a heat exchanger according to claim 12 substantially as herein described with reference to and as shown in the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US26690581A | 1981-05-26 | 1981-05-26 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| GB2099558A true GB2099558A (en) | 1982-12-08 |
Family
ID=23016476
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB8208645A Withdrawn GB2099558A (en) | 1981-05-26 | 1982-03-24 | Heat recovery steam generator |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPS57210202A (en) |
| KR (1) | KR830010337A (en) |
| GB (1) | GB2099558A (en) |
| IT (1) | IT1150882B (en) |
| NL (1) | NL8201698A (en) |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0281151A3 (en) * | 1987-03-05 | 1990-01-17 | Babcock-Hitachi Kabushiki Kaisha | Waste heat recovery boiler |
| US4920751A (en) * | 1989-01-24 | 1990-05-01 | Pyropower Corporation | System and method for reheat steam temperature control in circulating fluidized bed boilers |
| US5038568A (en) * | 1989-11-20 | 1991-08-13 | Pyropower Corporation | System for reheat steam temperature control in circulating fluidized bed boilers |
| AT394100B (en) * | 1988-09-14 | 1992-01-27 | Sgp Va Energie Umwelt | HEAT STEAM GENERATOR |
| ES2068080A2 (en) * | 1992-05-05 | 1995-04-01 | Ae Sociedad Anonima | Improvements to systems for generating steam (vapour) by recovery |
| US5605118A (en) * | 1994-11-15 | 1997-02-25 | Tampella Power Corporation | Method and system for reheat temperature control |
| EP1162348A3 (en) * | 2000-06-06 | 2004-06-09 | Kabushiki Kaisha Toshiba | Combined cycle power plant |
| WO2009106563A3 (en) * | 2008-02-26 | 2010-11-11 | Alstom Technology Ltd | Method for regulating a boiler and control circuit for a boiler |
| AT512176A4 (en) * | 2012-05-31 | 2013-06-15 | Siemens Ag Oesterreich | heat recovery steam generator |
| CN103438422A (en) * | 2013-08-01 | 2013-12-11 | 中山市多创电器设备有限公司 | Small-sized multi-pass flue high-efficiency gas-fired steam generator |
| WO2015165668A1 (en) * | 2014-04-28 | 2015-11-05 | Alstom Technology Ltd | System and method for fluid medium preheating |
| WO2016096847A1 (en) * | 2014-12-19 | 2016-06-23 | Alstom Technology Ltd | System and method for fluid medium preheating |
| JP2019007704A (en) * | 2017-06-27 | 2019-01-17 | 川崎重工業株式会社 | Waste heat boiler and waste heat recovery system |
| US11892160B1 (en) * | 2022-09-01 | 2024-02-06 | Hrst, Inc. | System to achieve full combustion turbine load in HRSG limited combined cycle plants |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58214702A (en) * | 1982-06-09 | 1983-12-14 | 三井造船株式会社 | Method and device for operating waste-heat recovery device |
| EP0147407B1 (en) * | 1983-05-23 | 1988-06-01 | Solar Turbines Incorporated | Steam generator control systems |
| US5361827A (en) * | 1992-12-29 | 1994-11-08 | Combustion Engineering, Inc. | Economizer system for vapor generation apparatus |
| DE10117989C1 (en) * | 2001-04-10 | 2002-05-23 | Alstom Power Energy Recovery Gmbh | Steam creating system, for heating by exhaust gas, has two or more water/steam circuits, each with at least one evaporator device |
-
1982
- 1982-03-24 GB GB8208645A patent/GB2099558A/en not_active Withdrawn
- 1982-04-23 IT IT20898/82A patent/IT1150882B/en active
- 1982-04-23 NL NL8201698A patent/NL8201698A/en not_active Application Discontinuation
- 1982-05-25 KR KR1019820002309A patent/KR830010337A/en not_active Withdrawn
- 1982-05-26 JP JP57088161A patent/JPS57210202A/en active Pending
Cited By (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0281151A3 (en) * | 1987-03-05 | 1990-01-17 | Babcock-Hitachi Kabushiki Kaisha | Waste heat recovery boiler |
| AT394100B (en) * | 1988-09-14 | 1992-01-27 | Sgp Va Energie Umwelt | HEAT STEAM GENERATOR |
| US4920751A (en) * | 1989-01-24 | 1990-05-01 | Pyropower Corporation | System and method for reheat steam temperature control in circulating fluidized bed boilers |
| US5038568A (en) * | 1989-11-20 | 1991-08-13 | Pyropower Corporation | System for reheat steam temperature control in circulating fluidized bed boilers |
| ES2068080A2 (en) * | 1992-05-05 | 1995-04-01 | Ae Sociedad Anonima | Improvements to systems for generating steam (vapour) by recovery |
| US5605118A (en) * | 1994-11-15 | 1997-02-25 | Tampella Power Corporation | Method and system for reheat temperature control |
| EP1162348A3 (en) * | 2000-06-06 | 2004-06-09 | Kabushiki Kaisha Toshiba | Combined cycle power plant |
| US10167743B2 (en) | 2008-02-26 | 2019-01-01 | General Electric Technology Gmbh | Method for controlling a steam generator and control circuit for a steam generator |
| WO2009106563A3 (en) * | 2008-02-26 | 2010-11-11 | Alstom Technology Ltd | Method for regulating a boiler and control circuit for a boiler |
| AT512176A4 (en) * | 2012-05-31 | 2013-06-15 | Siemens Ag Oesterreich | heat recovery steam generator |
| AT512176B1 (en) * | 2012-05-31 | 2013-06-15 | Siemens Ag Oesterreich | heat recovery steam generator |
| CN103438422A (en) * | 2013-08-01 | 2013-12-11 | 中山市多创电器设备有限公司 | Small-sized multi-pass flue high-efficiency gas-fired steam generator |
| WO2015165668A1 (en) * | 2014-04-28 | 2015-11-05 | Alstom Technology Ltd | System and method for fluid medium preheating |
| JP2017514097A (en) * | 2014-04-28 | 2017-06-01 | ゼネラル エレクトリック テクノロジー ゲゼルシャフト ミット ベシュレンクテル ハフツングＧｅｎｅｒａｌ Ｅｌｅｃｔｒｉｃ Ｔｅｃｈｎｏｌｏｇｙ ＧｍｂＨ | Fluid medium preheating system |
| US10393369B2 (en) | 2014-04-28 | 2019-08-27 | General Electric Company | System and method for fluid medium preheating |
| WO2016096847A1 (en) * | 2014-12-19 | 2016-06-23 | Alstom Technology Ltd | System and method for fluid medium preheating |
| CN107110488A (en) * | 2014-12-19 | 2017-08-29 | 通用电器技术有限公司 | Feed water preheating system bypass |
| CN107110488B (en) * | 2014-12-19 | 2020-10-16 | 通用电器技术有限公司 | Feed water preheating system bypass |
| JP2019007704A (en) * | 2017-06-27 | 2019-01-17 | 川崎重工業株式会社 | Waste heat boiler and waste heat recovery system |
| US11892160B1 (en) * | 2022-09-01 | 2024-02-06 | Hrst, Inc. | System to achieve full combustion turbine load in HRSG limited combined cycle plants |
Also Published As
| Publication number | Publication date |
|---|---|
| IT1150882B (en) | 1986-12-17 |
| JPS57210202A (en) | 1982-12-23 |
| NL8201698A (en) | 1982-12-16 |
| KR830010337A (en) | 1983-12-30 |
| IT8220898A0 (en) | 1982-04-23 |
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