Multiple pass economizer and method for SCR temperature control

Abstract

A control system for maintaining a desired heat exchanger outlet flue gas temperature across a range of boiler loads. The heat exchanger includes a plurality of tubular configurations in heat exchange contact with the flue gas with each tubular configuration having a separate feedwater inlet. Flue gas temperature control is achieved by modulating the feedwater flow rates through the tubular configurations. In a system having two tubular configurations, the overall heat transfer capacity of the heat exchanger may be reduced to maintain the desired heat exchanger outlet flue gas temperature by reducing feedwater flow through one tubular configuration and overflowing the other, while maintaining the total flow of feedwater through the heat exchanger substantially constant.

Description

FIELD AND BACKGROUND OF THE INVENTION

The present invention relates generally to the field of Selective Catalyst Reactor (SCR) temperature control and in particular to a system and method for maintaining the combustion or flue gas entering the SCR system at or above the optimal catalytic reaction temperature, even when operating the boiler at reduced loads.

In operating a boiler with a Selective Catalyst Reactor (SCR) system, the effectiveness of the SCR is dependant upon the flue gas temperature entering the catalyst reactor. Most can operate within a temperature range of about 450 degrees F. to about 840 degrees F. Optimum performance may typically occur between about 570 degrees F. to about 750 degrees F. Typically, the desired gas temperature entering the SCR is about 580 degrees F. or greater. At a temperature of about 580 degrees F., the reaction of ammonia with NOx is optimized and the amount of the ammonia needed for the catalytic reaction is minimized. Therefore, for economic reasons the desired gas temperature entering the catalyst reactor should be maintained within the optimum temperature range of about 570 degrees F. to about 750 degrees F. at all loads.

However, as boiler load varies, the boiler exit gas temperature will drop below the optimal temperature of about 580 degrees F. To increase the gas temperature to about 580 degrees F., current practice has been to use an economizer gas bypass. The economizer gas bypass is used to mix the hotter gases upstream of the economizer with the cooler gas that leaves the economizer. By controlling the amount gas through the bypass system, a boiler exit flue gas temperature of about 580 degrees F. can be maintained at lower boiler loads.

With this approach, static mixing devices, pressure reducing vanes/plates and thermal mixing devices are required to make the different temperature flue gases mix before the gas mixture reaches the inlet of the catalytic reactor. In most applications, obtaining the strict mixing requirements for flow, temperature and the mixing of the ammonia before the catalyst reactor is often difficult.

In another approach to dealing with decreasing flue gas temperature entering a SCR reactor at reduced boiler loads, an economizer was fitted with a feedwater bypass to partially divert the feedwater away from the economizer in order to maintain the flue gas temperature.

Additional details of SCR systems for NOx removal are provided in Chapter 34 of Steam/its generation and use, 41^st Edition, Kitto and Stultz, Eds., Copyright® 2005, The Babcock & Wilcox Company, the text of which is hereby incorporated by reference as though fully set forth herein. Flue gas temperature control using conventional economizers are described in U.S. Pat. No. 7,021,248 to McNertney, Jr. et al. and U.S. Pat. No. 6,609,483 to Albrecht et al., the texts of which are hereby incorporated by reference as though fully set forth herein.

SUMMARY OF THE INVENTION

It is an object of the present invention to provide a system and method for increasing the outlet temperature of flue gas passing through the economizer by reducing the water flow in selected tubes and/or sections of the economizer without the need to divert feedwater away from the economizer. When these selected tubes or sections are reduced in flow, the remaining sections or tubes in the economizer are overflowed so that the total flow is maintained through the economizer. To increase the economizer gas outlet temperature, a certain percentage of the tubes in the economizer will have their heat transfer reduced by decreasing the flow through these tubes. The increase in water flow in the remaining tubes has a minimal effect on the heat transfer of the remaining tubes, resulting in an overall decrease in the total gas side heat transfer of the economizer and as a result increases the gas outlet temperature from the economizer.

It is another object of the present invention to provide a system and a method for maintaining a desired economizer outlet gas temperature across a range of boiler loads by providing two or more sections or compartments of liquid-cooled heat transfer surfaces or tubes in the flow path of the flue gas, wherein the flow rate of each section or compartment is controlled independently of the other sections or compartments, determining the flow rate that is required in each section or compartment in order to produce a combined/overall heat transfer capacity sufficient to maintain the desired economizer outlet gas temperature, and adjusting of the flow rate of each section or compartment of the economizer.

In one aspect, the system is configured to maintain the flue gas entering a catalytic reactor within a desired temperature range that will promote optimal catalytic reaction, irrespective of the boiler load. Preferably, the flue gas temperature is maintained within a range of about 570 degrees F. to about 750 degrees F., preferably about 580 degrees F. In a normal boiler application, the water side of the economizer is used to cool the flue gas that flows over the surface that is installed in the boiler. The system of the present invention separates the heat transfer surfaces of the economizer to increase the outlet temperature of the flue gases to the desired temperature of about 570 degrees F. to about 750 degrees F., preferably, 580 degrees F. at lower boiler loads. This is accomplished by selectively changing the flow rates through different portions of the economizer. By determining the proper amounts and locations of the heating surface, the desired economizer outlet gas temperature can be maintained within the desired temperature range or at a desired temperature across the desired steam generator load range through the control of the flow rates of water through the different sections of the economizer.

It is a further object of the present invention to provide a system for maintaining a flue or combustion gas stream being directed into downstream device such as an SCR assembly within a desired temperature range or at a desired (e.g., optimal) temperature comprising: an economizer located upstream of and in fluid communication with the SCR assembly, wherein the economizer comprises at least two tubular configurations having different heat transfer characteristics, disposed in a cross and or counter-current heat exchange relationship with the flow path of the gas stream generated by a boiler and having a flue inlet and a flue outlet, the boiler being located upstream of and in fluid communication with the economizer, each tubular configuration comprises a feedwater inlet and a feedwater outlet, the outlet of both tubular configurations being attached to an outlet header and the inlet of each tubular configuration being attached to a separate inlet header, and a control system configured to independently control the flow of feedwater through each tubular configuration while maintaining a substantially constant total flow of feedwater through the economizer, the flow of feedwater through each tubular configuration is adjusted in a manner that transfers an appropriate amount of heat from the gas stream to maintain the gas stream at the desired optimal temperature.

It is a further object of the present invention to provide a method of maintaining a gas stream being directed into a downstream device such as an SCR assembly within a desired temperature range or at a desired (e.g., optimal) temperature, the SCR assembly being located downstream of and in fluid communication with an economizer, the method comprising disposing, within the economizer, at least two tubular configurations in a cross and or counter-current heat exchange relationship with the flow path of the gas stream, the economizer having a flue inlet and a flue outlet, each tubular configuration comprises a feed water inlet and a feed water outlet, the outlet of both tubular configurations being attached to an outlet header and the inlet of each tubular configuration being attached to a separate inlet header, monitoring the gas temperature at the flue inlet or flue outlet, the feedwater temperature at the feedwater inlet and outlet, and the flow of feedwater through the economizer, controlling the flow of feedwater conveyed through each tubular configuration, based on the measured temperatures and flow, to provide the tubular configurations with a combined heat transfer capacity that is effective to maintain the gas temperature at the desired level, wherein the heat transfer capacity of the tubular configurations is decreased by increasing the flow of feedwater through at least one of the tubular configurations and by reducing the flow of feedwater through the other tubular configurations.

While the present invention is particularly suited to maintaining a desired flue gas temperature entering a downstream SCR device, it will be appreciated that the invention may be used to maintain a desired gas temperature which may required by other types of downstream devices, and for other purposes. One type of downstream device could be an air heater which typically uses the heat in the flue gas leaving the steam generator to heat the incoming air for combustion. In some cases it is desirable to control the flue gas temperature entering the air heater within a desired range or at a desired temperature above the acid dew point temperature, such as during low load operation, to reduce the possibility of condensation occurring which could form acidic compounds which could lead to corrosion of the air heater. Other types of downstream devices include various types of pollution control equipment; e.g., particulate removal devices such as electrostatic precipitators or fabric filters, and flue gas desulfurization devices such as wet or dry flue gas desulfurization equipment.

The various features of novelty which characterize the invention are pointed out with particularity in the claims annexed to and forming a part of this disclosure. For a better understanding of the invention, its operating advantages and specific objects attained by its uses, reference is made to the accompanying drawings and descriptive matter in which a preferred embodiment of the invention is illustrated.

BRIEF DESCRIPTION OF THE DRAWINGS

In the drawings:

FIG. 1 is a schematic of a gas temperature control system according to a first embodiment of the present invention;

FIG. 2 is a schematic of an embodiment of the present invention showing two tubular configurations positioned adjacent one another in a non-overlapping relationship;

FIG. 3 is a schematic of an embodiment of the present invention showing three tubular configurations positioned adjacent one another in a non-overlapping relationship;

FIG. 4 is a schematic of an embodiment of the present invention showing application of the invention to a parallel gas path convection pass design;

FIG. 5 is a schematic of an embodiment of the present invention showing application of the invention to a longitudinal flow economizer, where the concept is applied to control the flow to individual panels of tubes forming the economizer;

FIG. 6 is a schematic rear view looking into the convection pass of FIG. 5;

FIG. 7 is a schematic view illustrating a partial rear view of the tubes in the serpentine arrangement of FIG. 1 to show the variations in fluid flow and flue gas temperature resulting therefrom;

FIGS. 8 and 9 are schematic views illustrating a partial rear view of the tubes in a serpentine arrangement similar to that shown in FIG. 1 to show how variations in economizer outlet fluid temperature due to the variations in fluid flow and flue gas temperature can be accommodated in the outlet headers and supporting stringer tubes; and

FIGS. 10 and 11 are schematic views of a control system as applied to the present invention.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

Referring now to the drawings, in which like reference numerals are used to refer to the same or functionally similar elements, FIG. 1 shows an economizer 3 for receiving flue gas generated by a boiler (not shown), located upstream of and in fluid communication with the economizer 3. As used in the present application and as is known to those skilled in the art, the term boiler is used herein to broadly refer to apparatus used for generating steam and may include both drum-type boilers and those of the once-through type. For a general description of such types of boilers or steam generators, the reader is referred to the aforementioned STEAM 41^st reference, particularly the Introduction and Selected color plates, and Chapters 19, 20, and 26, the text of which is hereby incorporated by reference as though fully set forth herein. The economizer 3 includes a flue inlet and a flue outlet, and is located in a convection pass 13 upstream of and in fluid communication with a Selective Catalytic Reactor (SCR) assembly (not shown). Within the economizer 3, there is arranged two or more tubular configurations 1, 2 for providing modular heat transfer surfaces for recovery or extraction of heat from the flue gas. The tubular configurations 1, 2 are preferably disposed in a cross and or counter-current heat exchange relationship with respect to the flow path 14 of the flue gas. It is also contemplated that the tubular configurations may be disposed in a cross and or co-current heat exchange relationship with the flow path 14 of the flue gas.

Each tubular configuration 1, 2 is attached on one end to an inlet header 11, and on the other end, the tubular configurations 1, 2 may each be connected to a separate (not shown) or to a common outlet header 12, which is supported by stringer tubes S. A feedwater line 15 is connected to each inlet header 11, and on each feedwater line 15 there is preferably provided a control valve 5. Each feedwater line 15 may also include a bypass line 7 installed around the control valve 5 for cleaning or flushing the feedwater lines 15 or the tubular configurations 1, 2, or for performing maintenance on the control valve 5. The feedwater lines 15 are connected to the main feedwater line 16 through a distributor 8. While individual sets of control valve 5 and bypass valve 7 may be installed on each feedwater line 15, it will be appreciated that a single control valve 5, bypass line 7 “pair” which is installed in only one feedwater line 15 may be required. The provision of a control valve 5, bypass line 7 pair on all feedwater lines 15 ensures optimum control of the flow through each of the tubular configurations 1, 2, and may be particularly useful at lower boiler loads, but this degree of sophistication and control may not be required in all applications.

In one embodiment, each tubular configuration 1, 2 comprises a plurality of serpentine or stringer tubes arranged horizontally or vertically back and forth within the economizer 3. The tubes in one tubular configuration may be positioned in an offset relationship with respect to the tubes of the other tubular configuration. The tubes may be offset vertically, horizontally, diagonally, or longitudinally or offset in a combination of two or more such orientations. Preferably, the tubular configurations 1, 2 are positioned adjacent to one another in the convection pass 13 in an overlapping or non-overlapping relationship, and extend or expand substantially along a flow path 14 of the flue gas passing across the economizer 3. In an alternate embodiment, the heat transfer capacity of each tubular configuration is not identical. It will also be appreciated that the tubes forming the tubular configurations 1, 2 may or may not employ extended surface such as fins to achieve a desired amount of heat transfer to the feedwater flowing through the economizer 3.

An existing economizer 3 can be modified or retrofitted according to the present invention, such that a selected tubular configuration is fed with sufficient feedwater to effectively reduce the overall heat transfer capacity of the economizer 3. The remaining feedwater is circulated into the remaining tubes in the other tubular configuration. The tubes in the selected tubular configuration would receive more than the normal flow which will slightly increase the heat transfer of this tubular configuration. Also, by determining the appropriate quantity of tubes for each tubular configuration or economizer bank, the effective heat transfer of the economizer 3 can be reduced so that the desired economizer outlet gas temperature is obtained. In FIG. 1, the stringer tubes S that are used to support convective superheat heat transfer surface (not shown; located above the economizer 3) are shown. In most cases, these stringer tubes S will require the full flow from the economizer 3 because the gas temperatures increase in the upper regions of the convection pass and the need for cooling would be greater for these stringer tubes S to meet the stress requirement for supporting these additional heat transfer surfaces.

The temperature monitoring required to adjust the proportioning values of the system can be monitored by knowing the outlet gas temperature or by knowing the inlet gas temperature along with the water side temperatures, both inlet and outlet, and the water side fluid flow through the system. Preferably, temperature and flow rate monitoring, and adjustment of the flow rate in each tubular configuration or economizer bank are carried out by a controller 9.

In operation, temperature sensors are provided at the flue inlet and/or at the flue outlet 4, at the feedwater inlet and at the feedwater outlet. A flow meter (not shown) is also provided for the main feedwater line to measure the economizer 3 fluid flow through the system. The temperature sensors and flow meter are in signal communication 10 with controller 9 and are calibrated to transmit measurements to the controller 9 for the feedback control of the flow of feedwater through each tubular configuration 1, 2.

For example, when the controller 9 detects a drop in the boiler load or in the gas temperature at the economizer flue inlet or outlet, the flow of feedwater through each tubular configuration is adjusted to reduce the combined heat transfer capacity of the economizer. This can be achieved by increasing the flow of feedwater through one tubular configuration to decrease the flow and heat transfer of the other tubular configuration.

FIG. 2 shows the tubular configurations in the economizer positioned adjacent one another in a non-overlapping relationship. The heat transfer of the overall economizer system can be reduced and the desired outlet gas temperature can be obtained by changing the flow rates in the adjacent tubular configurations 1′, 2′. In both embodiments, the two different water pathways through the economizer have two different heat transfer characteristics. For example the tube or pathway 1′ in FIG. 2 is shorter than the tube 2′. In the embodiment of FIG. 1, the tubes may have different heat transfer characteristic due to different surface treatments of the tubes, different diameters of the tubes, different placement in the gas flow path or different lengths.

FIG. 3 is a schematic of an embodiment of the present invention showing three tubular configurations positioned adjacent one another in a non-overlapping relationship, and is otherwise similar in concept and operation to FIG. 2. This concept may be particularly useful for controlling gas temperature to prevent it from falling below the acid dew point temperature at which condensation may begin to occur, reducing the possibility of condensation occurring which could form acidic compounds that can corrode downstream devices such as air heaters. Again, while each feedwater line 15 may also include a bypass line 7 installed around its associated control valve 5 for cleaning or flushing the feedwater lines 15 or the tubular configurations 1, 2, or for performing maintenance on the control valve 5, it will be appreciated that a control valve 5, bypass line 7 “pair” does not need to be installed in each feedwater line 15; in a three tubular configuration arrangement, a control valve 5, bypass line 7 pair need only be supplied on two of the three tubular configurations. This arrangement may again be particularly useful at lower boiler loads, depending upon the degree of control desired.

In addition, under certain low flow conditions, it may be necessary to provide orifice means at one or both of the inlets and outlets of individual tubes in a given tubular configuration to provide additional pressure drop for flow stability in these tubes. Orificing these tubes, particularly the lower velocity flow paths, provides additional pressure drop which will tend to equalize the flow distribution between each of the tubes in that tubular configuration.

FIG. 4 illustrates application of the principles of the present invention to a parallel gas path convection pass design. The parallel gas paths in the convection pass 20 are established by a baffle 22 as is known to those skilled in the art. As shown therein, the economizer 3 may have a lower portion which extends across both of the parallel gas paths, while an upper portion may reside only in a single one of the parallel gas paths. Opposite the upper portion of the economizer 3, in the other gas path, may be provided steam cooled surface, such as superheater or reheater surface 24. The baffle 22 may or may not extend into the lower portion of the economizer 3, and may be steam or water cooled surface depending upon the flue gas temperatures.

FIGS. 5 and 6 are drawn to an embodiment of the present invention as applied to a longitudinal flow economizer, where the concept is applied to control the flow to individual panels 26 of tubes forming the economizer 3. The individual panels 26 of tubes are provided with panel inlet headers 28 and panel outlet headers 30. Feedwater from the economizer inlet headers 11 are fed to the panel inlet headers 28 by means of supply tubes 32. Feedwater flow through the panels 26 and is collected at the panel outlet headers 30. Feedwater is then conveyed from the panel outlet headers 30 via riser tubes 34 to the economizer outlet header 12.

FIG. 6 is a schematic rear view looking into the convection pass of FIG. 5, viewed in the direction of arrows 6-6 of FIG. 5. It is understood that while two tubular panel configurations 1, 2 are shown, an additional third tubular panel configuration flow path could be employed as well.

FIG. 7 is a schematic view illustrating a partial rear view of the tubes in the serpentine arrangement of FIG. 1 to show the variations in fluid flow and flue gas temperature resulting therefrom. The tubes comprising flow path 1 (higher velocity economizer fluid) are denoted by solid dark circles, while the tubes comprising flow path 2 (lower velocity economizer fluid) are denoted by open circles. The higher velocity economizer fluid tubes extract more heat from the flue gas passing across these tubes, and as a result the flue gas temperature leaving these banks of tubes is lower than the flue gas temperature leaving those banks of tubes which have a lower economizer fluid flow therethrough.

FIGS. 8 and 9 are schematic views illustrating a partial rear view of the tubes in a serpentine arrangement similar to that shown in FIG. 1 to show how the variations in economizer 3 outlet fluid temperatures due to the variations in fluid flow and flue gas temperature can be accommodated in outlet headers 12, 12′ and supporting stringer tubes S. As before, the tubes comprising flow path 1 (higher velocity economizer fluid) are denoted by solid dark circles, while the tubes comprising flow path 2 (lower velocity economizer fluid) are denoted by open circles. In some economizer arrangements, the economizer outlet header may be a continuous header 12, with a single common interior portion, where feedwater heated by the various tubular configurations in the economizer 3 is collected and then dispersed via the stringer tubes S. While theoretically the economizer feedwater may travel anywhere along the length of this outlet header 12, in practice the feedwater travels the shortest route from the tubular configurations feeding the outlet header 12 into the nearest adjacent stringer tubes S. This type of economizer outlet header is schematically illustrated in FIG. 8. In other types of economizer arrangements, the economizer outlet header may be formed of a plurality of separate, shorter headers which are then field girth welded together at their ends E to make the entire economizer outlet header. In this type of economizer outlet header, designated 12′ and schematically illustrated in FIG. 9, the feedwater can only be conveyed into and out of the interior portions of each separate header, the ends E of each header preventing fluid flow into adjacent separate headers. It will thus be appreciated that fewer tubular configurations supply feedwater to these separate headers and fewer stringer support tubes S convey feedwater from these separate headers. Significant temperature differences between the temperature of the fluid within the stringer tubes S are to be avoided since such temperature differences can lead to differential thermal expansion of the stringer tubes S. In order to encourage mixing of the hotter and cooler feedwater fluids entering either type of economizer header 12 or 12′, a baffle means B may be employed to encourage mixing of the hotter and cooler feedwater streams within the headers 12, 12′ prior to the feedwater exiting into the stringer support tubes S, thereby equalizing the temperatures within the stringer tubes S. The baffle means B may be a simple plate located to cause the feedwater flow to divert as desired, or it may be a more complex structure such as a perforated plate with holes sized and/or spaced in a particular configuration.

While two types of economizer outlet headers 12, 12′ are shown in FIGS. 8 and 9 it will be appreciated that only one type of economizer outlet header, 12 or 12′, would typically be employed for an economizer in a given steam generator. Similarly, while the earlier Figs. have employed the reference numeral 12 for the outlet header, it will be appreciated that either type of header 12 or 12′ may be employed in all of these embodiments.

As discussed earlier, the present invention is particularly suited to maintaining a desired flue gas temperature entering a downstream SCR device. However, it will be appreciated that the invention may be used to maintain a desired gas temperature which may required by other types of downstream devices, and for other purposes. One type of downstream device could be an air heater which typically uses the heat in the flue gas leaving the steam generator to heat the incoming air for combustion. In some cases it is desirable to control the flue gas temperature entering the air heater within a desired range or at a desired temperature above the acid dew point temperature, such as during low load operation, to reduce the possibility of condensation occurring which could form acidic compounds which could lead to corrosion of the air heater. Other types of downstream devices include various types of pollution control equipment; e.g., particulate removal devices such as electrostatic precipitators or fabric filters, and flue gas desulfurization devices such as wet or dry flue gas desulfurization equipment.

In the case of the present invention, and as particularly applied to apparatus and methods for controlling the temperature of flue gas temperature exiting from an economizer, it will be appreciated that economizer gas outlet and/or gas inlet temperatures may be used to control the water flow rate through portions of the heat exchanger for the purpose of affecting the temperature of the flue gas after it has passed across the heat exchanger or economizer. However, due to the low flow rates which may be required for obtaining the desired outlet flue gas temperature, such a flue gas temperature control system may not provide a very quick response with respect to the boiler's capabilities for load control and operation, particularly when there is a large difference between the feedwater rates for the different passes through the economizer or heat exchanger.

Accordingly, another aspect of the present invention involves a control system and operation method which can accommodate such operating conditions. The system and method is not only applicable to the present invention but also to other heat exchanger systems that control the flow through different portions of a heat exchanger to achieve a desired flue gas temperature exiting from the heat exchanger.

FIGS. 10 and 11 illustrate the application of this concept to two different water proportioning or biasing systems. As illustrated in FIGS. 10 and 11, the present invention uses the feedwater flow rate entering the economizer to engage/disengage the economizer water internal proportion or bias system. Once engaged, the measured feedwater flow to the economizer is used to generate a proportioned or biased flow rate demand signal. The demand signal is then compared to the measured underflow proportioned or biased flow rate. If there is a difference between the demand signal flow rate and the measured flow rate, the control valve(s) modulating the proportioned or biased flow is/are adjusted.

More particularly, referring to FIG. 10, there is shown the application of the principles of the present invention to an embodiment of the present invention. In this case, feedwater is provided via main feedwater line 16 to the individual tubular configuration flow paths 1, 2 making up the economizer 3 via feedwater lines 15. A flow element FE 50 provided in line 16 produces a measured feedwater flow signal which is conveyed to a high/low limiter unit 52 and to a demand signal generator unit 54. The demand signal generator unit 54 produces a proportioned or biased flow rate demand signal, here an underflow rate demand signal, which is based upon the measured feedwater flow entering the economizer 3. This underflow rate demand signal is then conveyed to flow controller with bias unit 56. Flow controller with bias unit 56 also receives an actual measured underflow rate from flow element FE 58, indicative of the flow rate through the tubular configuration 1. Flow controller with bias unit 56 compares the underflow rate demand signal from unit 54 with the actual measured underflow rate from flow element FE 58, and produces a control valve signal which is conveyed to control valve 5 to modulate the feedwater flow through tubular configuration 1. The control valve signal from unit 56 is also conveyed to a signal inverter unit 60, and an inverted control valve signal is conveyed to the other control valve 5 to modulate the feedwater flow through tubular configuration 2. Since the unit 56 is a flow controller with bias capability, changes can easily be made to adjust the underflow rate demand signal in order to accommodate actual field performance; i.e., to adjust the flow splits between tubular configurations 1 and 2, in order to achieve a desired flue gas temperature exiting the economizer and entering the downstream device, such as an SCR.

The demand signal generator unit 54 may generate the underflow rate demand signal in any manner known to those skilled in the art; lookup tables, calculations according to a predetermined equation(s) of underflow rate demand as a function of boiler load, etc. The demand signal generator unit 54 may also include a plurality of such tables or equations corresponding to different fuel types to be burned in the boiler.

The high/low limiter unit 52 receives the measured feedwater flow signal from flow element FE 50 and produces a high/low limit signal which is provided to block valve 62, located in the feedwater line 15 flow path supplying feedwater to tubular configuration 1. The high/low limiter is designed to position the block valve 62 at a specific open position, depending upon the boiler load as indicated by the boiler measured feedwater flow signal. For example, assume a boiler with a nominal megawatt (MW) capacity of 600 MW. The boiler operation may be considered to fall into one of three operating ranges: 0-200 MW, 200-400 MW, and 400-600 MW, and these ranges will determine the manner of operation of the control system of the multiple pass economizer according to the present invention.

In the 0-200 MW operating range, both the block valve 62 and the control valve 5 in the flow path supplying the tubular configuration 1 would normally be open. In the 200-400 MW operating range, the flue gas temperatures leaving the economizer 3 have increased over those experienced in the 0-200 MW range, but are typically not yet high enough to permit proper SCR operation. Thus, the principles of the present invention are employed; the block valve 62 would be closed to a specific setting in this case to provide additional flow resistance to tubular configuration 1, thereby allowing the control valves 5 to operate with more flexibility to modulate the feedwater flow through both tubular configurations 1, 2, and the flue gas temperature leaving the economizer 3 increases to a desired value. As boiler megawatt load continues to increase, into the 400-600 MW operating range, the feedwater modulating principles of the present invention can be gradually “phased out” and the control valves 5 can be opened wide and the block valve 62 can be opened in such a manner to obtain balance flow conditions in both tubular configurations 1, 2, since the flue gas temperature exiting from the economizer 3 is above the desired minimum value. While three, equally sized operating “ranges” have been described, unequal operating ranges may be employed. The general idea is that there are typically lower boiler operating ranges where the principles of the invention are generally not applied, an intermediate operating range where the invention is primarily used, and an upper boiler operating range where the principles of the present invention are not required and thus modulation of the control valves is gradually phased out because the flue gas temperatures are above the desired minimum levels.

Turning now to FIG. 11, there is shown the application of the principles of the present invention to another embodiment which is quite similar to the one disclosed in FIG. 10. In this case, one fundamental difference is that instead of two control valves 5 in each of the feedwater flow paths 15 supplying feedwater to tubular configurations 1, 2, there is only a single control valve 5 present and which is modulated to control feedwater flow through a single tubular configuration; in this case, tubular configuration 2 (but which alternatively could have been tubular configuration 1, if desired). Another difference involves that fact that the single control valve 5 and the block valve 62 are located in parallel flow paths, rather than being in series with one another as in FIG. 10. Also, the block valve 62 in FIG. 11 could be operated in various conditions, fully open, partially open or fully closed, since the control valve 5 provides a flow path around block valve 62. Otherwise, the principles of operation are the same as in FIG. 10. Measured feedwater flow to the economizer 3 is used to generate a proportioned or biased flow rate demand signal at unit 54. The demand signal is then conveyed to the flow controller with bias unit 56 where it is compared to the measured underflow proportioned or biased flow rate from flow element FE 58. If there is a difference between the demand signal flow rate and the measured flow rate, the control valve 5 modulating the proportioned or biased flow is adjusted. Bias is applied as required to tune the performance of the system.

While the control system described above and with particular reference to FIGS. 10 and 11 can be used without reference to any measured flue gas temperatures, it is envisioned that a combination of the two approaches can be employed. That is, the measured feedwater flow to the economizer 3 can be used to generate a proportioned or biased flow rate demand signal at unit 54, and establish an initial flow rate. Then, a temperature measurement, such as the flue gas leaving the economizer, can then be used as a check or as a trim value to “fine tune” the positions of the control valve(s) 5.

It will thus be appreciated that the control system and operation method is particularly suited to operating conditions, such as low boiler load conditions, where the major portion of the water flow to the economizer must be proportioned or biased to meet the desired or target flue gas outlet temperature. The normal method of using outlet gas temperature to control water flow is not effective when a major amount of the water is proportioned or biased because the residence time of the water flowing through the (underflow section of the) economizer heating surface can no longer be measured in seconds or several minutes but stretches to almost an hour. This lengthy residence time in turn lengthens the time it takes to effectively make a change in gas temperature to the point that gas temperature can no longer be used to control the proportioned or biased water flow rate.

The advantage of the invention is that it allows systems which proportion or biased water flow rate in the economizer sections for the purpose of raising exiting gas temperature to be effective at lower boiler loads than can be achieved by a system which uses outlet gas temperature to control the feedwater proportioning or biased water flow rate. This allows an SCR located downstream of the boiler, if the boiler is so equipped, to continue to operate at lower boiler loads than previously possible using this type of system.

While specific embodiments of the invention have been shown and described in detail to illustrate the application of the principles of the invention, it will be understood that the invention may be embodied otherwise without departing from such principles. For example, the present invention may be applied to new boiler or steam generator construction involving selective catalytic reactors or other types of downstream devices, or to the replacement, repair or modification of existing boilers or steam generators where selective catalytic reactors or other types of downstream devices and related equipment are or have been installed as a retrofit. In some embodiments of the invention, certain features of the invention may sometimes be used to advantage without a corresponding use of the other features. Accordingly, all such changes and embodiments properly fall within the scope of the following claims.

Claims

1. A system for sourcing a heated flue gas stream, directing the gas stream through a downstream device and maintain the gas stream entering the device within a desired temperature range or at a desired temperature, comprising: a heat exchanger located upstream gas flow-wise of the device,the heat exchanger having a flue gas inlet and a flue gas outlet and at least two tubular configurations disposed in a cross and/or counter-current heat exchange relationship with the flow path of the flue gas stream,the heated flue gas source being located upstream gas flow-wise of the heat exchanger,each tubular configuration having a feedwater inlet and a feedwater outlet, the outlet of both tubular configurations being attached to a separate or common outlet header and the inlet of each tubular configuration being attached to a separate inlet header,a control system configured to independently control the flow of feedwater through each tubular configuration while maintaining a substantially constant total flow of feedwater through the heat exchanger,a demand signal generator means for generating a proportioned or biased flow rate demand signal as a function of measured feedwater flow to the heat exchanger and fuel type used in the heated flue gas source,means for comparing a measured flow rate in at least one of the tubular configurations to the proportioned or biased flow rate demand signal, means for determining if there is a difference between the demand signal flow rate and the measured flow rate, and control valve means being responsive to said difference for modulating the flow of feedwater through at least one of the tubular configurations, andwherein the flow of feedwater through each tubular configuration is adjusted in a manner that transfers an appropriate amount of heat from the flue gas stream to maintain the flue gas stream entering the device within the desired temperature range or at the desired temperature.

2. The system of claim 1, wherein the control system determines whether to control the flow of feedwater through each tubular configuration while maintaining a substantially constant total flow of feedwater through the heat exchanger to transfer an appropriate amount of heat from the gas stream to maintain the gas stream within the desired temperature range or at the desired temperature based upon whether the heated flue gas source is in a lower, intermediate or upper operating range.

3. The system of claim 1, wherein the heated gas source is a boiler.

4. A system for sourcing and passing a heated flue gas stream through a heat exchanger and through a device located downstream gas flow-wise of the heat exchanger and means for controlling the flow of feedwater through at least a first and a second tubular configuration of the heat exchanger to maintain the flue gas stream entering the device within a desired temperature range or at a desired temperature, the control means comprising: a first flow element for producing a measured feedwater flow signal indicative of the actual feedwater flow rate entering the heat exchanger;a demand signal generator for receiving the measured feedwater flow signal and producing a proportioned or biased underflow rate demand signal based upon the measured feedwater flow rate entering the heat exchanger;a second flow element for producing an actual measured underflow rate indicative of the feedwater flow rate through the first tubular configuration;a controller with bias unit for receiving and comparing the underflow rate demand signal and the actual measured underflow flow rate, and producing a control valve signal;a first control valve for receiving the control valve signal to modulate the feedwater flow through the first tubular configuration;a signal inverter unit for receiving the control valve signal, and producing an inverted control valve signal;a second control valve for receiving the inverted control valve signal to modulate the feedwater flow through the second tubular configuration; andwherein the feedwater flow splits between the first and second tubular configurations are adjusted to maintain the flue gas stream entering the device within the desired temperature range or at the desired temperature while maintaining a substantially constant total flow of feedwater through the heat exchanger.

5. The system of claim 4, wherein the heat exchanger has a flue gas inlet and a flue gas outlet, a first temperature sensor mounted about the flue gas inlet and/or outlet of the heat exchanger for measuring the inlet and outlet gas temperature, a second temperature sensor for measuring the feedwater temperature at the inlet and outlet of the tubular configurations; and wherein the first and second temperature sensor are in signal communication with the control means.

6. The system of claim 5, wherein the first and second temperature sensor are positioned and calibrated to provide the control means with the appropriate measurements for adjusting the heat transfer rate of the heat exchanger.

7. The system of claim 4, wherein the heated flue gas source is a boiler.

8. The system of claim 7, wherein the demand signal generator produces the flow rate demand signal from at least one of tables, calculations according to predetermined equation (s) of underflow rate demand as a function of boiler load, and tables or equations corresponding to the different fuel types to be burned in the boiler.

9. The system of claim 7, including a line for supplying feedwater to the first tubular configuration, a block valve located in the feedwater supply line, and a high/low limiter unit for producing a high/low limit signal to position the block valve according to boiler load as indicated by the measured feedwater flow signal.

10. The system of claim 9, wherein at low boiler load the block valve and the first control valve are open, at intermediate boiler load the block valve is closed to a specific setting to provide additional flow resistance to the first tubular configuration thereby allowing the first control valve to operate with more flexibility to modulate the feedwater flow through both the first and second tubular configuration, at high load the first control valve is wide open and the block valve is opened in such manner as to obtain balanced flow conditions in both the first and second tubular configuration.

11. A system for sourcing and passing a heated flue gas stream through a heat exchanger and through a device located downstream gas flow-wise of the heat exchanger and means for controlling the flow of feedwater through a selected one of at least two tubular configurations of the heat exchanger to maintain the flue gas stream entering the device within a desired temperature range or at a desired temperature, the control means comprising: a first flow element for producing a measured feedwater flow signal indicative of the actual feedwater flow rate entering the heat exchanger;a demand signal generator for receiving the measured feedwater flow signal and producing a proportioned or biased underflow rate demand signal based upon the measured feedwater flow rate entering the heat exchanger;a second flow element for producing a measured underflow proportioned or biased flow rate indicative of the feedwater flow rate through a control valve to the selected tubular configuration;a flow controller with bias unit for receiving and comparing the underflow flow rate demand signal and the measured underflow proportioned or biased flow rate, and producing a control valve signal, the control valve being responsive to the control valve signal for modulating feedwater flow through the selected tubular configuration; andwherein the feedwater flow through the selected tubular configuration is adjusted to maintain the flue gas stream entering the device within the desired temperature range or at the desired temperature while maintaining a substantially constant total flow of feedwater through the heat exchanger.

12. The system of claim 11, wherein the heat exchanger has a flue gas inlet and a flue gas outlet, a first temperature sensor mounted about the flue gas inlet and/or outlet of the heat exchanger for measuring the inlet and outlet gas temperature, a second temperature sensor for measuring the feedwater temperature at the inlet and outlet of the tubular configurations; and wherein the first and second temperature sensor are in signal communication with the control means.

13. The system of claim 12, wherein the first and second temperature sensor are positioned and calibrated to provide the control means with the appropriate measurements for adjusting the heat transfer rate of the heat exchanger.

14. The system of claim 11, wherein the heated flue gas source is a boiler.

15. The system of claim 14, wherein the demand signal generator produces the flow rate demand signal from at least one of tables, calculations according to predetermined equation (s) of underflow rate demand as a function of boiler load, and tables or equations corresponding to the different fuel types to be burned in the boiler.

16. The system of claim 14, including a line for supplying feedwater to the selected tubular configuration, a block valve located in the feedwater supply line, and a high/low limiter unit for producing a high/low limit signal to position the block valve according to boiler load as indicated by the measured feedwater flow signal.

17. The system of claim 16, wherein at low boiler load the block valve and the control valve are open, at intermediate boiler load the block valve is closed to a specific setting to provide additional flow resistance to the selected tubular configuration thereby allowing the control valve to operate with more flexibility to modulate the feedwater flow through the selected tubular configuration, at high load the control valve is wide open and the block valve is opened in such manner as to obtain balanced flow conditions in both tubular configurations.

18. A method for controlling the feedwater flow through a system including a heat exchanger having at least a first and a second tubular configuration and a heated flue gas source, directing the flue gas through a downstream device and including a control means for maintaining the gas stream entering the device within a desired temperature range or at a desired temperature, the method comprising the steps of: measuring the actual feedwater flow rate entering the heat exchanger;producing a measured feedwater signal indicative of the actual feedwater flow rate entering the heat exchanger;conveying the measured feedwater signal to a demand signal generator to produce a proportioned or biased underflow rate demand signal based upon the measured feedwater flow rate entering the heat exchanger;measuring the actual underflow rate indicative of the feedwater flow through the first tubular configuration;conveying the underflow rate demand signal to a controller with bias unit to produce a control valve signal by comparing the underflow rate demand signal and the actual measured underflow rate;conveying the control valve signal to a first control valve to modulate the feedwater flow rate through the first tubular configuration;conveying the control valve signal to a signal inverter unit to produce an inverted control valve signal;conveying the inverted control valve signal to a second control valve to modulate the feedwater flow through the second tubular configuration; andadjusting the feedwater splits between the first and second tubular configurations to maintain the flue gas temperature entering the device within the desired temperature range or at the desired temperature while maintaining a substantially constant total flow of feedwater through the heat exchanger.

19. The method of claim 18, further comprising the steps of: producing a flue gas temperature signal measured about the inlet and/or outlet of the heat exchanger;producing a feedwater temperature signal measured at the inlet and outlet of the tubular configurations; andconveying the flue gas and feedwater temperature signal to the control means.

20. The method of claim 19, further comprising the steps of positioning and calibrating the flue gas and feedwater temperature signal to provide the control means with the appropriate measurements for adjusting the heat transfer rate of the heat exchanger.

21. The method of claim 18, wherein the heated flue gas source is a boiler.

22. The method of claim 21, further comprising the step of producing the flow rate demand signal from at least one of tables, calculations according to predetermined equation (s) of underflow rate demand as a function of boiler load, and tables or equations corresponding to the different fuel types to be burned in the boiler.

23. The method of claim 21, including a line for supplying feedwater to the first tubular configuration, a block valve located in the feedwater supply line, and a high/low limiter unit for producing a high/low limit signal, and further comprising the step of conveying the high/low limit signal to position the block valve according to boiler load as indicated by the measured feedwater flow signal.

24. The method of claim 23, further comprising the steps of: at low boiler load, maintaining the block valve and the first control valve open;at intermediate boiler load, closing the block valve to a specific setting to provide additional flow resistance to the first tubular configuration thereby allowing the first control valve to operate with more flexibility to modulate the feedwater flow through both the first and second tubular configuration; andat high load, maintaining the control valve wide open and the block valve opened in such manner as to obtain balanced flow conditions in both the first and second tubular configuration.

25. A method for controlling the feedwater flow through a system including a heat exchanger having at least two tubular configurations and a heated flue gas source, directing the flue gas through a downstream device and including a control means for maintaining the gas stream entering the device within a desired temperature range or at a desired temperature, the method comprising the steps of: measuring the actual feedwater rate entering the heat exchanger;producing a measured feedwater signal indicative of the actual feedwater flow rate entering the heat exchanger;conveying the measured feedwater signal to a demand signal generator to produce a proportioned or biased underflow rate demand signal based upon the measured feedwater flow rate entering the heat exchanger;producing a measured underflow proportioned or biased flow rate indicative of the feedwater flow rate through a control valve to a selected one of the two tubular configurations;conveying the underflow rate demand signal to a controller with bias unit to produce a control valve signal by comparing the underflow rate demand signal and the measured underflow proportioned or biased flow rate;conveying the control valve signal to the control valve to modulate the feedwater flow rate through the selected tubular configuration; andadjusting the feedwater flow through the selected tubular configuration to maintain the flue gas temperature entering the device within the desired temperature range or at the desired temperature while maintaining a substantially constant total flow of feedwater through the heat exchanger.

26. The method of claim 25, further comprising the steps of: producing a flue gas temperature signal measured about the inlet and/or outlet of the heat exchanger;producing a feedwater temperature signal measured at the inlet and outlet of the tubular configurations; andconveying the flue gas and feedwater temperature signals to the control means.

27. The method of claim 26, further comprising the steps of positioning and calibrating the flue gas and feedwater temperature signal to provide the control means with the appropriate measurements for adjusting the heat transfer rate of the heat exchanger.

28. The method of claim 25, wherein the heated flue gas source is a boiler.

29. The method of claim 28, further comprising the step of producing the flow rate demand signal from at least one of tables, calculations according to predetermined equation (s) of underflow rate demand as a function of boiler load, and tables or equations corresponding to the different fuel types to be burned in the boiler.

30. The method of claim 29, including a line for supplying feedwater to the selected tubular configuration, a block valve located in the feedwater supply line, and a high/low limiter unit for producing a high/low limit signal, and further comprising the step of conveying the high/low limit signal to position the block valve according to boiler load as indicated by the measured feedwater flow signal.

31. The method of claim 30, further comprising the steps of: at low boiler load, maintaining the block valve and the control valve open;at intermediate boiler load, closing the block valve to a specific setting to provide additional flow resistance to the selected tubular configuration thereby allowing the control valve to operate with more flexibility to modulate the feedwater flow through the selected tubular configuration; andat high load, maintaining the control valve wide open and the block valve opened in such manner as to obtain balanced flow conditions in both tubular configurations.