CN101737091B - Last-stage moving blade of air-cooled feed pump steam turbine - Google Patents
Last-stage moving blade of air-cooled feed pump steam turbine Download PDFInfo
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- CN101737091B CN101737091B CN2009102650234A CN200910265023A CN101737091B CN 101737091 B CN101737091 B CN 101737091B CN 2009102650234 A CN2009102650234 A CN 2009102650234A CN 200910265023 A CN200910265023 A CN 200910265023A CN 101737091 B CN101737091 B CN 101737091B
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- 229910001220 stainless steel Inorganic materials 0.000 claims description 4
- 239000010935 stainless steel Substances 0.000 claims description 4
- 238000001816 cooling Methods 0.000 description 8
- 238000005457 optimization Methods 0.000 description 4
- 238000004458 analytical method Methods 0.000 description 3
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- 239000000463 material Substances 0.000 description 2
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Abstract
The invention discloses a last-stage moving blade of an air-cooled feed pump steam turbine, comprising a blade body, wherein the blade body is an abnormal-shaped body formed by overlapping a plurality of characteristic sections according to a specific rule, the effective height of the blade body is H=365.0mm, and the root diameter of the blade body is Dr=906.8mm. The last-stage moving blade comprises the following characteristic parameters: an established angle c1, a chord length b1, a maximum thickness w1, an axial width Xa and a sectional area A. The overlapping rule of the sections is that the sections are in continuous and smooth transition along a blade height direction from a root end to a top end. The relative value of the blade height H is monotonically increased from 0.0 to 1.0; the established angle c1 is monotonically decreased from 81.830 to 13.670. The changing rule of the chord length b1 is no more than 1.61 and no less than 1.0; the changing rule of the maximum thickness w1 is no more than 2.265 and no less than 1.0; the changing rule of the axial width Xa no more than 3.75 and no less 1.0; and the changing rule of the sectional area A is no more than 4.58 and no less than 1.0. The invention has good dynamic property, small dynamic stress and good damping characteristic and is especially suitable for a 1000MW supercritical unit air-cooled steam 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 air cooling turbine of power 1000MW ultra supercritical unit.
Background technique:
Steam turbine is one of thermal power plant three big main force equipment; The moving vane that is installed on the rotating shaft of steam turbine is a vital critical component in the steam turbine; The structural design of final stage moving blade particularly is because of its core technology that becomes steam turbine technological wide, with high content of technology that relates to.The capacity of steam turbine is bigger, generating density is high more, requires its initial conditions high more, and exhaust annulus area is big more; The exhaust stage blade that needs is just long more, and exhaust stage blade is long more, and is just high more to the blade material requirement of strength; Pneumatic and the VIBRATION DESIGN of blade is just more difficult, and therefore, the exploitation of steam turbine final blade becomes in the world the emphasis of each big steam turbine MANUFACTURER concern; Also be its difficult point that manufactures and designs, its level has been represented developer's comprehensive strength.
Steam turbine is as a kind of power plant; As the driver of various loads,, also just different to the performance requirement of steam turbine because the constant speed of load or speed governing operation state are different; Blade particularly; 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.And the Economy of air cooling turbine and Security are closely related with the heating power of low-pressure final stage, pneumatic, intensity, VIBRATION DESIGN to a great extent; Wherein maximum with the low-pressure final stage design difficulty especially; Must make overall plans; Carry out the scheme optimization under numerous and diverse multifactor constraint conditio, just can design high performance exhaust stage blade.At present, be used for the feed pump turbine on the air cooling 1000MW ultra supercritical thermal power generation unit, 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 rational in infrastructure, last-stage moving blade of air-cooled feed pump steam turbine that dynamic stress is low; 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 1000MW supercritical unit air cooling turbine.
The present invention adopts such technological scheme to realize:
A kind of last-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, seamlessly transit, 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, maximum ga(u)ge w1, axial width Xa, sectional area A; The rule that coincides in cross section is, 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=365.0mm, root directly are Dr=906.8mm; 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 13.670 by 81.830 dullnesses; The relative value Changing Pattern of chord length b1 from the root cross section to the top section is: 1.61 >=b1 >=1.0; The relative value Changing Pattern of maximum ga(u)ge w1 from the root cross section to the top section is: 2.265 >=w1 >=1.0; The relative value Changing Pattern of axial width Xa from the root cross section to the top section is: 3.75 >=Xa >=1.0; The relative value Changing Pattern of the area A from the root cross section to the top section is: 4.58 >=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 back of the body arc resistance Buddhist nun working surface A1 and inner arc damping working surface B1, and A1, B1 are the planes that is parallel to each other; The integral shroud inner arc damping working surface B1 of adjacent blades and back of the body arc resistance Buddhist nun working surface A1 coincide each other; The shape of integral shroud has characteristic parameter: the identical gap S of adjacent blades; The integral shroud top pitch P of adjacent blades, gap between said adjacent blades and integral shroud top pitch satisfy following formula:
350≤P/S。
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 moving vane of said structure to have good dynamic characteristics, dynamic stress is little, and damping characteristic is good.With this moving vane (365mm) make air-cooled feed pump steam turbine the time, its design power is 16000W, speed adjustable range is between 40.8Hz～110Hz, back pressure excursion allowable is 7kPa～65kPa, meets usage requirement fully.Has wide market application prospect.
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: the present invention adopts stainless steel material, is designed and manufactured into blade 1, blade root 2 and the integral shroud 3 with unitary construction by this patent, and blade 1, blade root 2 and integral shroud 3 three parts are to use with a kind of high-intensity performance to make completion stainless steel integratedly.Wherein, blade 1 blade is the variable cross section distorted-structure, and the width of blade, thickness and cross-section area are successively decreased to the top by root, seamlessly transit.This moving vane is installed in the impeller groove on the rotating shaft cylindrical through blade root 2, and every circle race is installed 70 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 design vector of this moving vane is selected the steam turbine of ultra supercritical air cooling 1000MW grade; The design power of this steam turbine is 16000W, and speed adjustable range is between 40.8Hz～110Hz, and back pressure excursion allowable is 7kPa～65kPa; In this design back pressure ranges; The final stage moving blade air flue height that final scheme is confirmed is 365.0mm, root footpath Dr (906.8mm), and its annulus area equals 1.46m
2This feed pump turbine one has 6 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 1000MW; 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.
This moving vane blade is the obform body that is coincided and form by a specific rule by the certain characteristics cross section; Its effective height (being the blade partial-length of blade) H is that 365.0mm, root footpath (are that blade installation is behind rotor; Its place, blade root cross section diameter of a circle also is the diameter of rotor wheel rim) Dr=906.8mm; 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, maximum ga(u)ge w1, axial width Xa, 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.
The identical gap of S-adjacent blades.
The integral shroud top pitch of the adjacent blade of P-.
(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: aerodynamic characteristics is that root is that subsonic speed blade profile, middle part are that transonic speed blade profile, top are the supersonic speed blade profile.The cross-section area edge of basic blade profile highly dullness reduces; Being turriform changes; The relative value of the high H of the leaf (ratio of the high value of a certain depth of section of blade and total leaf; This blade height is 365mm, if current blade profile height is 146mm, then the relative value of this depth of section is 146/365=0.4 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 13.670 by 81.830 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: 1.61 >=b1 >=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: 2.265 >=w1 >=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: 3.75 >=Xa >=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: 4.58 >=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 inner arc damping working surface B1, and A1, B1 are the planes that is parallel to each other, and integral shroud thickness is H1 (10mm＜H1＜15mm); 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 coincide each other, and the shape of integral shroud has characteristic parameter: the identical gap S of adjacent blades; The integral shroud top pitch P of adjacent blades, gap between adjacent blades and integral shroud top pitch satisfy relation: 350≤P/S.
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, come in contact between the adjacent blades shroud working surface, produce bigger pressure stress; When blade working, increase blade rigid; Make the free vane under the static state when rated speed, limit the twist recovery on leaf top significantly, 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. last-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, seamlessly transit, and said blade is the obform body that is coincided and formed 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), maximum ga(u)ge (w1), axial width (Xa), sectional area (A); The rule that coincides in cross section is, 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)=365.0mm, root footpath (Dr)=906.8mm; 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 13.670 by 81.830 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 1.61 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 2.265 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 3.75 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 4.58 dullnesses.
2. last-stage moving blade of air-cooled feed pump steam turbine according to claim 1; It is characterized in that: said integral shroud has back of the body arc resistance Buddhist nun's working surface (A1) and inner arc damping working surface (B1), and back of the body arc resistance Buddhist nun's working surface (A1), inner arc damping working surface (B1) are the planes that is parallel to each other; 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) coincide each other; The shape of integral shroud has characteristic parameter: the identical gap (S) of adjacent blades; The integral shroud top pitch (P) of adjacent blades, gap between said adjacent blades and integral shroud top pitch satisfy following formula:
350≤P/S。
3. last-stage moving blade of air-cooled feed pump steam turbine according to claim 1 is characterized in that: said blade root is a fir-tree root.
4. last-stage moving blade of air-cooled feed pump steam turbine according to claim 3 is characterized in that: said blade root is four tooth lineal shape fir-tree roots.
5. last-stage moving blade of air-cooled feed pump steam turbine according to claim 1 is characterized in that: said blade is processed with stainless steel.
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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 |
| FR2998012B1 (en) * | 2012-11-09 | 2018-07-13 | Safran Helicopter Engines | COMPRESSION ASSEMBLY FOR TURBOMACHINE |
| 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 |
| CN113623019B (en) * | 2020-05-09 | 2023-09-15 | 中国石化工程建设有限公司 | Flue gas turbine moving blade assembly and flue gas turbine |
| 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 |
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| 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 |
| CN2828321Y (en) * | 2005-10-12 | 2006-10-18 | 哈尔滨汽轮机厂有限责任公司 | Penultimate vane of large air-cooling steam turbine |
| CN200952408Y (en) * | 2006-06-28 | 2007-09-26 | 哈尔滨汽轮机厂有限责任公司 | Special last stage blades for large air-cooled turbine |
| CN201170120Y (en) * | 2008-03-21 | 2008-12-24 | 哈尔滨汽轮机厂有限责任公司 | Large-scale supercritical, more supercritical air cooling steam turbine last stage blades |
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Patent Citations (4)
| 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 |
| CN2828321Y (en) * | 2005-10-12 | 2006-10-18 | 哈尔滨汽轮机厂有限责任公司 | Penultimate vane of large air-cooling steam turbine |
| CN200952408Y (en) * | 2006-06-28 | 2007-09-26 | 哈尔滨汽轮机厂有限责任公司 | Special last stage blades for large air-cooled turbine |
| CN201170120Y (en) * | 2008-03-21 | 2008-12-24 | 哈尔滨汽轮机厂有限责任公司 | Large-scale supercritical, more supercritical air cooling steam turbine last stage blades |
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