CN113027547B - Inlet structure of drainage cooling section of flow guide type heater and design method - Google Patents
Inlet structure of drainage cooling section of flow guide type heater and design method Download PDFInfo
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- CN113027547B CN113027547B CN202110379848.XA CN202110379848A CN113027547B CN 113027547 B CN113027547 B CN 113027547B CN 202110379848 A CN202110379848 A CN 202110379848A CN 113027547 B CN113027547 B CN 113027547B
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- 238000001816 cooling Methods 0.000 title claims abstract description 141
- 238000000034 method Methods 0.000 title claims abstract description 19
- 230000002209 hydrophobic effect Effects 0.000 claims abstract description 104
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 22
- 230000007704 transition Effects 0.000 claims description 3
- 238000004364 calculation method Methods 0.000 claims description 2
- 230000009286 beneficial effect Effects 0.000 abstract description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 14
- 239000012530 fluid Substances 0.000 description 4
- 238000009434 installation Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000010248 power generation Methods 0.000 description 2
- 230000001172 regenerating effect Effects 0.000 description 2
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 230000005514 two-phase flow Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 238000004880 explosion Methods 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 238000004781 supercooling Methods 0.000 description 1
- 238000010408 sweeping Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/08—Cooling; Heating; Heat-insulation
- F01D25/12—Cooling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
- F01D21/003—Arrangements for testing or measuring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention discloses an inlet structure of a flow guide type heater hydrophobic cooling section and a design method thereof.A plurality of flow guide blade grids are arranged on a hydrophobic cooling end plate at the upstream side of the heater hydrophobic cooling section and a hydrophobic cooling end plate at the downstream side of the heater hydrophobic cooling section to form flow guide blade grid channels with equal outlet flow areas, outlets of drainage holes are uniformly arranged at the upper parts of the flow guide blade grid channels, inlets of the drainage holes are arranged at the lower end surfaces of the hydrophobic cooling end plate at the upstream side of the heater hydrophobic cooling section and the hydrophobic cooling end plate at the downstream side of the heater hydrophobic cooling section, and the drainage holes fully utilize the pressure difference power at the inlet and the outlet, so that the drainage at a high pressure area at the inlet of the hydrophobic cooling section can directly reach the interior of the hydrophobic cooling section under the driving of a pressure gradient, which is beneficial to further improving the siphon capacity of the hydrophobic cooling section and finally improving the siphon structural performance and the low siphon structural stability.
Description
Technical Field
The invention belongs to the field of power generation of steam turbines, and particularly relates to an inlet structure of a drainage cooling section of a flow guide type heater and a design method of the inlet structure.
Background
At present, the system of a large-scale thermal power plant is widely designed by adopting regenerative cycle, and the regenerative cycle is realized by configuring a water supply heater. The feedwater heater is an important device for improving the economic efficiency of a thermal power plant, and is generally structurally divided into a superheat section, a saturation section and a supercooling section according to different steam-water heat exchange modes in the feedwater heater. The superheat section of the heater utilizes the sensible heat of superheated steam extraction of the steam turbine stage section to heat the feed water in the pipe, and after the steam is baffled by a plurality of partitions, the superheated steam can be cooled to be 25-30 ℃ higher than the saturation temperature; the saturation section heats the feed water in the pipe by using the latent heat of extracted steam, the steam is prevented from contacting with the outside of the pipe, and the steam is condensed into water because the wall surface temperature is lower than the steam saturation temperature; the cooling dredging section heats the feed water in the pipe by utilizing the sensible heat of the condensed water. The temperature of the drainage outlet is lower than the saturation temperature by setting the dredging end, the temperature difference between the drainage outlet and the high feed water is 5.6-8.3 ℃, and the temperature of the large unit is generally 5.6 ℃. In the current engineering design, the dredging section mainly adopts a siphon structure, and saturated water outside the dredging section is pumped into the dredging section through a siphon orifice and is sent to a next-stage heater. The current influence of factors such as power peak regulation, generating set operating mode are complicated, and the heater not only will be operated under rated condition, still probably bears the influence of various abnormal operating mode simultaneously, therefore obvious fluctuation phenomenon about the heater water level will appear. The commonly used cooling section of the heater is in a single-channel plane end wall design form, when the working condition changes to cause the water level of the heater to swing, the balance state of a siphon structure is extremely easy to be damaged, steam in a partial saturated section can enter the cooling section, and the steam-liquid two-phase flow phenomenon is caused to occur, so that the difference of the water-draining end of the heater is increased, the pipe wall of the next-stage heater is further aggravated to erode to thin the pipe wall, and severe persons have safety accidents such as pipe explosion.
Therefore, the development of the drain cooling section structure of the heater suitable for wide-area water level operation of the heater has great significance for ensuring the safety of the normalized wide-load operation of the power generation turbine unit.
Disclosure of Invention
The invention aims to overcome the defects and provides an inlet structure of a drainage cooling section of a flow guide type heater and a design method thereof, which can meet the technical requirement of ensuring the siphon stability of the drainage cooling section under the working condition of large swing of the water level of the heater caused by the rapid change of the load of a steam turbine.
In order to achieve the purpose, the inlet structure of the flow guide type heater drainage cooling section comprises a plurality of flow guide blade grids arranged on a drainage cooling end plate on the upstream side of the heater drainage cooling section and a drainage cooling end plate on the downstream side of the heater drainage cooling section, wherein flow guide blade grid channels are formed by adjacent flow guide blade grids, drainage hole inlets are formed in the bottoms of the drainage cooling end plate on the upstream side of the heater drainage cooling section and the drainage cooling end plate on the downstream side of the heater drainage cooling section, drainage hole outlets are formed in the end surfaces of the drainage cooling end plate on the upstream side of the heater drainage cooling section and the drainage cooling end plate on the downstream side of the heater drainage cooling section, and the drainage hole outlets are arranged at the upper part of the flow guide blade grid channels.
The guide vane cascade channel is tapered from top to bottom.
The middle ridge line of the guide vane cascade channel is generated by a multi-order Bezier curve.
All the guide vane cascade channels have the same area.
The hydrophobic cooling end plate on the upstream side of the hydrophobic cooling section of the heater and the hydrophobic cooling end plate on the downstream side of the hydrophobic cooling section of the heater jointly form a siphon section inlet of the hydrophobic cooling section of the heater.
A design method of an inlet structure of a drainage cooling section of a flow guide type heater comprises the following steps:
arranging a plurality of flow guide blade grids on a hydrophobic cooling end plate at the upstream side of a hydrophobic cooling section of the heater and a hydrophobic cooling end plate at the downstream side of the hydrophobic cooling section of the heater, so that adjacent flow guide blade grids form a flow guide blade grid channel;
the wedge angle phi of the inlet edge of the guide vane cascade ranges from 15 degrees to 60 degrees. The turning angle beta of the guide vane cascade ranges from 105 degrees to 155 degrees;
the radial length B of the guide vane cascade is smaller than the radial dimension H of the hydrophobic cooling end plate, and the calculation method is as follows:
H＝B+ΔR
wherein: Δ R is 5-15% h;
the ridge line in the guide vane cascade is generated by a multi-order B spline curve, and the control equation is as follows:
wherein t is ∈ [0,1 ]]Is a coordinate point, P i As a control point, w i Are the weight coefficients.
Drainage hole inlets are formed in the bottoms of the hydrophobic cooling end plate on the upstream side of the hydrophobic cooling section of the heater and the hydrophobic cooling end plate on the downstream side of the hydrophobic cooling section of the heater, and drainage hole outlets are formed in the end surfaces of the hydrophobic cooling end plate on the upstream side of the hydrophobic cooling section of the heater and the hydrophobic cooling end plate on the downstream side of the hydrophobic cooling section of the heater, so that the drainage hole outlets are arranged at the upper part of the guide vane grid channel;
radius R of drainage hole inlet and drainage hole outlet 1 Is 2-4 cm, and the radius R of the uniform transition section of the arc of the guide line of the inlet of the drainage hole and the outlet of the drainage hole 2 Is 1-6 cm.
Compared with the prior art, the invention arranges the plurality of flow guide blade grids on the hydrophobic cooling end plate at the upstream side of the hydrophobic cooling section of the heater and the hydrophobic cooling end plate at the downstream side of the hydrophobic cooling section of the heater, so as to form flow guide blade grid channels with the same outlet flow area, the outlets of the drainage holes are uniformly arranged on the upper parts of the flow guide blade grid channels, the inlets of the drainage holes are arranged on the lower end surfaces of the hydrophobic cooling end plate at the upstream side of the hydrophobic cooling section of the heater and the hydrophobic cooling end plate at the downstream side of the hydrophobic cooling section of the heater, and the drainage holes fully utilize the pressure difference power at the inlets and the outlets, so that the drainage at the high pressure area at the inlet of the hydrophobic cooling section can directly reach the interior of the hydrophobic cooling section under the driving of the pressure gradient, thereby being beneficial to further improving the siphon capacity of the hydrophobic cooling section and finally improving the siphon structural performance and the low siphon structural stability.
The design method of the invention is that by adding the guide vane grid structure, after hydrophobic flow enters the guide vane grid at the inlet of the siphon section, the flow velocity of fluid can be increased according to the incompressible stable flow continuous equation relation due to the shrinkage of the cross-sectional area of the flow, thereby enhancing the siphon suction capacity. And secondly, the inlet position of the drainage hole is arranged at the lower end face of the drainage cooling end plate, and the outlet position of the drainage hole is designed at the downstream of the outlet of the flow guide blade cascade. Similarly, as can be seen from the relationship of the incompressible steady flow equation of continuity, since the pressure in the guide vane cascade channel decreases significantly as the fluid flow rate increases, the guide vane cascade outlet appears as a low pressure flow region with a pressure much lower than that in the inlet region of the hydrophobic cooling section. The invention can effectively improve the siphon stability of the drainage cooling section, thereby avoiding the occurrence of the phenomenon of vapor-liquid two-phase flow when the water level of the heater swings, and further improving the operation safety of the unit.
Drawings
FIG. 1 is a schematic view of the relative fit installation of the present invention in a heater;
FIG. 2 is an enlarged view of a portion of the present invention;
FIG. 3 is a three-dimensional view of the structure of the present invention; (a) is a perspective view, and (b) is a perspective view;
FIG. 4 is a meridian plane elevation of the present invention;
FIG. 5 is a three-dimensional view of the structure of the downstream end plate of the hydrophobic cooling section in accordance with the present invention; (a) is a perspective view, and (b) is a perspective view;
FIG. 6 is a schematic size diagram of a downstream end plate structure of the hydrophobic cooling section in accordance with the present invention;
wherein, 1, a heater, 2, a heater hydrophobic cooling section, 3, a heater hydrophobic cooling section siphon section inlet, 4, a heater hydrophobic cooling section upstream side hydrophobic cooling end plate, 5, a heater hydrophobic cooling section downstream side hydrophobic cooling end plate, 6, the lower end face of a hydrophobic cooling end plate of a hydrophobic cooling section of the heater, 7, a heat exchange tube bundle of the heater, 8, a flow guide cascade, 9, a flow guide cascade channel, 10, a drainage hole, 11, a drainage hole inlet, 12 and a drainage hole outlet.
Detailed Description
The invention is further described below with reference to the accompanying drawings.
Referring to fig. 1 to 6, a flow guide type heater drainage cooling section inlet structure comprises a plurality of flow guide blade grids 8 arranged on a hydrophobic cooling end plate 4 at the upstream side of a heater drainage cooling section and a hydrophobic cooling end plate 5 at the downstream side of the heater drainage cooling section, wherein the adjacent flow guide blade grids 8 form a flow guide blade grid channel 9, drainage hole inlets 11 are formed in the bottoms of the hydrophobic cooling end plate 4 at the upstream side of the heater drainage cooling section and the hydrophobic cooling end plate 5 at the downstream side of the heater drainage cooling section, drainage hole outlets 12 are formed in the lower end face 6 of the hydrophobic cooling end plate at the heater drainage cooling section, and the drainage hole outlets 12 are arranged at the upper part of the flow guide blade grid channel 9. The hydrophobic cooling end plate 4 of the hydrophobic cooling section upstream side of heater and the hydrophobic cooling end plate 5 of the hydrophobic cooling section downstream side of heater constitute hydrophobic cooling section siphon section entry 3 of heater jointly, and hydrophobic cooling section siphon section entry 3 of heater sets up at the hydrophobic cooling section 2 of heater 1.
A design method of an inlet structure of a drainage cooling section of a flow guide type heater comprises a design method of a guide vane cascade and a design method of a drainage hole 10.
The design method of the guide vane cascade comprises the following steps:
the inlet of the siphon section is assembled on the inner end surfaces of the upper and the downstream side hydrophobic cooling end plates of the hydrophobic cooling section of the heater by additionally designing a flow guide blade grid and independently processing and forming the flow guide blade grid by adopting a welding method. The flow guide blade cascade channel is in a tapered shape, and the molded line is determined by a front edge inlet small circle, a tail edge outlet small circle and a middle ridge line. The middle ridge line is generated by a multi-order Bezier curve. Three groups of guide vane grids with different chord lengths are designed at the position of the drainage cooling end plate to form two tapered channels, and the flow areas of outlets of the two tapered channels are equal. When the guide vane cascade is designed, the initial design parameters need to be given, including: the geometric inlet angle, chord length, small radius of the inlet at the front edge, small radius of the outlet at the tail edge, wedge angle at the inlet edge, wedge angle at the outlet edge, turning angle, installation angle and the like of the blade profile. The wedge angle phi of the inlet edge of the guide vane cascade ranges from 15 degrees to 60 degrees. The turning angle beta of the guide vane cascade ranges from 105 degrees to 155 degrees.
When in design, the radial length B of the guide vane cascade is slightly smaller than the radial dimension H of the hydrophobic cooling end plate.
H＝B+ΔR
Wherein: Δ R ranging from 5% to 15%
The ridge line in the guide vane cascade is generated by a multi-order B spline curve according to the given initial design parameters, and the control equation is
Wherein t is ∈ [0,1 ]]Is a coordinate point, P i As a control point, w i Are weight coefficients.
The design method of the drainage hole 10 is as follows:
the drainage holes are uniformly arranged at the lower end faces of the upper and lower drainage cooling end plates, and the outlets are arranged at the downstream of the flow guide blade grid outlets on the inner end faces of the upper and lower drainage cooling end plates. The drainage holes are of the uniform cross section type, are generated along the guide wire by a sweeping method, and the horizontal section and the vertical section of the guide wire are uniformly transited by circular arcs. The radius R1 of the drainage hole ranges from 2 cm to 4cm, and the radius R2 of the uniform transition section of the arc of the guide wire ranges from 1 cm to 6cm.
The working principle of the invention is as follows:
according to the invention, firstly, by adding the guide vane grid structure, after hydrophobic flow enters the tapered guide vane grid at the inlet of the siphon section, the flow velocity of fluid can be increased according to the incompressible stable flow continuous equation relation due to the shrinkage of the through-flow sectional area, so that the siphon suction capacity is enhanced. Secondly, the inlet position of the newly designed drainage hole is arranged at the lower end face of the drainage cooling end plate, and the outlet position of the drainage hole is arranged at the downstream of the outlet of the tapered guide vane cascade. Similarly, according to the relationship of the incompressible stable flow equation of continuity, since the pressure in the guide vane cascade channel is obviously reduced along with the increase of the flow velocity of the fluid, the outlet of the guide vane cascade is presented as a low-pressure flow area, and the pressure is far lower than the inlet area of the hydrophobic cooling section. The arrangement of the drainage holes fully utilizes the pressure difference power at the inlet and the outlet, so that the drainage of a high-pressure area at the inlet of the drainage cooling section can directly reach the interior of the drainage cooling section under the driving of a pressure gradient, which is beneficial to further improving the siphon capacity of the drainage cooling section.
Claims (4)
1. A design method of an inlet structure of a hydrophobic cooling section of a flow guide type heater is characterized in that the inlet structure comprises a plurality of flow guide blade grids (8) arranged on a hydrophobic cooling end plate (4) at the upstream side of the hydrophobic cooling section of the heater and a hydrophobic cooling end plate (5) at the downstream side of the hydrophobic cooling section of the heater, wherein the adjacent flow guide blade grids (8) form a flow guide blade grid channel (9), drainage hole inlets (11) are formed in the bottoms of the hydrophobic cooling end plate (4) at the upstream side of the hydrophobic cooling section of the heater and the hydrophobic cooling end plate (5) at the downstream side of the hydrophobic cooling section of the heater, drainage hole outlets (12) are formed in the end surfaces of the hydrophobic cooling end plate (4) at the upstream side of the hydrophobic cooling section of the heater and the hydrophobic cooling end plate (5) at the downstream side of the hydrophobic cooling section of the heater, and the drainage hole outlets (12) are arranged at the upper part of the flow guide blade grid channel (9);
the guide vane cascade channel (9) is tapered from bottom to top;
a hydrophobic cooling end plate (4) at the upstream side of the hydrophobic cooling section of the heater and a hydrophobic cooling end plate (5) at the downstream side of the hydrophobic cooling section of the heater jointly form a siphon section inlet (3) of the hydrophobic cooling section of the heater;
the design method comprises the following steps:
a plurality of flow guide blade grids (8) are distributed on a hydrophobic cooling end plate (4) on the upstream side of a hydrophobic cooling section of the heater and a hydrophobic cooling end plate (5) on the downstream side of the hydrophobic cooling section of the heater, so that adjacent flow guide blade grids (8) form a flow guide blade grid channel (9);
the wedge angle phi of the inlet edge of the guide vane cascade ranges from 15 degrees to 60 degrees, and the turning angle beta of the guide vane cascade ranges from 105 degrees to 155 degrees;
the radial length B of the guide vane cascade is smaller than the radial dimension H of the hydrophobic cooling end plate, and the calculation method is as follows:
wherein:
5% -15% H;
the ridge line in the guide vane cascade is generated by a multi-order B spline curve, and the control equation is as follows:
wherein,
as a point of the coordinate, a coordinate point,
in order to be a control point, the control point,
are the weight coefficients.
2. The design method of the inlet structure of the hydrophobic cooling section of the flow guiding heater according to claim 1, characterized in that the middle ridge line of the guide blade grid channel (9) is generated by a multi-step Bezier curve.
3. The design method of the inlet structure of the hydrophobic cooling section of the flow guide heater according to claim 1, characterized in that the areas of all the guide vane cascade channels (9) are the same.
4. The design method of the inlet structure of the hydrophobic cooling section of the flow guide type heater according to claim 1, characterized in that the bottoms of the hydrophobic cooling end plate (4) at the upstream side of the hydrophobic cooling section of the heater and the hydrophobic cooling end plate (5) at the downstream side of the hydrophobic cooling section of the heater are provided with the drainage hole inlets (11), the end surfaces of the hydrophobic cooling end plate (4) at the upstream side of the hydrophobic cooling section of the heater and the hydrophobic cooling end plate (5) at the downstream side of the hydrophobic cooling section of the heater are provided with the drainage hole outlets (12), and the drainage hole outlets (12) are arranged at the upper part of the flow guide cascade channels (9);
radius R of inlet (11) and outlet (12) of drainage hole 1 Is 2-4 cm, and the radius R of the guide line circular arc uniform transition section of the inlet (11) and the outlet (12) of the drainage hole 2 Is 1-6 cm.
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| CN202110379848.XA CN113027547B (en) | 2021-04-08 | 2021-04-08 | Inlet structure of drainage cooling section of flow guide type heater and design method |
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| CN202110379848.XA CN113027547B (en) | 2021-04-08 | 2021-04-08 | Inlet structure of drainage cooling section of flow guide type heater and design method |
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| TW200636169A (en) * | 2005-04-01 | 2006-10-16 | Shwin-Chung Wong | A flow distributor for a fan |
| CN101113678A (en) * | 2007-07-31 | 2008-01-30 | 孙敏超 | Outlet flowing intersecting surface changing adjustable turbo nozzle ring |
| CA2643567A1 (en) * | 2008-11-10 | 2010-05-10 | Organoworld Inc. | Fluid directing system for turbines |
| EP2581015B1 (en) * | 2011-10-12 | 2015-01-21 | Black & Decker Inc. | A vacuum cleaner |
| US10280772B2 (en) * | 2015-06-22 | 2019-05-07 | Saudi Arabian Oil Company | Flow distribution device and method |
| CN107237718A (en) * | 2017-08-02 | 2017-10-10 | 河海大学 | A kind of multi-stage impeller tumbler for absorbing tide energy |
| CN111412339A (en) * | 2020-04-22 | 2020-07-14 | 西安西热节能技术有限公司 | Drainage near T-shaped pipe of three-section type regenerative system and design method |
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