CN113970254A - Full-countercurrent direct air-cooling condensing method - Google Patents
Full-countercurrent direct air-cooling condensing method Download PDFInfo
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Abstract
The full-countercurrent direct air-cooling condensing method utilizes the characteristics of the flowing speed of the exhaust steam from bottom to top in the single-row pipe and the turbulent flow to eliminate the adverse effect of the condensate water flowing downwards along the pipe wall on heat transfer, so that the whole inner surface of the vertically arranged single-row pipe has a good coefficient of the exhaust steam condensation heat transfer film, and the full-countercurrent direct air-cooling condensing method has reliable practicability; the first stage countercurrent air-cooling condenser and the second stage countercurrent air-cooling condenser are formed by the large-section single exhaust pipes, so that the large-section single exhaust pipes are used as exhaust steam air-cooling condensing elements and exhaust steam channels, and exhaust steam distribution pipes can be omitted in the arrangement of the air-cooling condenser on the circumference of the air duct, so that the structure of the exhaust steam air-cooling condenser is simplified, the manufacturing cost of the device is reduced, and the air-cooling condensing method and the technical structure with lower cost and better performance are provided for natural ventilation direct air cooling, mechanical ventilation direct air cooling and mixed ventilation direct air cooling.
Description
Technical Field
The invention belongs to the field of heat exchange, and particularly relates to an air-cooled condenser device which directly carries out heat exchange type dividing wall condensation on exhaust steam of a steam turbine by adopting air as a cooling medium.
Background
The existing air-cooled power plant, the key equipment for condensing the exhaust steam of the steam turbine by using air, is also called as a power station air cooler, and is mainly divided into direct air cooling and indirect air cooling: the method is characterized in that the exhaust steam of the steam turbine directly enters an air cooler for condensation, which is called direct air cooling for short, and the condensation heat of the exhaust steam of the steam turbine is brought into the air cooler for cooling through circulating cooling water, which is called indirect air cooling for short.
Because the specification of the base pipe shown in the figures 1, 2, 3 and 4 is 219mm multiplied by 19mm multiplied by 1.5mm, the internal exhaust steam circulation section is 34 square centimeters, and the wall thickness is 1.5 millimeters, the flat single-row pipe heat exchange element is also called a single-row pipe, has a relatively large steam circulation section and relatively good condensate separation; the cooling air circulation resistance of the fins outside the tube is relatively small, especially the cleaning effect of the radiating fins is far better than that of an elliptical or circular base tube, the cooling air circulation resistance is particularly suitable for the A-shaped inclined arrangement of mechanical ventilation shown in figure 13, and the cooling air circulation resistance is widely applied to direct air-cooled condensers of power plants for many years.
The current technical scheme of direct air cooling in power plants is that the single-row pipes are combined into an A-shaped air cooling condenser with a concurrent flow and countercurrent flow structure, for example, the air cooling condenser of a 600Mw air cooling unit is arranged 45 meters away from the ground and has an area of 8000 m more2On the huge high altitude steel structure platform, 56 110kw large axial flow fans arranged below the air cooling condenser tube bundle blow air vertically upwards to enable the large axial flow fans to penetrate through the condenser tube bundle and take away the latent heat of condensation released by the dead steam condensation in the tube bundle, so that the purpose of directly condensing the dead steam of the steam turbine by air is achieved. The advantages of this arrangement: firstly, the water resource is greatly saved, and meanwhile, the air cooling system has the advantages of simple structure, small investment and occupied area and lower indirect air cooling ratio; the defects are that the operating back pressure of the steam turbine is high, the wind resistance is poor, and hot air circulation is easy to occur, so that the output of the steam turbine is reduced; the operating fan has high power consumption, high maintenance cost and high noise, the kwh coal consumption is more than 5 percent higher than that of a water cooling unit, and the resource utilization aspect essentially increases the coal consumption and CO2The saving of water resources due to the emission is greatly restricted by the price difference between the coal and the water.
In view of the above disadvantages of direct air cooling in power plants, various natural draft air cooling systems have been developed, and it is desired to reduce or completely eliminate the power consumption of the fan to increase the economic efficiency of the air cooling power plant: CN205262240U, replace the fan with the natural draft tower, with the air cooling condenser that contains the big platform of air cooling, directly arrange the simple integrated configuration in the natural draft tower, because must build air cooling tower and the big platform of steel construction more than 30 meters simultaneously, the investment must greatly increase, just can have the effect of saving fan power consumption, obviously it is difficult to realize commercialization.
CN109780882A and CN102980417B adopt an aerodynamic structure of a natural draft air cooling tower that cooling air horizontally penetrates through inclined finned tubes and air cools a radiator on a vertical windward side, and hopefully utilize the lifting force of hot air in the air cooling tower to realize natural draft and save a fan and power consumption; however, the adoption of long round finned tube heat exchange elements reduces the welding and tube box engineering quantity, but increases the flow resistance of the dead steam in the tube, and the adoption of short finned tubes reduces the flow resistance, but doubles the welding and tube box engineering quantity and the welding spot leakage probability; by adopting an elliptical or flat single-row pipe, a condensing heat exchange surface, namely a long axis C-D (see figure 3), must be parallel to the flow direction of flowing cooling air to ensure a good ventilation section and cooling air volume, but a large amount of condensate covers the condensing surface in the pipe, so that the coefficient of a condensing heat transfer film in the pipe is sharply reduced; especially, the single-row pipes with the specification of 220 multiplied by 20 multiplied by 1.5 or 219 multiplied by 19 multiplied by 1.5 are forced to adopt high back pressure operation in order to prevent the finned pipes from being frozen in the favorable power generation season with low temperature in winter because the inner sections of the pipes are too small under the existing air quantity condition and the circulation resistance of exhaust steam is large, so that the annual average kwh coal consumption of air-cooled power generation is more than 5 percent higher than that of a water-cooled unit; in addition, the single-row pipes with the specifications of 220 multiplied by 20 multiplied by 1.5 and 219 multiplied by 19 multiplied by 1.5 are adopted, the windward side of the single-row pipes is arranged on the circumferential tangent plane of the lower part of the air cooling tower, so that the circumferential arrangement length of the windward side is doubled compared with that of the single-row pipes adopting the triangular arrangement, the 660Mw unit is adopted, the diameter of the bottom of the air cooling island is increased from 134 meters to 268 meters under the condition of the same air inlet height, and the investment of the air cooling island is greatly increased.
CN107120980A, a mixed ventilation direct air cooling system vertically arranged outside an air cooling condenser tower, mainly improves the high-temperature cooling air volume in summer, like other direct air cooling condensers, does not notice the important problem of the exhaust steam circulation resistance, does not solve the expression of the exhaust steam resistance of an air condensing element, and does not achieve the effect of a water cooling unit in actual operation.
Volumetric flow of dead steam of large steam turbines todayThe amount is even 10000m3More than one second, the flow velocity is even more than 200 m/second, and the pressure loss of nearly kilopascal can be formed in the condensing fin tube; secondly, a large number of single-row finned tubes are arranged in parallel in a large space to carry out dead steam condensation, the dead steam is condensed in each finned tube of the first section in a downstream manner, and the condensation amount of the dead steam is greatly different due to various reasons; the flow speed ratio of the dead steam in an inlet pipe section and an outlet pipe section in the same fin pipe is 6-7 times or even higher, and the local resistance change is more than dozens of times; fourthly, the temperature difference is large especially in winter, summer and day and night in China; the frequent environmental strong wind; economic loss, energy consumption and CO caused by high back pressure operation of steam turbine2The increase of emissions undoubtedly provides a new topic and a serious challenge for the optimization of the air cooling system of the air cooling power plant; the 219x19x1.5 single-row tube structure of the current specification can only be used in the inclined arrangement shown in fig. 13, thereby greatly limiting the design of the air-cooling condenser with better performance.
Disclosure of Invention
The invention aims to develop a steam turbine which has low exhaust steam back pressure, good wind resistance, high steam turbine output and high hot air circulation resistance; the running wind power consumption is low, even no fan power consumption and low noise; compared with a water cooling unit, the kwh coal consumption does not increase the kwh coal consumption and CO2The air cooling condenser is used for realizing the same water resource saving and has no limit on economic benefit by the price difference of coal and water.
The full-countercurrent direct air-cooling condensing method is characterized in that:
the exhaust steam of the steam turbine sequentially enters from bottom to top through a main pipe (ZG), an exhaust steam ring pipe (1a) and a branch pipe (1), and is composed of a steam inlet header (2), a first-stage countercurrent condenser (NQQ1) consisting of large-section single-row pipes (3), a first header (4), a second-stage countercurrent condenser (NQQ2) consisting of large-section single-row pipes (5), a second header (6), a third-stage countercurrent condenser (NQQ3) consisting of currently universal single-row pipes (7), a third header (8), a pipeline (9), a fourth header (10), a fourth-stage countercurrent condenser (NQQ4) consisting of universal single-row pipes (11), an outlet header (12) which are tightly connected, a plurality of single-row finned pipes are vertically arranged, and an air-cooling condensing unit (N) with a vertically arranged windward side; the exhaust steam flows downwards attached to the inner wall of the single-row pipe from bottom to top in the air-cooling condensing unit (N) for multiple times, and the low-temperature condensate is in countercurrent contact with the exhaust steam for heat transfer, cooling and condensing to form liquid water; after multi-stage condensation and enrichment, trace non-condensable gas carried in the exhaust steam enters a non-condensable gas collecting pipe (1b) through a non-condensable gas outlet pipe (13) and is extracted out of an air cooling island by a vacuum pump through a vacuum pump inlet pipe (1c) together with non-condensable gas of other countercurrent air cooling condensing units (N);
the two air-cooling condensing units (N) with vertical windward sides and the shutter (F) or the fan (S) form a countercurrent condensing triangle; the plurality of countercurrent condensing triangles are arranged along the circumference of the lower part of the wind tube (FT) to form a full countercurrent natural ventilation direct air cooling island or a full countercurrent mixed ventilation direct air cooling island.
Secondly, a large-section single-row pipe (3) of the first-stage secondary countercurrent condenser (NQQ1), wherein the cross-sectional area of single-pipe steam passing is 2-4 times of the current general 218X19X1.5 specification 34 square centimeter, and the ratio of the length (L-2t) to the width (W-2t) of the inner section (see the attached figure 15): the (L-2t)/(W-2t) is 5-8, and because the steam flow of the section is the maximum and the steam condensation load is about 30% of the total amount, enough steam flow cross section is ensured, and the circulation resistance of the dead steam is reduced;
the large-section single-row pipe (5) of the second-stage secondary countercurrent condenser (NQQ2) has a single-pipe steam-passing sectional area which is 1.5-3 times that of the current common 218X19X1.5 specification and 34 square centimeters, and the ratio (L-2t)/(W-2t) of the length (L-2t) to the width (W-2t) of the inner section is 5.5-10.5; the condensing load of the section is 30-40% of the total amount, and a proper ventilation section is also ensured, so that the circulation resistance of the dead steam is reduced;
the single-tube discharge area of the single-tube steam-passing section (7) of the third-stage secondary countercurrent condenser (NQQ3) is 1-2 times of the current general 218X19X1.5 specification, and the ratio of the length (L) to the width (W) of the inner section is as follows: L/W is 7-13.5; the section of the condensing load is 30-40% of the total amount, because the exhaust steam amount of the section is reduced by about 2/3, the circulation resistance of the exhaust steam is greatly reduced, and the length-width ratio is more beneficial to the condensation of the exhaust steam as the main consideration;
the ratio of the length (L) to the width (W) of the inner section of the single-row pipe (11) of the fourth-stage secondary countercurrent condenser (NQQ3) is as follows: L/W is 13.5; the condensing load of the section is 2-5% of the total amount, the main function of the section is to improve the condensing rate of exhaust steam, enrich non-condensable gas, reduce the vacuum pumping load and reduce the power consumption of a vacuum pump.
The difference between the condensation load and the condensation water amount of the first three stages is not large, and the corresponding single-row tubes with the length (L) and the width (W) are adopted, so that the exhaust steam circulation resistance of each section of the condenser can be greatly reduced, and the high turbulent flow Reynolds number Re and the distribution thereof in the whole fin tube can be obtained; the heat transfer film coefficient of the dead steam condensation on the inner wall of the single exhaust pipe from the inlet to the outlet can keep good numerical value by the characteristic that the dead steam flows from bottom to top in the vertical air-cooled condensed steam single exhaust pipe and the local flow velocity and turbulent flow Reynolds number of the dead steam in the air-cooled condensed steam single exhaust pipe are reduced along with the displacement of the dead steam, so that the defects of thickening and heat resistance increase of the dead steam condensate flowing downwards along the pipe wall can be just eliminated, the thickened condensate flowing downwards along the pipe wall is always stirred vigorously by the dead steam with higher flow velocity and Reynolds number, the thickness of the condensate viscous flow layer causing the heat resistance can not be increased, and the heat transfer film coefficient of the dead steam condensation on the inner wall of the single exhaust pipe from the inlet to the outlet can be kept to have good numerical value, thereby reliably ensuring the heat transfer efficiency of the reverse flow condensation of the dead steam and the condensate thereof.
Fourthly, because of the direct air-cooling and condensing process of the dead steam, especially the exhausted steam discharged by a large-scale steam turbine per second reaches ten thousand cubic meters, and depends on the combined action of huge space environments of millions and even tens of millions of cubic meters, the operation must be completed within the time length of 1 second, and the volume of the dead steam is sharply reduced by ten thousand times; two more than ten thousand finned tubes are connected in parallel to finish about 80% of condensation load in stage concurrent condensation, thousands of finned tubes are connected in parallel to finish about 20% of condensation and condensation in countercurrent condensation, and due to the combined action of a huge air flow field, a temperature field (sunlight) and a huge internal exhaust steam flow field of a space environment, various factors can frequently interfere and reduce the performance of the air-cooled condenser;
the exhaust steam adopts multi-stage countercurrent condensation, so that the interference can be better eliminated, and compared with the traditional two-stage condensation, the exhaust steam which is not well condensed by a certain finned tube of the second stage can be condensed in three stages; the third stage of the exhaust steam which is not condensed is condensed at the fourth stage, so that the non-condensed steam in the exhaust steam can be collected and enriched by more than ten times, the overall effect of the air-cooled condenser is effectively improved, the exhaust steam back pressure of the steam turbine is reduced, and the capacity and the energy consumption of the vacuum pump can be greatly reduced.
And fifthly, part of the condensed water which is subjected to the countercurrent condensation of the exhaust steam of each section enters an upper header which is connected with the upper end port of the single-row tube along with the steam flow, and the other part of the condensed water flows into a lower header which is connected with the lower end port of the single-row finned tube of each section and flows to the edge area of the tube plate of the header through a drainage component (YL).
Sixthly, a U-shaped water seal downcomer (J3) is arranged between the header (10) and the header (6) so that condensed water in the header (10) can flow into the header (6) by utilizing liquid level pressure difference; the exhaust steam in the header (6) can only enter the header (8) through a countercurrent condensation single discharge pipe (7) in a condenser (NQQ3) with the resistance far smaller than the U-shaped water seal liquid level pressure difference during partial cooling condensation; condensed water in the header (8) enters the header (10) through a pipeline (9);
a second downcomer (J2) is arranged between the header (6) and the header (4) so that condensed water in the header (6) can flow into the header (4) by utilizing the potential difference; a U-shaped water seal (J2U) is arranged at the water outlet of the second downcomer (J2), so that exhaust steam in the header (4) can only enter the header (6) through a countercurrent condensation single discharge pipe (5) in a condenser (NQQ2) with resistance far smaller than the liquid level pressure difference of the U-shaped water seal (J2U);
a first downcomer (J1) is arranged between the header (4) and the header (2) so that condensed water in the header (4) can flow into the header (2) by utilizing the potential difference; the water outlet of the first downcomer (J1) is provided with a U-shaped water seal (J1U) so as to ensure that exhaust steam in the header (2) can only enter the header (4) through a countercurrent condensation single discharge pipe (3) in a condenser (NQQ1) with resistance far smaller than the liquid level pressure difference of the U-shaped water seal (J1U).
Seventhly, the outlet of the single-row pipe (3) in the first header (4) is higher than the tube plate by more than 30 mm so as to prevent condensate on the tube plate from flowing into the single-row pipe (3) and ensure that the condensate on the tube plate can only flow to the steam inlet header (2) through a downcomer (J1);
the outlet of the single-row pipe (5) in the second header (6) is 20 mm higher than the tube plate to prevent condensate on the tube plate from flowing into the single-row pipe (5) and ensure that the condensate on the tube plate can only pass through the downcomer (J2) and the first header (4);
the outlet of the single-row pipe (7) in the third header (8) is 10 mm higher than the tube plate, so that condensate on the tube plate can not flow into the single-row pipe (7), and the condensate on the tube plate can only pass through the downcomer (J3) and the second header (6).
Eighthly, the single-row pipes for countercurrent condensation can also be arranged in a non-vertical inclined mode to carry out countercurrent condensation on the dead steam.
Ninth, the countercurrent condensation section of the invention can be designed into multistage countercurrent condensation of one section, two sections, three sections and the like according to requirements; it is also possible to design co-current condensation in any stage.
Ten, the included angle (e) between the central line C-D of the section of the single-row pipe and the central line A-C of the condensing unit shown in the attached figure 8 is less than 90 degrees, the included angle can be optimized between 70 degrees and 90 degrees, the air can be favorably fed into the windward side, and the condensing effect is improved.
Eleven, the countercurrent condensing triangle adopts the horn arrangement as shown in figure 16, wherein the included angle between two windward surfaces on the air inlet side is larger than the vertex angle m1(m2 is larger than m1), so that the air inlet condition of the windward surface on the outer side is improved and optimized.
On the basis that the included angle (e) between the central line C-D of the single-row pipe section and the central line A-C of the condensing unit is smaller than 90 degrees, the included angle m2 of the part of the windward side of the air inlet side can be properly increased, namely m2 is larger than m1 and is between 5 degrees and 15 degrees, so that the condition of feeding the single-row pipe on the air inlet side is improved and optimized, and the condensing effect is improved, see the attached figure 17.
Thirteen, the shutter (F) of the invention is shown in figure 18, the rotating shaft is vertically arranged, the window leaf can rotate at an angle of +/-90 degrees left and right, the shutter (F) blades at two sides of the central line of the shutter can rotate forward and backward, and the shutter can adjust the air volume (FL) and the air direction (FX); in the blowing period, the shutters (F) on the circumference of the lower part of the air duct are respectively adjusted to control different air intake quantities, and the air intake quantities of two windward sides of each countercurrent condensing triangle are uniform;
the louver (F) of the first-stage secondary countercurrent condenser (NQQ1), the louver (F) of the second-stage secondary countercurrent condenser (NQQ2) and the louver (F) of the third-stage secondary countercurrent condenser (NQQ3) are designed to be regulated and controlled respectively, the air temperature is higher than 0 ℃, freezing accidents can never happen, and the three-stage louver (F) is fully opened (QK) so as to improve the air cooling air quantity to the maximum extent;
the air temperature is 0-10 ℃, the heat transfer temperature difference is increased, the required air volume is reduced, a louver (F) of the third section of secondary countercurrent condenser (NQQ3) is closed, the louver (F) of the first section of secondary countercurrent condenser (NQQ1) is fully opened (QK), and the louver (F) of the second section of secondary countercurrent condenser (NQQ2) is used for adjusting the air volume (FL);
when the air temperature is less than-10 hours, the heat transfer temperature difference is larger, the air draft capacity of the air duct (FT) is strong, and the required air volume is further reduced, so the shutters (F) of the third and second sections of countercurrent condensers (NQQ3), (NQQ2) can be completely closed (GB), and the shutters (F) of the first section of countercurrent condenser (NQQ1) are fully opened (QK) or the air volume is adjusted; under the condition, about 60 percent of cooling air flow passes through the windward side of the first-stage secondary countercurrent condenser (NQQ1) to enter the wind cylinder (FT), and 40 percent of cooling air flow goes upward in the triangular space, wherein 3/4 passes through the windward side of the second-stage secondary countercurrent condenser (NQQ2) to enter the wind cylinder (FT), and 1/4 goes upward to pass through the windward side of the first-stage secondary countercurrent condenser (NQQ1) to enter the wind cylinder (FT).
The following positive effects can be obtained by adopting the invention:
by utilizing the air draft function of the air duct (FT), 8000 square meters of huge steel platforms with the height of more than 45 meters and 56 large axial flow fans with the height of 110kw of 660Mw direct air cooling coal-fired generating sets are omitted, the running power consumption of an air cooling island can be reduced by 95 percent and the maintenance cost can be reduced by 90 percent, and the cooling air cost is greatly reduced, so that the back pressure of a steam turbine can be greatly reduced, and the heat efficiency of the whole generating set is improved.
Compared with an indirect air cooling island, the invention omits a waste steam water-cooling condenser with 40000 square meters of a 660Mw large-scale unit and three circulating water pumps with 1600kw, thereby effectively reducing the construction investment of the indirect air cooling island by at least 10%, the operation energy consumption by 95% and the maintenance cost by 90%.
Compared with the direct air cooling island, the invention has the advantages that because the density of the exhaust steam is low, the countercurrent condenser can be overlapped for many times in the height direction to obtain the required windward side, the occupied area can be greatly reduced, the invention is a large-scale generator set with the exhaust steam total amount reaching 2 x 1056 tons per hour of 2 x 660Mw, a key condition is created by sharing one air duct, the occupied area of land resources is reduced by times, the civil engineering cost is reduced, and the manufacturing cost of the air duct can be greatly reduced due to the square root relation between the section of the air duct and the circumference.
The air duct is shared, the steam circular ducts of the two sets of air cooling condensers are connected through the valve, when the loads of the two sets of units are different, the abundant air cooling capacity of the low-load unit can be fully utilized, the air cooling effect of the high-load unit is improved, when one set of unit operates, the air cooling performance of the idle unit can be greatly improved, and better economic benefits are created.
By adopting multi-stage countercurrent condensation, the non-condensable gas in the exhaust steam is effectively enriched, and the capacity and the power consumption of a vacuum pump can be reduced by over 75 percent;
the single-row pipes are vertically arranged to form a vertical windward side, a countercurrent condensing triangle is formed by the single-row pipes and the louver, and the single-row pipes are arranged along the periphery of the lower part of the wind cylinder (FT), so that the wind cylinder has a good mechanical structure without any support, the hot air height in the wind cylinder can be effectively increased, the air draft capacity is increased, and the manufacturing cost of the wind cylinder is reduced.
The single-row pipe (3) and the single-row pipe (5) with large cross section greatly reduce the circulation resistance of the exhaust steam, are exhaust steam condensing elements, increase the function of an exhaust steam channel and save the traditional steam distribution pipeline with hundreds of meters and total weight of more than hundreds of tons.
The length of the exhaust steam branch pipe (1) is short, thereby reducing the resistance of the exhaust steam and saving materials.
The condensed water flows by utilizing potential difference potential energy, and passes through the branch pipe (1), the ring pipe (1a), the main pipe (ZG) and the condensed water tank (NJSC), thereby simplifying the process pipeline and saving the pipeline material.
Because the countercurrent condensing elements of the first secondary countercurrent condenser (NQQ3) and the second secondary countercurrent condenser (NQQ2) adopt a large-section single exhaust pipe, the exhaust steam flux is multiplied, and the countercurrent condensing elements have good heat supply and anti-freezing capabilities, and the louver accurately regulates and controls the air quantity of each countercurrent condensing section and each direction of the circumference at low temperature in winter, thereby creating key conditions for the low-back-pressure operation of the steam turbine and the improvement of the heat efficiency of the low-pressure cylinder of the steam turbine;
by adopting the invention, in summer, the air temperature is properly reduced by adopting isenthalpic cooling, and the temperature can be over 30 ℃ to ensure that the exhaust back pressure of the steam turbine is as low as 20 kPa.
Drawings
FIG. 1 is a view of a current universal 219X19X1.5 specification single-row pipe for direct air cooling facing the wind;
FIG. 2 is a schematic view of a 219x19x1.5 standard single row pipe in a downwind direction for the current direct air cooling;
FIG. 3 shows the direction of exhaust steam inlet and outlet of a single row of tubes with the current general direct air cooling specification of 219X19X1.5, namely a cross-sectional view, wherein C-D is a cross-sectional center line;
fig. 4 shows the cross-sectional dimension of a 219 × 19 × 1.5 standard single row tube commonly used in the existing direct air cooling, where q is the fin height q is 19mm, W is the base tube cross-sectional width, and W is 19 mm;
FIG. 5 is a cross-sectional view of a finned tube with an elliptical base tube used in a current small and medium-sized direct air cooling island;
FIG. 6 is a schematic structural diagram of a single-row pipe vertically arranged in a vertical windward side and forming a full-countercurrent direct air-cooling multistage condensed-steam windward side according to the present invention;
in the figure:
1, an inlet branch pipe;
1a, a steam exhaust ring pipe;
1b, a non-condensable gas collecting pipe;
1c, a vacuum pump inlet pipe;
2, an inlet steam header;
3, a single-tube large-section single-tube bank with a steam passing cross-sectional area 2-4 times of that of the current 218X19X1.5 standard, namely a single-tube bank with a width (W) larger than the height (q) of the fins (W > q) and a ratio of the length (L-2t) of the inner section of the base tube to the width (W-2t) of the inner section of the base tube smaller than 13.5 (in units of millimeter integers), namely a single-tube bank with [ (L-2t)/(W-2t) ] < 13.5, and is shown in figure 15;
4, a first header;
5, a large-section single-row pipe with the steam-through sectional area 1.5-3 times of that of the current general 218X19X1.5 specification;
6, a second header;
7, the single-tube steam-passing sectional area is 1-2 times of that of the current general 218X19X1.5 specification;
8, a third header;
9, a pipeline (9) is used for conveying the dead steam and the condensed water in the third header to a fourth header;
10, a fourth header;
11, current common 218X19X1.5 standard single row pipe;
12, a fifth header for collecting the exhaust steam of the noncondensable gas from the single-row pipe (7);
13, a non-condensable gas outlet pipe;
NQQ1, first stage counter-current condenser;
NQQ2, second stage counter-current condenser;
NQQ3, third stage secondary countercurrent condenser;
NQQ4, fourth stage secondary countercurrent condenser;
j1, a first downcomer;
J1U, first downcomer U-shaped water seal;
j2, a second downcomer;
J2U, second downcomer U-shaped water seal;
j3; a U-shaped downcomer;
q is the height of the single-row tube fin, and is unit millimeter, wherein q in the invention is the height q of the common single-row tube fin, which is 19 millimeters;
w, the base pipe of the single-row pipe has the width including the pipe wall thickness t and is in unit millimeter;
FIG. 6a is a schematic view of a full-countercurrent direct air-cooling condensation windward side of a condensation triangle according to the present invention;
in the figure:
n is the code of the full countercurrent direct air-cooling condensation unit shown in the figures 6 and 6 a;
FIG. 6b is a schematic view of a full-countercurrent direct air-cooling condensing windward side applied to a medium and small-sized turbine;
FIG. 7 is a top view of a condensing triangle formed by the full countercurrent direct air-cooling condensing unit and the louver (F) according to the present invention;
in the figure:
f, a shutter for regulating and controlling air quantity and wind direction;
A-B and A-C are respectively central lines of two full-countercurrent direct air-cooling condensation units (N), and the included angle of two lines is the included angle of two condensation triangles;
FIG. 7a, shows a top view of downcomer J1, downcomer J2, Udowncomer J3 in the condensing delta design position;
FIG. 7b is a top view of a condensing triangle formed by the full countercurrent direct air-cooling condensing unit (N) and the fan (S);
FIG. 8 is a view showing that an angle (e) between the center line C-D of the cross section of a single row of tubes and the center line A-C of a condensing unit is smaller than 90 degrees, which is 70 degrees, in order to facilitate air intake of the single row of tubes and improve the condensing effect;
FIG. 9 is a schematic cross-sectional view of a plurality of countercurrent condensing triangles circumferentially arranged along the lower part of an air duct (FT) to form a full countercurrent natural draft direct air cooling island or a full countercurrent mixed draft direct air cooling island;
in the figure:
FT, wind tube for cooling air to obtain flow power by using hot air density reduction;
NJSC, condensate tank;
ZG, exhaust steam from the turbine and the main pipe;
FIG. 10 is a schematic plan sectional view of a full countercurrent natural draft direct air cooling island or a full countercurrent mixed draft direct air cooling island formed by arranging a plurality of countercurrent condensing triangles along the circumference of the lower part of an air duct (FT) according to the present invention;
in the figure:
DK, the crossing position of the air cooling island is accessed;
ZC, a wind barrel support column at the position of the wind inlet surface of the wind barrel;
FIG. 11 is a schematic view of the header with the single row of tube outlets above the tube sheet, where y is 10-30 mm;
FIG. 12 is a visual comparison of the cross section of a large-section single row tube with the current common 219X19X1.5 cross section;
FIG. 13 is a view showing the unique arrangement and operation of a 219 × 19 × 1.5 standard single row pipe in the prior art;
FIG. 14 is a schematic view of a single-row-pipe steam inlet provided with a condensed water drainage member and an arrangement manner;
in the figure: YL, drainage member code;
FIG. 15 is a simplified schematic of a large cross-section single row of tubes for the first stage and the second stage according to the present invention;
in the figure: the unit is millimeter;
l, the section length of the base pipe of the single-row pipe;
w, the section height of the base pipe of the single-row pipe;
h, the section height of the single row of tubes containing the fin height;
19, single row tube serpentine fin height;
200, length of single-row tube radiating fins;
t, the wall thickness of the base pipe of the single-row pipe is 1.5mm uniformly;
FIG. 16 is a schematic diagram showing a part of a condensing triangular radiator with a larger included angle m2 & gt m1 on the windward side;
m1, top angle of windward side;
m2, the included angle of the windward side of the air inlet side;
in fig. 17, on the basis that the single-row pipes are inclined to the windward side as shown in fig. 8, the windward side of the air inlet side is partially turned by a proper angle, so that the condensation triangle, particularly the condensation effect on the outer side, can be improved better.
FIG. 18 is a schematic top view of the shutter in three operating states;
in the figure:
GB, which indicates that the blind is operated in the closed state,
FL, represent the shutter works in the air quantity regulation control state;
FX represents that the louver works in a wind direction adjusting and controlling state, and eliminates the harm of uneven air inlet on the windward side of two countercurrent condensing turbines when ambient wind appears by guiding the wind direction of the angle of the louver;
QK, representing the shutter works in the full-open state;
FIG. 19 is a graph of a typical year-hour cumulative frequency distribution;
fig. 20 is a plot of turbine exhaust back pressure provided by an air cooling island according to the present invention.
Detailed Description
The following description will be given of the specific embodiment of the present invention, taking a 2X 66 ten thousand kw unit and a 1065 ton/hr steam exhaust load as an example.
Cumulative weather element statistic value of project weather station
The cumulative frequency distribution curve of the project typical year and temperature hour (see the attached figure 19 of the specification).
The main design parameters of the NDC system of the 2X 660MW unit (all-steel straight-tube structure tower) are adopted
| Serial number | Item | Parameter(s) |
| 1 | Cooling area of radiator (ten thousand m)2) | 2×160 |
| 2 | Design air temperature (DEG C) | 14 |
| 3 | Design back pressure (kPa) | 9.1 |
| 4 | Design air temperature in summer (DEG C) | 31 |
| 5 | Summer design backpressure (kPa) | 21 |
| 6 | Number of cooling triangle | 2X 49 pieces) |
| 7 | Cooling triangular height (m) | 33(3 layers) |
| 8 | Effective width of radiator (m) | 5.6 |
| 9 | Zero meter column diameter (m) at the bottom of cooling tower | 125 |
| 10 | Outside diameter of bottom radiator of cooling tower (m) | 168 |
| 11 | Height of cooling tower (m) | 180 |
| 12 | Height of air inlet of cooling tower | 33 |
| 13 | Outlet diameter (m) | 123 (two machines share one tower) |
| 14 | Radiator tube type | Single row of tubes |
The steam turbine exhaust back pressure curve provided by the air cooling island of the invention project is adopted (see the attached figure 20 in the specification).
The natural ventilation air cooling island formed by full countercurrent direct air cooling condensation adopts large air volume to reduce the temperature rise of cooling air from 30 ℃ of mechanical ventilation to 20 ℃ so as to effectively reduce the condensation temperature of exhaust steam to 10 ℃ and reduce the backpressure of a steam turbine to 21kPa at 31 ℃ and can control the backpressure of the exhaust steam to operate at 5kPa for a long time in winter in low-temperature seasons, so that an air cooling unit reaches or approaches to the kwh heat consumption of a water cooling unit.
The foregoing is a detailed description of the invention and no limitation to the specific embodiments thereof is intended, as one skilled in the art will readily appreciate that many modifications and variations are possible without departing from the inventive concepts herein.
Claims (10)
1. The full-countercurrent direct air-cooling condensing method is characterized in that: the exhaust steam of the steam turbine enters from bottom to top through a main pipe (ZG), an exhaust steam ring pipe (1a) and a branch pipe (1), and is composed of a steam inlet header (2), a first-stage countercurrent condenser (NQQ1) composed of large-section single discharge pipes (3), a first header (4), a second-stage countercurrent condenser (NQQ2) composed of large-section single discharge pipes (5), a second header (6), a third-stage countercurrent condenser (NQQ3) composed of currently universal single discharge pipes (7), a third header (8), a pipeline (9), a fourth header (10), a fourth-stage countercurrent condenser (NQQ4) composed of universal single discharge pipes (11), and an outlet header (12) which are tightly connected, wherein a plurality of single rows of finned tubes are vertically arranged, and a countercurrent air cooling condenser unit (N) is vertically arranged on the windward side; the exhaust steam flows downwards attached to the inner wall of the single-row pipe from bottom to top in the air-cooling condensing unit (N) for multiple times, and the low-temperature condensate is in countercurrent contact with the exhaust steam for heat transfer, cooling and condensing to form liquid water; micro non-condensable gas carried in the exhaust steam enters a non-condensable gas collecting pipe (1b) through a non-condensable gas outlet pipe (13) after multi-stage condensation and enrichment, and passes through a vacuum pump inlet pipe (1c) together with non-condensable gas of other countercurrent air-cooling condensing units (N);
the two countercurrent air-cooling condensing units (N) with vertical windward sides and the shutter (F) or the fan (S) form a countercurrent condensing triangle; the plurality of countercurrent condensing triangles are arranged along the circumference of the lower part of the air duct (FT) to form a full countercurrent natural ventilation direct air cooling island, or a mixed ventilation direct air cooling island of full countercurrent mechanical ventilation and natural ventilation, or a full countercurrent mechanical ventilation direct air cooling island.
2. The full countercurrent direct air-cooling condensing method according to the claim 1, characterized in that the large section single-row pipe (3) of the first stage countercurrent condenser (NQQ1) has a single-pipe steam-passing sectional area 2-4 times of the current general 219X19X1.5 specification 34 square centimeter, and the ratio of the length (L-2t) to the width (W-2t) of the internal section is as follows: (L-2t)/(W-2t) is 5-8;
the large-section single-row pipe (5) of the second-stage countercurrent condenser (NQQ2), the single-pipe steam-passing sectional area is 1.5-3 times of the current general 219X19X1.5 specification 34 square centimeter, and the ratio of the length (L-2t) to the width (W-2t) of the inner section is as follows: (L-2t)/(W-2t) 5.5 to 10.5;
the single-tube bank (7) of the third-stage secondary countercurrent condenser (NQQ3) has a single-tube steam-passing sectional area 1-2 times of the current general 219X19X1.5 specification, and the ratio of the length (L-2t) to the width (W-2t) of the inner section is as follows: (L-2t)/(W-2t) 7-13.5;
the ratio of the length (L-2t) to the width (W-2t) of the inner section of the single-row pipe (11) of the fourth-stage secondary countercurrent condenser (NQQ3) is as follows: (L-2t)/(W-2t) ═ 13.5.
3. The full countercurrent direct air-cooling condensing method according to claim 1, characterized in that the partial flow velocity and turbulent reynolds number of the exhaust steam in the vertical air-cooling condensing single discharge pipe are reduced along with the displacement of the exhaust steam by the flowing of the exhaust steam from bottom to top in the vertical air-cooling condensing single discharge pipe, which can be used for eliminating the disadvantages of the thickening and the increasing of the thermal resistance of the exhaust steam condensate in the downward flowing of the pipe wall; the condensate which flows downwards and thickens along the pipe wall is stirred vigorously by the dead steam with higher flow speed and Reynolds number all the time, so that the thickness of a condensate stagnation layer which causes thermal resistance cannot be increased, and the heat transfer film coefficient of the single-row pipe condensed from the inlet to the outlet of the dead steam on the inner wall can keep a good value, thereby reliably ensuring the heat transfer efficiency of the reverse flowing condensation of the dead steam and the condensate thereof.
4. The full countercurrent direct air-cooled condensing method according to claim 1, characterized in that the exhaust steam is condensed in a multistage countercurrent manner to enrich the non-condensed steam in the exhaust steam.
5. The full countercurrent direct air-cooling condensing method according to claim 1, characterized in that the condensed water flowing into the lower header from the single row pipe flows to the edge area of the header pipe plate through the flow guiding component (YL);
a U-shaped water seal downcomer (J3) is arranged between the header (10) and the header (6) so that condensed water in the header (10) flows into the header (6) by utilizing liquid level pressure difference; the exhaust steam in the header (6) can only enter the header (8) through a countercurrent condensation single discharge pipe (7) in a condenser (NQQ3) with the resistance far smaller than the U-shaped water seal liquid level pressure difference during partial cooling condensation;
a second downcomer (J2) is arranged between the header (6) and the header (4) so that condensed water in the header (6) can flow into the header (4) by utilizing the potential difference; a U-shaped water seal (J2U) is arranged at the water outlet of the second downcomer (J2), so that exhaust steam in the header (4) can only enter the header (6) through a countercurrent condensation single discharge pipe (5) in a condenser (NQQ2) with resistance far smaller than the liquid level pressure difference of the U-shaped water seal (J2U);
a first downcomer (J1) is arranged between the header (4) and the header (2) so that condensed water in the header (4) can flow into the header (2) by utilizing the potential difference; the water outlet of the first downcomer (J1) is provided with a U-shaped water seal (J1U) so as to ensure that exhaust steam in the header (2) can only enter the header (4) through a countercurrent condensation single discharge pipe (3) in a condenser (NQQ1) with resistance far smaller than the liquid level pressure difference of the U-shaped water seal (J1U).
6. The full countercurrent direct air-cooling condensing method according to the claim 1, characterized in that the outlet of the single row pipe (3) in the first header (4) is higher than the pipe plate by more than 30 mm, so as to prevent the condensate on the pipe plate from flowing into the single row pipe (3) and make the condensate on the pipe plate flow to the steam inlet header (2) only through the downcomer (J1);
the outlet of the single-row pipe (5) in the second header (6) is 20 mm higher than the tube plate to prevent condensate on the tube plate from flowing into the single-row pipe (5) and ensure that the condensate on the tube plate can only pass through the downcomer (J2) and the first header (4);
the outlet of the single-row pipe (7) in the third header (8) is 10 mm higher than the tube plate, so that condensate on the tube plate can not flow into the single-row pipe (7), and the condensate on the tube plate can only pass through the downcomer (J3) and the second header (6).
7. The full-countercurrent direct air-cooling condensing method according to claim 1, characterized in that the countercurrent condensing stage can be designed as multistage countercurrent condensing of one stage, two stages, three stages and the like according to requirements; it is also possible to design co-current condensation in any stage.
8. The full countercurrent direct air-cooled condensing method according to claim 1, characterized in that the single row of countercurrent condensing pipes can be arranged in a non-vertical inclined mode to perform countercurrent condensing of the exhausted steam.
9. The full countercurrent direct air-cooling condensing method according to claim 1, characterized in that the included angle (e) between the central line C-D of the single-row pipe section and the central line A-C of the condensing unit is less than 90 degrees, and is preferably 70 degrees to 90 degrees;
the countercurrent condensing triangle adopts the structure that the included angle m2 of two windward surfaces at the air inlet side is larger than the vertex angle m1(m2 is more than m 1);
on the basis that the included angle (e) between the central line C-D of the section of the single-row pipe and the central line A-C of the condensing unit is smaller than 90 degrees, the included angle m2 of the part of the windward side of the air inlet side can be properly increased, namely m2 is larger than m1 and is 3 degrees to 30 degrees.
10. The full countercurrent direct air-cooling condensing method according to the claim 1, characterized in that the louver (F) is vertically arranged with its rotation axis, the louver can rotate by ± 90 ° from left to right, the louver (F) blades on both sides of the center line of the louver can rotate forward and backward;
a louver (F) of the first-stage secondary countercurrent condenser (NQQ1), a louver (F) of the second-stage secondary countercurrent condenser (NQQ2) and a louver (F) of the third-stage secondary countercurrent condenser (NQQ3) are designed to be regulated and controlled respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010708737.4A CN113970254B (en) | 2020-07-22 | Full countercurrent direct air-cooling condensing method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010708737.4A CN113970254B (en) | 2020-07-22 | Full countercurrent direct air-cooling condensing method |
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| CN113970254A true CN113970254A (en) | 2022-01-25 |
| CN113970254B CN113970254B (en) | 2024-10-25 |
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