CN112664966A - Steam jet parameter design method of steam soot blower - Google Patents
Steam jet parameter design method of steam soot blower Download PDFInfo
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Abstract
The invention relates to a steam jet parameter design method of a steam soot blower, wherein the steam soot blower comprises a steam soot blower, a gun barrel and a nozzle assembly, the nozzle assembly comprises a first nozzle assembly and a second nozzle assembly, the first nozzle assembly comprises a throttling pipe with a throttling shrinkage hole arranged inside, and the throttling pipe is arranged inside the throttling pipe; the second nozzle assembly includes a venturi nozzle in communication with the barrel, and the design method includes marking the throttle tube, the venturi nozzle, and designing various parameters of the throttle tube or the venturi nozzle. The design method of the invention can improve the steam purging uniformity, the circumferential radians of the heating area and the purging area of the nozzle assembly of the soot blower are correspondingly increased along with the increase of the radius of the rotor of the air preheater, and the circumferential angles corresponding to the purging tracks of each group are approximately equal, so that the heating and purging steam quantities of the heat exchange elements in unit area of different areas in the radial direction of the rotor tend to be consistent, and the phenomena of under-blowing of the heat exchange elements at the outer side of the rotor of the air preheater and over-blowing of the heat exchange elements at the inner side of.
Description
Technical Field
The invention relates to a steam soot blower, in particular to a steam jet parameter design method of the steam soot blower.
Background
The conventional rotor rotary air preheater matched with the coal-fired power plant boiler is divided into a smoke sub-bin, a secondary air sub-bin and a primary air sub-bin in the circumferential direction, a rotor consists of an upper flat plate type heat exchange element and a lower flat plate type heat exchange element, and the rotary process sequentially passes through the smoke sub-bin, the secondary air sub-bin and the primary air sub-bin to perform periodic heat storage and heat release processes: in the flue gas sub-bin, high-temperature flue gas passes through the heat exchange element from top to bottom, the heat release temperature of the flue gas is reduced, and the heat storage temperature of the heat exchange element is increased; in the secondary air sub-bin and the primary air sub-bin, cold secondary air and cold primary air pass through the heat exchange element from bottom to top, the heat absorption temperature of cold air is increased, and the heat release temperature of the heat exchange element is reduced. In the flue gas sub-bin, ammonia escaping from the upstream SCR denitration system and SO in the flue gas3Ammonium bisulfate deposition ash is easily formed on the surface of the heat exchange element at the cold end of the rotor of the air preheater to block a flue gas channel between the heat exchange elements.
In order to keep the channels between the heat exchange elements of the air preheater smooth, steam soot blowers are generally arranged above the hot end heat exchange element and below the cold end heat exchange element of the flue gas bin-divided rotor, the surfaces of the heat exchange elements are intermittently and online washed by steam jet, and the surface deposition ash is blown off by shearing. In the flue gas sub-bin, flue gas flows through the heat exchange element from top to bottom, the steam jet of the hot-end steam soot blower blows downwards in a downstream mode, the steam jet of the cold-end steam soot blower blows upwards in a counter-current mode, the steam pressure in a barrel of the soot blower is about 0.8-1.07 MPa, and the temperature is about 300-350 ℃.
In order to improve the purging effect of ammonium bisulfate deposition ash among the heat exchange elements of the air preheater, the steam soot blower tries various technical improvements:
patent publication No. CN208566739 discloses a high-pressure water online cleaning device for a rotary air preheater, which contains high-pressure water and steam together to form a dual-fluid soot blower, and can spray high-pressure water and steam for blowing soot separately.
The patent with publication number CN204881327 discloses a steam soot blower for a rotary air preheater and the paper "optimization of blowing track and operation mode of an air preheater soot blower", which propose a rake type multi-nozzle soot blower based on a single-pipe nozzle to improve the retention time of a steam blowing section of a rotor heat exchange element.
The patent with publication number CN111623365 discloses a rotary air preheater refined automatic soot blowing system and a soot blowing control method, and provides an online monitoring method for the fouling blockage of a heat exchange element, and a steam soot blower is automatically determined to be put into operation according to the fouling degree.
In the air preheater steam soot blower technology, CN204881327 increases the residence time of a steam purging cross section of a heat exchange element of an air preheater rotor on the circumference, but for high-cohesiveness deposited ash containing ammonium bisulfate, the effect of the conventional steam soot blower is limited, mainly because when jet steam reaches the surface of the heat exchange element, although the central jet flow speed of 80-120 m/s is still kept, the temperature of the purged steam is reduced to about 100-150 ℃ due to entrainment of surrounding low-temperature flue gas. In the face of high-viscosity deposition ash containing ammonium bisulfate, even if the steam jet has a strong scouring and shearing effect, the strength of the deposition ash cannot be weakened by heating and gasifying the ammonium bisulfate in the deposition ash due to low temperature of jet steam, and the sweeping effect of the steam soot blower on the deposition ash containing the ammonium bisulfate is also seriously reduced.
Disclosure of Invention
The invention aims to provide a steam jet parameter design method of a steam soot blower.
In order to achieve the purpose, the invention adopts the technical scheme that:
a steam jet flow parameter design method of a steam soot blower is used for a rotary air preheater, the steam soot blower comprises a steam soot blower, a gun barrel communicated with the steam soot blower and a plurality of nozzle assemblies communicated with the gun barrel, each nozzle assembly comprises a first nozzle assembly and a second nozzle assembly, each first nozzle assembly comprises a throttle pipe communicated with the gun barrel at one end and connected with a spray head at the other end, and a throttle shrinkage cavity is formed in each throttle pipe; the second nozzle assembly comprises a venturi nozzle communicated with the gun barrel, and the design method comprises the following steps:
marking the throttle pipe as 1, marking the Venturi nozzle as 2, marking the inlet of the throttle pipe as (1, 0), marking the throttle shrinkage cavity as (1,1), and marking the outlet of the throttle pipe as (1, 2); the inlet of the Venturi nozzle is marked as (2,0), the throat of the Venturi nozzle is marked as (2,1), the outlet of the Venturi nozzle is marked as (2,2), and the steam flow G of a single throttle pipe or the Venturi nozzle is designed1Comprises the following steps:
wherein: a. the1The cross section area of the throat of the throttle pipe or the Venturi nozzle; c. C1The steam velocity at the throat of a throttle pipe or a venturi nozzle; v. of1Is the specific volume of steam; h is0Stagnation vapor enthalpy in the barrel; p1Critical steam enthalpy at the throat of a throttle pipe or a venturi nozzle; p0Stagnation steam pressure in the gun tube; p1Critical steam pressure at the throat of a throttle pipe or a venturi nozzle; gamma is the adiabatic coefficient of the superheated steam.
Preferably, the steam flow G of a single throttle pipe or a Venturi nozzle is designed1The method comprises the following steps: h is0According to the steam pressure P0And temperature T0Checking enthalpy and entropy diagram, and obtaining critical pressure P at throttle shrinkage cavity and Venturi nozzle throat position by using isentropic principle1Then, searching an enthalpy entropy diagram to obtain steam enthalpy h1And specific volume v1。
Preferably, the steam velocity c of the spray holes on the top surface of the spray head is designed1，2Comprises the following steps:
wherein: v. of1,2The specific volume of steam of a jet hole on the top surface of the spray head; a. the1，2The surface area of the top of the spray head; phi is the ratio of the flow area of the jet hole.
Further preferably, the steam velocity c of the injection holes of the top surface of the shower head is designed1，2The method comprises the following steps: stagnation steam pressure P in gun barrel0And temperature T0After the steam enthalpy is determined, the temperature and specific volume v of the decompressed and expanded steam are searched on an enthalpy-entropy diagram according to the steam pressure at the outlet of the spray nozzle1,2。
Preferably, the steam velocity c of the venturi nozzle outlet is designed2,2Steam flow rate G2,2And the steam flow deviation xi is as follows:
wherein: h is2,2Is the vapor enthalpy at the outlet of the venturi nozzle; c. C2,2Is the venturi nozzle outlet steam velocity; a. the2,2Is the venturi nozzle exit area; v. of2,2The specific volume of the steam at the outlet of the Venturi nozzle; g2,1Is the steam flow of the throat of the Venturi nozzle.
Further preferably, the steam velocity c of the venturi nozzle outlet is designed2,2Steam flow rate G2,2The method comprises the following steps: by stagnation of steam pressure P in the barrel0And temperature T0Determining enthalpy value and entropy value, and setting Venturi nozzle outlet steam pressure P2,2The initial value is the critical pressure P of the throat of the Venturi nozzle2,1When the steam flow deviation xi is more than 5%, adjusting the steam pressure at the outlet of the venturi nozzle to be 1.1 times of the previous value, and searching the enthalpy-entropy diagram again to calculate the steam flow at the outlet of the venturi nozzle; when the deviation is less than-5%, adjusting the outlet steam pressure of the Venturi nozzle to be 0.9 times of the previous value, and searching the enthalpy entropy diagram again to calculate the steam flow of the outlet Venturi nozzle until the deviation of the two is not more than +/-5%.
Preferably, designing the steam sweeping radius R, sweeping central jet speed c, jet flow G of the steam sweeping section and central jet temperature T of the steam sweeping section of the Venturi nozzleaComprises the following steps:
wherein: r2Is the venturi nozzle exit radius; s is the distance from the outlet of the Venturi nozzle to the lower surface of the heat exchange element at the cold end of the rotor; theta is a venturi nozzle spread angle; t iseIs ambient temperature; t is2,2Is the venturi nozzle outlet steam temperature.
Preferably, the steam consumption G of the steam soot blower is designedtotalComprises the following steps:
in the formula: g1，jThrottling the steam flow of the pipeline for the jth group of nozzle assemblies; g2，j，iThe steam flow of the ith Venturi nozzle of the jth nozzle assembly; n is the total number of nozzle assemblies; m isjThe total number of venturi nozzles of the j-th nozzle assembly; j is the nozzle assembly of the second group; i is the second venturi nozzle.
Preferably, the method further comprises evaluating the steam heating and purging effect of the steam sootblower:
(1) the nozzle assembly on the gun barrel forms a steam heating area and a purging area on the lower surface of a cold end heat exchange element of the air preheater rotor, and the central angle corresponding to the arc length in the circumferential direction of each area is designed as follows:
(2) the residence time of the heat exchange elements of the air preheater rotor in the circumferential direction passing through the steam heating area and the purging area of each nozzle assembly is designed as follows:
(3) according to the steam flow of the throttle pipe and the Venturi nozzle, the heating steam flow and the purging steam flow of different groups of nozzle assemblies are designed:
M1,j＝G1，1,j (17)
(4) after obtaining the heating steam flow of every group nozzle assembly and sweeping the steam flow, according to the heating and the area of sweeping on the circumference of the radial position of the air preheater rotor of every group nozzle assembly, the steam receiving quantity of the heat exchange element in unit area on the design circumference:
(5) the relative deviation method is adopted, the unit area heat exchange element of the n groups of nozzle assemblies is designed to receive the relative deviation of the heating steam quantity, and the unit area heat exchange element of the n groups of nozzle assemblies is designed to receive the relative deviation of the blowing steam quantity:
in the formula: ag1，jThe central angle corresponding to the j group of heating areas; a. therc，jThe arc length of the heating area of the j group is the arc length of the heating area of the j group; rr，jThe radius of the air preheater rotor corresponding to the j group of nozzle assemblies; ag2，jThe central angle corresponding to the jth group of purging areas; riThe vapor purge radius of the venturi nozzle; delta tau1，jThe time for the heat exchange element at the cold end of the rotor to stop in the j group of heating areas is determined; delta tau2，jThe time for the heat exchange element at the cold end of the rotor to stop in the purge area of the j group is taken as the time; c. CrpmThe rotational speed of the air preheater rotor; m1，jThe heating steam flow of the j group of nozzle assemblies; g1，1，jThe steam flow at the throttling shrinkage hole of the j group of nozzle assemblies; m2，jPurge steam flow for the jth group of nozzle assemblies; g2，1，j,iThe steam flow at the throat of the ith Venturi nozzle of the jth nozzle assembly is measured; SFUA1，jThe heating steam quantity received by the heat exchange element at the j group of nozzle assemblies in unit area of the cold end of the rotor is used; SFUA21，jThe purge steam amount received by the heat exchange element at the j group of nozzle assemblies in unit area of the cold end of the rotor is used; RD1，jThe heating steam quantity of the j group of nozzle assemblies is relatively deviated; RD2，jThe relative deviation of the purge steam amount for the j-th group of nozzle assemblies.
Further preferably, the relative deviation of the amount of hot steam is less than ± 10%, and the relative deviation of the amount of purge steam is less than ± 20%.
Due to the application of the technical scheme, compared with the prior art, the invention has the following advantages:
the design method of the invention can improve the steam purging uniformity, the circumferential radians of the heating area and the purging area of the nozzle assembly of the soot blower are correspondingly increased along with the increase of the radius of the rotor of the air preheater, and the circumferential angles corresponding to the purging tracks of each group are approximately equal, so that the heating and purging steam quantities of the heat exchange elements in unit area of different areas in the radial direction of the rotor tend to be consistent, and the phenomena of under-blowing of the heat exchange elements at the outer side of the rotor of the air preheater and over-blowing of the heat exchange elements at the inner side of.
Drawings
FIG. 1 is a schematic front view of a rotary air preheater according to the present embodiment;
FIG. 2 is a schematic top view of the rotary air preheater of the present embodiment;
FIG. 3 is a front view of the nozzle assembly of this embodiment;
FIG. 4 is a schematic diagram of the temperature distribution at the circumferences of the hot end and the cold end of the heat exchange element of the air preheater in this embodiment;
FIG. 5a is a cross-sectional view of a throttle tube;
FIG. 5b is a cross-sectional view of a venturi nozzle.
In the above drawings:
1. a rotor; 10. a central sleeve; 11. dividing the smoke into bins; 12. primary air separation; 13. secondary air is divided into bins; 130. a cold secondary air inlet duct; 131. a hot secondary air outlet duct; 14. a seal member; 15. a heat exchange element; 150. a cold end bottom surface; 151. a cold end top surface; 152. a hot end top surface; 20. a steam soot blower; 21. a barrel; 22. a throttle pipe; 220. throttling and reducing the hole; 221. a resistance block; 23. a spray head; 24. a distribution pipe; 25. a venturi nozzle; 26. a three-way pipe; 30. a heating zone; 31. a purging zone; 4. deposition temperature interval of ammonium bisulfate.
Detailed Description
The technical solutions of the present invention will be described clearly and completely with reference to the accompanying drawings, and it should be understood that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
As shown in fig. 1 and 2, the rotary air preheater with a steam soot blower includes a rotor 1 rotating around a central sleeve 10, a flue gas sub-bin 11, a primary air sub-bin 12 and a secondary air sub-bin 13 are distributed in the rotor 1 along the circumferential direction thereof, the flue gas sub-bin 11, the primary air sub-bin 12 and the secondary air sub-bin 13 are spaced by a sector seal 14, and a metal heat exchange element 15 is disposed on the rotor 1. The rotation process is in proper order through flue gas branch storehouse 11, overgrate air branch storehouse 13 and primary air branch storehouse 12, carries out periodic heat accumulation, exothermic process: in the flue gas sub-bin 11, high-temperature flue gas passes through the heat exchange element 15 from top to bottom, the heat release temperature of the flue gas is reduced, and the heat storage temperature of the heat exchange element 15 is increased; in the primary air sub-bin 12 and the secondary air sub-bin 13, cold primary air and cold secondary air pass through the heat exchange element 15 from bottom to top, the heat absorption temperature of cold air is increased, and the heat release temperature of the heat exchange element 15 is reduced.
The air preheater further comprises a steam soot blower which is arranged in the secondary air sub-bin cold secondary air inlet air duct 130 and close to the sealing member 14 at one side of the flue gas sub-bin 11.
As shown in fig. 3: the steam sootblower includes a steam sootblower 20, lance tubes 21 communicating with the steam sootblower 20 extending in a radial direction of the rotor 1, and a plurality of sets of nozzle assemblies communicating with the lance tubes 21.
The total length of the gun barrel 21 is equal to the radius of the rotor 1, the gun barrel 21 is divided into n sections at equal intervals of 1-2 m, n groups of nozzle assemblies are arranged at intervals from inside to outside along the radial direction of the rotor 1 according to the length of each section, namely the number of the nozzle assemblies is increased from the 1 st group to the n th group from the end of the gun barrel 21 close to the central sleeve 10 to the outermost side of the rotor 1. The gun tube 21 is movably arranged in the radial direction of the rotor 1, and the moving stroke of the gun tube 21 in the radial direction of the rotor 1 is the distance between two adjacent nozzle assemblies.
The nozzle assembly includes a first nozzle assembly, a second nozzle assembly, the first nozzle assembly being located upstream of the second nozzle assembly in a direction of rotation of the rotor. Wherein:
the first nozzle assembly comprises a throttling pipe 22 with one end communicated with the gun barrel 21 and a nozzle 23 communicated with the other end of the throttling pipe 22, a throttling shrinkage cavity 220 and a circular resistance block 221 positioned at the downstream of the throttling shrinkage cavity 220 are arranged in the throttling pipe 22, the throttling shrinkage cavity 220 and the resistance block 221 are connected with the throttling pipe 22 through nuts, the aperture of the throttling shrinkage cavity 220 is smaller than the pipe diameter of the throttling pipe 22, and the inlet caliber of the nozzle 23 is smaller than the outlet caliber of the nozzle. The length of the throttle pipe 22 is 400-500mm, and the pipe diameter is 20-30 mm.
In this embodiment: the spray head 23 comprises a quadrangular pyramid cavity body with the bottom communicated with the throttle pipe 22 and an arc top surface covering the top of the pyramid cavity body, the top surface is provided with a spray hole, and the distance between the top surface of the spray head 23 and the lower surface of the cold end heat exchange element 15 is 10-15 mm. The spray holes are uniformly and densely distributed on the top surface of the spray head 23, the diameter of the spray holes is about 1-3 mm, the sum of the areas of the spray holes is about 40% -60% of the area of the top surface of the spray head 23, and particularly, a shower type spray head can be adopted. In addition 23 arc top surface of shower nozzle is that venturi nozzle 25 efflux steam sweeps radial 1.0 ~ 1.5 times at rotor 1 radial width, and the arc length is that venturi nozzle 25 efflux steam sweeps radial 1 ~ 6 times, and the arc length increases along with the grow of nozzle assembly serial number.
After high-pressure high-temperature steam in the gun barrel 21 passes through the throttling shrinkage hole 220, the resistance block 221 and the spray head 23, the high-pressure high-temperature steam is decompressed and expanded into low-pressure high-temperature steam under the heat insulation and non-work-doing isenthalpic principle, the temperature of the steam in the spray head 23 is about 300 ℃, the static pressure of the steam is slightly higher than that of external cold secondary air by 200-500 Pa, the speed of steam jets at the outlet of spray holes on the top surface of the spray head 23 is about 20-30 m/s, the steam jets are converged into a vertical upward low-speed high-temperature steam jet, the speed of the jet entering a 15 channel of a cold-end heat exchange element of the rotor 1 is about 15-23 m/s, a steam heating area is formed on the circumference, the speeds of the low-speed high-temperature steam jets of different numbered nozzle assemblies are equal, the flow is set through the diameter of.
The second nozzle assembly includes a distribution tube 24 in communication with the barrel 21, at least one venturi nozzle 25 in communication with the distribution tube 24. The distribution pipes 24 can be made of a rake type blow pipe, for example, 1-5 venturi nozzles 25 of the same type are arranged on each distribution pipe 24, and the number of the venturi nozzles 25 on the distribution pipe 24 gradually increases as the number of the nozzle assemblies increases from the 1 st group to the nth group. The diameter of the throat of the Venturi nozzle 25 is about 6-10 mm, the diameter of the outlet is about 8-12 mm, the diffusion angle is 10-15 degrees, under the principle of isentropic technical work of adiabatic decompression expansion, the speed of the steam jet at the outlet reaches 1-2 times of Mach number, the temperature is rapidly reduced to about 100-150 ℃, the expansion distance between the throat and the outlet of the Venturi nozzle 25 is properly reduced, the steam jet at the outlet is in an incomplete expansion state, the temperature of the steam jet is greater than 120 ℃, and the pressure is about 0.2-0.3 MPa and is higher than the atmospheric pressure of the surrounding environment. The distance between the outlet of the venturi nozzle 25 and the lower surface of the cold end heat exchange element 15 is about 400-600 mm, the purging radius of the steam jet of the single venturi nozzle 25 on the lower surface of the heat exchange element 15 is about 50-100 mm, the center distance between every two adjacent venturi nozzles 25 is equal to 0.5-1 steam jet purging radius, the steam jet purging tracks of the same group of venturi nozzles 25 are overlapped by 0.5-1 purging radius, and a steam purging area is formed along the circumference. After a large amount of ambient cold secondary air is sucked along the way, the central speed of the steam jet when the steam jet reaches the lower surface of the heat exchange element 15 is reduced to about 100-150 m/s, the temperature of the steam jet is gradually reduced, and the temperature of the steam jet is kept to be close to 100 ℃ by means of gradual release of latent heat of steam gasification.
The throttle pipe 22, the distribution pipe 24 and the gun barrel 21 are connected through a tee 26 and nuts, and the distance between the tee 26 and the gun barrel 21 is 10-20 mm. The centre line of the throttle pipe 22, the centre line of the distribution pipe 24 and the centre line of the venturi nozzle 25 extend in the axial direction of the rotor 1, and the centre line of the barrel 21 extends in the radial direction of the rotor 1.
The boiler steam enters a gun barrel 21 of a steam soot blower 20 after throttling and pressure reduction, after further pressure reduction and expansion through a high-low speed nozzle assembly, two kinds of vertical upward steam jet flows of low-speed high-temperature and high-speed low-temperature are formed at a plurality of radial positions of a rotor 1 in a cold secondary air duct, the steam jet flows in the same direction with cold secondary air and enters a cold-end heat exchange element 15 channel of an upper rotor 1 from bottom to top, the heat exchange element 15 firstly passes through ammonium bisulfate in deposition ash on the surface of a gasification heating area heat exchange element 15 formed by the low-speed high-temperature steam jet flow in the circumferential rotation process, the deposition ash is removed through a purging area formed by the high-speed low-temperature steam jet flow, and the gasified ammonium bisulfate and stripped deposition ash enter a boiler hearth along.
The gun barrel 21 is radially from inside to outside at rotor 1, and the central angle size that the circumference arc length of the 1 st group to the n th group's nozzle assembly's fan-shaped heating region corresponds is close, and rotor 1 cold junction heat exchange element 15 is no less than 0.2s at the dwell time of each group steam heating region, and the dwell time in each group steam purging region is no less than 0.2 s. The gun tube 21 can be intermittently pushed and directly retreated, the pushing step length is 0.5-1 times of the steam purging radius of the Venturi nozzle on the lower surface of the heat exchange element, the overlap of purging tracks is increased when the multiple is small, and the air preheater rotor rotates for 1-2 circles within the stopping time of each step length. According to the degree that the differential pressure on the flue gas side of the air preheater displayed by the DCS online analyzer of the unit is higher than the design value, the steam soot blower is operated for 1 time at different time intervals of 8 hours, 1 day and 1 week, and the larger the degree that the differential pressure on the flue gas side is higher than the design value, the shorter the soot blowing interval time is.
The following details describe the steam jet parameter design of the steam sootblower in this embodiment:
marking the throttle pipe as 1, marking the Venturi nozzle as 2, marking the inlet of the throttle pipe as (1, 0), marking the throttle shrinkage cavity as (1,1), and marking the outlet of the throttle pipe as (1, 2); the inlet of the venturi nozzle is marked (2,0), the throat of the venturi nozzle is marked (2,1), the outlet of the venturi nozzle is marked (2,2),
the steam flow of the throttle pipe and the Venturi nozzle can be calculated by adopting the formulas (1) to (3) according to the critical steam states of the throttle shrinkage cavity and the Venturi nozzle throat position 1. Wherein h is0According to the steam pressure P0And temperature T0Checking enthalpy and entropy diagram, and obtaining critical pressure P at throttle shrinkage cavity and Venturi nozzle throat position by using isentropic principle1Then, searching an enthalpy entropy diagram to obtain steam enthalpy h1And specific volume v1Designing the steam flow G of a single throttle pipe or a Venturi nozzle1Comprises the following steps:
wherein: a. the1The cross section area of the throat of the throttle pipe or the Venturi nozzle; c. C1The steam velocity at the throat of a throttle pipe or a venturi nozzle; v. of1Is the specific volume of steam; h is0Stagnation vapor enthalpy in the barrel; p1Critical steam enthalpy at the throat of a throttle pipe or a venturi nozzle; p0Stagnation steam pressure in the gun tube; p1Critical steam pressure at the throat of a throttle pipe or a venturi nozzle; gamma is the adiabatic coefficient of the superheated steam.
The pressure of the steam at the outlet of the spray head is 200-500 Pa higher than that of the external environment, the steady flow steam before and after the throttling and shrinking hole in the throttle pipe belongs to an adiabatic expansion work-free isenthalpic process, and the pressure P of stagnation steam in the gun pipe is used0And temperature T0After determining the enthalpy of the steam, according toThe pressure of the steam at the outlet of the nozzle is checked on an enthalpy-entropy diagram to obtain the temperature and specific volume v of the steam after decompression and expansion1,2Calculating the steam velocity c of the spray hole on the top surface of the spray head by using the formula (4)1，2Comprises the following steps:
wherein: v. of1,2The specific volume of steam of a jet hole on the top surface of the spray head; a. the1，2The surface area of the top of the spray head; phi is the ratio of the flow area of the jet hole.
The steady flow steam at the front and back of the throat of the Venturi nozzle belongs to the technical work isentropic process of adiabatic expansion, and is formed by stagnation steam pressure P in a gun barrel0And temperature T0Determining enthalpy value and entropy value, and setting Venturi nozzle outlet steam pressure P2,2The initial value is the critical pressure P of the throat of the Venturi nozzle2,1The enthalpy, the temperature and the specific volume of the steam at the outlet of the Venturi nozzle are obtained by searching an enthalpy-entropy diagram, the outlet steam jet velocity is calculated by using a formula (5), the outlet steam flow is calculated by using a formula (6), the flow deviation between the throat and the outlet of the Venturi nozzle is calculated by using a formula (7), when the deviation is more than 5%, the outlet steam pressure is adjusted to be 1.1 times of the previous value, and the enthalpy-entropy diagram is searched again to calculate the outlet steam flow; when the deviation is less than-5%, adjusting the outlet steam pressure to be 0.9 times of the previous value, and searching the enthalpy entropy diagram again to calculate the outlet steam flow; until the deviation between the two is not more than +/-5%, determining the steam pressure, the temperature and the speed of the outlet of the nozzle:
wherein：h2,2Is the vapor enthalpy at the outlet of the venturi nozzle; c. C2,2Is the venturi nozzle outlet steam velocity; a. the2,2Is the venturi nozzle exit area; v. of2,2The specific volume of the steam at the outlet of the Venturi nozzle; g2,2The flow rate of the steam at the outlet of the Venturi nozzle; g2,1The steam flow of the throat of the Venturi nozzle; xi is the steam flow deviation.
The steam at the outlet of the Venturi nozzle is free jet, after the distance between the outlet of the Venturi nozzle and the lower surface of the cold-end heat exchange element of the rotor is determined, the steam sweeping radius of a single Venturi nozzle is calculated by using an equation (8), the central speed is calculated by using an equation (9), the on-way jet flow is calculated by using an equation (10), the jet temperature is calculated by using an equation (11), and when the calculated value of the jet temperature is lower than 100 ℃, the peripheral steam of the jet gradually releases latent heat of vaporization to enable the jet temperature to be close to but not higher than 100 ℃:
wherein: r is the steam purging radius of the Venturi nozzle; r2Is the venturi nozzle exit radius; s is the distance from the outlet of the Venturi nozzle to the lower surface of the heat exchange element at the cold end of the rotor; theta is a venturi nozzle spread angle; c is the speed of the central jet of purging; g is the jet flow of the steam purging cross section; t isaIs the central jet temperature of the steam sweep cross section; t iseIs ambient temperature; t is2,2Is the venturi nozzle outlet steam temperature.
Is obtained byAfter the steam flow of the throttle pipe and the Venturi nozzle in each group of nozzle assemblies, the steam consumption G of the steam soot blower is calculated by the formula (12)total：
In the formula: g1，jThrottling the steam flow of the pipeline for the jth group of nozzle assemblies; g2，j，iThe steam flow of the ith Venturi nozzle of the jth nozzle assembly; n is the total number of nozzle assemblies; m isjThe total number of venturi nozzles of the j-th nozzle assembly; j is the nozzle assembly of the second group; i is the second venturi nozzle.
The flue gas side resistance of the air preheater recorded on line by the DCS of the unit can reflect the blockage degree of the ammonium bisulfate-containing deposition ash on the heat exchange element channel of the rotor of the air preheater, but the influence of factors such as running load is too much, and the steam heating and purging effect of the steam soot blower body needs to be evaluated.
(1) The nozzle assembly on the gun barrel forms a steam heating area and a purging area on the lower surface of a cold end heat exchange element of an air preheater rotor, the central angle corresponding to the circumferential arc length of each area can be calculated by using a formula (13) and a formula (14) respectively, the central angle corresponding to n heating areas is close to the size, and the central angle corresponding to n purging areas is close to the size:
(2) the residence time of the heat exchange elements of the air preheater rotor passing through the steam heating area and the purging area of each nozzle assembly in the circumferential direction can be calculated by the formulas (15) and (16), the residence time of n heating areas is close, and the residence time of n purging areas is close:
(3) and calculating the heating steam flow and the purging steam flow of different groups of nozzle assemblies by using an equation (17) and an equation (18) according to the steam flow of the throttling pipe and the Venturi nozzle:
M1,j＝G1，1,j(17)
(4) after the heating steam flow and the blowing steam flow of each group of nozzle assemblies are obtained, according to the heating and blowing areas on the circumference of the radial position of the rotor of the air preheater where each group of nozzle assemblies are located, the steam receiving quantity of the heat exchange elements in unit area on the circumference is calculated by using a formula (19) and a formula (20):
(5) calculating the relative deviation of the heating steam quantity received by the heat exchange elements per unit area of the n groups of nozzle assemblies by using an equation (21) and the relative deviation of the purging steam quantity received by the heat exchange elements per unit area of the n groups of nozzle assemblies by using an equation (22) by using a relative deviation method, wherein the conventional requirement is that the relative deviation of the heating steam quantity is less than +/-10 percent and the relative deviation of the purging steam quantity is less than +/-20 percent:
in the formula: ag1，jThe central angle corresponding to the j group of heating areas; a. therc，jThe arc length of the heating area of the j group is the arc length of the heating area of the j group; rr，jThe radius of the air preheater rotor corresponding to the j group of nozzle assemblies; ag2，jThe central angle corresponding to the jth group of purging areas; riThe vapor purge radius of the venturi nozzle; delta tau1，jThe time for the heat exchange element at the cold end of the rotor to stop in the j group of heating areas is determined; delta tau2，jThe time for the heat exchange element at the cold end of the rotor to stop in the purge area of the j group is taken as the time; c. CrpmThe rotational speed of the air preheater rotor; m1，jThe heating steam flow of the j group of nozzle assemblies; g1，1，jThe steam flow at the throttling shrinkage hole of the j group of nozzle assemblies; m2，jPurge steam flow for the jth group of nozzle assemblies; g2，1，j,iThe steam flow at the throat of the ith Venturi nozzle of the jth nozzle assembly is measured; SFUA1，jThe heating steam quantity received by the heat exchange element at the j group of nozzle assemblies in unit area of the cold end of the rotor is used; SFUA21，jThe purge steam amount received by the heat exchange element at the j group of nozzle assemblies in unit area of the cold end of the rotor is used; RD1，jThe heating steam quantity of the j group of nozzle assemblies is relatively deviated; RD2，jThe relative deviation of the purge steam amount for the j-th group of nozzle assemblies.
The air preheater of a 1000MW unit is taken as an embodiment for further explanation.
1) 2 sets of 34-VI (T) -2000-SMR type rotor rotary 3-bin air preheaters matched with a 1000MW unit, wherein the diameter of a rotor of each air preheater is 16400mm, and the diameter of a central sleeve is 1560 mm; the air heater rotor is divided into 2 layers from top to bottom at rotor hot end and rotor cold junction: the upper layer heat exchange element is made of low-carbon steel, the height of the upper layer heat exchange element is 1100mm, and the thickness of the upper layer heat exchange element is 0.5 mm; the lower layer heat exchange element is enamel-plated corten steel, the height is 1000mm, the thickness is 1.2mm, and the through-flow porosity is about 78%.
2) The central angle of the smoke sub-bin is 165 degrees, the secondary air sub-bin is 100 degrees, the primary air sub-bin is 50 degrees, and the total of 3 fan-shaped sealing pieces is 45 degrees; the rotor of the air preheater rotates along the smoke bin, the secondary air bin and the primary air bin at the rotating speed of 1.2r/min, the temperature of the cold secondary air in the cold secondary air inlet air channel at the bottom of the secondary air bin under the full load of the unit is 23 ℃, and the static pressure is 0.103140 MPa.
3) And under the rated load of the unit, the temperature distribution of the top surface of the hot end heat exchange element of the rotor, the top surface of the cold end heat exchange element of the rotor and the temperature distribution of the bottom surface of the cold end heat exchange element of the rotor in the circumferential direction are calculated and obtained, as shown in fig. 4. In the flue gas sub-bin, the temperature of inlet flue gas is 364.8 ℃, the temperature of outlet flue gas is 1231℃, and ammonium bisulfate in the flue gas is condensed and deposited on the surface of a rotor cold end heat exchange element with the temperature of about 150-190 ℃. When the air preheater rotor heat exchange element leaves the flue gas sub-bin and enters the secondary air sub-bin, the temperature of the heat exchange element reaches the highest temperature, and an ammonium bisulfate deposition area is formed in an area of about 400-600 mm above the lower surface of the heat exchange element.
4) In the cold overgrate air wind channel of overgrate air branch storehouse bottom import, near the sealing member between branch storehouse of flue gas and the overgrate air branch storehouse, arrange the steam soot blower of a this embodiment, the barrel is consistent with air heater rotor radial length 7420mm, and the barrel length is 7420mm, plays to the air heater rotor outside from the telescopic rifle head that is close to the center and sets up 5 groups of nozzle assembly altogether, and the distance between the adjacent nozzle assembly is 1484 mm.
5) Barrel diameter 50mm, 5 sets of nozzle assemblies are shown in table 1 for relevant design parameters: the 1 st group is positioned at the radial position 2264mm of the rotor, and is provided with 1 Venturi nozzle and 1 throttling shrinkage hole with the diameter of 5.4 mm; the 2 nd group is positioned at the 3748mm radius and is provided with 2 Venturi nozzles and 1 throttling shrinkage cavity with the diameter of 7.0 mm; the 3 rd group is positioned at the 5232mm radius and is provided with 2 Venturi nozzles and 1 throttling shrinkage cavity with the diameter of 8.2 mm; the 4 th group is positioned at the position of 6716mm of radius and is provided with 3 Venturi nozzles and 1 throttling shrinkage hole with the diameter of 9.2 mm; the 5 th group is located at 8200mm radius and is provided with 4 Venturi nozzles and 1 throttling shrinkage cavity with the diameter of 10.3 mm. The distance from the outlet of the Venturi nozzle to the lower surface of the cold-end heat exchange element of the rotor is 500 mm.
Table 1 nozzle assembly design parameters:
6) the steam pressure in the gun tube is 0.78MPa, the temperature is 310 ℃, after decompression and expansion through a throttle shrinkage hole or a venturi nozzle throat, the steam pressure at the outlet of the throttle tube is 0.103MPa, the temperature is 302 ℃, the steam pressure at the outlet of the venturi nozzle is 0.2MPa, and the temperature is 150.5 ℃. The details are shown in Table 2.
Table 2 soot blower steam parameter variation:
7) the speed of steam jet at the outlet of the venturi nozzle is 547m/s, the central speed of the steam jet reaching the lower surface of the heat exchange element at the cold end of the rotor is reduced to 156m/s, the speed of the steam jet at the radius of 1/4 is 65m/s, and the purging radius is 58 mm; the speed of the steam jet at the outlet of the throttle pipe is 25m/s, and the speed of the steam jet entering the channel of the cold-end rotor heat exchange element is reduced to 19.2 m/s. The steam flow rate of the steam sootblower is 46.7kg/min, the heating steam flow rate is 16.0kg/min and the total is 62.7kg/min, the relative deviation of the steam flow received by the heat exchange elements in unit area of 5 groups of heating areas in the radial direction of the rotor of the air preheater is-1.7% -2.0%, and the relative deviation of the steam flow received by the heat exchange elements in unit area of the purging area is-16.6% -16.4%. The details are shown in Table 3.
Table 3 sootblower steam jet parameters:
8) consistent with the vapor purge radius length of the venturi nozzle, the barrel advance step size was 58mm, advance speed was 0.806mm/s, advance stroke was 1484mm, and purge time was 1842 s.
The above embodiments are merely illustrative of the technical ideas and features of the present invention, and the purpose thereof is to enable those skilled in the art to understand the contents of the present invention and implement the present invention, and not to limit the protection scope of the present invention. All equivalent changes and modifications made according to the spirit of the present invention should be covered within the protection scope of the present invention.
Claims (10)
1. A steam jet flow parameter design method of a steam soot blower is used for a rotary air preheater, the steam soot blower comprises a steam soot blower, a gun barrel communicated with the steam soot blower and a plurality of nozzle assemblies communicated with the gun barrel, each nozzle assembly comprises a first nozzle assembly and a second nozzle assembly, each first nozzle assembly comprises a throttle pipe communicated with the gun barrel at one end and connected with a spray head at the other end, and a throttle shrinkage cavity is formed in each throttle pipe; the second nozzle assembly include with the barrel venturi nozzle that is linked together, its characterized in that: the design method comprises the following steps:
marking the throttle pipe as 1, marking the Venturi nozzle as 2, marking the inlet of the throttle pipe as (1, 0), marking the throttle shrinkage cavity as (1,1), and marking the outlet of the throttle pipe as (1, 2); the inlet of the Venturi nozzle is marked as (2,0), the throat of the Venturi nozzle is marked as (2,1), the outlet of the Venturi nozzle is marked as (2,2), and the steam flow G of a single throttle pipe or the Venturi nozzle is designed1Comprises the following steps:
wherein: a. the1The cross section area of the throat of the throttle pipe or the Venturi nozzle; c. C1The steam velocity at the throat of a throttle pipe or a venturi nozzle; v. of1Is the specific volume of steam; h is0Stagnation vapor enthalpy in the barrel; p1Critical steam enthalpy at the throat of a throttle pipe or a venturi nozzle; p0Stagnation steam pressure in the gun tube; p1Critical steam pressure at the throat of a throttle pipe or a venturi nozzle; gamma is the adiabatic coefficient of the superheated steam.
2. The steam jet parameter design method of a steam sootblower of claim 1, characterized in that: designing steam flow G of a single throttle pipe or Venturi nozzle1The method comprises the following steps: h is0According to the steam pressure P0And temperature T0Checking enthalpy and entropy diagram, and obtaining critical pressure P at throttle shrinkage cavity and Venturi nozzle throat position by using isentropic principle1Then, searching an enthalpy entropy diagram to obtain steam enthalpy h1And specific volume v1。
3. The steam jet parameter design method of a steam sootblower of claim 1, characterized in that: designing the steam velocity c of the spray hole on the top surface of the spray head1，2Comprises the following steps:
wherein: v. of1,2The specific volume of steam of a jet hole on the top surface of the spray head; a. the1，2The surface area of the top of the spray head; phi is the ratio of the flow area of the jet hole.
4. The steam jet parameter design method of a steam sootblower of claim 3, characterized in that: designing the steam velocity c of the spray hole on the top surface of the spray head1，2The method comprises the following steps: stagnation steam pressure P in gun barrel0And temperature T0After the steam enthalpy is determined, according to the steam pressure of the outlet of the spray nozzleThe temperature and specific volume v of the decompressed and expanded steam are found on an enthalpy-entropy diagram1,2。
5. The steam jet parameter design method of a steam sootblower of claim 1, characterized in that: design of the steam velocity c at the outlet of the Venturi nozzle2,2Steam flow rate G2,2And the steam flow deviation xi is as follows:
wherein: h is2,2Is the vapor enthalpy at the outlet of the venturi nozzle; c. C2,2Is the venturi nozzle outlet steam velocity; a. the2,2Is the venturi nozzle exit area; v. of2,2The specific volume of the steam at the outlet of the Venturi nozzle; g2,1Is the steam flow of the throat of the Venturi nozzle.
6. The steam jet parameter design method of a steam sootblower of claim 5, characterized in that: design of the steam velocity c at the outlet of the Venturi nozzle2,2Steam flow rate G2,2The method comprises the following steps: by stagnation of steam pressure P in the barrel0And temperature T0Determining enthalpy value and entropy value, and setting Venturi nozzle outlet steam pressure P2,2The initial value is the critical pressure P of the throat of the Venturi nozzle2,1When the steam flow deviation xi is more than 5%, adjusting the steam pressure at the outlet of the venturi nozzle to be 1.1 times of the previous value, and searching the enthalpy-entropy diagram again to calculate the steam flow at the outlet of the venturi nozzle; when the deviation is smallAnd when the steam pressure of the outlet of the Venturi nozzle is adjusted to be 0.9 times of the previous value at the time of-5 percent, and the enthalpy entropy diagram is searched again to calculate the steam flow of the outlet Venturi nozzle until the deviation of the steam pressure and the enthalpy entropy diagram is not more than +/-5 percent.
7. The steam jet parameter design method of a steam sootblower of claim 1, characterized in that: designing the steam purging radius R, purging central jet flow speed c, jet flow G of the steam purging cross section and central jet flow temperature T of the steam purging cross section of the Venturi nozzleaComprises the following steps:
wherein: r2Is the venturi nozzle exit radius; s is the distance from the outlet of the Venturi nozzle to the lower surface of the heat exchange element at the cold end of the rotor; theta is a venturi nozzle spread angle; t iseIs ambient temperature; t is2,2Is the venturi nozzle outlet steam temperature.
8. The steam jet parameter design method of a steam sootblower of claim 1, characterized in that: designing steam consumption G of steam soot blowertotalComprises the following steps:
in the formula: g1，jThrottling the steam flow of the pipeline for the jth group of nozzle assemblies; g2，j，iThe steam flow of the ith Venturi nozzle of the jth nozzle assembly; n is the total number of nozzle assemblies; m isjThe total number of venturi nozzles of the j-th nozzle assembly; j is the nozzle assembly of the second group; i is the second venturi nozzle.
9. The steam jet parameter design method of a steam sootblower of claim 1, characterized in that: the method further includes evaluating steam heating and purging effects of the steam sootblowers:
(1) the nozzle assembly on the gun barrel forms a steam heating area and a purging area on the lower surface of a cold end heat exchange element of the air preheater rotor, and the central angle corresponding to the arc length in the circumferential direction of each area is designed as follows:
(2) the residence time of the heat exchange elements of the air preheater rotor in the circumferential direction passing through the steam heating area and the purging area of each nozzle assembly is designed as follows:
(3) according to the steam flow of the throttle pipe and the Venturi nozzle, the heating steam flow and the purging steam flow of different groups of nozzle assemblies are designed:
M1,j＝G1，1,j (17)
(4) after obtaining the heating steam flow of every group nozzle assembly and sweeping the steam flow, according to the heating and the area of sweeping on the circumference of the radial position of the air preheater rotor of every group nozzle assembly, the steam receiving quantity of the heat exchange element in unit area on the design circumference:
(5) the relative deviation method is adopted, the unit area heat exchange element of the n groups of nozzle assemblies is designed to receive the relative deviation of the heating steam quantity, and the unit area heat exchange element of the n groups of nozzle assemblies is designed to receive the relative deviation of the blowing steam quantity:
in the formula: ag1，jThe central angle corresponding to the j group of heating areas; a. therc，jThe arc length of the heating area of the j group is the arc length of the heating area of the j group; rr，jThe radius of the air preheater rotor corresponding to the j group of nozzle assemblies; ag2，jThe central angle corresponding to the jth group of purging areas; riThe vapor purge radius of the venturi nozzle; delta tau1，jFor rotor cold end heat exchange element to pass through heating zone of j groupTime; delta tau2，jThe time for the heat exchange element at the cold end of the rotor to stop in the purge area of the j group is taken as the time; c. CrpmThe rotational speed of the air preheater rotor; m1，jThe heating steam flow of the j group of nozzle assemblies; g1，1，jThe steam flow at the throttling shrinkage hole of the j group of nozzle assemblies; m2，jPurge steam flow for the jth group of nozzle assemblies; g2，1，j,iThe steam flow at the throat of the ith Venturi nozzle of the jth nozzle assembly is measured; SFUA1，jThe heating steam quantity received by the heat exchange element at the j group of nozzle assemblies in unit area of the cold end of the rotor is used; SFUA21，jThe purge steam amount received by the heat exchange element at the j group of nozzle assemblies in unit area of the cold end of the rotor is used; RD1，jThe heating steam quantity of the j group of nozzle assemblies is relatively deviated; RD2，jThe relative deviation of the purge steam amount for the j-th group of nozzle assemblies.
10. The steam jet parameter design method of a steam sootblower of claim 9, characterized in that: in (5): the relative deviation of the hot steam amount is less than +/-10 percent, and the relative deviation of the purging steam amount is less than +/-20 percent.
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