CN201330620Y - Novel high pressure clapboard static cascade applicable to steam turbine varying duty running - Google Patents
Novel high pressure clapboard static cascade applicable to steam turbine varying duty running Download PDFInfo
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- CN201330620Y CN201330620Y CNU2008202333983U CN200820233398U CN201330620Y CN 201330620 Y CN201330620 Y CN 201330620Y CN U2008202333983 U CNU2008202333983 U CN U2008202333983U CN 200820233398 U CN200820233398 U CN 200820233398U CN 201330620 Y CN201330620 Y CN 201330620Y
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- main flow
- leading edge
- leaf grating
- clapboard
- ring
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Abstract
The utility model discloses a novel high pressure clapboard static cascade applicable to steam turbine varying duty running, which has the advantages of high efficiency, high strength and stable running. The structure is that the static cascade comprises a clapboard outer ring, and the inner side is provided with a clapboard external belt; a clapboard inner belt corresponds to the clapboard external belt; the clapboard inner belt is arranged on a clapboard body; a plurality of main flow cascades and a plurality of leading edge lengthened guide cascades are arranged between the clapboard external belt and the clapboard inner belt; the main flow cascades and the leading edge lengthened guide cascades are arranged at the horizontal split part at intervals along the circumferential direction of the clapboard body; that is to say, at least one main flow cascade is arranged between the two adjacent leading edge lengthened guide cascades; at the same time, the main flow cascade is arranged evenly at other parts of the circumference of the clapboard body; each main flow cascade and each leading edge lengthened guide cascade adopt the same inner back arch profile stream discharge molded line; a guiding runner is formed between the two adjacent leading edge lengthened guide cascades; and a main runner is arranged between the two main flow cascades and between the main flow cascade and the leading edge lengthened guide cascade.
Description
Technical field
The utility model relates to a kind of impulse steam turbine diaphragm nozzle grid, relates in particular to a kind of high pressure stage diaphragm nozzle grid that are applicable to the Under Variable Conditions of Steam Turbine operation.
Background technique
The steam turbine set of bearing the Thermal Power Station of heat energy and two kinds of product Joint Production of electric energy is called co-generation turbine.The operating conditions of steam turbine under design condition is called design conditions.Co-generation turbine is in actual moving process, be subject to the factor affecting such as variation, steam parameter fluctuation of the thermoelectric burden requirement of outer bound pair, thereby cause the variation of interior parameters of steam turbine set and component stressing conditions, the operating conditions of this off-design operating mode is called the variable working condition of steam turbine.In order to improve Economy and the Security that co-generation turbine moves under variable working condition, just require in the through-flow design process of steam turbine, to select for use the blade profile that loss is little, intensity is high that adapts to variable parameter operation.
The steam turbine blade profile can be divided into impulse blade profile and reactionary style blade profile according to working principle.The expansion of steam flow is quickened mainly to carry out in static cascade in the level that the impulse blade profile constitutes, and the effect of moving blades is that steam kinetic energy is changed into mechanical energy.In steam turbine, be called leaf grating by the blade row that equidistant arrangement forms with identical blade profile, identical established angle; The passage that forms between two adjacent blade profiles in leaf grating is called the leaf grating runner; Steam is finished the whole process that changes into mechanical energy from heat energy in the leaf grating runner, so blade profile is the main determining factor of Turbine Flow Path efficient.Profile loss is meant the energy loss of steam flow when leaf grating flows, and it comprises the tail loss of frictional loss in the boundary layer on the blade profile surface and back edge.
The angle of cut of 2 public tangent lines of blade profile intrados and impeller contour is called the blade profile established angle.Inlet angles are meant formed angle between direction when steam flow enters the leaf grating runner and the blade profile front.The angle of how much inlet angles of inlet angles and leaf grating is called the angle of attack, when it is the Under Variable Conditions of Steam Turbine operation cascade loss is had one of factor of considerable influence.
In High temperature and High pressure Steam Turbine flow passage component design proposal, because the high-pressure section flow area is little, blade height is short, and pressure reduction is big before and after the impulse steam turbine stator blade, and the dividing plate axial width is bigger.Early stage design adopts narrow blades to add reinforcing rib structure, as shown in Figure 3.Because molded lines and the blade profile of stiffening rib do not match, and stiffening rib can not realize complete matching with narrow blades, so cause high pressure diaphragm nozzle grid flow of steam to lose greatly.
The model utility content
The utility model is at existing turbine high-pressure level group diaphragm nozzle grid project organization and problems occured in operation, a kind of high efficiency, high strength are provided, have adapted to the novel high pressure stage diaphragm nozzle grid that are applicable to the Under Variable Conditions of Steam Turbine operation of co-generation turbine variable parameter operation fully.
For achieving the above object, the utility model is realized by the following technical solutions:
A kind of novel high pressure stage diaphragm nozzle grid that are applicable to the Under Variable Conditions of Steam Turbine operation, it comprises the dividing plate outer shroud, be provided with shroud outside the dividing plate in dividing plate outer shroud inboard, corresponding with the outer shroud of dividing plate is shroud in the dividing plate, shroud is installed on the partition body in the dividing plate, be provided with a plurality of main flow leaf gratings and a plurality of leading edge lengthening guide-ring in described dividing plate periphery and the dividing plate between shroud, main flow leaf grating and leading edge lengthening guide-ring are the interval arrangement at the horizontal flange place along the partition body circumferencial direction, promptly are provided with at least one main flow leaf grating between two adjacent leading edges lengthening guide-rings; Simultaneously, in all the other of partition body circumference the main flow leaf grating is installed uniformly then everywhere; Each main flow leaf grating adopts identical interior back of the body arc steam output side molded lines with each leading edge lengthening guide-ring, constitutes the water conservancy diversion runner between adjacent two leading edges lengthening guide-ring, constitutes the main flow runner between the main flow leaf grating and between main flow leaf grating and leading edge lengthening guide-ring.
The pass that described main flow cascade blade is counted n and leading edge lengthening guide-ring number of blade N is: 2 (N-6)≤n≤2N.
Described main flow leaf grating molded lines adopts back of the body arc transition circle structure in the little steam admission side; Leading edge lengthening guide-ring molded lines also adopts back of the body arc transition circle structure in the little steam admission side simultaneously.
S1=68 °～76 ° of described leading edge lengthening guide-ring established angle β; S2=36 °～44 ° of main flow leaf grating established angle β
Between described main flow leaf grating and leading edge lengthening guide-ring identical with pitch between the main flow leaf grating.
Described leading edge lengthening guide-ring is consistent with the trailing edge thickness of main flow leaf grating, and two class leaf grating molded lines have identical maximum ga(u)ge simultaneously.
Novel diaphragm nozzle grid of the present utility model are made up of main flow leaf grating and leading edge lengthening guide-ring, the two adopts identical interior back of the body arc steam output side molded lines, the through-flow zone that steam enters dividing plate is at first carried out water conservancy diversion through the water conservancy diversion runner that leading edge lengthening guide-ring constitutes to steam flow, and then enters between the main flow leaf grating and the main flow leaf grating is finished the acceleration of expanding with the main flow runner between the lengthening guide-ring.Except that dividing plate horizontal flange place employing main flow leaf grating is arranged at interval with the lengthening guide-ring, all the other all adopt many main flows leaf grating arrangement everywhere on the dividing plate circumferencial direction.
The main flow leaf grating adopts advanced design method, by back of the body camber line in the control blade steam flow expansion accelerating region is moved behind the blade profile lagging edge, the boundary layer in most of zone, blade profile surface is in laminar flow regime, reduce the blade profile frictional loss, make the boundary layer of convex surface steam output side be difficult for producing the separation of flow, thereby reduce blade profile tail district; The pressure reduction of convex surface is less in the blade grid passage leading portion, transverse-pressure gradient is also less, thereby the generation and the development of root end wall secondary flow have been postponed, the leaf grating runner second half section quickens because of steam flow expands, the speed of main flow area is higher, reduced the accumulation of leaf grating root and top boundary layer steam flow, secondary flow loss is reduced.Two kinds of advanced persons' Blade Design Method combines, and has reduced profile loss effectively.
During the Under Variable Conditions of Steam Turbine operation, diaphragm nozzle grid steam flow comes flow path direction with the off-design value, and for impulse steam turbine, stator blade has been born most of enthalpy drop, so the angle of attack adaptability of stator blade directly influences the off design performance of unit.Main vapour leaf grating molded lines adopts back of the body arc transition circle Ds1 design in the little steam admission side, under the condition that guarantees blade strength, Ds1 only is 16%～23% of blade profile maximum ga(u)ge Ds3, has reduced 45%～52% than traditional blade profile, so have bigger angle of attack adaptability scope than traditional blade profile.
Leading edge lengthening guide-ring molded lines adopts back of the body arc transition circle Ds4 in the little steam admission side, reduced effectively because the caused choked flow effect of guide-ring thickness steam, adopt the high-order fair curve to be connected between the steam admission side fillet of guide-ring and maximum ga(u)ge, such molded lines design can make steam turbine when variable parameter operation, in the water conservancy diversion runner, alleviate because the steam flow inlet angle changes at the formed diffusion of inlet part, the steam flow percentage speed variation connects level and smooth, has improved the flow of steam efficient of water conservancy diversion runner.
The lengthening section of leading edge lengthening guide-ring has improved the welding rigidity of the inside and outside shroud of turbine high-pressure level section welding diaphragm effectively, and pressure reduction changes requirement to the dividing plate bulk strength before and after when having satisfied variable parameter operation.Because adopted the design of laminar flow blade profile, the maximum ga(u)ge Ds3 of main flow leaf grating blade profile increases by 43%～58% with respect to traditional blade profile, improve leaf grating and adapted to the ability that Under Variable Conditions of Steam Turbine is moved, strengthened the rigidity of main flow blade.
The beneficial effects of the utility model are: simple in structure, and efficient height, intensity height, the high Security and the stability of unit operation.
Description of drawings
Fig. 1 is the utility model diaphragm nozzle grid structural representations;
Fig. 2 is the utility model diaphragm nozzle grid pitch circle schematic cross-section;
Fig. 3 is conventional diaphragm nozzle grid structural representation;
Fig. 4 is conventional diaphragm nozzle grid pitch circle schematic cross-section;
Fig. 5 is the utility model leading edge lengthening guide-ring and main flow leaf grating layout plan;
Fig. 6 is leading edge lengthening airflow fence and main flow leaf grating molded lines contrast figure;
Fig. 7 is the I part partial enlarged drawing of Fig. 6.
Wherein 1, the dividing plate outer shroud, 2, the outer shroud of dividing plate, 3, shroud in the dividing plate, 4, partition body, 5, leading edge lengthening guide-ring, 6, the main flow leaf grating, 7, main flow runner, 8, the water conservancy diversion runner, 9, stiffening rib, 10, narrow blades, 11, main flow runner throat, 12, leading edge lengthening guide-ring blade profile line, 13, main flow leaf grating blade profile line, 14, back of the body arc steam output side molded lines, 15, inner arc steam output side molded lines.
Embodiment
Below in conjunction with drawings and Examples the utility model is further specified.
By Fig. 3, Fig. 4 as can be known, existing diaphragm nozzle grid are to adopt outer shroud 2 of dividing plate and interior 3 of the shrouds of dividing plate that the structure of stiffening rib 9 and narrow blades 10 is set.
Fig. 1, among Fig. 2, diaphragm nozzle grid structure of the present utility model is: it comprises dividing plate outer shroud 1, be provided with shroud 2 outside the dividing plate in dividing plate outer shroud 1 inboard, corresponding with peripheral 2 bands of dividing plate is shroud 3 in the dividing plate, enclosing 3 bands in the dividing plate is installed on the partition body 4,3 of shrouds are provided with a plurality of main flow leaf gratings 6 and a plurality of leading edge lengthening guide-ring 5 in described dividing plate peripheral 2 and the dividing plate, main flow leaf grating 6 and leading edge lengthening guide-ring 5 are the interval arrangement at the horizontal flange place along partition body 4 circumferencial directions, and promptly two adjacent 5 of guide-rings of leading edges lengthening are provided with at least one main flow leaf grating 6; Simultaneously, in all the other of partition body 4 circumference main flow leaf grating 6 is installed uniformly then everywhere; Each main flow leaf grating 6 adopts identical back of the body arc steam output side molded lines 14 and inner arc steam output side molded lines 15 with each leading edge lengthening guide- ring 5,5 of adjacent two leading edges lengthening guide-rings constitute water conservancy diversion runner 8, and 6 of main flow leaf gratings and main flow leaf grating 6 and 5 of leading edge lengthening guide-rings constitute main flow runner 7.
Main flow leaf grating blade profile line 13 adopts back of the body arc transition circle structure in the little steam admission side; Leading edge lengthening guide-ring blade profile line 12 also adopts back of the body arc transition circle structure in the little steam admission side simultaneously.
The width B s1 of leading edge lengthening guide-ring 5 is 72%～82% of partition body 4 width B, and having solved effectively is in operation bears partition body 4 inside and outside ring of turning torque because high pressure stage section spacer width B is far longer than the strength problem of main flow leaf grating 6 width B s2.Two 5 of guide-rings of leading edge lengthening have constituted the water conservancy diversion runner 8 of steam flow; 6 of main flow leaf gratings and main flow leaf grating 6 and 5 of guide-rings of leading edge lengthening have constituted the main flow runner 7 of steam flow.
Fig. 5 has shown the arrangement of two class leaf gratings of these novel diaphragm nozzle grid.By Pneumatic Calculation analysis and test and analysis of partition body semi-finals degree and test, the number of blade N of the number of blade n of main flow leaf grating 7 and leading edge lengthening guide-ring 5 closes and is: 2 (N-6)≤n≤2N.S1=68 °～76 ° of leading edge lengthening guide-ring 5 established angle β, s2=36 °～44 ° of main flow leaf grating established angle β, because it has the interior back of the body of identical steam output side camber line with main flow leaf grating 6, so no matter how two class leaf gratings were upwards arranged in 4 weeks of partition body, pitch t between wantonly two stator blades equates, and main flow runner throat 11 all is identical, and this has just guaranteed the stability of flow of steam.
Fig. 6, Fig. 7 show leading edge lengthening guide-ring 5 and the interior conformity of carrying on the back the camber line of main flow leaf grating 6 steam output sides, and particularly trailing edge thickness Ds2 is on all four, and two class leaf grating molded lines have identical maximum ga(u)ge Ds3.Between the main flow leaf grating and leading edge lengthening guide-ring identical with pitch between the main flow leaf grating.
The embodiment of the diaphragm nozzle grid that are applicable to variable parameter operation that the utility model proposes is the static cascades of welding diaphragm that are used for the high pressure stage section of ultrahigh pressure and High Temperature High Pressure cogeneration of heat and power impulse steam turbine.By Aerodynamic optimization design and analysis of experiments to main flow leaf grating and leading edge lengthening guide-ring molded lines, reduced profile loss, improve the flow efficiency of steam in blade grid passage, guaranteed the intensity of high pressure stage section dividing plate leaf grating simultaneously, improved the Security and the stability of unit operation.
Claims (5)
1. novel high pressure stage diaphragm nozzle grid that are applicable to Under Variable Conditions of Steam Turbine operation, it comprises the dividing plate outer shroud, be provided with shroud outside the dividing plate in dividing plate outer shroud inboard, corresponding with the outer shroud of dividing plate is shroud in the dividing plate, shroud is installed on the partition body in the dividing plate, it is characterized in that, be provided with a plurality of main flow leaf gratings and a plurality of leading edge lengthening guide-ring in described dividing plate periphery and the dividing plate between shroud, main flow leaf grating and leading edge lengthening guide-ring are the interval arrangement at the horizontal flange place along the partition body circumferencial direction, promptly are provided with at least one main flow leaf grating between two adjacent leading edges lengthening guide-rings; Simultaneously, in all the other of partition body circumference the main flow leaf grating is installed uniformly then everywhere; Each main flow leaf grating adopts identical interior back of the body arc steam output side molded lines with each leading edge lengthening guide-ring, constitutes the water conservancy diversion runner between adjacent two leading edges lengthening guide-ring, constitutes the main flow runner between the main flow leaf grating and between main flow leaf grating and leading edge lengthening guide-ring.
2. the novel high pressure stage diaphragm nozzle grid that are applicable to the Under Variable Conditions of Steam Turbine operation as claimed in claim 1, its main flow leaf grating molded lines adopt back of the body arc transition circle structure in the little steam admission side; Leading edge lengthening guide-ring molded lines also adopts back of the body arc transition circle structure in the little steam admission side simultaneously.
3. the novel high pressure stage diaphragm nozzle grid that are applicable to the Under Variable Conditions of Steam Turbine operation as claimed in claim 1 is characterized in that, s1=68 °～76 ° of described leading edge lengthening guide-ring established angle β; S2=36 °～44 ° of main flow leaf grating established angle β
4. the novel high pressure stage diaphragm nozzle grid that are applicable to Under Variable Conditions of Steam Turbine operation as claimed in claim 2 is characterized in that, between described main flow leaf grating and leading edge lengthening guide-ring identical with pitch between the main flow leaf grating.
5. the novel high pressure stage diaphragm nozzle grid that are applicable to the Under Variable Conditions of Steam Turbine operation as claimed in claim 2, it is characterized in that, described leading edge lengthening guide-ring is consistent with the trailing edge thickness of main flow leaf grating, and the molded lines of two class leaf gratings has identical maximum ga(u)ge simultaneously.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008202333983U CN201330620Y (en) | 2008-12-31 | 2008-12-31 | Novel high pressure clapboard static cascade applicable to steam turbine varying duty running |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008202333983U CN201330620Y (en) | 2008-12-31 | 2008-12-31 | Novel high pressure clapboard static cascade applicable to steam turbine varying duty running |
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| CN201330620Y true CN201330620Y (en) | 2009-10-21 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008202333983U Expired - Fee Related CN201330620Y (en) | 2008-12-31 | 2008-12-31 | Novel high pressure clapboard static cascade applicable to steam turbine varying duty running |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102052095A (en) * | 2010-07-07 | 2011-05-11 | 北京全四维动力科技有限公司 | Asymmetric diaphragm static cascade and asymmetric blades in nozzle set for axial flow steam turbine |
| CN104213948A (en) * | 2014-08-28 | 2014-12-17 | 浙江鸿峰重工机械有限公司 | Baffle plate for steam turbine |
-
2008
- 2008-12-31 CN CNU2008202333983U patent/CN201330620Y/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102052095A (en) * | 2010-07-07 | 2011-05-11 | 北京全四维动力科技有限公司 | Asymmetric diaphragm static cascade and asymmetric blades in nozzle set for axial flow steam turbine |
| CN102052095B (en) * | 2010-07-07 | 2013-12-04 | 北京全四维动力科技有限公司 | Asymmetric diaphragm static cascade and asymmetric blades in nozzle set for axial flow steam turbine |
| CN104213948A (en) * | 2014-08-28 | 2014-12-17 | 浙江鸿峰重工机械有限公司 | Baffle plate for steam turbine |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20091021 Termination date: 20141231 |
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| EXPY | Termination of patent right or utility model |