CN100408935C - Composite equal flow speed design method of angle tube type boiler flag type convection heat receiving surface - Google Patents
Composite equal flow speed design method of angle tube type boiler flag type convection heat receiving surface Download PDFInfo
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- CN100408935C CN100408935C CNB2006100431328A CN200610043132A CN100408935C CN 100408935 C CN100408935 C CN 100408935C CN B2006100431328 A CNB2006100431328 A CN B2006100431328A CN 200610043132 A CN200610043132 A CN 200610043132A CN 100408935 C CN100408935 C CN 100408935C
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Abstract
Using measures of changing tube bundle diameter of flag type convection heating surface in each stage, optimizing heat transfer temperature, pressure, and heat transfer area of heating surface in each stage, reducing flag type length of tube bundle and flow area directly, etc. the composite design method implements design for optimizing equal speed of fume flow of flag type convection heating surface in each stage so that average speed of fume flow at heating surface in each stage reaches to higher than 8m/s. it is favorable for reducing ash deposit at heating surface and enhancing heat transfer by increasing speed of fume flow. Realizing design of equal flow speed, the invention does not increase technical complexity for manufacturing membrane type wall. Advantages are: lowering ash deposit, increasing coefficient of heat transfer, reducing convection heating surface, dual energy saving from raw material and operational maintenance.
Description
Technical field
The invention belongs to the Thermal Power Engineering applied technical field, relate to a kind of Composite Uniform Flow Design Method Of Angle Pipe Type Boiler Flag Type Convective Heating Surface.
Background technology
Corner tube boiler has self-supporting, and water circulates, structural advantage and whole energy advantage that the little grade of steel quantity consumption is outstanding, as shown in Figure 1.Label shown in the figure is: 1, fire grate; 2, face arch; 3, burner hearth; 4, drum; 5, Crust blocks pipe bundle; 6, reversal chamber; 7, first order flag formula heating surface; 8, screen is cut apart in the centre; 9, wall after the tail vertical well; 10, second level flag formula heating surface; 11, rear arch; 12, third level flag formula heating surface.The corner tube boiler overall structure is that " ∏ shape " arranges that the left side is a burner hearth, and the right side is a tail vertical well, cuts apart screen 8 interfaces as burner hearth and tail vertical well with the centre.Because corner tube boiler radiation of burner hearth heating surface adopts full film water cold wall structure, flue gas temperature of hearth outlet is low, and three grades of general employings of tail vertical well flag formula convection heating surface or level Four arrange that apse rate is big.During routine corner tube boiler conceptual design, because fin panel casing assembling, manufacturing process complexity, the convection current cross-sectional shaft area generally remains unchanged, by the formula in the specification of the present invention (1) as can be known, flue gas flow rate and temperature are directly proportional, and along with the decline of flue-gas temperature, heating surface flue gas flow rates at different levels descend successively, the flue gas flow rate of final stage flag formula heating surface often is lower than 5m/s, and some designs not good enough boiler even is lower than 4.7m/s.For a long time, flue gas flow rate is low excessively, and the heating surface heat transfer coefficient descends greatly, influences the effective output of boiler; And flue gas flow rate is low excessively, causes flag formula heating surface serious flying dust deposition, particularly corner-tube hot-water boiler to occur, and the heating surface water temperature is low, and the tube wall metal temperature is low, and especially after the condensation of sulfuric acid vapor dewfall, the sticking dust stratification of low temperature is long-pending to be tied even more seriously.Some boilers need blow ash manipulation every day, do not blow ash for a long time and may cause the vexed plug of flue gas, and the air-introduced machine load increases, and the boiler operatiopn maintenance workload is big, blows ash manipulation and wastes energy, and has a strong impact on the safe operation of corner tube boiler.
For a long time, angle tube type boiler flag type convection heating surface flue gas flow rate phenomenon on the low side is never solved effectively.In recent years, the researcher has proposed some and has improved flag formula convection heating surface flue gas flow rate, improve flying dust deposition and the measure of vexed plug situation when the solution circulation road moved, these measures all do not obtain more satisfactory effect after implementing, crucial problem is that the researcher just adopts single measure simply, is difficult to receive actual effect; Also have, after adopting the variable cross-section method, screen is cut apart in wall membrane wall or centre behind the flow through shaft bend loss will the occurring of corner tube boiler, and boiler capacity increases to after the 29MW (40t/h), it is back wall or cutting apart screen all needs to be split into 2～3 self-contained dispatching from the factory of smaller screen, the difficulty of construction of bend loss field joint assembling is big, increased the complexity of membrane wall assembling, manufacturing process, is difficult to make the best of both worlds, existing improvement technology has two kinds of schemes, as shown in Figures 2 and 3:
(1) the variable cross-section design of adopting the back wall once to turn.As shown in Figure 2.Tail vertical well is entered back wall membrane wall before the third level flag formula convection heating surface formation bend loss of inwardly turning back, reduce third level flag formula tube bank length and circulation area, first order heating surface is because of the flue-gas temperature height, flue gas flow rate can reach more than the 9m/s, third level heating surface is little because of the flue gas circulation area, and flue gas flow rate can reach more than the 8m/s; And second level heating surface circulation area does not become, and flue gas flow rate only reaches more than 6m/s, and second level flue gas flow rate is on the low side;
(2) the variable cross-section design of adopting back wall secondary to turn.As shown in Figure 3, be the second level flue gas flow rate phenomenon on the low side of avoiding (1) to occur, tail vertical well is entered back wall membrane wall before second, third grade flag formula convection heating surface inwardly turns back successively and forms two bend loss, reduce second and third level flag formula tube bank length and circulation area according to the uniform flow design concept respectively, can realize the uniform flow design of three grades of flag formula heating surfaces, flue gas flow rates at different levels all can reach more than the 8m/s.But, the back wall membrane wall of tail vertical well was made up of two bend loss at a middle straight length tube panel and two ends originally, and after improving design, back wall membrane wall will be by middle three straight length tube panels, middle two bend loss of two bend loss tube panels and two ends are formed, welding and assembly technology are complicated unusually, never use aborning.
And above (1), (2) similar techniques scheme be with between burner hearth and the tail vertical well cut apart that screen (Fig. 1, sequence number 8) is turned back once backward or secondary forms bend loss, it is identical to the lifting effect of flow velocity and the problem that causes and (1), (2) scheme.
Summary of the invention
The object of the present invention is to provide the method for the compound uniform flow design of a kind of angle tube type boiler flag type convection heating surface, adopt the caliber that changes heating surfaces at different levels, optimize heating surface heat transfer temperature and pressure at different levels and heat transfer area, change the uniform flow efficient heat transfer of three kinds of composite design method realization angle tube type boiler flag type convection heating surfaces such as circulation area of final stage heating surface, effectively prevent the deposition obstruction of flying dust on heating surface.
In order to realize above-mentioned task, the present invention takes following technical solution:
A kind of Composite Uniform Flow Design Method Of Angle Pipe Type Boiler Flag Type Convective Heating Surface is characterized in that, this method comprises the following steps:
Change the tube bank diameter of three grades of flag formula convection heating surfaces of corner tube boiler, make first order flag formula heating surface tube beam diameter less than second level flag formula heating surface tube beam diameter, and second level flag formula heating surface tube beam diameter is identical with third level flag formula convection heating surface tube bank diameter;
Optimize heating surface heat transfer temperature and pressure at different levels, heat transfer area and heat output thereof, improve the flue gas mean temperature of second level convection heating surface;
The length and the circulation area that directly reduce third level flag formula heated surface bundle improve flue gas flow rate; Make first order flag formula convection heating surface flue gas flow rate greater than 9.6m/s; Second level flag formula convection heating surface flue gas flow rate is greater than 8.0m/s; Third level flag formula convection heating surface flue gas flow rate is greater than 8.0m/s.
Method of the present invention when design or improvement, does not change the tail vertical well gas flue planform and the size of membrane wall all around, does not change the tail vertical well gas flue conventional manufacturing process of membrane wall all around.
The technical scheme that the present invention proposes promptly can be applicable to the structural design of new product, can be applied to the reducing energy consumption at labour industry and boiler for domestic again, and its improvement cost is low.The know-why that this invention proposes is removed and is applied to corner tube boiler, also is adapted to all water-tube boilers.This invention technology apply the heat transfer coefficient that can significantly improve heating surface, reduce the raw materials consumption of boiler, can effectively improve exerting oneself of active service operation boiler.What is more important, compound uniform flow design can effectively prevent the serious deposition of flying dust on heating surface, save and frequently blow the great number surcharge that ash brings, guarantee the safety and economic operation of boiler, and compound uniform flow design concept is not cost with the fabrication technique of complexity, is the designing technique theory that is worthy to be popularized.
Description of drawings
Fig. 1 is the corner tube boiler full figure;
Fig. 2 is turning structure figure of wall after the tail vertical well;
Fig. 3 is wall secondary turning structure figure after the tail vertical well;
Fig. 4 is compound uniform flow method for designing key diagram, and wherein (b) is the A-A profile of (a); Label shown in the figure is: 41, rear arch; 42, screen is cut apart in the centre; 43, Crust blocks pipe bundle; 44, the back wall of tail vertical well; 45, first order flag formula convection heating surface; 46, second level flag formula convection heating surface; 47, third level flag formula convection heating surface; 48, flue is cut apart plate; 49, side wall membrane wall; 50, back wall vertical water pipe, 51, band steel; 52, flag formula water pipe tube bank.
Temperature nodes was determined and heat distribution figure when the multistage heating surface of Fig. 5 afterbody was arranged
Wherein: θ
4, θ
3And θ
2It is respectively the import cigarette temperature of three grades of flag formula convection heating surfaces;
θ
3, θ
2And θ
1It is respectively the outlet cigarette temperature of three grades of flag formula convection heating surfaces;
θ
PYBe meant the exhaust gas temperature of afterbody air preheater outlet;
t
3, t
2And t
1It not the inlet water temperature of three grades of flag formula convection heating surfaces;
t
4, t
3And t
2It is respectively the outlet water temperature of three grades of flag formula convection heating surfaces;
t
K0And t
K1The import and the outlet temperature that refer to afterbody air preheater air respectively;
Below in conjunction with accompanying drawing with adopt fine structure that this method obtains and result of calculation the present invention is described in further detail.
The specific embodiment
Composite Uniform Flow Design Method Of Angle Pipe Type Boiler Flag Type Convective Heating Surface of the present invention, adopt and change flag formula convection heating surface water pipe diameters at different levels, change flag formula convection heating surface heat transfer temperature and pressure at different levels and optimize heat transfer area, change the compound uniform flow method for designing of final stage flag formula convection heating surface tube bank length and circulation area, realize the optimal design of flag formula convection heating surface thermal property, make three grades of different heating surfaces of cigarette temperature obtain mean flow rate and reach the desirable operating mode of the above uniform flow of 8m/s.What is more important, the present invention is when optimizing thermal property, and welding and the tube panel bending technique with the membrane wall heating surface of complexity is not cost.Compound uniform flow method for designing can improve flue gas flow rate effectively, reduces the flying dust deposition; Enhancing heat transfer reduces metal consumption, realizes the dual energy-conservation of raw material and operation maintenance.
When adopting method design of the present invention or improvement, do not change the tail vertical well gas flue planform and the size of membrane wall all around, do not change the tail vertical well gas flue conventional manufacturing process of membrane wall all around.
Fig. 4 is compound uniform flow method for designing key diagram, and wherein (b) is the A-A profile of (a); Label shown in the figure is: 41, rear arch; 42, screen is cut apart in the centre; 43, Crust blocks pipe bundle; 44, the back wall of tail vertical well; 45, first order flag formula convection heating surface; 46, second level flag formula
Convection currentHeating surface; 47, third level flag formula convection heating surface; 48, flue is cut apart plate; 49, side wall membrane wall; 50, back insulation wall water pipe, 51, band steel; 52, flag formula water pipe tube bank.
Directly reduce the increase that third level flag formula convection heating surface tube bank length realizes flue gas flow rate, should be noted that: it is not to adopt the mode that changes tail vertical well periphery heated face structure shape to realize that the present invention reduces to restrain length, reduces that the flue degree of depth realizes but adopt flue to cut apart plate (sequence number 48 among Fig. 4); In view of third level flag formula convection heating surface smoke inlet temperature less than 350 ℃, therefore, select for use the enamel of mild steel spraying steel plate anti-low-temperature corrosion or pottery just can guarantee enough service life as long as adopt flue to cut apart plate 48.
The wall bag wall of tail vertical well flag formula convection heating surface is the membrane wall heating surface, and shown in figure (a), the side wall membrane wall 49 that tail vertical well is cut apart 42 (cutting apart radiation of burner hearth and afterbody convection heating surface) of screen and back wall membrane wall 44 and both sides by the centre is formed.The A-A profile has illustrated the version of wall 44 and side wall membrane wall 49 after the tail vertical well, back wall membrane wall adopts Lincoln weld or electrogas process in a row to weld by back insulation wall water pipe 50 and band steel 51, perforate is less than back insulation wall water pipe 50 on the wall vertical water pipe 44 of back because of needs for the caliber of flag formula heating surface water pipe 52, and the diameter of flag formula heating surface water pipe 52 is φ 32～φ 42 left and right sides mm; The diameter of back insulation wall water pipe 50 is generally φ 51～φ 63.5mm.In fact, according to the structure of membrane wall heating surface, the transverse pitch S1 of flag formula convection heating surface tube bank is determined that by the transverse pitch of back wall vertical water pipe the space S2 between the flag formula heating surface water pipe is exactly the passage of flue gas circulation.According to the knowledge of Principles of Boiler, the flue gas flow rate that can calculate flag formula flag formula convection heating surface as follows is as follows:
Formula (1) has provided a simple fact, that is, flue gas flow rate Wy is decided by calculated fuel consumption B
j, unit interval flue gas flow V
y, flue gas circulation area F, average flue-gas temperature θ
PjUnder the nominal situation, promptly boiler uses definite fuel under rated capacity or rated heating capacity condition, and under the close burning condition and the situation of leaking out, the flue gas volume that its Fuel Consumption and fuel combustion generate is a definite numerical value; Therefore, flue gas flow rate only and two variablees relation is arranged, that is: flue gas circulation area F, flue gas mean temperature θ
Pj
(1) flue gas circulation area F
The flue gas circulation area is a geometric parameter, and according to the A-A cutaway view of Fig. 4, flue gas flow rate can be calculated by following three geometric formulas of recombinating mutually and obtain:
F＝a×b-(X+1)×d2×b (2)
F＝[a-(X+1)×d2]×b (3)
F＝[(X+2)×S2]×b (4)
F equals the poor of tail vertical well cross-sectional area and flag formula tube bank cross-sectional area in the formula (2).
F is the transformation for mula after formula (1) extracts common factor b in the formula (3).
F is that flag formula tube bank gap and flag formula length of tube are long-pending in the formula (4).
By formula (2), (3), (4) as can be seen: increase flag formula tube bank diameter d 2, reduce flag formula tube bank gap S2, reduce flag formula tube bank length b and can reduce the flue gas circulation area, improve flue gas flow rate.
Choose less caliber and do the tube bank of first order flag formula, increase the second level and third level flag formula heating surface caliber, as first order flag formula heated surface bundle diameter d 2 is φ 32, φ 38, φ 42 or φ 45, and then the second level and third level water pipe diameter correspond to φ 38, φ 42 respectively, φ 45 or φ 48.
Because, first order flag formula heating surface 45 flue-gas temperatures are than higher, and flue gas flow rate is big, get the flue gas flow rate that little caliber helps reducing the tube bank of first order flag formula, but it is bigger that second level flag formula heating surface 46 and third level flag formula heating surface 47 flue-gas temperatures descend, and should keep bigger flag formula heating surface caliber.
Third level flag formula is heated 47 because average cigarette temperature descends, and simple dependence increases caliber and is difficult to effectively improve flue gas flow rate, therefore, must reduce flag formula tube bank length b, could improve flow velocity by efficiently and effectively.
(2) flue gas mean temperature θ
Pj
Flue gas mean temperature θ
PjBy heated medium arithmetic average temperature t
PjAddition obtains with temperature and pressure Δ t:
θ
pj＝t
pj+Δt (5)
So-called temperature and pressure Δ t is exactly the mean temperature difference of two kinds of fluids in heating surface at the corresponding levels that participates in heat exchange.By thermal conduction study as can be known, to simple following current or adverse current, temperature and pressure can be calculated as follows:
Δ t
dBe meant the two media temperature difference of a bigger end in the heating surface two ends;
Δ t
xBe meant the medium temperature difference that the other end is less.
When the flow arrangement of two kinds of fluids neither following current also under the situation of non-adverse current, as cross-current, series connection mixed flow etc.Can consider during calculating the temperature and pressure of counter-flow arrangement are revised and obtained, not repeat them here.
Formula (6) shows: temperature and pressure are decided by the maximum temperature difference Δ t of two kinds of fluids of heat exchanger inlet and outlet end
dWith minimum temperature difference Δ t
x, therefore, change Δ t
dWith Δ t
x, can obtain the temperature and pressure of the heating surfaces at different levels of distribution rationally, thereby form reasonable adjusting flue gas mean temperature and mean flow rate.Temperature nodes was determined and heat distribution figure when Fig. 5 showed the multistage heating surface of corner-tube hot-water boiler afterbody and arranges, can see θ
3And θ
2Heat transfer area, heat distribution and the flue gas mean temperature of determining to change heating surfaces at different levels of temperature nodes.On the basis of making software, heat transfer area, heat output be can optimize according to Fig. 5, rational flue gas mean temperature and rational flue gas flow rate obtained.
Designed flow velocity is meant the average speed on the flow area of flue gas mean temperature defined in the Calculation of Heat Transfer.Although people know the decisive role of flue-gas temperature to flue gas flow rate, the researcher ignores flue-gas temperature or the useful effect of heat transfer temperature and pressure on the adjusting flue gas flow rate always.And in fact, the classification of flag formula convection heating surface will be played the effect of regulating heating surface flue gas temperature and pressure at different levels and flue gas flow rate, as in order to improve second level flue gas flow rate, need be optimized to realize the optimization of flue gas flow rate first order exit gas temperature and heat transfer temperature and pressure.The key of optimizing is flue gas mean temperature maximum or a temperature and pressure maximum of guaranteeing that the gentle second level outlet of first order outlet cigarette cigarette temperature is determined.In order to optimize flue gas flow rate, we have worked out the conduct heat optimal design of temperature and pressure of the auxiliary software for calculation of corresponding calculated machine, give full play to flue gas mean temperature or temperature and pressure regulating action to flue gas flow rate, under the situation that does not reduce second level flag formula tube bank length b, flue gas flow rate is brought up to more than the 8m/s.
Performance evaluation:
According to above explanation, the applicant has worked out corner tube boiler CAD software for calculation, and on the basis of whole heating power software for calculation, embed the compound uniform flow method for designing of flag formula convection heating surface, program can design philosophy be according to the rules optimized the water pipe diameter of flag formula convection heating surfaces at different levels, the heat transfer temperature and pressure, circulation area, average flue-gas temperature and flue gas flow rate, according to compound uniform flow method for designing, our designing and calculating the corner-tube hot-water boiler of a large amount of specific model, the first order flag formula convection heating surface flue gas flow rate of optimal design is greater than 9.6m/s; Second level flag formula convection heating surface flue gas flow rate is greater than 8.5m/s; Final stage flag formula convection heating surface flue gas flow rate has been realized the uniform flow design concept of flag formula convection heating surfaces at different levels substantially greater than 8.3m/s; Particularly the flue gas flow rate of final stage convection heating surface is brought up to more than the 8.7m/s, improved whole 4m/s than the final stage convection heating surface flue gas flow rate 4.7m/s of corner tube boiler of design in the past.Table 1 has provided structure and the flow parameter summary sheet by compound uniform flow method for designing design-calculated angle tube type boiler flag type heating surface.
The structure of certain angle tube type boiler flag type heating surface of table 1 and flow parameter summary sheet
| Title | Symbol | Unit | First order flag formula heating surface | First order flag formula heating surface | First order flag formula heating surface |
| Caliber | d2×δ | mm×mm | Φ38×4.0 | Φ42×4.0 | Φ42×4.0 |
| Transverse pitch | S1 | mm | 80.00 | 80.00 | 80.00 |
| The flue gas circulation area | F | m2 | 12.27 | 11.12 | 8.72 |
| Import cigarette temperature | θ in | ℃ | 860.00 | 598.00 | 341.00 |
| Flue gas flow rate | Wy | m/s | 9.91 | 8.82 | 8.71 |
Claims (3)
1. a Composite Uniform Flow Design Method Of Angle Pipe Type Boiler Flag Type Convective Heating Surface is characterized in that, this method comprises the following steps:
Change the tube bank diameter of the flag formula convection heating surfaces at different levels of corner tube boiler, make first order flag formula heating surface tube beam diameter less than second level flag formula heating surface tube beam diameter, and keep second level flag formula heating surface tube beam diameter identical with third level flag formula convection heating surface tube bank diameter;
Optimize first, second grade heating surface heat transfer temperature and pressure and heat transfer area, promptly change heat output, improve the flue gas mean temperature of second level heating surface;
Adopting flue to cut apart plate reduces the flue degree of depth and realizes that the length and the circulation area that directly reduce third level flag formula heated surface bundle improve flue gas flow rate; Make first order flag formula convection heating surface flue gas flow rate greater than 9.6m/s; Second level flag formula convection heating surface flue gas flow rate is greater than 8.0m/s; Third level flag formula convection heating surface flue gas flow rate is greater than 8.0m/s.
2. the method for claim 1 is characterized in that, described flue is cut apart enamel or the pottery that plate is selected mild steel spraying steel plate anti-low-temperature corrosion for use.
3. the method for claim 1 is characterized in that, described first order flag formula heating surface tube beam diameter is φ 32, φ 38, φ 42 or φ 45, and then the second level and third level water pipe diameter correspond to φ 38, φ 42 respectively, φ 45 or φ 48.
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| CNB2006100431328A CN100408935C (en) | 2006-07-10 | 2006-07-10 | Composite equal flow speed design method of angle tube type boiler flag type convection heat receiving surface |
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| CNB2006100431328A CN100408935C (en) | 2006-07-10 | 2006-07-10 | Composite equal flow speed design method of angle tube type boiler flag type convection heat receiving surface |
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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102042684B (en) * | 2010-10-11 | 2013-04-24 | 无锡华光锅炉股份有限公司 | Structure for self-support tail end convection heating surface |
| CN102353143A (en) * | 2011-08-29 | 2012-02-15 | 上海新业锅炉高科技有限公司 | Compound water circulation system in corner tube-type hot-water boiler |
| CN103134040B (en) * | 2011-11-25 | 2015-01-07 | 郭强 | Angle tube type boiler coiler convection heating surface structure |
| CN103134039B (en) * | 2011-11-25 | 2015-01-21 | 郭强 | Angle tube type boiler coiler convection heating surface flue gas channel variable cross-section structure |
| CN104075745A (en) * | 2013-03-27 | 2014-10-01 | 上海赫特能源科技有限公司 | Boiler combustion test furnace |
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| CN2210359Y (en) * | 1994-09-08 | 1995-10-18 | 沈阳锅炉厂 | Composite combustion type hot water boiler |
| RU2052716C1 (en) * | 1993-11-24 | 1996-01-20 | Акционерное общество открытого типа "Центральное конструкторское бюро "Энергоремонт" | Boiler furnace bottom |
| CN2269560Y (en) * | 1996-05-22 | 1997-12-03 | 锦州第二锅炉厂 | Forced circulation cornue type water heating boiler |
| CN2577191Y (en) * | 2002-10-09 | 2003-10-01 | 王森 | Natural draught angle pipe type coal-burning pressure-bearing water-heating boiler |
| CN2695857Y (en) * | 2004-04-06 | 2005-04-27 | 开原锅炉制造有限责任公司 | Cornue boiler with protective downtake |
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Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2177162Y (en) * | 1993-10-25 | 1994-09-14 | 锦州第二锅炉厂 | Angled tube forced circulation boiler |
| RU2052716C1 (en) * | 1993-11-24 | 1996-01-20 | Акционерное общество открытого типа "Центральное конструкторское бюро "Энергоремонт" | Boiler furnace bottom |
| CN2210359Y (en) * | 1994-09-08 | 1995-10-18 | 沈阳锅炉厂 | Composite combustion type hot water boiler |
| CN2269560Y (en) * | 1996-05-22 | 1997-12-03 | 锦州第二锅炉厂 | Forced circulation cornue type water heating boiler |
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| CN1900620A (en) | 2007-01-24 |
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