Title of Invention	EVAPORATOR SURFACE STRUCTURE OF A CIRCULATING FLUIDIZED BED BOILER AND A CIRCULATING FLUIDIZED BED BOILER WITH SUCH AN EVAPORATOR SURFACE STRUCTURE
Abstract	Evaporator surface structure of a circulating fluidized bed boiler, comprising at least one separate vertical evaporator surface unit arranged within a distance from the fur¬nace walls, formed of water tube panels, extending from the bottom of the furnace of the circulating fluidized bed boiler to the ceiling thereof, the evaporator surface unit consisting of two cross-wise joined vertical water tube panels. Preferably, a first water tube panel of each evaporator surface unit is parallel to the water tubes of the furnace ceiling and a second water tube panel is perpendicular to that. The upper ends of the water tubes of each water tube panel are preferably connected to separate headers parallel with the water tube panels, and the water tube panels are advantageously suspended to hang of the headers in such a way that each evaporator surface unit is connected to the ceiling of the furnace by a structure enabling vertical movement between the evaporator surface unit and the ceiling.

Title of Invention

EVAPORATOR SURFACE STRUCTURE OF A CIRCULATING FLUIDIZED BED BOILER AND A CIRCULATING FLUIDIZED BED BOILER WITH SUCH AN EVAPORATOR SURFACE STRUCTURE

Abstract

Evaporator surface structure of a circulating fluidized bed boiler, comprising at least one separate vertical evaporator surface unit arranged within a distance from the fur¬nace walls, formed of water tube panels, extending from the bottom of the furnace of the circulating fluidized bed boiler to the ceiling thereof, the evaporator surface unit consisting of two cross-wise joined vertical water tube panels. Preferably, a first water tube panel of each evaporator surface unit is parallel to the water tubes of the furnace ceiling and a second water tube panel is perpendicular to that. The upper ends of the water tubes of each water tube panel are preferably connected to separate headers parallel with the water tube panels, and the water tube panels are advantageously suspended to hang of the headers in such a way that each evaporator surface unit is connected to the ceiling of the furnace by a structure enabling vertical movement between the evaporator surface unit and the ceiling.

Full Text	EVAPORATOR SURFACE STRUCTURE OF A CIRCULATING FLUIDIZED BED BOILER AND A CIRCULATING FLUIDIZED BED BOILER WITH SUCH AN EVAPORATOR SURFACE STRUCTURE The present invention relates to an evaporator surface stmcture of a circulating flu-idized bed boiler (CFB boiler) according to the preamble of claim 1 and a circulating fluidized bed boiler wifrt such an evaporator surface structure. The invention espe¬cially relates to an evaporator surface structure an-anged in a furnace of a large CFB boiler, typically a once-through utility boiler of over 400 MWe. In CFB boilers the evaporation of the heated feed water, i.e. boiling takes place mostly by means of the water tube panels in the outer walls of the boiler furnace. When increasing the efficiency of the boiler, the cross-sectional area of the furnace must be Increased proportionally with the efficiency to be able to combust the re¬quired amount of fuel with a flow speed of oxynegous fluidizing gas corresponding the original flow speed. Since it is not advantageous to form the shape of the hori¬zontal cross-section of the boiler very oblong nor to increase the height of the boiler too much, the total area of the evaporator surfaces formed by the outer walls of the furnace tends to remain too small in large boilers. For example, if oxygen-enriched air is used instead of air as fluidizing gas, the surface area of the furnace walls available for evaporator surfaces may decrease even more. The additional need for evaporator surface may increase also when using low-ash fuel with good heat value, for example, dry coal. To ensure sufficient evaporator surface area in large boilers, it has been suggested to have different kind of additional evaporator surfaces disposed in the furnace, US patents US 3,736,908 and 5,215,042 disclose the division of the furnace by longitu¬dinal, transverse or crosswise water tube walls extending from wall to wall, the lower part of which has an opening or openings enabling the flow of material. US patent 5,678,497 suggests the increase of heat exchange surface in the furnace by dividing the furnace into two by a longitudinal partition having short transverse wall portions connected thereto. Despite the openings in the partitions, both of the above-mentioned embodiments have a risk of not having the flows of the solid ma¬terial and the gas in balance between the different parts of the divided furnace, which may, for example, increase environmental emissions or even cause oscillat¬ing operation in the whole boiler. US patent 6,470,833 discloses an arrangement, where the operation of the furnace of the CFB boiler is improved by forming addi¬tional evaporator surfaces to separate, closed evaporator cavities extending from the bottom to the ceiling of the furnace, The disadvantage with these evaporator cavities is that they decrease the bottom surface area available and increase heat exchange surface area only relatively little. The purpose of the present invention is to provide an evaporator surface stajcture for a circulating fluidized bed boiler diminishing problems related to the prior art evaporator surface structures for circulating fluidized bed boiler. The purpose of the invention is especially to provide a simple and durable evapora¬tor surface structure for a circulating fluidized bed boiler, enabling a sufficient evaporation efficiency without disturbing the combustion process of the boiler. It is also a purpose of the invention to provide a circulating fluidized bed boiler with such an evaporator surface structure. In order to solve the above-mentioned prior art problems it suggested to provide an evaporator surface structure for a circulating fluidized bed boiler and a circulating fluidized bed boiler with an evaporator surface structure with characterizing features defined in the characterizing part of the independent apparatus claims. Thus, it is a characterizing feature of the evaporator surface structure for a circulat¬ing fluidized bed boiler in accordance with the present invention that is comprises at least one separate vertical evaporator surface unit within a distance from the walls of the furnace, formed of water tube panels, extending from the furnace bottom of the circulating fluidized bed boiler to the ceiling, the evaporator surface consisting of two cross-wise joined vertical water tube panels. The water tube panels of the evaporator surface units in accordance with the inven¬tion are preferably conventional water tube panels, formed by joining a group of wa¬ter tubes by means of fins, i.e. by narrow metal plates so that they form at least par¬tially gas-tight planar panel. The height of the water tube panels in the evaporator surface units corresponds thus to the height of the furnace and their width is pref¬erably 1-5 m, most preferably 2-3 m. When two such panels are joined cross-wise, a durable and rigid structure is provided. The evaporator surface structure formed by evaporator surface units in accordance with the invention is reliable in use, even when assembled in a furnace of a large CFB boiler, the height of which can be 40-50 m, even though the width of the water tube panels were, for example, only 2-3 m. Since no empty space is left inside the evaporator surface units, as in the arrange¬ment of US patent 6,470,833, the evaporator surface structure in accordance with the invention does not substantially decrease the cross-sectional area available for the combustion process in the furnace and does not thus cause any need to in¬crease the outer dimensions of the furnace. The evaporator surface units are sepa¬rate and spaced apart from the outer walls, and therefore the gases and solids in the furnace are allowed to move as freely as possible in all parts of the furnace. Thus, the different parts of the furnace are in balance with each other and the op¬eration of the boiler can easily be adjusted so that the environmental emissions are minimized. In some cases, it is possible to arrange only one evaporator surface unit in accor¬dance with the invention to a small CFB boiler, but large boilers preferably have two or more evaporator surface units. According to a preferred embodiment, a boiler comprises three longitudinally subsequent evaporator surface units. Especially in very large boilers, there can be four or even more evaporator surface units and they can be arranged to the furnace also othenA/ise than longitudinally subsequently, for example, in two rows. The water tube panels of the evaporator surface units are preferably in right angle with each other. By using this arrangement, the formation of too tight corners as for movement of solid material, so called dead corners, is avoided. In some cases, the smallest angle between the panels may, however, to some extent differ from the right angle. The water tube panels of the evaporator units are preferably symmetrically cross¬wise, whereby additional heat exchange surface is obtained evenly in every direc¬tion. Especially, the water tube panels of the evaporator surface units closest to the side walls of the furnace may, however, be joined cross-wise in T-form in such a way that the panel portion on the side wall side is missing. Thereby, the flow of the solid material in close proximity to the sidewall is as free as possible. In some cases it may be advantageous to join the water tube panels of the evaporator surface units to each other also in the shape of L, which is here considered a special case of cross-wise combining, the panel portions of two directions being missing. Accord¬ing to one preferred embodiment, one or two symmetrically cross-wise joined evaporator units are formed in the middle of the furnace and an evaporator surface unit fonned cross-wise in T-form in close proximity to each sidewall. The evaporator surface units are preferably arranged to the furnace in such a way that a first water tube panel of each evaporator surface unit is parallel with the water tubes of the fumace ceiling, i.e. in longitudinal direction of the cross-section of the fumace. Thereby, a second water tube panel is preferably perpendicular to the first panel, i.e. in transverse direction of the furnace. In some cases, it may be advanta¬geous to arrange water tube panels of the evaporator surface units also in inclined position relative to the walls of the boiler. When the perpendicularly connected water tube panels of the evaporator surface units are arranged parallel with the furnace walls, the water tubes of the water tube panels can be arranged in a simple way to run between the water tubes of the wa¬ter tube panel in the furnace ceiling. Naturally, if the diameters of the tubes of the water tube panels in the evaporator surface units are larger than the distances be¬tween the tubes of the water tube panel in the ceiling, i.e. the widths of the fins be¬tween the tubes, the water tubes of the ceiling must be bent in a suitable way so that the tubes in the water tube panels have enough space to run between the wa¬ter tubes in the ceiling. A preferred method of bending the tubes in the water tube panels of the evaporator surface units in the upper part of the furnace is later dis¬cussed more in detail. The symmetrically cross-wise set water tube panels can preferably be approxi¬mately of the same width. According to a preferred embodiment, the width of the transverse panels in the furnace is, however, about 1.5 to 2 times the width of the longitudinal panels. A sufficient evaporator surface area is thus gained, although the panels are arranged such a way that the flames of the startup burners in the front and rear walls do not reach them. Preferably an opening or openings is/are formed to the panels, especially to the lower part of the broader panels in the evaporator surface units, so as to allow free movement of the solid material in the furnace. The most preferred widths and ratios of widths of the panels depend, for example, on the number of the evaporator units and on the dimensions of the boiler furnace. The ratio of the widths of the first and second water tube panels is prefera¬bly between 1:3-3:1. According to a preferred embodiment of the present invention, the water tubes of the water tube panels in each evaporator surface unit are connected from the upper part to separate outlet headers an-anged at different heights parallel with the water tube panels. When the water tubes of the evaporator unit are joined this way in¬stead of one outlet header to two separate outlet headers, the connecting of the water tubes to the outlet headers is made easier and the connecting tubes of the water tubes outside the furnace can be maintained short and their bendings rela¬tively simple. Steam is led from the outlet headers, the lengths of which are preferably approxi¬mately the same as the widths of the corresponding water tube panels, preferably by means of connecting ducts to a separator for water and vapor. Especially when the boiler is a once-through utility boiler, the outlet headers of each evaporator sur¬face unit are preferably joined to each other by means of a steam pressure balancing tube. Further, the outlet headers of the evaporator surface units are preferably joined by steam pressure balancing tubes also to the outlet headers of the water tube panels in the sidewalls of the furnace. The water tube panels of the evaporator surface units according to the invention are preferably suspended to hang from the outlet headers of the water tube panels. Therefore, a sufficient portion, preferably at least a fourth, most preferably at least a third of the water tubes of the water tube panels is joined vertically, without bend-ings, to the lower edge of the outlet headers. The outlet headers are preferably sus¬pended to hang from the stationary supporting structure of the boiler. Since the water tube panels of the evaporator surface units located in the fumace according to the invention are heated in the furnace from both sides, the panels must be designed, especially in once-through utility boilers, in such a way that the flow of the heated feed water is distributed in a desired way between them and the evaporator surfaces of the on only one side heated outer walls of the fumace. Ac¬cording to a preferred embodiment, the water tubes of the evaporator surfaces in the outer walls of a once-through utility boiler are conventional, smooth water tubes and the water tubes of the evaporator surfaces in the fumace are so called rifled tubes to ensure efficient heat exchange and cooling of the evaporator surfaces. Correspondingly, the diameters of the water tubes in the evaporator surfaces inside the furnace and the distance between the tubes may be different from the diame¬ters and the distance between the water tubes in the outer walls of the boiler. Es¬pecially, when the distance between the tubes in the water tube panels of the evaporator surface units is greater than the distance between the water tubes of the furnace ceiling, the water tubes of the water tube panels in the evaporator surfaces perpendicular to the direction of the water tubes of the ceiling must be bent in such a way that at least in some locations at least two water tubes of the water tube pan¬els of the evaporator surfaces run through the same opening between the water tubes of the ceiling. According to a preferred arrangement, the ratio between the distance of the cen¬tral points of the water tubes in the water tube panels of the evaporator surface units and the distance between the central points of the water tubes of the ceiling of the furnace is approximately 2:3. Thereby, advantageously every second wa¬ter tube of the furnace ceiling is bent towards the adjacent tube at the points where the water tubes in the water tube panels perpendicular to the tubes of the furnace ceiling are led through the ceiling so as to provide a sufficient opening in every other space between the water tubes of the ceiling for bringing the water tubes in the water tube panels of the evaporation surface unit through the ceiling. Bringing the water tubes of the water tube panels In the evaporator surface units through the ceiling can then be arranged preferably in such a way that every third water tube runs unbent through an opening formed between the water tubes of the ceiling and the next two tubes are bent to run in line through the same open¬ing. A regular arrangement, in which some of the water tubes run unbent through the ceiling, can be provided also when the ratio of the distance between the center points of the water tubes in the water tube panels of the evaporator surface units to the distance between the center points of the water tubes in the furnace ceiling is N:M, where N and M are unequal small integers, preferably smaller than five. If, for example, N is three and M is four, four tubes of the panel in the evaporator surface unit can be brought to run regularly through every third space between the water tubes in the ceiling, whereby every fourth tube of the panel in the evaporator sur¬face unit can run vertically. The above described differences between the evaporator surfaces in accordance with the invention and the evaporator surfaces in the outer walls of the furnace re¬sult in that the temperature distribution in the evaporator surfaces inside the furnace does not necessarily in all situations correspond to the temperature distribution in the water tube panels in the outer walls of the boiler. These differences thus possi¬bly cause some deviation in the thermal expansion of the water tube panels in ac¬cordance with the invention compared to the thermal expansion of the rest of the boiler. Generally, large CFB boilers are suspended from above, whereby the lower part of the boiler and all equipment to be connected thereto are designed in such a way that when the boiler temperature is raised to the operational temperature and the length of the boiler walls increases because of thermal expansion, the lower part of the boiler can move downwards even as much as tens of centimeters. Since the temperature of the evaporator surface structures located in the furnace may be, for example, during the start up of the boiler higher than the temperature of the outer walls of the boiler, the evaporator surface structures are preferably ar¬ranged so that they can move relative to the outer walls of the furnace. According to a preferred embodiment of the present invention, this is carried out in such a way that the lower parts of the evaporator surface units in the evaporator surface struc¬ture are stationarily mounted to the boiler bottom, but the upper parts of the evapo¬rator surface units may move relative to the ceiling. Therefore, the evaporator sur¬face structure is arranged spaced apart from the sidewalls of the boiler and the out¬let headers supporting the structure are preferably suspended to hang by means of flexible elements. The strain of the flexible element for example, a spring, of the suspension is preferably adjustable in order to eliminate possible vibration in the evaporator surface unit. In such an arrangement, it is not possible to attach the evaporator surface structure stationarily to the ceiling of the boiler, but the joint comprises a vertically flexible structure, preferably a bellows. Such a structure enables the connection of the eva¬porator surface structure gas-tight to the ceiling, but the structure may to some ex¬tent move vertically relative to the ceiling. The invention is described more in detail below, with reference to the accompany¬ing drawings, in which Fig. 1 schematically illustrates a vertical cross-sectional view of a circulating fluid-ized bed boiler having an evaporator surface structure in accordance with a preferred embodiment of the present invention. Fig. 2 schematically illustrates a horizontal cross-sectional view of a circulating fluid-ized bed boiler having an evaporator surface structure in accordance with another preferred embodiment of the present invention. Fig. 3 schematically illustrates an upper part of the evaporator surface unit in ac¬cordance with a preferred embodiment of the present invention. Fig. 1 illustrates a CFB boiler 10 in accordance with a preferred embodiment of the present invention, comprising a furnace 12 suspended to hang from a stationary supporting structure 14 by means of suspending means 16, for example, by hanger rods. The boiler in accordance with the invention may be a natural circulation boiler, in other words a drum boiler, but most preferably it is a supercritical once-through utility boiler. The furnace is limited by a bottom 18, a ceiling 20 and sidewalls 22, which are usually of water tube structure. The furnace is also provided with other conventional parts of a CFB boiler, such as inlet means for fuel and combustion air, outlet means for flue gas and bottom ash as well as dust separators and return ducts connected thereto. For simplicity, these details, which are irrelevant in view of the present invention are not shown in Fig. 1. The outer walls 22 of the furnace are normally manufactured of water tube panels, in which the feed water which is preheated in the heat exchange section of the flue gas channel is evaporated, i.e. turned to vapor. According to the present invention, the CFB boiler illustrated in Fig. 1 also contains an evaporator surface structure 24 arranged inside the furnace 12, the evaporator surface structure comprising three vertical evaporator surface units 26 extending from the bottom 18 of the furnace to the ceiling 20. The evaporator surface units 26 consist of two water tube panels 28, 30 connected to each other perpendicularly in a cross-wise configuration. The preheated feed water and the possible liquid being returned from the steam separator is brought to inlet headers 32, 34 connected to the lower part of the water tube panels 28, 30 of the evaporator surface units, from where it is led to the panels 28, 30 to be evaporated, and further as vapor to the outlet headers 36, 38. If the boiler is a so called drum boiler, the driving force in getting the water and steam upwards is the weight of the liquid column in the drop leg of the drum. However, if the boiler is a so called forced circulation boiler, especially a so called supercritical once-through utility boiler, the driving force Is pressure generated by the pump of the water cycle. The inlet headers 32, 34 and outlet headers 36, 38 are preferably arranged cross-wise parallel to the panels, at different levels relative to each other. The steam generated in the evaporator surface units 26, possibly still containing some liquid water, is led from the outlet headers 36, 38 to a steam separator (not shown in Fig. 1). The separated steam is led from the steam separator further to superheaters arranged, for example, in the flue gas channel. The water tube panels 28, 30 are preferably suspended to hang from the support¬ing structure 14 by means of supporting means, e.g., hanger rods 40, 42, con¬nected to the outlet headers 36, 38. The water tube panels 28, 30 are preferably assembled stationarily through the bottom 18 of the furnace In such a way that the panels cannot move relative to the bottom. Since the water tube panels 28, 30 ar¬ranged inside the furnace can in some cases be at a temperature-different from that of the water tube panels of the sidewalls 22, the heat expansions of these different panels may differ from each other. Therefore, the water tube panels 28, 30 are preferably joined to the furnace ceiling 20 by means of cross-shaped bellows 44 enabling the vertical movement. In order to keep the support of the panels func¬tional in all conditions, the hanger rods 40, 42 also comprise a spring-like element 46. The strain of the flexible element of the support is preferably adjustable so as to be able to eliminate vibration of the evaporator surface unit, for example, transverse or rotary vibration. In an embodiment in accordance with Fig. 1, all evaporator surface units 26 are identical, extending to every direction in the shape of a cross. Fig. 2 schematically illustrates a horizontal cross-section of another preferred embodiment showing that the most central 48 of the four evaporator surface units set to the furnace 12' are of the shape of a symmetrical cross, extending to every direction, but the units 50 closest to the end walls 52 of the furnace are of T-shape in such a way that the panel part on the end wall side is missing from the evaporator surface unit. The water tube panels 54, 56 of the evaporator surface units in accordance with the invention are preferably stationarily assembled to each other in right angle fonning a durable construction, which provides a lot of additional heat exchange surface to the furnace 12. The angle between the panels may also deviate to some extent from the right angle, especially if there are two panel parts missing from the cross-structure formed by the panels and the cross-section of the panels is of L-shape. The evaporator surface units 48, 50 are preferably arranged in line to the greatest dimension of the furnace 12, but in some cases the units may also be located oth¬erwise, for example, in two lines. The widths of the evaporator surface units 54, 56 are preferably approximately equal. It may, however, often be advantageous to use panel widths that are to a certain extent different, for example, in such a way that the panels 54 that are transverse relative to the furnace are 1,5 to 2 times wider than the corresponding longitudinal panels 56. Thereby, the material flows coming from the front and rear walls of the furnace, in other words from the long outer walls thereof, or, for exam¬ple, the flames of the start up burners, may be arranged in such a way that they do not directly hit to the longitudinal water tube panels 56. Especially when the width of the panel parts in the evaporator surface units is a significant portion of the corresponding dimension of the furnace, an opening 58 or openings is/are formed to the panels, especially to the lower parts thereof to enable as free flow of the solid material in the furnace as possible. Fig. 3 'lilustrHtes more in detail the inlets of the water tube panels 62, 64 in an evaporator surface unit 60 of the shape of a symmetric cross through the furnace ceiling 20 by means of a bellows box 66, and the connecting of water tubes of the panels 62, 64 to the water cycle of the boiler. The vapor formed in evaporator sur¬face unit 60 is preferably gathered to two outlet headers 36, 38 parallel to the water tube panels 62, 64. Thereby, the extensions of the water tubes required for con¬necting the water tubes of the water tube panels 62, 64 to different sides of the out¬let headers 36, 38, and especially the tube bends 68 thereof, can be formed in a simple manner to a compact space. The vapor gathered in outlet headers 36, 38 is guided to the steam separator by means of connecting tubes 70, 72 connected to outlet headers 36, 38. For balanc- ing the vapor pressure, the inlet headers 36, 38 are preferably connected together by a balancing tube 74. Correspondingly, the outlet headers 36, 38 are preferably connected to outlet headers of the sidewalls (not in Fig. 3) by means of balancing tubes 76, 78. Fig. 3 also shows the attaching means 80 of the hanger rods of the evaporator surface unit 60 connected to the outlet headers 36, 38. If the distances of the center points of the water tubes in the water tube panels 62, 64 of the evaporator surface unit 60 are the same as the distances of the center points of the water tubes 84 in the water tube panel 82 of the furnace ceiling and the diameters of the water tubes of the panels 62, 64 are smaller than widths of the fins in the water tube panel 82 of the ceiling 20 of the furnace, it is possible simply to lead the water tubes 62, 64 directly through the furnace ceiling 20 through open¬ings formed in the fins of the water tube panel 82. If the width of the fins is not suffi¬cient, the water tubes 84 of the furnace ceiling 20 must be bent to form these open¬ings through the ceiling. If, in turn, the water tubes in the water tube panels 62, 64 are situated closer to each other than the water tubes in the water tube panel 82, at least a portion of the water tubes 86 of the water tube panel 62 perpendicular to the water tubes 84 in the furnace ceiling 20 must be bent for leading the tubes through the ceiling. According to a preferred embodiment of the present invention, a lower part of the cross-shaped bellows box 66 is stationarily connected to the water tube panel 82 of the furnace ceiling 20, and, correspondingly, a cover 88 of the bellows box is sta¬tionarily connected to the water tubes in the water tube panels of the evaporator surface unit 60. There is a flexible element 90, preferably a metal bellows, between the lower part of the bellows box 66 and the cover 88 thereof, for enabling the verti¬cal motion of the water tubes in the water tube panels 62, 64 relative to the furnace ceiling 20. The bellows box 66 and the furnace ceiling 20 together form a gas-tight construction preventing the escaping of the combustion gases and furnace particles through the furnace ceiling. Water tubes 84' in the furnace ceiling 20 inside a branch 92 of the bellows box 66 parallel to the water tubes 84 of the furnace ceiling 20 are bent when required in such a way that a sufficient opening (not shown in Fig. 3) is formed to lead the wa¬ter tubes of the corresponding panel portion 64 of the evaporator surface unit 60 through the ceiling. Correspondingly, water tubes 84" inside a branch 94 of the bel¬lows box 66 perpendicular to the water tubes 84 of the furnace ceiling 20 are bent, if necessary, in such a way that openings (not shown in Fig. 3) are formed to lead water tubes of the corresponding panel portion 62 of the evaporator surface unit through the ceiling. According to a preferred embodiment of the invention, the ratio of the distance of the central points of the water tubes in the water tube panels 62, 64 of the evapora¬tor surface unit 60 and the distance of the central points of water tubes 70 of water tube panel 82 of the ceiling 20 is 2:3. Thereby, it is possible to advantageously bend three water tubes of the panel 62 to form a line parallel to the water tubes 84 of the furnace ceiling 20, which line is led through the ceiling 20 through the same opening formed between the water tubes 84". Fig. 3 does not show the bending of the water tubes in the panel 62 to line, but the upper parts of the lines thus formed are to be seen above the branch 94 of the box 66. The invention has been described above with reference to some exemplary em¬bodiments. These embodiments are, however, not given to limit the scope of in¬vention, but the invention is limited merely by the accompanying claims and the definitions therein. CLAIMS 1. Evaporator surface structure (24) of a circulating fiuidized bed boiler (10), comprising at least one vertical and separate evaporator surface unit (26) spaced apart from the walls of the furnace, formed of water tube panels, extending from the furnace bottom (18) of the circulating fluidized bed boiler to the ceiling (20) of the furnace, characterized in that the evaporator surface unit consists of two cross¬wise joined vertical water tube panels (28, 30). 2. Evaporator surface structure in accordance with claim 1, characterized in that frie evaporator surface stnjcture (24) comprises at least two evaporator surface units (26). 3. Evaporator surface structure in accordance with claim 1 or 2, characterized in that the water tube panels (28, 30) are perpendicular to each other. 4. Evaporator surface structure in accordance with claim 3, characterized in that the water tube panels (28, 30) of at least one evaporator surface unit are sym¬metrically cross-wise. 5. Evaporator surface structure in accordance with claim 3, characterized in that the water tube panels of at least one evaporator surface unit (50,52) are con¬nected cross-wise in T shape. 6. Evaporator surface stnjcture in accordance with claim 3, characterized in that a first water tube panel (64) of each evaporator surface unit is parallel to the water tubes (84) of the furnace ceiling (20) and a second water tube panel (62) is perpendicular thereto, 7. Evaporator surface structure in accordance with claim 6, characterized in that the ratio of the widths of the first (64) and the second (62) water tube panels is from 1:3 to 3:1. 8. Evaporator surface structure in accordance with claim 6, characterized in that the water tubes of the water tube panels (62.64) are joined from their upper part to headers (36, 38) parallel to the water tube panels. 9. Evaporator surface structure in accordance with claim 8, characterized in that the boiler is a once-through utility boiler and the headers (36, 38) of each evaporator surface unit are joined to each other by a steam pressure balancing tube (74). 10. Evaporator surface structure in accordance with claim 8, characterized in that boiler is a once-through utility boiler and the headers (36, 38) of the evaporator surface units are joined by a steam pressure balancing tube (76, 78) to the headers of the water tube panels in the sidewalls of the furnace. 11. Evaporator surface structure in accordance with claim 8, characterized in that water tube panels are suspended to hang from said headers. 12. Evaporator surface structure in accordance with claim 11, characterized in that headers are flexibly suspended to hang from the stationary supporting structure of the boiler. 13. Evaporator surface structure in accordance with claim 12, characterized in that the strain of the flexible element (46) of the suspension is adjustable in order to eliminate the vibration of the evaporator surface unit. 14. Evaporator surface structure in accordance with claim 12, characterized in that each evaporator surface unit is joined to the ceiling of the furnace by a flexible structure (66) enabling the vertical movement between the evaporator surface unit and the ceiling. 15. Evaporator surface structure in accordance with claim 14, characterized in that the structure (66) enabling the movement between the evaporator surface unit and the ceiling comprises a bellows (90). 16. Evaporator surface structure in accordance with claim 11, characterized in that at least a portion of the water tubes in the second water tube pane! (62) is ar¬ ranged to form lines parallel to the water tubes (84) of the ceiling (20) at the level of the ceiling. 17. Evaporator surface structure in accordance with claim 16, characterized in that the ratio of the distance between the center points of the water tubes (86) in the second water tube panels (62) to the distance of the water tubes (84) of the water tube panels in the ceiling (20) is N:M, where N and M are unequal small integers. 18. Evaporator surface structure in accordance with claim 17, characterized in that N and M are less than five, 19. Evaporator surface structure in accordance with claim 18, characterized In that N is 2 and M is 3. 20. A circulating fluldized bed boiler (10), comprising a bottom (18), a ceiling (20) and a furnace (12) defined by sidewalls (22), and having an evaporator surface staicture (14), characterized in that the evaporator surface structure Is in accor¬ dance with one of the preceding claims 1-19.

Full Text

EVAPORATOR SURFACE STRUCTURE OF A CIRCULATING FLUIDIZED BED
BOILER AND A CIRCULATING FLUIDIZED BED BOILER WITH SUCH AN
EVAPORATOR SURFACE STRUCTURE
The present invention relates to an evaporator surface stmcture of a circulating flu-idized bed boiler (CFB boiler) according to the preamble of claim 1 and a circulating fluidized bed boiler wifrt such an evaporator surface structure. The invention espe¬cially relates to an evaporator surface structure an-anged in a furnace of a large CFB boiler, typically a once-through utility boiler of over 400 MWe.
In CFB boilers the evaporation of the heated feed water, i.e. boiling takes place mostly by means of the water tube panels in the outer walls of the boiler furnace. When increasing the efficiency of the boiler, the cross-sectional area of the furnace must be Increased proportionally with the efficiency to be able to combust the re¬quired amount of fuel with a flow speed of oxynegous fluidizing gas corresponding the original flow speed. Since it is not advantageous to form the shape of the hori¬zontal cross-section of the boiler very oblong nor to increase the height of the boiler too much, the total area of the evaporator surfaces formed by the outer walls of the furnace tends to remain too small in large boilers. For example, if oxygen-enriched air is used instead of air as fluidizing gas, the surface area of the furnace walls available for evaporator surfaces may decrease even more. The additional need for evaporator surface may increase also when using low-ash fuel with good heat value, for example, dry coal.
To ensure sufficient evaporator surface area in large boilers, it has been suggested to have different kind of additional evaporator surfaces disposed in the furnace, US patents US 3,736,908 and 5,215,042 disclose the division of the furnace by longitu¬dinal, transverse or crosswise water tube walls extending from wall to wall, the lower part of which has an opening or openings enabling the flow of material. US patent 5,678,497 suggests the increase of heat exchange surface in the furnace by dividing the furnace into two by a longitudinal partition having short transverse wall portions connected thereto. Despite the openings in the partitions, both of the

above-mentioned embodiments have a risk of not having the flows of the solid ma¬terial and the gas in balance between the different parts of the divided furnace, which may, for example, increase environmental emissions or even cause oscillat¬ing operation in the whole boiler. US patent 6,470,833 discloses an arrangement, where the operation of the furnace of the CFB boiler is improved by forming addi¬tional evaporator surfaces to separate, closed evaporator cavities extending from the bottom to the ceiling of the furnace, The disadvantage with these evaporator cavities is that they decrease the bottom surface area available and increase heat exchange surface area only relatively little.
The purpose of the present invention is to provide an evaporator surface stajcture for a circulating fluidized bed boiler diminishing problems related to the prior art evaporator surface structures for circulating fluidized bed boiler.
The purpose of the invention is especially to provide a simple and durable evapora¬tor surface structure for a circulating fluidized bed boiler, enabling a sufficient evaporation efficiency without disturbing the combustion process of the boiler.
It is also a purpose of the invention to provide a circulating fluidized bed boiler with such an evaporator surface structure.
In order to solve the above-mentioned prior art problems it suggested to provide an evaporator surface structure for a circulating fluidized bed boiler and a circulating fluidized bed boiler with an evaporator surface structure with characterizing features defined in the characterizing part of the independent apparatus claims.
Thus, it is a characterizing feature of the evaporator surface structure for a circulat¬ing fluidized bed boiler in accordance with the present invention that is comprises at least one separate vertical evaporator surface unit within a distance from the walls of the furnace, formed of water tube panels, extending from the furnace bottom of the circulating fluidized bed boiler to the ceiling, the evaporator surface consisting of two cross-wise joined vertical water tube panels.

The water tube panels of the evaporator surface units in accordance with the inven¬tion are preferably conventional water tube panels, formed by joining a group of wa¬ter tubes by means of fins, i.e. by narrow metal plates so that they form at least par¬tially gas-tight planar panel. The height of the water tube panels in the evaporator surface units corresponds thus to the height of the furnace and their width is pref¬erably 1-5 m, most preferably 2-3 m. When two such panels are joined cross-wise, a durable and rigid structure is provided. The evaporator surface structure formed by evaporator surface units in accordance with the invention is reliable in use, even when assembled in a furnace of a large CFB boiler, the height of which can be 40-50 m, even though the width of the water tube panels were, for example, only 2-3 m.
Since no empty space is left inside the evaporator surface units, as in the arrange¬ment of US patent 6,470,833, the evaporator surface structure in accordance with the invention does not substantially decrease the cross-sectional area available for the combustion process in the furnace and does not thus cause any need to in¬crease the outer dimensions of the furnace. The evaporator surface units are sepa¬rate and spaced apart from the outer walls, and therefore the gases and solids in the furnace are allowed to move as freely as possible in all parts of the furnace. Thus, the different parts of the furnace are in balance with each other and the op¬eration of the boiler can easily be adjusted so that the environmental emissions are minimized.
In some cases, it is possible to arrange only one evaporator surface unit in accor¬dance with the invention to a small CFB boiler, but large boilers preferably have two or more evaporator surface units. According to a preferred embodiment, a boiler comprises three longitudinally subsequent evaporator surface units. Especially in very large boilers, there can be four or even more evaporator surface units and they can be arranged to the furnace also othenA/ise than longitudinally subsequently, for example, in two rows.
The water tube panels of the evaporator surface units are preferably in right angle

with each other. By using this arrangement, the formation of too tight corners as for movement of solid material, so called dead corners, is avoided. In some cases, the smallest angle between the panels may, however, to some extent differ from the right angle.
The water tube panels of the evaporator units are preferably symmetrically cross¬wise, whereby additional heat exchange surface is obtained evenly in every direc¬tion. Especially, the water tube panels of the evaporator surface units closest to the side walls of the furnace may, however, be joined cross-wise in T-form in such a way that the panel portion on the side wall side is missing. Thereby, the flow of the solid material in close proximity to the sidewall is as free as possible. In some cases it may be advantageous to join the water tube panels of the evaporator surface units to each other also in the shape of L, which is here considered a special case of cross-wise combining, the panel portions of two directions being missing. Accord¬ing to one preferred embodiment, one or two symmetrically cross-wise joined evaporator units are formed in the middle of the furnace and an evaporator surface unit fonned cross-wise in T-form in close proximity to each sidewall.
The evaporator surface units are preferably arranged to the furnace in such a way that a first water tube panel of each evaporator surface unit is parallel with the water tubes of the fumace ceiling, i.e. in longitudinal direction of the cross-section of the fumace. Thereby, a second water tube panel is preferably perpendicular to the first panel, i.e. in transverse direction of the furnace. In some cases, it may be advanta¬geous to arrange water tube panels of the evaporator surface units also in inclined position relative to the walls of the boiler.
When the perpendicularly connected water tube panels of the evaporator surface units are arranged parallel with the furnace walls, the water tubes of the water tube panels can be arranged in a simple way to run between the water tubes of the wa¬ter tube panel in the furnace ceiling. Naturally, if the diameters of the tubes of the water tube panels in the evaporator surface units are larger than the distances be¬tween the tubes of the water tube panel in the ceiling, i.e. the widths of the fins be¬tween the tubes, the water tubes of the ceiling must be bent in a suitable way so

that the tubes in the water tube panels have enough space to run between the wa¬ter tubes in the ceiling. A preferred method of bending the tubes in the water tube panels of the evaporator surface units in the upper part of the furnace is later dis¬cussed more in detail.
The symmetrically cross-wise set water tube panels can preferably be approxi¬mately of the same width. According to a preferred embodiment, the width of the transverse panels in the furnace is, however, about 1.5 to 2 times the width of the longitudinal panels. A sufficient evaporator surface area is thus gained, although the panels are arranged such a way that the flames of the startup burners in the front and rear walls do not reach them. Preferably an opening or openings is/are formed to the panels, especially to the lower part of the broader panels in the evaporator surface units, so as to allow free movement of the solid material in the furnace. The most preferred widths and ratios of widths of the panels depend, for example, on the number of the evaporator units and on the dimensions of the boiler furnace. The ratio of the widths of the first and second water tube panels is prefera¬bly between 1:3-3:1.
According to a preferred embodiment of the present invention, the water tubes of the water tube panels in each evaporator surface unit are connected from the upper part to separate outlet headers an-anged at different heights parallel with the water tube panels. When the water tubes of the evaporator unit are joined this way in¬stead of one outlet header to two separate outlet headers, the connecting of the water tubes to the outlet headers is made easier and the connecting tubes of the water tubes outside the furnace can be maintained short and their bendings rela¬tively simple.
Steam is led from the outlet headers, the lengths of which are preferably approxi¬mately the same as the widths of the corresponding water tube panels, preferably by means of connecting ducts to a separator for water and vapor. Especially when the boiler is a once-through utility boiler, the outlet headers of each evaporator sur¬face unit are preferably joined to each other by means of a steam pressure balancing tube. Further, the outlet headers of the evaporator surface units are preferably

joined by steam pressure balancing tubes also to the outlet headers of the water tube panels in the sidewalls of the furnace.
The water tube panels of the evaporator surface units according to the invention are preferably suspended to hang from the outlet headers of the water tube panels. Therefore, a sufficient portion, preferably at least a fourth, most preferably at least a third of the water tubes of the water tube panels is joined vertically, without bend-ings, to the lower edge of the outlet headers. The outlet headers are preferably sus¬pended to hang from the stationary supporting structure of the boiler.
Since the water tube panels of the evaporator surface units located in the fumace according to the invention are heated in the furnace from both sides, the panels must be designed, especially in once-through utility boilers, in such a way that the flow of the heated feed water is distributed in a desired way between them and the evaporator surfaces of the on only one side heated outer walls of the fumace. Ac¬cording to a preferred embodiment, the water tubes of the evaporator surfaces in the outer walls of a once-through utility boiler are conventional, smooth water tubes and the water tubes of the evaporator surfaces in the fumace are so called rifled tubes to ensure efficient heat exchange and cooling of the evaporator surfaces.
Correspondingly, the diameters of the water tubes in the evaporator surfaces inside the furnace and the distance between the tubes may be different from the diame¬ters and the distance between the water tubes in the outer walls of the boiler. Es¬pecially, when the distance between the tubes in the water tube panels of the evaporator surface units is greater than the distance between the water tubes of the furnace ceiling, the water tubes of the water tube panels in the evaporator surfaces perpendicular to the direction of the water tubes of the ceiling must be bent in such a way that at least in some locations at least two water tubes of the water tube pan¬els of the evaporator surfaces run through the same opening between the water tubes of the ceiling.
According to a preferred arrangement, the ratio between the distance of the cen¬tral points of the water tubes in the water tube panels of the evaporator surface

units and the distance between the central points of the water tubes of the ceiling of the furnace is approximately 2:3. Thereby, advantageously every second wa¬ter tube of the furnace ceiling is bent towards the adjacent tube at the points where the water tubes in the water tube panels perpendicular to the tubes of the furnace ceiling are led through the ceiling so as to provide a sufficient opening in every other space between the water tubes of the ceiling for bringing the water tubes in the water tube panels of the evaporation surface unit through the ceiling. Bringing the water tubes of the water tube panels In the evaporator surface units through the ceiling can then be arranged preferably in such a way that every third water tube runs unbent through an opening formed between the water tubes of the ceiling and the next two tubes are bent to run in line through the same open¬ing.
A regular arrangement, in which some of the water tubes run unbent through the ceiling, can be provided also when the ratio of the distance between the center points of the water tubes in the water tube panels of the evaporator surface units to the distance between the center points of the water tubes in the furnace ceiling is N:M, where N and M are unequal small integers, preferably smaller than five. If, for example, N is three and M is four, four tubes of the panel in the evaporator surface unit can be brought to run regularly through every third space between the water tubes in the ceiling, whereby every fourth tube of the panel in the evaporator sur¬face unit can run vertically.
The above described differences between the evaporator surfaces in accordance with the invention and the evaporator surfaces in the outer walls of the furnace re¬sult in that the temperature distribution in the evaporator surfaces inside the furnace does not necessarily in all situations correspond to the temperature distribution in the water tube panels in the outer walls of the boiler. These differences thus possi¬bly cause some deviation in the thermal expansion of the water tube panels in ac¬cordance with the invention compared to the thermal expansion of the rest of the boiler. Generally, large CFB boilers are suspended from above, whereby the lower part of the boiler and all equipment to be connected thereto are designed in such a way that when the boiler temperature is raised to the operational temperature and

the length of the boiler walls increases because of thermal expansion, the lower part of the boiler can move downwards even as much as tens of centimeters.
Since the temperature of the evaporator surface structures located in the furnace may be, for example, during the start up of the boiler higher than the temperature of the outer walls of the boiler, the evaporator surface structures are preferably ar¬ranged so that they can move relative to the outer walls of the furnace. According to a preferred embodiment of the present invention, this is carried out in such a way that the lower parts of the evaporator surface units in the evaporator surface struc¬ture are stationarily mounted to the boiler bottom, but the upper parts of the evapo¬rator surface units may move relative to the ceiling. Therefore, the evaporator sur¬face structure is arranged spaced apart from the sidewalls of the boiler and the out¬let headers supporting the structure are preferably suspended to hang by means of flexible elements. The strain of the flexible element for example, a spring, of the suspension is preferably adjustable in order to eliminate possible vibration in the evaporator surface unit.
In such an arrangement, it is not possible to attach the evaporator surface structure stationarily to the ceiling of the boiler, but the joint comprises a vertically flexible structure, preferably a bellows. Such a structure enables the connection of the eva¬porator surface structure gas-tight to the ceiling, but the structure may to some ex¬tent move vertically relative to the ceiling.
The invention is described more in detail below, with reference to the accompany¬ing drawings, in which
Fig. 1 schematically illustrates a vertical cross-sectional view of a circulating fluid-ized bed boiler having an evaporator surface structure in accordance with a preferred embodiment of the present invention.
Fig. 2 schematically illustrates a horizontal cross-sectional view of a circulating fluid-ized bed boiler having an evaporator surface structure in accordance with another preferred embodiment of the present invention.

Fig. 3 schematically illustrates an upper part of the evaporator surface unit in ac¬cordance with a preferred embodiment of the present invention.
Fig. 1 illustrates a CFB boiler 10 in accordance with a preferred embodiment of the present invention, comprising a furnace 12 suspended to hang from a stationary supporting structure 14 by means of suspending means 16, for example, by hanger rods. The boiler in accordance with the invention may be a natural circulation boiler, in other words a drum boiler, but most preferably it is a supercritical once-through utility boiler. The furnace is limited by a bottom 18, a ceiling 20 and sidewalls 22, which are usually of water tube structure. The furnace is also provided with other conventional parts of a CFB boiler, such as inlet means for fuel and combustion air, outlet means for flue gas and bottom ash as well as dust separators and return ducts connected thereto. For simplicity, these details, which are irrelevant in view of the present invention are not shown in Fig. 1.
The outer walls 22 of the furnace are normally manufactured of water tube panels, in which the feed water which is preheated in the heat exchange section of the flue gas channel is evaporated, i.e. turned to vapor. According to the present invention, the CFB boiler illustrated in Fig. 1 also contains an evaporator surface structure 24 arranged inside the furnace 12, the evaporator surface structure comprising three vertical evaporator surface units 26 extending from the bottom 18 of the furnace to the ceiling 20. The evaporator surface units 26 consist of two water tube panels 28, 30 connected to each other perpendicularly in a cross-wise configuration.
The preheated feed water and the possible liquid being returned from the steam separator is brought to inlet headers 32, 34 connected to the lower part of the water tube panels 28, 30 of the evaporator surface units, from where it is led to the panels 28, 30 to be evaporated, and further as vapor to the outlet headers 36, 38. If the boiler is a so called drum boiler, the driving force in getting the water and steam upwards is the weight of the liquid column in the drop leg of the drum. However, if the boiler is a so called forced circulation boiler, especially a so called supercritical once-through utility boiler, the driving force Is pressure generated by the pump of

the water cycle. The inlet headers 32, 34 and outlet headers 36, 38 are preferably arranged cross-wise parallel to the panels, at different levels relative to each other. The steam generated in the evaporator surface units 26, possibly still containing some liquid water, is led from the outlet headers 36, 38 to a steam separator (not shown in Fig. 1). The separated steam is led from the steam separator further to superheaters arranged, for example, in the flue gas channel.
The water tube panels 28, 30 are preferably suspended to hang from the support¬ing structure 14 by means of supporting means, e.g., hanger rods 40, 42, con¬nected to the outlet headers 36, 38. The water tube panels 28, 30 are preferably assembled stationarily through the bottom 18 of the furnace In such a way that the panels cannot move relative to the bottom. Since the water tube panels 28, 30 ar¬ranged inside the furnace can in some cases be at a temperature-different from that of the water tube panels of the sidewalls 22, the heat expansions of these different panels may differ from each other. Therefore, the water tube panels 28, 30 are preferably joined to the furnace ceiling 20 by means of cross-shaped bellows 44 enabling the vertical movement. In order to keep the support of the panels func¬tional in all conditions, the hanger rods 40, 42 also comprise a spring-like element 46. The strain of the flexible element of the support is preferably adjustable so as to be able to eliminate vibration of the evaporator surface unit, for example, transverse or rotary vibration.
In an embodiment in accordance with Fig. 1, all evaporator surface units 26 are identical, extending to every direction in the shape of a cross. Fig. 2 schematically illustrates a horizontal cross-section of another preferred embodiment showing that the most central 48 of the four evaporator surface units set to the furnace 12' are of the shape of a symmetrical cross, extending to every direction, but the units 50 closest to the end walls 52 of the furnace are of T-shape in such a way that the panel part on the end wall side is missing from the evaporator surface unit.
The water tube panels 54, 56 of the evaporator surface units in accordance with the invention are preferably stationarily assembled to each other in right angle fonning a durable construction, which provides a lot of additional heat exchange surface to

the furnace 12. The angle between the panels may also deviate to some extent from the right angle, especially if there are two panel parts missing from the cross-structure formed by the panels and the cross-section of the panels is of L-shape. The evaporator surface units 48, 50 are preferably arranged in line to the greatest dimension of the furnace 12, but in some cases the units may also be located oth¬erwise, for example, in two lines.
The widths of the evaporator surface units 54, 56 are preferably approximately equal. It may, however, often be advantageous to use panel widths that are to a certain extent different, for example, in such a way that the panels 54 that are transverse relative to the furnace are 1,5 to 2 times wider than the corresponding longitudinal panels 56. Thereby, the material flows coming from the front and rear walls of the furnace, in other words from the long outer walls thereof, or, for exam¬ple, the flames of the start up burners, may be arranged in such a way that they do not directly hit to the longitudinal water tube panels 56.
Especially when the width of the panel parts in the evaporator surface units is a significant portion of the corresponding dimension of the furnace, an opening 58 or openings is/are formed to the panels, especially to the lower parts thereof to enable as free flow of the solid material in the furnace as possible.
Fig. 3 'lilustrHtes more in detail the inlets of the water tube panels 62, 64 in an evaporator surface unit 60 of the shape of a symmetric cross through the furnace ceiling 20 by means of a bellows box 66, and the connecting of water tubes of the panels 62, 64 to the water cycle of the boiler. The vapor formed in evaporator sur¬face unit 60 is preferably gathered to two outlet headers 36, 38 parallel to the water tube panels 62, 64. Thereby, the extensions of the water tubes required for con¬necting the water tubes of the water tube panels 62, 64 to different sides of the out¬let headers 36, 38, and especially the tube bends 68 thereof, can be formed in a simple manner to a compact space.
The vapor gathered in outlet headers 36, 38 is guided to the steam separator by means of connecting tubes 70, 72 connected to outlet headers 36, 38. For balanc-

ing the vapor pressure, the inlet headers 36, 38 are preferably connected together by a balancing tube 74. Correspondingly, the outlet headers 36, 38 are preferably connected to outlet headers of the sidewalls (not in Fig. 3) by means of balancing tubes 76, 78. Fig. 3 also shows the attaching means 80 of the hanger rods of the evaporator surface unit 60 connected to the outlet headers 36, 38.
If the distances of the center points of the water tubes in the water tube panels 62, 64 of the evaporator surface unit 60 are the same as the distances of the center points of the water tubes 84 in the water tube panel 82 of the furnace ceiling and the diameters of the water tubes of the panels 62, 64 are smaller than widths of the fins in the water tube panel 82 of the ceiling 20 of the furnace, it is possible simply to lead the water tubes 62, 64 directly through the furnace ceiling 20 through open¬ings formed in the fins of the water tube panel 82. If the width of the fins is not suffi¬cient, the water tubes 84 of the furnace ceiling 20 must be bent to form these open¬ings through the ceiling. If, in turn, the water tubes in the water tube panels 62, 64 are situated closer to each other than the water tubes in the water tube panel 82, at least a portion of the water tubes 86 of the water tube panel 62 perpendicular to the water tubes 84 in the furnace ceiling 20 must be bent for leading the tubes through the ceiling.
According to a preferred embodiment of the present invention, a lower part of the cross-shaped bellows box 66 is stationarily connected to the water tube panel 82 of the furnace ceiling 20, and, correspondingly, a cover 88 of the bellows box is sta¬tionarily connected to the water tubes in the water tube panels of the evaporator surface unit 60. There is a flexible element 90, preferably a metal bellows, between the lower part of the bellows box 66 and the cover 88 thereof, for enabling the verti¬cal motion of the water tubes in the water tube panels 62, 64 relative to the furnace ceiling 20. The bellows box 66 and the furnace ceiling 20 together form a gas-tight construction preventing the escaping of the combustion gases and furnace particles through the furnace ceiling.
Water tubes 84' in the furnace ceiling 20 inside a branch 92 of the bellows box 66 parallel to the water tubes 84 of the furnace ceiling 20 are bent when required in

such a way that a sufficient opening (not shown in Fig. 3) is formed to lead the wa¬ter tubes of the corresponding panel portion 64 of the evaporator surface unit 60 through the ceiling. Correspondingly, water tubes 84" inside a branch 94 of the bel¬lows box 66 perpendicular to the water tubes 84 of the furnace ceiling 20 are bent, if necessary, in such a way that openings (not shown in Fig. 3) are formed to lead water tubes of the corresponding panel portion 62 of the evaporator surface unit through the ceiling.
According to a preferred embodiment of the invention, the ratio of the distance of the central points of the water tubes in the water tube panels 62, 64 of the evapora¬tor surface unit 60 and the distance of the central points of water tubes 70 of water tube panel 82 of the ceiling 20 is 2:3. Thereby, it is possible to advantageously bend three water tubes of the panel 62 to form a line parallel to the water tubes 84 of the furnace ceiling 20, which line is led through the ceiling 20 through the same opening formed between the water tubes 84". Fig. 3 does not show the bending of the water tubes in the panel 62 to line, but the upper parts of the lines thus formed are to be seen above the branch 94 of the box 66.
The invention has been described above with reference to some exemplary em¬bodiments. These embodiments are, however, not given to limit the scope of in¬vention, but the invention is limited merely by the accompanying claims and the definitions therein.

CLAIMS
1. Evaporator surface structure (24) of a circulating fiuidized bed boiler (10), comprising at least one vertical and separate evaporator surface unit (26) spaced apart from the walls of the furnace, formed of water tube panels, extending from the furnace bottom (18) of the circulating fluidized bed boiler to the ceiling (20) of the furnace, characterized in that the evaporator surface unit consists of two cross¬wise joined vertical water tube panels (28, 30).
2. Evaporator surface structure in accordance with claim 1, characterized in that frie evaporator surface stnjcture (24) comprises at least two evaporator surface units (26).
3. Evaporator surface structure in accordance with claim 1 or 2, characterized in that the water tube panels (28, 30) are perpendicular to each other.
4. Evaporator surface structure in accordance with claim 3, characterized in that the water tube panels (28, 30) of at least one evaporator surface unit are sym¬metrically cross-wise.
5. Evaporator surface structure in accordance with claim 3, characterized in that the water tube panels of at least one evaporator surface unit (50,52) are con¬nected cross-wise in T shape.
6. Evaporator surface stnjcture in accordance with claim 3, characterized in that a first water tube panel (64) of each evaporator surface unit is parallel to the water tubes (84) of the furnace ceiling (20) and a second water tube panel (62) is perpendicular thereto,
7. Evaporator surface structure in accordance with claim 6, characterized in that the ratio of the widths of the first (64) and the second (62) water tube panels is from 1:3 to 3:1.

8. Evaporator surface structure in accordance with claim 6, characterized in that the water tubes of the water tube panels (62.64) are joined from their upper part to headers (36, 38) parallel to the water tube panels.
9. Evaporator surface structure in accordance with claim 8, characterized in that the boiler is a once-through utility boiler and the headers (36, 38) of each evaporator surface unit are joined to each other by a steam pressure balancing tube (74).
10. Evaporator surface structure in accordance with claim 8, characterized in that boiler is a once-through utility boiler and the headers (36, 38) of the evaporator surface units are joined by a steam pressure balancing tube (76, 78) to the headers of the water tube panels in the sidewalls of the furnace.
11. Evaporator surface structure in accordance with claim 8, characterized in that water tube panels are suspended to hang from said headers.

12. Evaporator surface structure in accordance with claim 11, characterized in that headers are flexibly suspended to hang from the stationary supporting structure of the boiler.
13. Evaporator surface structure in accordance with claim 12, characterized in that the strain of the flexible element (46) of the suspension is adjustable in order to eliminate the vibration of the evaporator surface unit.
14. Evaporator surface structure in accordance with claim 12, characterized in that each evaporator surface unit is joined to the ceiling of the furnace by a flexible structure (66) enabling the vertical movement between the evaporator surface unit and the ceiling.
15. Evaporator surface structure in accordance with claim 14, characterized in that the structure (66) enabling the movement between the evaporator surface unit

and the ceiling comprises a bellows (90).
16. Evaporator surface structure in accordance with claim 11, characterized in
that at least a portion of the water tubes in the second water tube pane! (62) is ar¬
ranged to form lines parallel to the water tubes (84) of the ceiling (20) at the level of
the ceiling.
17. Evaporator surface structure in accordance with claim 16, characterized in
that the ratio of the distance between the center points of the water tubes (86) in the
second water tube panels (62) to the distance of the water tubes (84) of the water
tube panels in the ceiling (20) is N:M, where N and M are unequal small integers.
18. Evaporator surface structure in accordance with claim 17, characterized in
that N and M are less than five,
19. Evaporator surface structure in accordance with claim 18, characterized In
that N is 2 and M is 3.
20. A circulating fluldized bed boiler (10), comprising a bottom (18), a ceiling (20)
and a furnace (12) defined by sidewalls (22), and having an evaporator surface
staicture (14), characterized in that the evaporator surface structure Is in accor¬
dance with one of the preceding claims 1-19.

Documents:

6252-CHENP-2008 CORRESPONDENCE OTHERS. 29-10-2013.pdf

6252-CHENP-2008 AMENDED CLAIMS 12-06-2014.pdf

6252-CHENP-2008 EXAMINATION REPORT REPLY RECEIVED 12-06-2014.pdf

6252-CHENP-2008 EXAMINATION REPORT REPLY RECIEVED 11-12-2014.pdf

6252-CHENP-2008 FORM-3 12-06-2014.pdf

6252-CHENP-2008 POWER OF ATTORNEY 12-06-2014.pdf

6252-chenp-2008 abstract.pdf

6252-chenp-2008 abstract_page_1.jpg

6252-chenp-2008 abstract_page_2.jpg

6252-chenp-2008 claims.pdf

6252-chenp-2008 correspondance others.pdf

6252-chenp-2008 correspondence others.pdf

6252-chenp-2008 description (complete).pdf

6252-chenp-2008 drawings.pdf

6252-chenp-2008 form-18.pdf

6252-chenp-2008 form-3.pdf

6252-chenp-2008 form-5.pdf

6252-chenp-2008 pct.pdf

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Patent Number

265045

Indian Patent Application Number

6252/CHENP/2008

PG Journal Number

06/2015

Publication Date

06-Feb-2015

Grant Date

03-Feb-2015

Date of Filing

17-Nov-2008

Name of Patentee

FOSTER WHEELER ENERGIA OY

Applicant Address

METSANNEIDONKUJA 8, FI-2130 ESPOO,

Inventors:

#	Inventor's Name	Inventor's Address
1	LANKINEN, PENTTI,	PETAIKONKATU 22 AS 7, FI-78200 VARKAUS,

PCT International Classification Number

F22B29/06

PCT International Application Number

PCT/FI07/50284

PCT International Filing date

2007-05-18

PCT Conventions:

#	PCT Application Number	Date of Convention	Priority Country
1	FI20060488	2006-05-18	Finland