CN1168458A - Steam generator - Google Patents

Abstract

One supercritical pressure varying steam generator can restrain unbalance in outlet temperature of evaporating tubes caused by the unevenly distributed heat load inside boiler and reduce heat stress in boiler ball. The evaporating tubes near the combustor and with large heat absorption are inclined to the vertical line at an angle of 15 deg and the combustor bellows is also inclined correspondingly and separated into two or three sections. The evaporating tubes at the upper and lower parts are laid vertically. Therefore, the evaporating tubes absorb heat homogeneously, have the same number at the upper, low and central parts owing to the small inclined angles and can support their self weight for simple structure. The combustor with inclined bellows is so mounted to evaporating tubes that the heat load is homogeneous.

Description

Steam raising plant

The present invention relates to the steam raising plant of supercritical pressure variable-pressure operation.

Be installed in fossil fuel such as combusting heavy oil, coal, natural gas, utilize its combustion heat to produce burner in the steam raising plant (boiler) of steam, its number also will increase if steam raising plant maximizes, its configuration mode roughly can be divided into: as shown in Figure 14 (a) and (b) at front side combustion-type that the boiler antetheca burns, opposed firing formula as shown in Figure 15 (a) and (b), and the combustion-type that circles round that is blown into to boiler central authorities from the boiler bight as shown in Figure 16 (a) and (b) in the burning of boiler front and back.

The combustion system that circles round wherein, shown in Figure 16 (b), since be fuel is aimed at the boiler center with combustion air imaginary circle tangentially is blown into and the flame that rotates in the formation of boiler central authorities except flameholding, can also make boiler load more even, and the NOx growing amount also lacks.In this case, the bellows of burner are as Figure 16 (a) and the configuration longitudinally of vertical ground as shown in Figure 17.

On the one hand, with fin many evaporation tubes are welded into tabularly, and this evaporation tube are configured to state shown in Figure 180 vertically and are assembled into boiler, boiler water rises in this evaporation tube and absorbs the heat that produces in the boiler.

; when high load capacity during with supercritical pressure operation, underload in the variable-pressure operation boiler with the subcritical pressure boiler operation; when underload; in the high heat load district, become the gas-liquid two-phase flow state of water, steam coexistence in the evaporation tube; its result can produce and make the unsettled film boiling phenomenon of tube wall temperature, thereby can damage evaporation tube.For this reason, then adopt following method in the past, that is, use that inner the special construction pipe of helical form projection shown in Figure 19 is arranged is the vertical evaporation tube of so-called reflex rifling pipe as the high heat load district, when underload, tube fluid stirred and stablize the method for tube wall temperature; Perhaps make the boiler evaporating pipe in high heat load district become about 30 ° of ground tilted configuration with respect to level, the evaporation tube number that reduces this part improves velocity in pipes and makes the stable method of tube wall temperature as shown in Figure 20.

In the existing boiler shown in Figure 18, because the difference of the position of fuel, boiler load, use burner etc., heat load distribution changes often in the boiler, its result just makes that the heat absorption distribution meeting that is configured in each vertical tube on the boiler perisporium produces from 60% to 140% very big difference as shown in phantom in Figure 11, just may produce the unbalanced greatly of metal temperature that the boiler wall exports.Its tendency does not have great difference because of its height in boiler.

In addition, in the occasion of using the boiler of inclination evaporation tube shown in Figure 20, because the evaporation tube that tilts is into helical, spiral and rise and constitute the furnace wall, though can make the change of heat load distribution in the boiler be tending towards even, but, need to use special lifting plate owing to can not lean on furnace wall tubes itself to support the weight of pot wall.Again owing to turn to the quantity of the position pipe of vertical tube to be increased to twice from the inclination evaporation tube, use the breeches pipe shown in Figure 21 or connect by connector, make structure become complicated.

And when in the prior art burner wind-box vertically longitudinally being disposed, owing to partly or on the total length of specific evaporation tube usually can not receive the radiations heat energy of combustion gas in the stove or on other specific evaporation tube, always bear high thermic load at burner, will produce big differences in absorbed heat as illustrated in fig. 12 at the boiler export place, because unbalanced, on the boiler wall, will have acted on sizable thermal stress and often caused its damage in the temperature that constitutes between the pipe of boiler wall.

The inventor is in order to solve above-mentioned the problems of the prior art, and the steam raising plant that proposes is to adopt following solution in the steam raising plant that moves aspect supercritical pressure and subcritical pressure boiler power two, the feature of its 1st solution is to make the evaporation tube that constitutes the boiler wall get vertical direction on top and bottom, then gets with respect to plumb line at middle body to become 10 ° of directions to 35 ° of inclinations; The feature of its 2nd solution is except above-mentioned feature, also makes burner wind-box tilt also to be divided into up and down multistage along the gradient of above-mentioned evaporation tube.

In above-mentioned the 1st solution, because making the evaporation tube that constitutes the furnace wall is towards having only 10 ° with respect to plumb line to the direction of 35 ° of inclinations on the central part of above-below direction, just can be across the many furnace wall width central portions of heat absorption configuration each evaporation tube in ground, bight few with heat absorption, thereby each evaporation tube heat absorption is tending towards evenly, and the temperature that alleviates the boiler wall outlet is unbalanced.

Because its inclination angle is less, thus do not need as existing spiral coil boiler, will change the pipe number on top, furnace wall, bottom and the central portion, as long as change pipe distance.Thereby also needn't use breeches pipe and tube connector plug-in unit.Again because the inclination angle is little, the deadweight of inclination evaporation tube can be supported by self and not need special suspention tool etc.

In above-mentioned the 2nd solution, because burner wind-box tilts along the gradient of above-mentioned evaporation tube, the installation site that has disperseed burner in the horizontal direction, so can make thermic load even, also because its burner wind-box is divided into 2 or 3 sections, so can make to be configured in the locational evaporation tube of burner and also to be disperseed, the heat absorption that can make each steam the ground pipe is more even.

Fig. 1 is the side view of expression the present invention the 1st embodiment boiler.

Fig. 2 is the horizontal cross of Fig. 1.

Fig. 3 is the partial enlarged drawing of Fig. 1.

Fig. 4 is the side view of expression the present invention the 2nd embodiment boiler.

Fig. 5 is the partial enlarged drawing of Fig. 4.

Fig. 6 is the horizontal cross of Fig. 4.

Fig. 7 is the cutaway view along VII-VII line among Fig. 5.

Fig. 8 is the burner stereogram among above-mentioned the 2nd embodiment.

Fig. 9 is the round vertical view that circles round when said burner is tilted.

Figure 10 is the vertical heat absorption distribution map of expression boiler evaporating pipe.

Figure 11 is the horizontal direction heat absorption distribution map of the boiler wall of above-mentioned the 1st embodiment that compares with prior art.

Figure 12 represents the plane and the boiler hot absorptivity figure of the combustion-type burner that circles round in the past.

Figure 13 is the plane and the boiler hot absorptivity figure of the burner that circles round of above-mentioned the 2nd embodiment.

Figure 14 represents an example of front side combustion-type burner portion in the past, (a) is front view, (b) is plane.

Figure 15 represents an example of opposed firing formula burner portion in the past, (a) is front view, (b) is plane.

Figure 16 represents an example of the combustion-type burner portion of circling round in the past, (a) is front view, (b) is plane.

Figure 17 is a detail drawing local among Figure 16 (a).

Figure 18 is the side view of the expression example in vertical tube boiler wall in the past.

Figure 19 is the fragmentary perspective cross sectional view of one of the expression particular tube of using in the high heat load portion of vertical tube wall in the past example.

Figure 20 is the side view of one of expression spiral coil furnace wall in the past example.

Figure 21 is the figure (detail drawing of XXI portion among Figure 20) of one of the breeches pipe that uses on the spiral coil furnace wall that is illustrated in the past example.

Embodiment:

Fig. 1 is the boiler side view of expression the present invention the 1st embodiment, and Fig. 2 is its horizontal cross, and Fig. 3 is a partial enlarged drawing among Fig. 1.

In the present embodiment, constitute the evaporation tube of boiler wall (1), its underpart evaporation tube (2) is along vertical direction with top evaporation tube (4) and the evaporation tube (3) of central portion is to dispose along the direction that only becomes 15 ° of inclinations with respect to plumb line.Vertical direction heat absorption in the boiler distributes as shown in Figure 10, and the top from hypomere burner position to epimere burner is the high heat load band.In the present embodiment, dispose to evaporation tube (4), (2) under the burner wind-box from heat absorption rate low upper boiler and bottom vertically, the burner region that absorbs heat at height then disposes evaporation tube (3) with about 15 ° inclination angle.

Below, evaporation tube spacing, caliber and the fin width of present embodiment are described according to Fig. 3.The evaporation tube of bottom (2), because the specific volume of tube fluid is little, external diameter of pipe is that 28.6mm, tube pitch are 44.5mm.Fin width is 15.9mm.The evaporation tube of central portion (3) has identical external diameter 28.6mm, and the pipe distance is 43.0mm (44.5mm * COS15 a °), and fin width is 14.4mm, in the top evaporation tube (4), because the steam containing ratio increases the pressure loss and becomes big in the pipe, external diameter of pipe increases to 31.8mm.Pipe is apart from being all 44.5mm mutually with the bottom, and fin width is 12.7mm, and its result makes the easier adjusting of all assignment of traffic.

In the present embodiment, the high burner district that thermic load is the highest (furnace wall short transverse central portion) constitutes with the evaporation tube with respect to the about 15 ° of inclinations of plumb line, make boiler heat absorption accumulative total be tending towards even significantly, promptly, shown in solid line among Figure 11, be maximum 120%, minimum 80%, the result who nearly 1/2 the unbalanced situation in past is carried out analog computation distinguishes, confirms that it has the unbalanced effect of sizable inhibition temperature.

The heat absorption pattern of boiler has same tendency substantially near burner top from the boiler bottom, this is confirmed by actual.Width as for the furnace wall, for the burner of bight burning be become each furnace wall the middle body heat absorption at most and heat absorption minimum ground in bight, the left and right sides distributes substantially symmetrically, only tilt 15 ° evaporation tube when constituting the furnace wall when using with respect to plumb line, and each evaporation tube becomes from bottom to the top of boiler and laterally moves 1/2 state that only is about the furnace wall width.That is, 1 evaporation tube is by big two zones little with heat absorption of heat absorption, so make heat absorption evenly.

The evaporation tube of above-below direction middle body is tilted under 15 ° the situation with respect to plumb line in the present embodiment, in the example of above-mentioned size, the difference of the pipe distance of its rake and vertical portion only is 3.4%, so do not use breeches pipe and tube connector plug-in unit also inclination and vertical pipe can be coupled together.Become the inclination evaporation tube in the past shown in Figure 20 of 30 ° of inclinations to compare with relative level and since in the present embodiment to the stress reduction of vertical load to about 1/2, so can pass by act on the special suspention plate that the stress on the furnace wall tubes uses for reduction.

Inclination evaporation tube of the present invention is with respect to the inclination angle of plumb line, can be in 10 ° to 35 ° scope when practical value.Can lose the effect that it corrects the heat load distribution inequality during 10 ° of less thaies, tipping tube can not be supported its deadweight when surpassing 35 °.

Fig. 4 is the boiler side view of the present invention the 2nd embodiment, and Fig. 5 is the partial enlarged drawing of Fig. 4, and Fig. 6 is the horizontal sectional drawing of Fig. 4, and Fig. 7 is the VII-VII line cutaway view among Fig. 5, and Fig. 8 is the stereogram of the burner among the 2nd embodiment.

Present embodiment is also the same with the 1st embodiment, constitutes in the evaporation tube of furnace wall (1), and bottom evaporation tube (2) and top evaporation tube (4) are along vertical direction, and the evaporation tube of central portion (3) plumb line relatively only tilts 15 °.In the present embodiment, burner wind-box (5) is tilted along the incline direction of above-mentioned evaporation tube (3), and be divided into 3 sections up and down, the center of the burner wind-box that respectively is partitioned into (5) is arranged on the roughly same plumb line, though thereby each burner horizontal direction position is different, also can spray to the tangential direction of imaginary circle in the horizontal section (6) to fuel and combustion air from each burner, and fuel and air nozzle are become along having a down dip 30 ° structure on about 15 ° of plane inclined.

In aforesaid embodiment, because burner wind-box (5) is divided into 3 sections up and down, and with respect to 15 ° of plumb line inclinations, so the installation site of burner has nothing in common with each other on the horizontal direction of furnace wall, the thermic load of burner height, higher near the burner blow-off outlet, ejection portion moves thermic load and also just is in the direction that is tending towards average.

And near burning portion, be not subjected to the thermal-radiating pipe that produces in the stove and be subjected to bigger thermal-radiating pipe close, produce temperature difference at these Guan Shanghui, but in the present embodiment, since the center configuration of each bellows (5) that is divided into multistage on the same distance of furnace wall side, and, making the evaporation tube (3a) that bears each more photothermal evaporation tube of bellows portion and not raying heat have nothing in common with each other with respect to 15 ° of plumb line inclinations, the result diminishes the temperature difference of boiler wall outlet.That is, have on the stove width of cloth direction of boiler export as shown in Figure 12 in the past 60～140% sizable inhomogeneous, but be 85～120% as illustrated in fig. 13 then in the present embodiment, obtained improving significantly.Thereby, reduced the unbalanced of furnace wall outlet metal temperature further, reduced the stress of boiler wall significantly.

In addition, in the present embodiment, as mentioned above, bellows (5) are tilted according to the gradient of evaporation tube (3), its result makes the bending of burner portion pipe become easy.

Again since the fuel of present embodiment and air nozzle can on have a down dip 30 °, when boiler during at high load capacity, making burner is level or downwards, when underload, makes progress for the control vapor (steam) temperature makes it.When burner was made progress, imaginary circle (6) will diminish as illustrated in fig. 9, makes the enhancing of circling round, even also can burn steadily when underload.

Use the present invention can make the boiler evaporating pipe even extraordinarily, can reduce the mutual temperature difference of boiler evaporating pipe outlet significantly in the heat absorption distribution of furnace wall width.Thereby reduce the stress of the boiler wall of causing, make it the running continuously of long-term safety ground owing to this temperature difference.Nor breeches pipe and tube connector plug-in unit needing in spiral coil boiler in the past do not need special reinforcement etc. yet.

Claims (2)

1. steam raising plant, can under supercritical pressure and two kinds of situations of subcritical pressure boiler, turn round, it is characterized in that, vertical direction is got in the top and the bottom that constitute the evaporation tube (2,3,4) of boiler wall (1), and middle body is then respectively towards only being 10 ° of directions to 35 ° of inclinations with respect to plumb line.

2. the steam raising plant described in claim 1 is characterized in that, burner wind-box (5) is along the gradient of above-mentioned evaporation tube (3) and tilt, and is divided into multistage up and down.

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