CN103362562B - Final moving blade of feed pump turbine - Google Patents
Final moving blade of feed pump turbine Download PDFInfo
- Publication number
- CN103362562B CN103362562B CN201310324536.4A CN201310324536A CN103362562B CN 103362562 B CN103362562 B CN 103362562B CN 201310324536 A CN201310324536 A CN 201310324536A CN 103362562 B CN103362562 B CN 103362562B
- Authority
- CN
- China
- Prior art keywords
- blade
- working surface
- section
- root
- arc working
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
The invention relates to a final moving blade of a feed pump turbine, which is characterized in the effective height of the blade is 630mm, and the relative value of the blade height H is monotonically increased to 1.0 from 0.0; correspondingly, a mounting angle c1 is monotonically reduced to 16.550 from 83.030; the change rule of the area A from a root section to a top section is: 8.935 is more than or equal to A is more than or equal to 1.0; the change rule of the axial width Xa from the root section to the top section is: 5.602 is more than or equal to Xa is more than or equal to 1.0; the change rule of the chord length b1 from the root section to the top section is: 1.63 is more than or equal to b1 is more than or equal to 1.0; and the change rule of the maximum thickness of W1 from the root section to the top section is: 4.227 is more than or equal to W1 is more than or equal to 1.0. The final stage blade of the feed pump turbine is suitable for the 100% capacity feed pump turbine with the power of 22-42MW, unidirectional exhaust (with one exhaust port), the rotary speed of 2600-5500 rpm, and the ultra-supercritical power of 1000MW grade.
Description
Technical field
the present invention relates to the final stage moving blade of feed pump turbine, be applicable to power 22MW ~ 42MW, 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 final stage moving blade is very long, and these operating conditionss significantly limit the design of final stage moving blade.And the Economy of feed pump turbine and Security to a great extent with the heating power of its final stage, pneumatic, intensity, VIBRATION DESIGN are closely related, wherein especially maximum with 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 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 the turbine speed of feed water pump is high, final stage moving blade steam passage height is very high, final stage moving blade centrifugal force is large, stress level superelevation, vibration are complicated, run in transonic speed, design difficulty is very large; The design of this final stage moving blade adopts straight-tooth fir-tree root, carries damping boss tie pieces, carries damping shroud, loop-forming structure runs.
100% capacity feed pump turbine field needed for ultra supercritical 1,000,000 unit, what the domestic and international producer such as Siemens adopted is two steam exhaust structures (2 steam-expelling ports), final stage moving blade is shorter, its efficiency can be influenced, we exploitation this feed pump turbine final stage moving blade, employing be single steam exhaust structure (1 steam-expelling port), final stage moving blade is very long, its efficiency is very high, is the domestic and international the longest final stage moving blade developed in this field at present.
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 22MW ~ 42MW, unidirectional steam discharge, 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 final stage moving blade, have integrally-built blade root, blade, shroud and boss tie pieces, described shroud is positioned at the top of blade, and boss tie pieces is positioned at the waist 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 reduced to 16.55 ° by 83.03 ° of dullnesses; Area A Changing Pattern from root cross section to top section is: 8.935 >=A >=1.0, axial width Xa Changing Pattern from root cross section to top section is: 5.602 >=Xa >=1.0, chord length b1 Changing Pattern from root cross section to top section is: 1.63 >=b1 >=1.0, and the maximum ga(u)ge W1 Changing Pattern from root cross section to top section is: 4.227 >=W1 >=1.0.
The effective height of described blade is H=630mm, root footpath is Dr=1200mm.
Described boss tie pieces has back of the body arc working surface S2 and inner arc working surface P2, and back of the body arc working surface S2 and inner arc working surface P2 is the plane be parallel to each other; The sectional shape of boss tie pieces has characteristic parameter: the distance A2 between back of the body arc working surface S2 and inner arc working surface P2, the distance T2 between back of the body arc working surface S2 and inner arc working surface P2 geometrical center; The included angle B 2 of described back of the body arc working surface S2 and turbine rotor medial axis X-axis meets relation:
A2=T2·COSB2； 40°≤B2≤50°；
The maximum ga(u)ge B in boss tie pieces cross section meets relation:
8mm≤B≤16mm。
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:
8mm<H1<16mm。
Described blade root is that 4 tooth linear axis are to embedded type vertical tree type blade root.
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 exhaust stage blade.630mm final stage moving blade newly developed has more advanced structural type--and damped type carries shroud, damped type carries overall lacing wire, 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 lacing wire structural representation;
Fig. 3 is the A direction view of Fig. 2;
Fig. 4 is shroud structure schematic diagram;
Fig. 5 is blade schematic cross-section.
Embodiment
see Fig. 1: adopt suitable alloyed steel blade and rotor material, be made up of 4 parts by the moving vane of this patent plan manufacture, respectively: shroud body 1, damping boss tie pieces 2, blade 3, blade root 4.Shroud body 1 is positioned at the top of blade 3, and boss tie pieces 2 is positioned at the waist of blade 3, and above-mentioned blade 3, blade root 4, shroud 1, boss tie pieces 2 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 4, often enclose race and install 84 blades, after all loading onto blade in the impeller groove of a week on impeller, just define the final stage moving blade of high-power feed pump turbine.Blade root 4 is that 4 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 of 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, effective height (the i.e. final stage moving blade steam passage height) H of the blade that final scheme is determined is 630mm, root footpath Dr is 1200 mm, and its annulus area equals 3.622 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 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 3 of feed pump turbine final stage moving blade of the present invention 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. 5, there is following characteristics parameter (i.e. the variable-definition of the design):
The effective height of H-blade is the distance between blade 3 top section and blade 3 cross sections, i.e. the steam passage height of feed pump turbine final stage moving blade.
The root footpath of Dr-blade root.
H1-shroud body 1 thickness.
Lj-damping boss tie pieces 2 position height: the perpendicular distance at blade 3 cross sections and damping boss tie pieces 2 center.
The thickness of B-damping boss tie pieces 2.
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 3 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 3 cross section axial widths.
O1-blade 3 cross-sectional exit throat openings: the minimum range of arc is carried on the back in Exit-edge and adjacent blade 3 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).
T2-pitch: adjacent two blade sustained height lacing wire cross sections are at the mounting distance of circumference.
T-pitch: adjacent two blade sustained height molded line cross sections are at the mounting distance of circumference.
W-blade root 4 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.
(1) blade design, along the pneumatic design in leaf several feature blade 3 cross sections high
See Fig. 1, Fig. 5: adopt this exhaust 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 reduced to 16.55 ° by 83.03 ° of dullnesses; Area A Changing Pattern from root cross section to top section is: 8.935 >=A >=1.0, and namely root cross section is decreased to 1.0 to the area A of top section by 8.935 dullnesses; Axial width Xa Changing Pattern from root cross section to top section is: 5.602 >=Xa >=1.0, and namely root cross section is decreased to 1.0 to the axial width Xa of top section by 5.602 dullnesses; Chord length b1 Changing Pattern from root cross section to top section is: 1.63 >=b1 >=1.0, and namely root cross section is decreased to 1.0 to the chord length b1 of top section by 1.63 dullnesses; Maximum ga(u)ge W1 Changing Pattern from root cross section to top section is: 4.227 >=W1 >=1.0, and namely root cross section is decreased to 1.0 to the maximum ga(u)ge W1 of top section by 4.227 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.
Several typical section molded line of blade 3 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 semi-finals degree 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 exhaust 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 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 3 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
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 3 structure that can meet aerodynamic characteristic and strength vibration characteristic requirements.The strength characteristics of blade 3 structure is: blade 3 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.
(4) 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: the position devised highly for Lj on blade 3 arranges boss tie pieces structure (wherein 0.45< Lj/H <0.65), and this boss thickness B meets 8mm<B<16mm(see Fig. 3).The function of this lacing wire structure is that working surface contact forms suitable pressure stress when rated speed, increases the damping of blade, significantly reduces blade dynamic stress, improve blade rigid simultaneously.Devise the shroud structure (see Fig. 4) had a style of one's own with blade 3, its thickness is H1(8mm<H1<16mm), 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=T1*COSB1, 200≤B1≤450, blade rigid is increased when blade working, the free vane under static state is made to 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≤2400 rev/min.Working surface pressure stress meets relation: the ultimate strength of 0.0126<F1≤0.055 times material.
Claims (5)
1. a feed pump turbine final stage moving blade, has integrally-built blade root, blade, shroud and boss tie pieces, and described shroud is positioned at the top of blade, and boss tie pieces is positioned at the waist 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 reduced to 16.55 ° by 83.03 ° of dullnesses; Area A Changing Pattern from root cross section to top section is: 8.935 >=A >=1.0, axial width Xa Changing Pattern from root cross section to top section is: 5.602 >=Xa >=1.0, chord length b1 Changing Pattern from root cross section to top section is: 1.63 >=b1 >=1.0, and the maximum ga(u)ge W1 Changing Pattern from root cross section to top section is: 4.227 >=W1 >=1.0.
2. the final stage moving blade of feed pump turbine according to claim 1, is characterized in that, the effective height of described blade is H=630mm, root footpath is Dr=1200mm.
3. the final stage moving blade of feed pump turbine according to claim 1, is characterized in that, described boss tie pieces has back of the body arc working surface S2 and inner arc working surface P2, and back of the body arc working surface S2 and inner arc working surface P2 is the plane be parallel to each other; The sectional shape of boss tie pieces has characteristic parameter: the distance A2 between back of the body arc working surface S2 and inner arc working surface P2, the distance T2 between back of the body arc working surface S2 and inner arc working surface P2 geometrical center; The included angle B 2 of described back of the body arc working surface S2 and turbine rotor medial axis X-axis meets relation:
A2=T2·COSB2； 40°≤B2≤50°；
The maximum ga(u)ge B in boss tie pieces cross section meets relation:
8mm≤B≤16mm。
4. feed pump turbine final stage moving blade according to claim 1, 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-axis meets relation:
A1=T1·COSB1； 35°≤B1≤52°；
Shroud thickness H1 meets relation:
8mm<H1<16mm。
5. feed pump turbine final stage moving blade according to claim 1, is characterized in that, described blade root is that 4 tooth linear axis are to embedded type vertical tree type blade root.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310324536.4A CN103362562B (en) | 2013-07-30 | 2013-07-30 | Final moving blade of feed pump turbine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310324536.4A CN103362562B (en) | 2013-07-30 | 2013-07-30 | Final moving blade of feed pump turbine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103362562A CN103362562A (en) | 2013-10-23 |
| CN103362562B true CN103362562B (en) | 2015-02-18 |
Family
ID=49364737
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310324536.4A Active CN103362562B (en) | 2013-07-30 | 2013-07-30 | Final moving blade of feed pump turbine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103362562B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104074554B (en) * | 2014-06-13 | 2016-01-13 | 东方电气集团东方汽轮机有限公司 | Indirect air cooling final stage moving blade |
| CN104775853B (en) * | 2015-04-16 | 2017-02-22 | 东方电气集团东方汽轮机有限公司 | Penultimate-stage moving blade for feed pump turbines |
| CN111852576B (en) * | 2020-06-23 | 2022-07-12 | 北京国能龙威发电技术有限公司 | Last-stage moving blade for water supply pump steam turbine |
| CN113221482B (en) * | 2021-05-26 | 2023-12-29 | 杭州汽轮控股有限公司 | Design method for combination of turbine final stage blade and exhaust cylinder |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01270301A (en) * | 1988-04-22 | 1989-10-27 | Koa Corp | Small-sized thermosensitive resistor and manufacture thereof |
| US5160242A (en) * | 1991-05-31 | 1992-11-03 | Westinghouse Electric Corp. | Freestanding mixed tuned steam turbine blade |
| JP4316168B2 (en) * | 2001-08-30 | 2009-08-19 | 株式会社東芝 | Method for selecting blade material and shape of steam turbine blade and steam turbine |
| CN2739360Y (en) * | 2004-09-29 | 2005-11-09 | 哈尔滨汽轮机厂有限责任公司 | Steam turbine end-stage moving vane |
| JP4713509B2 (en) * | 2007-01-26 | 2011-06-29 | 株式会社日立製作所 | Turbine blade |
| CN201606119U (en) * | 2009-11-25 | 2010-10-13 | 北京全四维动力科技有限公司 | Large steam turbine last-stage blade |
| CN102359397B (en) * | 2011-09-26 | 2014-02-26 | 哈尔滨汽轮机厂有限责任公司 | 1300mm moving blade of final stage for full-rotary-speed steam turbine |
| CN102926821A (en) * | 2012-11-07 | 2013-02-13 | 哈尔滨汽轮机厂有限责任公司 | 900mm last stage moving blade for combined cycle steam turbine |
-
2013
- 2013-07-30 CN CN201310324536.4A patent/CN103362562B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN103362562A (en) | 2013-10-23 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101349168B (en) | Last stage movable vane of air cooling steam turbine | |
| Zhu et al. | Optimization design of a reversible pump–turbine runner with high efficiency and stability | |
| CN100339559C (en) | Last stage rotor blade of steam turbine | |
| CN103362562B (en) | Final moving blade of feed pump turbine | |
| CN102108882A (en) | Last stage blade for half speed nuclear power steam turbine | |
| CN106194821A (en) | Centrifugal hydraulic turbine impeller and design method thereof | |
| CN101793167A (en) | Last-stage moving blade of air-cooled steam turbine | |
| CN101725373B (en) | Last-stage moving blade of air-cooled steam turbine | |
| CN102108881B (en) | Secondary final stage blade for half-RPM (Revolution per Minute) nuclear turbine | |
| CN101737091B (en) | Last-stage moving blade of air-cooled feed pump steam turbine | |
| CN101725374B (en) | Penult-stage moving blade of air-cooled steam turbine | |
| CN105422187A (en) | Water supply system of 660 MW-grade steam turbine and water pump steam turbine final-stage moving blade thereof | |
| CN104775853B (en) | Penultimate-stage moving blade for feed pump turbines | |
| CN101749052B (en) | Last-stage moving blade of air-cooling feed pump turbine | |
| JP2013015018A (en) | Turbine stator vane designing method, turbine stator vane, and steam turbine device using turbine stator vane | |
| CN102140934B (en) | Last-stage moving blade for 60 Hz wet cooling gas turbine | |
| CN106050320B (en) | The final stage moving blade of the feed pump turbine of 1000MW grade air-cooled steam turbine generator groups | |
| CN104074554B (en) | Indirect air cooling final stage moving blade | |
| Semenova et al. | Optimization design of the elbow draft tube of the hydraulic turbine | |
| CN102140932B (en) | Last-stage moving blade for wet cooling gas turbine | |
| Kim et al. | Non-axisymmetric endwall profile optimization of a high-pressure transonic turbine using approximation model | |
| CN102140935B (en) | Penult-stage moving blade for 60 Hz wet cooling gas turbine | |
| CN102140933B (en) | Final-stage moving blade of wet cooling steam turbine | |
| CN105484806A (en) | Last-stage moving blade of 3600 RPM wet-cooling steam turbine | |
| CN108194149A (en) | A kind of industrial steam turbine high efficiency drum grade movable vane piece |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |