CN108119187B - Low-pressure-stage moving blade of industrial steam turbine with variable rotation speed and large flow - Google Patents
Low-pressure-stage moving blade of industrial steam turbine with variable rotation speed and large flow Download PDFInfo
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- CN108119187B CN108119187B CN201810141352.7A CN201810141352A CN108119187B CN 108119187 B CN108119187 B CN 108119187B CN 201810141352 A CN201810141352 A CN 201810141352A CN 108119187 B CN108119187 B CN 108119187B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/14—Form or construction
- F01D5/141—Shape, i.e. outer, aerodynamic form
Abstract
The invention designs a low-pressure stage moving blade of a variable-rotation-speed high-flow industrial turbine, which is the last 3 stages of the low-pressure stage moving blade of the variable-rotation-speed high-flow industrial turbine and comprises a blade body, a shroud and a blade root, and is characterized in that the blade body, the shroud and the blade root are integrated by die forging from top to bottom, the profile line of the blade body is a variable-section torsion blade, the cross-section area from the root to the top is gradually reduced, and the adjacent sections are twisted relatively. The invention can safely operate under the conditions of back pressure of 5kPa-40kPa and rotation speed of 2400rpm-4000rpm, has the characteristics of high variable-rotation speed and variable-load efficiency, good intensity vibration performance, large mass flow, stable structure and convenient processing and assembly, and can be widely applied to industrial turbines with large load and variable rotation speed.
Description
Technical Field
The invention relates to a driving industrial turbine moving blade, in particular to a variable-rotation-speed high-flow industrial turbine low-pressure-stage moving blade.
Background
In the industrial driving field, especially in the key fields of large ethylene, large air separation and the like, the requirements of variable-rotation-speed large-flow high-power industrial turbines are continuously increased, and the high-efficiency and safe design of the variable-rotation-speed large-flow high-power industrial turbines gradually highlights importance. The low-pressure stage group blade has a severe operation condition and must meet the requirement of operation from a blocking condition to a blowing condition, so that the reliability of the low-pressure stage group blade directly influences the safe operation of the unit. The design technology of the low-pressure stage group moving blade becomes a core technology in the design of the steam turbine due to wide related technical range and high technical content, and relates to a plurality of disciplines such as thermodynamics, theoretical mechanics, hydrodynamics, material mechanics, materials and the like.
The line efficiency of the last 3-stage moving blades of most variable-speed industrial turbines before is not high, and most of the industrial turbines do not have shroud, so that steam leakage loss is increased. In order to increase the vibration reduction damping effect of the blades, most of the variable-rotation-speed industrial turbines adopt a loose lacing wire structure, so that the blades are partially grouped, the collision loss of water vapor is increased by the loose lacing wire structure, and the efficiency of the blades is reduced. The structure of the invention is very different from that of the traditional variable-speed industrial turbine last 3-stage moving blade.
Disclosure of Invention
The invention aims to solve the defects of the technology, and designs the last three-stage moving blade for the variable-speed high-flow industrial steam turbine, which has good variable working condition performance and strength vibration performance, and is reasonable in structure and convenient to assemble.
The invention designs a low-pressure stage moving blade of a variable-rotation-speed high-flow industrial turbine, which is the last 3 stages of the low-pressure stage moving blade of the variable-rotation-speed high-flow industrial turbine and comprises a blade body, a shroud and a blade root, and is characterized in that the blade body, the shroud and the blade root are integrally formed by die forging from top to bottom, the profile of the blade body is a variable-section torsion blade, the section area from the root to the top is gradually reduced, relative torsion exists between two adjacent sections, the height H of the working part of the blade is 196.0mm, the axial width V of the root is 78.11mm, the diameter of the root is 535.0mm, the axial width V1 of the top is 52.1mm, and the steam discharge area of the blade body is 2.9m 2 . The characteristic of the structure is that the profile line of the blade body is a variable cross section distortion profile, which is formed by overlapping a plurality of characteristic cross sections according to the characteristic rule, the profile line of the characteristic cross section is a closed curve surrounded by an inner arc curve and a back arc curve, the overlapping rule of the cross sections is that each cross section continuously and smoothly transits from the root to the top along the blade height direction, the cross section area from the root to the top is gradually reduced, and the adjacent cross sections are provided withRelative torsion.
The blade shroud ring part is of a Z-shaped structure and is provided with a back arc working face and an inner arc working face, the two working faces are planes which are parallel to each other, and in a working state, the back arc working face of the shroud ring is contacted with the inner arc working face of the adjacent blade shroud ring. The working face distance A1 of the shroud was 48.46mm and the working face geometric center distance T1 was 67.32mm. The thickness W of the shroud was 7.9mm and the axial width C1 was 56.09mm. The characteristic angle alpha 1 of the shroud is 50 degrees, the characteristic angle alpha 2 of the shroud is 95 degrees, and the transition fillet R is 1mm.
In a further scheme, the blade root is a T-shaped blade root, the axial width C of the blade root is 111.8mm, and the total height K of the blade root is 127.57mm.
The further scheme is that the relative blade height H of the blade body is monotonically increased from 0% to 100%, and the change rule of the pitch to chord ratio T/b from the blade root section to the blade top section is as follows: t/b is more than or equal to 0.56 and less than or equal to 0.77; the change rule of the axial width ratio T/B of the pitch from the blade root section to the blade top section to the blade profile section is as follows: T/B is more than or equal to 0.62 and less than or equal to 1.26; the change rule of the maximum thickness ratio T/Dmax of the pitch from the blade root section to the blade top section to the blade profile section is as follows: T/B is more than or equal to 2.26 and less than or equal to 7.05; the change rule of the ratio T/A of the pitch from the blade root section to the blade top section to the blade profile section area is more than or equal to 0.034 and less than or equal to 0.127; the variation range of the installation angle beta from the blade root section to the blade top section is 65.31-37.33 degrees, the variation range of the inlet angle alpha is 39.54-98.20 degrees, and the variation range of the outlet angle theta is 68.70-69.46 degrees.
In a further scheme, she Shengao degrees are respectively 0, 40.0mm,80.0mm,120.0mm,160.0mm and 196.0mm, and the axial widths of the corresponding blade body parts are respectively as follows: 78.11mm,73.71mm,69.17mm,64.19mm,58.02mm,52.10mm, respectively, with corresponding chord lengths of 86.11mm,86.07mm,85.62mm,85.76mm,85.43mm,85.38mm, respectively, with corresponding mounting angles of 65.31 °,59.59 °,54.21 °,48.45 °,42.63 °,37.33 °, respectively, with corresponding maximum thicknesses of 21.3mm,20.0mm,15.8mm,12.2mm,9.8mm,9.3mm, respectively, with corresponding inlet angles of 39.54 °,46.46 °,49.39 °,63.67 °,78.11 °,98.2 °, respectively, with corresponding outlet angles of 68.7 °,67.24 °,75.57 °,68.72 °,68.15 °,69.46 °, respectively.
The low-pressure-stage moving blade of the variable-rotation-speed high-flow industrial turbine is designed by adopting a ternary flow field design technology, has a certain torsion rule along the blade height direction, namely, gives consideration to the static strength requirement of the blade, also enables the blade to have good aerodynamic performance, has a blade body torsion rule designed according to a ternary flow theory, has reasonable distribution rule of various thermodynamic parameters along the blade body, and has the aerodynamic efficiency of 93% in the range of 5kPa-40kPa through calculation verification of professional computational fluid dynamics calculation software CFX, numeca and the like. In addition, the results of conventional stress analysis and three-dimensional finite element strength analysis show that the blade profile has enough strength performance, and airflow bending stress under various working conditions is smaller. The blade adopts the Z-shaped shroud band structure, and the torsion of the blade caused by centrifugal force during rotation is recovered to form a whole circle of connecting structure, so that the vibration frequency of various vibration modes is eliminated, the vibration mode of the blade is relatively simple, the dynamic stress of the blade is greatly reduced, the dynamic frequency modulation is facilitated, and the blade can be ensured to run safely and reliably under various working conditions. The blade root is a T-shaped blade root, is convenient to assemble and uniform in bearing, can firmly and stably combine the blade and the rotor, can safely run below 5kPa-40kPa and 4000rpm back pressure, can be widely applied to industrial turbines for ultra-large air separation devices above hundred thousand grades, large industrial turbines for 150 ten thousand tons/year ethylene devices and the like, and has wide market application prospects.
Drawings
FIG. 1 is a schematic diagram of the structure of the present invention;
FIG. 2 is a graph of the geometry of the airfoil at section A-A of FIG. 1;
FIG. 3 is a schematic view of a blade shroud attachment of the present invention;
FIG. 4 is a schematic view of a blade profile of the present invention;
FIG. 5 is a schematic view of the connection of three adjacent blades.
Detailed Description
The invention is further described below by way of implementation in conjunction with the accompanying drawings.
As shown in figures 1 and 3The invention discloses a low-pressure-stage moving blade of a variable-speed high-flow industrial turbine, which comprises a blade body 2, a shroud 1 and a blade root 3, wherein the blade body 2, the shroud 1 and the blade root 3 are integrated by die forging from top to bottom, the profile line of the blade body 2 is a variable-section torsion blade, the cross-section area from the root to the top is gradually reduced, the adjacent two sections are relatively twisted, the blade is formed by overlapping a plurality of characteristic sections according to a specific rule, the profile line of the characteristic sections is a closed curve surrounded by an inner arc curve and a back arc curve, and the overlapping rule of the sections is continuous smooth transition from the root to the top along the height direction of the blade. The She Shengao degree H is 196.0mm, the root axial width V is 78.11mm, the root diameter is 535.0mm, the top axial width V1 is 52.1mm, and the blade body steam exhaust area is 2.9m 2 . The axial width C of the blade root is 111.8mm. The thickness W of the shroud was 7.9mm and the axial width C1 of the shroud was 56.09mm. When the whole blade is assembled, the blade root 3 is circumferentially arranged in the wheel groove; the blade top is provided with a damping shroud 1, the whole blade is tightly assembled, and the shroud of the adjacent blade is tightly contacted with the shroud in a non-working state. The distance A1 of the working surface of the shroud is 48.46mm, and the distance T1 of the geometric center of the working surface is 67.32mm. In the working state, collision and friction damping between the working surfaces of the shroud can consume the resonance energy of the blade, and the dynamic stress of the blade is greatly reduced; the blade root 3 is a T-shaped blade root, the total height K of the blade root 3 is 42.03mm, the structure ensures that the blade can be firmly installed into the rim, the contact is stable, safe and reliable, the requirements of strength and vibration are ensured, and the long-term safe and efficient operation of the blade is ensured.
As shown in fig. 2, the relative blade height H of the blade body 2 increases monotonically from 0% to 100%, and the pitch-to-chord ratio T/b from the blade root section to the blade tip section changes with the following rule: t/b is more than or equal to 0.56 and less than or equal to 0.77; the change rule of the axial width ratio T/B of the pitch from the blade root section to the blade top section to the blade profile section is as follows: T/B is more than or equal to 0.62 and less than or equal to 1.26; the change rule of the maximum thickness ratio T/Dmax of the pitch from the blade root section to the blade top section to the blade profile section is as follows: T/B is more than or equal to 2.26 and less than or equal to 7.05; the change rule of the ratio T/A of the pitch from the blade root section to the blade top section to the blade profile section area is more than or equal to 0.034 and less than or equal to 0.127; the variation range of the installation angle beta from the blade root section to the blade top section is 65.31-37.33 degrees, the variation range of the inlet angle alpha is 39.54-98.20 degrees, and the variation range of the outlet angle theta is 68.70-69.46 degrees.
As shown in fig. 4, the heights of the blade body 2 are respectively 0, 40.0mm,80.0mm,120.0mm,160.0mm and 196.0mm, and the axial widths of the corresponding blade body parts are respectively: 78.11mm,73.71mm,69.17mm,64.19mm,58.02mm,52.10mm, respectively, with corresponding chord lengths of 86.11mm,86.07mm,85.62mm,85.76mm,85.43mm,85.38mm, respectively, with corresponding mounting angles of 65.31 °,59.59 °,54.21 °,48.45 °,42.63 °,37.33 °, respectively, with corresponding maximum thicknesses of 21.3mm,20.0mm,15.8mm,12.2mm,9.8mm,9.3mm, respectively, with corresponding inlet angles of 39.54 °,46.46 °,49.39 °,63.67 °,78.11 °,98.2 °, respectively, with corresponding outlet angles of 68.7 °,67.24 °,75.57 °,68.72 °,68.15 °,69.46 °, respectively.
As shown in fig. 5, 3 adjacent blades are connected to form a fan-shaped structure.
The specific parameters of the 6 blade body characteristic sections are as follows:
Claims (1)
1. the utility model provides a low pressure level moving blade of variable speed industrial steam turbine, includes blade body (2), shroud (1) and blade root (3), its characterized in that, blade body (2), shroud (1), blade root (3) die forging from top to bottom become an organic whole, blade body (2) molded lines are variable cross section torsion blade, and the cross-sectional area of root to top reduces gradually, has relative torsion between two adjacent cross-sections, and blade body height H is 196.0mm, and root axial width V is 78.11mm, and root diameter is 535.0mm, and top axial width V1 is 52.1mm, blade body (2) exhaust area is 2.9m 2 The method comprises the steps of carrying out a first treatment on the surface of the The shroud ring (1) is of a Z-shaped structure, the working face distance A1 of the shroud ring (1) is 48.46mm, the geometric center distance T1 of the working face is 67.32mm, the thickness W of the shroud ring is 7.9mm, the axial width C1 of the shroud ring is 56.09mm, the characteristic angle alpha 1 of the shroud ring is 50 degrees, the characteristic angle alpha 2 of the shroud ring is 95 degrees, and the transition fillet R of the shroud ring1 mm; the blade root (3) is a T-shaped blade root, the axial width C of the blade root (3) is 111.8 and mm, and the total height K of the blade root is 127.57 mm; the relative blade height of the blade body (2) is monotonically increased from 0% to 100%, and the change rule of the pitch to chord ratio T/b from the blade root section to the blade top section is as follows: t/b is more than or equal to 0.56 and less than or equal to 0.77; the change rule of the axial width ratio T/B of the pitch from the blade root section to the blade top section to the blade profile section is as follows: T/B is more than or equal to 0.62 and less than or equal to 1.26; the change rule of the maximum thickness ratio T/Dmax of the pitch from the blade root section to the blade top section to the blade profile section is as follows: T/Dmax is less than or equal to 2.26 and less than or equal to 7.05; the change rule of the ratio T/A of the pitch from the blade root section to the blade top section to the blade profile section area is more than or equal to 0.034 and less than or equal to 0.127; the variation range of the installation angle beta from the blade root section to the blade top section is 65.31-37.33 degrees, the variation range of the inlet angle alpha is 39.54-98.20 degrees, and the variation range of the outlet angle theta is 68.70-69.46 degrees.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810141352.7A CN108119187B (en) | 2018-02-11 | 2018-02-11 | Low-pressure-stage moving blade of industrial steam turbine with variable rotation speed and large flow |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810141352.7A CN108119187B (en) | 2018-02-11 | 2018-02-11 | Low-pressure-stage moving blade of industrial steam turbine with variable rotation speed and large flow |
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| CN108119187A CN108119187A (en) | 2018-06-05 |
| CN108119187B true CN108119187B (en) | 2023-10-17 |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109101722B (en) * | 2018-08-09 | 2022-03-22 | 东方电气集团东方汽轮机有限公司 | Composite forming design method for turbine blade |
| CN109695479B (en) * | 2018-08-22 | 2023-12-29 | 杭州汽轮动力集团股份有限公司 | High-rotating-speed high-load low-pressure-stage moving blade for industrial steam turbine |
| CN111963252B (en) * | 2020-09-03 | 2023-03-14 | 杭州汽轮动力集团股份有限公司 | Secondary and final moving blade and blade assembly of variable-rotating-speed large-flow industrial steam turbine |
| CN112160795B (en) * | 2020-10-30 | 2021-09-14 | 杭州汽轮机股份有限公司 | Full-rotating-speed low-pressure-stage moving blade, moving blade group and industrial steam turbine |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CA2009120A1 (en) * | 1989-02-03 | 1990-08-03 | Masao Siga | Steam turbine, rotor shaft thereof, and heat resisting steel |
| JP3315800B2 (en) * | 1994-02-22 | 2002-08-19 | 株式会社日立製作所 | Steam turbine power plant and steam turbine |
| CN201581936U (en) * | 2009-11-20 | 2010-09-15 | 哈尔滨汽轮机厂有限责任公司 | Special last-stage vane for large-scale 60Hz turbine |
| CN104196573A (en) * | 2014-07-28 | 2014-12-10 | 杭州汽轮机股份有限公司 | Low-pressure last stage blade of rotating speed-variable air cooling industrial steam turbine with steam exhaust area of 3.6 m2 |
-
2018
- 2018-02-11 CN CN201810141352.7A patent/CN108119187B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CA2009120A1 (en) * | 1989-02-03 | 1990-08-03 | Masao Siga | Steam turbine, rotor shaft thereof, and heat resisting steel |
| JP3315800B2 (en) * | 1994-02-22 | 2002-08-19 | 株式会社日立製作所 | Steam turbine power plant and steam turbine |
| CN201581936U (en) * | 2009-11-20 | 2010-09-15 | 哈尔滨汽轮机厂有限责任公司 | Special last-stage vane for large-scale 60Hz turbine |
| CN104196573A (en) * | 2014-07-28 | 2014-12-10 | 杭州汽轮机股份有限公司 | Low-pressure last stage blade of rotating speed-variable air cooling industrial steam turbine with steam exhaust area of 3.6 m2 |
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| CN108119187A (en) | 2018-06-05 |
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Address after: 311100 Building 1, No. 608, Kangxin Road, Linping District, Hangzhou, Zhejiang Patentee after: Hangzhou Turbine Power Group Co.,Ltd. Address before: 357 Shiqiao Road, Xiacheng District, Hangzhou City, Zhejiang Province Patentee before: HANGZHOU STEAM TURBINE Co.,Ltd. |
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