CN101749052B - Last-stage moving blade of air-cooling feed pump turbine - Google Patents
Last-stage moving blade of air-cooling feed pump turbine Download PDFInfo
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- CN101749052B CN101749052B CN200910265025A CN200910265025A CN101749052B CN 101749052 B CN101749052 B CN 101749052B CN 200910265025 A CN200910265025 A CN 200910265025A CN 200910265025 A CN200910265025 A CN 200910265025A CN 101749052 B CN101749052 B CN 101749052B
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Abstract
Te invention discloses a last-stage moving blade of an air-cooling feed pump turbine. A blade body is of an irregular body formed by laminating a plurality of feature sections in a specific rule, the effective height H of the blade body is equal to 290.0mm, and the root diameter Dr thereof is 815mm; the blade body has a feature parameter installation angle c1, a chord length b1, an axial width Xa, a maximum width w1 and a sectional area A; the section laminating rule is that the sections are laminated along the direction of the blade height from the root end to the top end, each section transits continuously and smoothly, the relative value of the blade height H can be monotonically increased to 1.0 from 0.0, the installation angle c1 is monotonically reduced to 30.880 from 79.330, the chord length b1 is more than or equal to 1.0 and less than or equal to 1.63; the axial width Xa is more than or equal to 1.0 and less than or equal to 2.94; the maximum width w1 is more than or equal to 1.0 and less than or equal to 1.3, and the sectional area A is more than or equal to 1.0 and less than or equal to 3.03. The last-stage moving blade can be especially suitable for being used in a 660MW supercritical-unit air cooling turbine.
Description
Technical field:
The present invention relates to the moving vane of steam turbine, specifically is a kind of final stage moving blade of air-cooled feed pump steam turbine.It is particularly suitable for the supercritical unit air cooling turbine that power is 660MW.
Background technique:
Steam turbine can be as the driver of various loads as a kind of power plant.The running state of load is different, the constant-speed operation that has, the need speed governing that has; Therefore also just different to the performance requirement of steam turbine; For example, in the large-scale thermal power machine group, the feed water pump of its main steam turbine; Need to regulate confluent according to the operation conditions of main steam turbine, this feed water pump is driven by feed pump turbine.Obviously, the structural design of feed pump turbine is than permanent rotating speed steam turbine complicacy, particularly blade, and when running speed changed, suffered excitation force was different, and the dynamic stress of blade must satisfy the usage requirement in the speed adjustable range.
Air cooling turbine is a kind of special steam turbine, and particularity shows: it often is in the little volume flow operating mode operation of high back pressure, and the back pressure excursion is big, variation is frequent, and these operating conditionss have greatly limited the design of exhaust stage blade.At present, be used for the feed pump turbine on high-power overcritical, the ultra supercritical thermal power generation unit of air cooling, China still can not produce, and all is from external introduction, reason be China as yet not independent development go out the final stage moving blade of air-cooled feed pump steam turbine.
The operating conditions of air-cooled feed pump steam turbine is quite abominable, and particularly final stage moving blade not only will satisfy the requirement of the large-scale variable speed roadability of feed water pump, also will satisfy the performance characteristic requirement that air cooling turbine becomes back pressure on a large scale.All design has proposed harsh requirement to the final stage moving blade of feed water pump for these, so the design difficulty of final stage moving blade is very big, and technology content is very high, and the manufacturer that has the ability to develop voluntarily this type of final stage moving blade at present is few.
External feed pump turbine; Its specification is also limited, has only subcritical 300MW grade, subcritical 600MW grade and the supporting feed pump turbine of overcritical 600MW grade generator set at present, is the supporting feed pump turbine of more high-grade generator set; Still still blank, see table 1.
Existing feed pump turbine of table 1 and final stage moving blade contrast thereof
| Classification | Feed pump turbine one | Feed pump turbine two | Feed pump turbine three | Feed pump turbine four |
| Application area | Subcritical 300MW | Subcritical 600MW | Overcritical 600MW | Condensation 1000MW |
| The power of the assembling unit | 3390W | 8053W | 9600W | 14000W |
| Final blade length | 209.55mm | 304.8mm | 365mm | 411mm |
| Structural type | Band lacing wire, no integral shroud | Band lacing wire, no integral shroud | No integral shroud, lacing wire is arranged | Integral shroud, rib-free are arranged |
| Leaving area | 0.6563×10 6mm 2 | 1.046×10 6mm 2 | 1.353×10 6mm 2 | 1.702×10 6mm 2 |
| Achievement puts into operation | Have | Have | Have | Have |
In addition, existing subcritical 300MW grade, subcritical 600MW grade and the supporting feed pump turbine of overcritical 600MW grade generator set, the characteristic parameter of its final stage moving blade has nothing in common with each other; There is not unified design code; Structure is more backward, and the dynamic stress of blade is high, and unit economy is relatively poor.
Summary of the invention:
The present invention provides a kind of final stage moving blade of air-cooled feed pump steam turbine; Its structural element is different from existing product; The leading indicator of its technical performance meets or exceeds existing like product; The whole synthesis performance is superior to existing like product, and it is particularly suitable for 660MW supercritical unit air cooling turbine.
The present invention adopts such technological scheme to realize:
A kind of final stage moving blade of air-cooled feed pump steam turbine; Blade, blade root and integral shroud with unitary construction; Said blade is the variable cross section distorted-structure; The width of blade, thickness and cross-section area are successively decreased to the top by root, the continuously smooth transition, and said blade is the obform body that is coincided and form by a specific rule by the certain characteristics cross section; The profile molded lines of said characteristic cross-section is by inner arc curve and the closed curve that back of the body arc curve surrounds, and has characteristic parameter: established angle c1, chord length b1, axial width Xa, maximum ga(u)ge w1, sectional area A; The rule that coincides in cross section be along the high direction of leaf from butt to the top, the continuous smooth transition in each cross section; Said blade effective height is that H=290.0mm, root directly are Dr=815mm; The relative value of the high H of leaf is added to 1.0 by 0.0 monotone increasing; Corresponding with it, the absolute value c1 of established angle is reduced to 30.880 by 79.330 dullnesses; The relative value Changing Pattern of chord length b1 from the root cross section to the top section is: 1.63 >=b1 >=1.0; The relative value Changing Pattern of axial width Xa from the root cross section to the top section is: 2.94 >=Xa >=1.0; The relative value Changing Pattern of maximum ga(u)ge w1 from the root cross section to the top section is: 1.3 >=w1 >=1.0; The relative value Changing Pattern of the area A from the root cross section to the top section is: 3.03 >=A >=1.0.
The correlated variables definition:
The effective height of H-blade, the i.e. length of the blade of blade part: the distance between blade top section and the blade root cross section.
Dr-root footpath: blade installation is behind rotor, and blade root cross section belongs to diameter of a circle.
The b1-chord length: the blade cross section is into and out of the distance on vapour limit.
C1-blade angle: chord length b1 and Y to angle.
Xa-axial width: blade root cross section axial width.
W1-maximum ga(u)ge: blade cross section tangential width.
Said integral shroud has the back of the body arc resistance Buddhist nun working surface A1 and the inner arc damping working surface B1 of irregular how much shapes; A1, B1 are parallel to each other in the geometric surface of identical change rule scope; The integral shroud inner arc damping working surface B1 of adjacent blades and back of the body arc resistance Buddhist nun working surface A1 fit each other, and the gap is 0.
Said blade root is a fir-tree root.
Said blade root is four tooth lineal shape fir-tree roots.
Said blade is processed with stainless steel.
The invention has the beneficial effects as follows:
Adopt the blade of said structure to have good dynamic characteristics, dynamic stress is little, and damping characteristic is good.With this moving vane (290mm) make air-cooled feed pump steam turbine the time; Its design power is 12750W, and speed adjustable range is between 40.8Hz～110Hz, and back pressure excursion allowable is 7kPa～65kPa; These technical features meet usage requirement fully, and the market prospects of this moving vane are wide.
Description of drawings:
Fig. 1 is a kind of structural representation of the present invention;
Fig. 2 is the blade schematic cross-section of Fig. 1;
Fig. 3 is the leaf and root structure schematic representation of Fig. 1;
Fig. 4 is the integral shroud plan structure schematic representation of Fig. 1.
Embodiment:
Referring to Fig. 1-Fig. 4: design vector of the present invention is selected the postcritical air cooling turbine of 660MW, and the design power of this steam turbine is 12700W, and speed adjustable range is between 40.8Hz～110Hz; Back pressure excursion allowable is 7kPa～65kPa; With this characteristic, the final stage moving blade air flue height that final design proposal is confirmed (being the effective height of blade, also is the length of the blade part of blade) H is 290.0mm; The root footpath (is that blade installation is behind rotor; Place, its blade root cross section diameter of a circle also is the diameter of rotor wheel rim) Dr is 815mm, its annulus area equals 1m
2This air cooling turbine one has 7 grades; With this root footpath and leaf height is that reference design has been accomplished the through-flow of air cooling turbine; The design is a design object with the whole cylinder low pressure flow passage of level steam turbines such as 660MW; Given low pressure inlet pressure, enthalpy, flow and back pressure under the prerequisite that guarantees the fairing of low pressure meridional channel, are optimized degree of reaction coupling in enthalpy drop at different levels, speed ratio and the level.
On the basis of the whole through-flow optimization of matching of cylinder, the design of controllable swirl type is the repeatedly cyclic design process of a complicacy in the final stage level.At first design basic quiet, movable vane fundamental mode molded lines; Press distributing of controllable swirl type design along the high efflux angles of leaf; Design space shaping rule quiet, movable vane; Come the optimization level flow field with full three-dimensional flow field computational analysis again, the step of going forward side by side is whole quiet, the space shaping rule of movable vane, is design object with pneumatic optimum.
Adopt the suitable stainless steel of performance, manufacture and design moving vane blade 1, blade root 2 and the integral shroud 3 with unitary construction by of the present invention, each several part is to use to make completion with a kind of high-intensity performance stainless steel integratedly.Blade pass is crossed blade root 2 and is installed in the impeller groove on the rotating shaft cylindrical, and every circle race is installed 64 blades, after all loading onto blade in the impeller groove in a week on the impeller, has just formed the final stage of feed pump turbine.
The blade of this moving vane is the variable cross section distorted-structure; The width of blade, thickness and cross-section area are successively decreased to the top by root; The continuously smooth transition; Blade is the obform body that is coincided and form by a specific rule by the certain characteristics cross section, and its effective height (being the blade height) is that H, root directly are Dr (be blade installation behind rotor, the root diameter at its blade root place); The profile molded lines of characteristic cross-section is by inner arc curve and the closed curve that back of the body arc curve surrounds, and has characteristic parameter: established angle c1, chord length b1, axial width Xa, maximum ga(u)ge w1, sectional area A.
The design's correlated variables definition:
The effective height of H-blade, the i.e. length of the blade of blade part: the distance between blade top section and the blade root cross section.
Dr-root footpath: blade installation is behind rotor, and blade root cross section belongs to diameter of a circle.
The b1-chord length: the blade cross section is into and out of the distance on vapour limit.
C1-blade angle: the chord length b1 and the circumferential angle of (Y to).
Xa-axial width: blade root cross section axial width.
W1-maximum ga(u)ge: blade cross section tangential width.
(1) blade profile design is along the pneumatic design in the high several features blade of leaf cross section
Adopt special-purpose through-flow designing program to design basic blade profile key element and the mounting point of this exhaust stage blade along high each cross section of leaf, along the characteristic of high each the basic blade profile of leaf be: the root of aerodynamic characteristics is that subsonic speed blade profile, middle part are that transonic speed blade profile, top are the supersonic speed blade profile.The rule that coincides in cross section is; The dynamic center of gravity in each cross section overlaps and is the center twisting formation with center of gravity line (being radial ray), along the high direction of leaf from butt to the top, the continuous smooth transition in each cross section; The cross-sectional area A edge of basic blade profile highly dullness reduces; Be turriform and change, and the relative value of the high H of leaf (ratio of a certain depth of section of blade and the high value of total leaf, this blade height is 290mm; If current blade profile height is 87mm, then the relative value of this depth of section is 87/290=0.3 at this moment) be added to 1.0 by 0.0 monotone increasing; Corresponding with it, the absolute value of established angle c1 is reduced to 30.88 ° by 79.33 ° of dullnesses; The relative value of chord length b1 from the root cross section to the top section (top section is 1.0) Changing Pattern is: 1.63 >=b1 >=1.0; The relative value of axial width Xa from the root cross section to the top section (top section is 1.0) Changing Pattern is: 2.94 >=Xa >=1.0; The relative value of maximum ga(u)ge w1 from the root cross section to the top section (top section is 1.0) Changing Pattern is: 1.3 >=w1 >=1.0; The relative value of the area A from the root cross section to the top section (top section is 1.0) Changing Pattern is: 3.03 >=A >=1.0.Adopt complete three-dimensional aerodynamic analysis process analysis and optimal design each blade profile cross section along the high shaping rule of leaf, guarantee the smooth connection of profile between each typical section simultaneously, finally realize the optimization of this leaf-level flow field characteristic.
(2) linkage structure of large deformation damping vane design
Because in working order down, there is bigger torsional deflection in the cross section that the blade middle and upper part is divided during with respect to state of rest, the linkage structure of blade that adopted structural finite element analysis method optimal design.Designed shroud (integral shroud) structure of having a style of one's own with blade; This integral shroud has the back of the body arc resistance Buddhist nun working surface A1 and the inner arc damping working surface B1 of irregular how much shapes; A1, B1 are parallel to each other in the geometric surface of identical change rule scope, and integral shroud thickness is H1 (8mm＜H1＜12mm).Because the special construction of integral shroud, when static, the integral shroud inner arc damping working surface B1 of adjacent blades and back of the body arc resistance Buddhist nun working surface A1 fit each other, and the gap is 0.
Carry shroud structure and stoped the horizontal channelling and the radial flow on leaf top aspect pneumatic; When rotating speed is increased to a certain degree; Produce bigger pressure stress between the adjacent blades shroud working surface, blade rigid is increased, make the free vane under the static state when rated speed, limit the twist recovery on leaf top fully; Form whole circle restraining structure, reduce the blade dynamic stress significantly.
(3) blade root design
The blade root of this moving vane is four tooth lineal shape fir-tree roots, and this structure makes combining that blade and rotor can be firm, stable, and is convenient to and the rotor assembling, and is easy and simple to handle, quick.
Claims (5)
1. the final stage moving blade of an air-cooled feed pump steam turbine; Blade, blade root and integral shroud with unitary construction; Said blade is the variable cross section distorted-structure; The width of blade, thickness and cross-section area are successively decreased to the top by root, the continuously smooth transition, and said blade is the obform body that is coincided and form by a specific rule by the certain characteristics cross section; The profile molded lines of said characteristic cross-section is by inner arc curve and the closed curve that back of the body arc curve surrounds, and has characteristic parameter: established angle (c1), chord length (b1), axial width (Xa), maximum ga(u)ge (w1), sectional area (A); The rule that coincides in cross section be along the high direction of leaf from butt to the top, the continuous smooth transition in each cross section; It is characterized in that:
Said blade effective height (H)=290.0mm, root footpath (Dr)=815mm; The relative value of leaf high (H) is added to 1.0 by 0.0 monotone increasing; Corresponding with it, the absolute value of established angle (c1) is reduced to 30.880 by 79.330 dullnesses; The relative value Changing Pattern of the chord length from the root cross section to the top section (b1) is to be reduced to 1.0 by 1.63 dullnesses; The relative value Changing Pattern of the axial width from the root cross section to the top section (Xa) is to be reduced to 1.0 by 2.94 dullnesses; The relative value Changing Pattern of the maximum ga(u)ge from the root cross section to the top section (w1) is to be reduced to 1.0 by 1.3 dullnesses; The relative value Changing Pattern of the sectional area from the root cross section to the top section (A) is to be reduced to 1.0 by 3.03 dullnesses.
2. the final stage moving blade of air-cooled feed pump steam turbine according to claim 1; It is characterized in that: said integral shroud has the back of the body arc resistance Buddhist nun working surface (A1) and the inner arc damping working surface (B1) of irregular how much shapes; Back of the body arc resistance Buddhist nun's working surface (A1), inner arc damping working surface (B1) are parallel to each other in the geometric surface of identical change rule scope; The integral shroud inner arc damping working surface (B1) of adjacent blades and back of the body arc resistance Buddhist nun's working surface (A1) are fitted each other, and the gap is 0.
3. the final stage moving blade of air-cooled feed pump steam turbine according to claim 1, it is characterized in that: said blade root is a fir-tree root.
4. the final stage moving blade of air-cooled feed pump steam turbine according to claim 3, it is characterized in that: said blade root is four tooth lineal shape fir-tree roots.
5. the final stage moving blade of air-cooled feed pump steam turbine according to claim 1, it is characterized in that: said blade is processed with stainless steel.
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| Application Number | Priority Date | Filing Date | Title |
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| CN200910265025A CN101749052B (en) | 2009-12-28 | 2009-12-28 | Last-stage moving blade of air-cooling feed pump turbine |
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| CN200910265025A CN101749052B (en) | 2009-12-28 | 2009-12-28 | Last-stage moving blade of air-cooling feed pump turbine |
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| CN101749052B true CN101749052B (en) | 2012-10-10 |
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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102140932B (en) * | 2011-04-29 | 2015-04-22 | 东方电气集团东方汽轮机有限公司 | Last-stage moving blade for wet cooling gas turbine |
| CN105298546B (en) * | 2015-11-27 | 2017-07-28 | 东方电气集团东方汽轮机有限公司 | A kind of turbine blade blade structure |
| CN106050320B (en) * | 2016-07-13 | 2018-05-22 | 东方电气集团东方汽轮机有限公司 | The final stage moving blade of the feed pump turbine of 1000MW grade air-cooled steam turbine generator groups |
| EP3511522A1 (en) | 2018-01-11 | 2019-07-17 | Siemens Aktiengesellschaft | Gas turbine blade and method for producing such blade |
| 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 |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2711391Y (en) * | 2004-06-09 | 2005-07-20 | 哈尔滨汽轮机厂有限责任公司 | Final stage blade for large air cooling turbine |
| CN2883679Y (en) * | 2006-03-15 | 2007-03-28 | 哈尔滨汽轮机厂有限责任公司 | Final blade of large-scale air cooling turbine |
| CN201103419Y (en) * | 2007-12-03 | 2008-08-20 | 哈尔滨汽轮机厂有限责任公司 | Second last blade of macrotype supercritical air cooling turbine |
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2711391Y (en) * | 2004-06-09 | 2005-07-20 | 哈尔滨汽轮机厂有限责任公司 | Final stage blade for large air cooling turbine |
| CN2883679Y (en) * | 2006-03-15 | 2007-03-28 | 哈尔滨汽轮机厂有限责任公司 | Final blade of large-scale air cooling turbine |
| CN201103419Y (en) * | 2007-12-03 | 2008-08-20 | 哈尔滨汽轮机厂有限责任公司 | Second last blade of macrotype supercritical air cooling turbine |
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