CN104775853A - Penultimate-stage moving blade for feed pump turbines - Google Patents
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Abstract
The invention relates to a penultimate-stage moving blade for feed pump turbines. The effective height of the blade is 358mm, and the relative value of the blade height H is monotonically increased from 0.0 to 1.0; correspondingly, the installation angle c1 is monotonically decreased from 84.260 to 25.130; the change law of the area A from the root section to the top section is: 3.606 greater than or equal to A greater than or equal to 1.0, the change law of the axial width Xa from the root section to the top section is: 2.581 greater than or equal to Xa greater than or equal to 1.0, the change law of the chord length b1 from the root section to the top section is: 1.133 greater than or equal to b1 greater than or equal to 1.0, and the change law of the maximum thickness W1 from the root section to the top section is: 2.964 greater than or equal to W1 greater than or equal to 1.0. The penultimate-stage moving blade is applicable to 100-percent capacity feed pump turbines among 24MW to 44MW power, unidirectional-exhaust (one exhaust port), 2600rpm to 5500rpm variable rotational speed and ultra-supercritical 1000MW class turbines.
Description
Technical field
The present invention relates to the secondary final stage moving blade of feed pump turbine, be applicable to power 24MW ~ 44MW, unidirectional steam discharge (1 relief opening), 100% capacity feed pump turbine of the level steam turbine such as variable speed, ultra supercritical 1000MW of rotating speed 2600 ~ 5500rpm.
Background technique
Feed pump turbine is a kind of special steam turbine, particularity shows: it is often in high rotating speed, variable speed, Variable power operating mode is run, and to adapt to the load variations of large machine, vapor pressure is low, temperature is low, but power is large, and last stage and penultimate stage rotor blade is very long, and these operating conditionss significantly limit the design of final stage, secondary final stage moving blade.And the Economy of feed pump turbine and Security are to a great extent with its final stage and penultimate heating power, pneumatic, intensity, VIBRATION DESIGN are closely related, wherein especially maximum with final stage, secondary final stage moving blade design difficulty, must make overall plans, the conceptual design carried out under numerous and diverse multifactor constraint conditio is preferred, just can design high performance feed pump turbine time final stage moving blade.
100% capacity feed pump turbine field needed for ultra supercritical 1,000,000 unit, because unit steam inlet condition is low, power is large, need leaving area large, drive that turbine speed high, the secondary final stage moving blade steam passage height of feed water pump is very high, very little, the secondary final stage moving blade centrifugal force of blade axial width large, stress level superelevation, vibration are complicated, run in transonic speed, design difficulty is very large.
Summary of the invention
Technical problem to be solved by this invention, be to provide a kind of rational in infrastructure, dynamic stress is low, be applicable to power 24MW ~ 44MW, unidirectional steam discharge, the secondary final stage moving blade of 100% capacity feed pump turbine of the level steam turbine such as variable speed, ultra supercritical 1000MW of rotating speed 2600 ~ 5500rpm.
The technical solution adopted in the present invention is:
A kind of feed pump turbine time final stage moving blade, have integrally-built blade root, blade, shroud, described shroud is positioned at the top of blade, and blade root is positioned at the root of blade; Described blade is the obform body coincided by a specific rule by some characteristic cross-sections, and its effective height is H, root footpath is Dr; The profile molded line of described characteristic cross-section is the closed curve surrounded by inner arc curve and back of the body arc curve, has characteristic parameter established angle c1, chord length b1, maximum ga(u)ge w1, sectional area A; The rule that coincides in cross section is: along leaf height direction from butt to top, the continuous and derivable transition of each cross section; The relative value of leaf height H by 0.0 monotone increasing to 1.0; Correspond, established angle c1 is by 84.26
0dullness is reduced to 25.13
0; Area A Changing Pattern from root cross section to top section is: 3.606>=A>=1.0, axial width Xa Changing Pattern from root cross section to top section is: 2.581>=Xa>=1.0, chord length b1 Changing Pattern from root cross section to top section is: 1.133>=b1>=1.0, and the maximum ga(u)ge W1 Changing Pattern from root cross section to top section is: 2.964>=W1>=1.0.
The effective height of described blade is H=358mm, root footpath is Dr=1146mm.
Described shroud has back of the body arc working surface S1 and inner arc working surface P1, and back of the body arc working surface S1 and inner arc working surface P1 is the plane be parallel to each other; The sectional shape of shroud has characteristic parameter: the distance A1 between back of the body arc working surface S1 and inner arc working surface P1, the distance T1 between back of the body arc working surface S1 and inner arc working surface P1 geometrical center; The included angle B 1 of described back of the body arc working surface S1 and turbine rotor medial axis X-axis meets relation:
A1=T1·COSB1； 35°≤B1≤52°；
Shroud thickness H1 meets relation:
7mm<H1<11mm；
Shroud end face tilts, and by leading edge to lagging edge axioversion, inclination angle meets relation:
22°≤θ1≤28°
Described blade root be 4 tooth linear axis to embedded type vertical tree type blade root, blade root platform end face be tilt, by leading edge to lagging edge axioversion, inclination angle meets relation:
8°≤θ2≤12°
The technique effect that the present invention produces is:
The present invention is on summary ultra supercritical 1000MW grade last stage vane of steam turbine design experiences basis of new generation, for meeting the demand of market to 100% capacity feed pump turbine of the level steam turbines such as ultra supercritical 1000MW, the designing technique of application advanced person in the present age, for successfully completing the design being applicable to 100% capacity feed pump turbine second last stage blade.358mm final stage moving blade newly developed has more advanced structural type---and damped type carries shroud, blade root adopts the linear axis of large carrying to design to embedded type vertical tree type blade root, the technical merit of blade is reached world-class levels, there is higher Economy and reliability.It is not only applicable to 100% capacity feed pump turbine requirement of the level steam turbines such as ultra supercritical 1000MW, and be that the macroeconomic improving electric power station system provides support, two 50% feed pump turbines are merged into 100% feed pump turbine, thus can reduce by a feed pump turbine group, greatly reduce equipment investment and capital construction and operating maintenance expense, there is wide market application foreground.
Accompanying drawing explanation
Fig. 1 is the structural representation of this blade;
Fig. 2 is shroud structure schematic diagram;
Fig. 3 is blade schematic cross-section.
Embodiment
See Fig. 1: adopt suitable alloyed steel blade and rotor material, be made up of 3 parts by the moving vane of this patent plan manufacture, respectively: shroud body 1, blade 2, blade root 3.Shroud body 1 is positioned at the top of blade 2, and above-mentioned blade 2, blade root 3, shroud 1 have integrally manufactured with the alloyed steel of same high-intensity performance.Blade is arranged in the impeller groove on rotating shaft cylindrical by blade root 3, often enclose race and install 82 blades, and after all loading onto blade in the impeller groove of a week on impeller, secondary final stage just defining high-power feed pump turbine is done work level.Blade root 3 is that four tooth linear axis are to embedded type vertical tree type blade root.
To 100% capacity feed pump turbine of the level steam turbines such as ultra supercritical 1000MW, every platform large-sized unit only needs a 100% capacity feed pump turbine, a 100% capacity feed pump turbine only 1 grade final stage moving blade (1 relief opening), the feed pump turbine only with large leaving area could meet large machine feedwater requirement, improves whole power station Economy simultaneously.For a large amount of equipment investments and maintenance expenses are saved in power station, improve its economic benefit.
The design vector of this moving vane selects 100% capacity feed pump turbine of the level steam turbines such as ultra supercritical 1000MW, the optimum design back-pressure of this machine is 5.0Kpa, within the scope of this design back-pressure, the secondary final stage moving blade steam passage height H that final scheme is determined is 358mm, root footpath Dr is 1146 mm, and its annulus area equals 1.69 m
2, with this root footpath and Ye Gao for reference design completes the through-flow of feed pump turbine.The design is through-flow for design object with 100% capacity feed pump turbine, given inlet pressure, enthalpy, flow and back pressure, under the prerequisite ensureing meridional channel fairing, optimizes degree of reaction coupling in enthalpy drop at different levels, speed ratio and level.
On the basis of the through-flow Optimized Matching of whole cylinder, in secondary final stage level, the design of Controllable-vortex flow pattern is a complicated repeatedly cyclic design process.First basic quiet, movable vane fundamental mode molded line is designed, by distributing along leaf height efflux angles of Controllable-vortex flow pattern design, design space shaping rule that is quiet, movable vane, optimization level flow field is carried out again with full three-dimensional flow field computational analysis, to go forward side by side the space shaping rule of whole quiet, the movable vane of a step, with pneumatic optimum for design object.
The blade 2 of feed pump turbine of the present invention time final stage moving blade is the obform body coincided by a specific rule by some characteristic cross-sections, the profile molded line of characteristic cross-section is the closed curve surrounded by inner arc curve and back of the body arc curve, see Fig. 1 ~ Fig. 3, there is following characteristics parameter (i.e. the variable-definition of the design):
H: the steam passage height of feed pump turbine time final stage moving blade, the distance between blade 2 top section and blade 2 cross sections.
Dr: the root footpath of blade root.
H1-shroud body 1 thickness.
The distance of A1-between shroud working surface S1, P1.
The horizontal sextant angle of B1 °-shroud working surface S1, P1 and X-axis.
T1-pitch: adjacent two blade sustained height shroud cross sections are at the mounting distance of circumference.
W1-blade 2 cross section tangential width (i.e. maximum ga(u)ge).
B1-chord length: blade cross section is into and out of the distance on vapour limit.
Xa-blade 2 cross section axial widths.
O1-blade 2 cross-sectional exit throat openings: the minimum range of arc is carried on the back in Exit-edge and adjacent blade 2 cross section.
α 1 °-outlet geometry angle: sin-1 (O1/T).
C1 °-blade profile established angle: the angle of chord length line and circumference (Y-direction).
T-pitch: adjacent two blade sustained height molded line cross sections are at the mounting distance of circumference.
W-blade root 3 axial width.
D-blade profile back of the body arc.
E-blade profile inner arc.
F-blade profile lagging edge.
G-blade profile leading edge.
θ 1-Ye Ding inclination angle.
θ 2-blade root inclination angle.
(1) blade design, along the pneumatic design in leaf several feature blade 2 cross sections high
See Fig. 1, Fig. 3: adopt this second last stage blade of special through-flow reconstruct programming along the basic blade profile key element in the high each cross section of leaf and mounting point, the feature along the high each basic blade profile of leaf is: aerodynamic characteristics is root is subsonic speed blade profile, middle and upper part is Transonic Blade Profile, top is supersonic speed blade profile.The cross-section area of basic blade profile reduces along highly dull, and change in turriform, established angle c1 is by 84.26
0dullness is reduced to 25.13
0; Area A Changing Pattern from root cross section to top section is: 3.606>=A>=1.0, and namely root cross section is decreased to 1.0 to the area A of top section by 3.606 dullnesses; Axial width Xa Changing Pattern from root cross section to top section is: 2.581>=Xa>=1.0, and namely root cross section is decreased to 1.0 to the axial width Xa of top section by 2.581 dullnesses; Chord length b1 Changing Pattern from root cross section to top section is: 1.133>=b1>=1.0, and namely root cross section is decreased to 1.0 to the chord length b1 of top section by 1.133 dullnesses; Maximum ga(u)ge W1 Changing Pattern from root cross section to top section is: 2.964>=W1>=1.0, and namely root cross section is decreased to 1.0 to the maximum ga(u)ge W1 of top section by 2.964 dullnesses.Basic blade profile is along highly dull twisting formation.Outlet geometry angle α 1 ° of edge of basic blade profile highly dullness controllably reduces.Adopt full three-dimensional pneumatic parser analysis and each blade profile cross section of optimal design along the high shaping rule of leaf, finally achieve the optimization of this leaf-level flow field characteristic.
This final stage moving blade design adopts straight-tooth fir-tree root, carry damping shroud, loop-forming structure runs, in order to coordinate through-flow steam passage shape, the leaf top portion of this final stage moving blade is with inclination angle theta 1, by leading edge to lagging edge axioversion, and 22 °≤θ 1≤28 °, the deck roof of leaf root part has worn inclination angle theta 2, by leading edge to lagging edge axioversion, and 8 °≤θ 2≤12 °.
Several typical section molded line of blade 2 partial design below moving vane top section, the blade profile between each typical section adopts profile to be smoothly connected, and high-order spline interpolation is obtained.Supersonic speed blade profile cross section is the Focal point and difficult point of blade design.In order to coordinate intensity and the pneumatic restriction to blade profile, doing to improve for several times to blade profile, finally substantially having achieved along ultimate strength stress design such as Ye Gao, meet the requirement of blade root 3 intensity and blade aerodynamic performance simultaneously.
Flow characteristic in moving vane runner is complicated, and all exist from subsonic speed, transonic speed, Supersonic Flow change along leaf height, the quality of molded line aerodynamic characteristic is one of successful key element of blade design.Best for target with aeroperformance; design a set of quiet, basic molded line of movable vane respectively; basic molded line usually can not meet the structure of blade, intensity, VIBRATION DESIGN requirement; when structure, intensity, the VIBRATION DESIGN of follow-up blade; analogy basins design can be carried out to fundamental mode; so not only can meet structure, intensity, VIBRATION DESIGN requirement, and can ensure that aeroperformance is substantially constant.
Complete on basic blade profile, just must carry out flow pattern and the three-dimensional pneumatic analysis and research of second last stage blade.Flow pattern research, mainly under whole cylinder (at least end three grades) environment, utilizes accurate three-dimensional method to come the enthalpy drop of design level, speed ratio, degree of reaction along leaf height distribution equal flow type parameter.On the basis of Controllable-vortex flow pattern design, quiet movable vane is carried out to three dimensional space is long-pending stacks meter.Stator blade mainly adopts tangential and axial composite-rotor bending is shaping, take peak efficiency as target; Movable vane mainly adopts dynamic center of gravity overlap and design by the twisting formation of radial ray, and during with blade in working order, the minimum and peak efficiency of flexure stress (to blade and blade root) of centrifugal force generation is target.As previously mentioned, the structure of pneumatic design and blade, intensity, VIBRATION DESIGN intercouple, sometimes be implacable, advanced secondary final blades design will reach the good coordination of the aerodynamic characteristic of blade and structure, intensity, vibration characteristics exactly, makes blade have high reliability and high Economy.Therefore, the full three-dimensional pneumatic design of blade generally will be obtained through permitting multivariant successive optimization.
(2) the blade 2 structural strength vibration characteristics design under large centrifugal load
In working order, the centrifugal force generation stress that blade respectively reverses variable cross section is very high, and stress is complicated, and the design of this strength vibration to blade is a challenge greatly.During this partial design, will the mutual restriction of following factors be subject to:
● the aerodynamic characteristic restriction of blade each cross section molded line
● the ultimate strength restriction of blade and rotor material
● the stress phase restriction in each cross section of blade
● blade vibration frequency modulation characteristic restricts
● the restriction of blade axial width
For overcoming above-mentioned main restraining factors, keeping the stress level in each cross section substantially suitable, thus applying the ultimate strength of material to greatest extent.Under the prerequisite of shape basic simlarity keeping each cross section, adjust stress and the vibration characteristics of blade, finally make each restraining factors mutually coordinate.Have employed full three-dimensional pneumatic and the weak lotus root of three-dimensional finite element intensity to close analytical method and carried out design analysis to this blade, final optimization pass devises blade 2 structure that can meet aerodynamic characteristic and strength vibration characteristic requirements.The strength characteristics of blade 2 structure is: blade 2 local maximum stress is less than the ultimate strength of blade material, and local maximum stress is less than 2.0 with the ratio of root cross section average stress.
(3) the linkage structure design of large deformation damping vane
Under in working order, the cross section that blade middle and upper part is divided, relative to there being larger torsional deflection during state of rest, adopts the structural finite element analysis Methods of optimization design linkage structure of blade.It is characterized by: devise the shroud structure (see Fig. 2) had a style of one's own with blade 2, its thickness is H1(7mm<H1<11mm).Carry horizontal channelling and radial flow that shroud structure prevents leaf top in pneumatic, when about rotating speed N1 rev/min, shroud working surface (S1 face) contacts with adjacent blades shroud working surface (P1 face), produce larger pressure stress F 1, the included angle B 1 of shroud working surface and X-axis (axis) meets relation: A1=T1COSB1
31 °≤B1≤52 °, increase blade rigid when blade working, make the free vane under static state limit the twist recovery on leaf top significantly when rated speed, form whole circle restraining structure, significantly reduce blade dynamic stress.The contact rotating speed of linkage structure meets relation: 0≤N1≤1800 rev/min.Working surface pressure stress meets relation: the ultimate strength of 0.0126<F1≤0.055 times material.
Claims (6)
1. a feed pump turbine time final stage moving blade, have integrally-built blade root, blade and shroud, described shroud is positioned at the top of blade, and blade root is positioned at the root of blade; Described blade is the obform body coincided by a specific rule by some characteristic cross-sections, and its effective height is H, root footpath is Dr; The profile molded line of described characteristic cross-section is the closed curve surrounded by inner arc curve and back of the body arc curve, has characteristic parameter established angle c1, chord length b1, maximum ga(u)ge w1, sectional area A; The rule that coincides in cross section is: along leaf height direction from butt to top, the continuous and derivable transition of each cross section; It is characterized in that, the relative value of leaf height H by 0.0 monotone increasing to 1.0; Correspond, established angle c1 is by 84.26
0dullness is reduced to 25.13
0; Area A Changing Pattern from root cross section to top section is: 3.606>=A>=1.0, axial width Xa Changing Pattern from root cross section to top section is: 2.581>=Xa>=1.0, chord length b1 Changing Pattern from root cross section to top section is: 1.133>=b1>=1.0, and the maximum ga(u)ge W1 Changing Pattern from root cross section to top section is: 2.964>=W1>=1.0.
2. the secondary final stage moving blade of feed pump turbine according to claim 1, is characterized in that, the effective height of described blade is H=358mm, root footpath is Dr=1146mm.
3. feed pump turbine according to claim 1 time final stage moving blade, is characterized in that, described shroud has back of the body arc working surface S1 and inner arc working surface P1, and back of the body arc working surface S1 and inner arc working surface P1 is the plane be parallel to each other; The sectional shape of shroud has characteristic parameter: the distance A1 between back of the body arc working surface S1 and inner arc working surface P1, the distance T1 between back of the body arc working surface S1 and inner arc working surface P1 geometrical center; The included angle B 1 of described back of the body arc working surface S1 and turbine rotor medial axis X meets relation:
A1=T1·COSB1； 35°≤B1≤52°；
Shroud thickness H1 meets relation:
7mm<H1<11mm。
4. feed pump turbine according to claim 3 time final stage moving blade, is characterized in that, described shroud end face tilts, and by leading edge to lagging edge axioversion, inclination angle theta 1 meets relation:
22°≤θ1≤28°。
5. feed pump turbine according to claim 1 time final stage moving blade, it is characterized in that, described blade root is that 4 tooth linear axis are to embedded type vertical tree type blade root.
6. feed pump turbine according to claim 5 time final stage moving blade, is characterized in that, the platform end face of described blade root tilts, and by leading edge to lagging edge axioversion, inclination angle theta 2 meets relation:
8°≤θ2≤12°。
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111963253A (en) * | 2020-09-03 | 2020-11-20 | 杭州汽轮机股份有限公司 | Penultimate-stage moving blade of steam turbine of full-capacity feed pump of power station |
| CN111963252A (en) * | 2020-09-03 | 2020-11-20 | 杭州汽轮机股份有限公司 | Secondary and final moving blade and blade assembly of variable-rotating-speed large-flow industrial steam turbine |
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| CN103362562A (en) * | 2013-07-30 | 2013-10-23 | 东方电气集团东方汽轮机有限公司 | Final moving blade of feed pump turbine |
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| CN104074554A (en) * | 2014-06-13 | 2014-10-01 | 东方电气集团东方汽轮机有限公司 | Indirect cold cooling last stage moving blade |
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| CN1730912A (en) * | 2005-07-31 | 2006-02-08 | 东方汽轮机厂 | Last stage rotor blade of steam turbine |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111963253A (en) * | 2020-09-03 | 2020-11-20 | 杭州汽轮机股份有限公司 | Penultimate-stage moving blade of steam turbine of full-capacity feed pump of power station |
| CN111963252A (en) * | 2020-09-03 | 2020-11-20 | 杭州汽轮机股份有限公司 | Secondary and final moving blade and blade assembly of variable-rotating-speed large-flow industrial steam turbine |
| CN111963253B (en) * | 2020-09-03 | 2022-12-16 | 杭州汽轮动力集团股份有限公司 | Penultimate-stage moving blade of steam turbine of full-capacity feed pump of power station |
| CN111963252B (en) * | 2020-09-03 | 2023-03-14 | 杭州汽轮动力集团股份有限公司 | Secondary and final moving blade and blade assembly of variable-rotating-speed large-flow industrial steam turbine |
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