CN108374691B - Variable-rotation-speed high-flow industrial turbine last-stage moving blade - Google Patents
Variable-rotation-speed high-flow industrial turbine last-stage moving blade Download PDFInfo
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- CN108374691B CN108374691B CN201810141411.0A CN201810141411A CN108374691B CN 108374691 B CN108374691 B CN 108374691B CN 201810141411 A CN201810141411 A CN 201810141411A CN 108374691 B CN108374691 B CN 108374691B
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- 238000009434 installation Methods 0.000 claims description 3
- 230000004323 axial length Effects 0.000 abstract 1
- 238000005516 engineering process Methods 0.000 description 5
- VGGSQFUCUMXWEO-UHFFFAOYSA-N Ethene Chemical compound C=C VGGSQFUCUMXWEO-UHFFFAOYSA-N 0.000 description 2
- 239000005977 Ethylene Substances 0.000 description 2
- 238000004458 analytical method Methods 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 2
- 238000007664 blowing Methods 0.000 description 2
- 238000013016 damping Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
Classifications
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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
-
- 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
- F01D5/147—Construction, i.e. structural features, e.g. of weight-saving hollow blades
-
- 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
- F01D5/22—Blade-to-blade connections, e.g. for damping vibrations
-
- 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
- F01D5/30—Fixing blades to rotors; Blade roots ; Blade spacers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/96—Preventing, counteracting or reducing vibration or noise
Abstract
The invention relates to the field of industrial turbine blades, and particularly discloses a final-stage moving blade which has high variable rotation speed, high flow rate and high pneumatic efficiency and meets the operation requirement of a heavy load variable working condition. The blade comprises a blade root, a blade body, a boss with holes on the blade body and a biconical rod. The blade body is a variable-section torsion blade, and the height is 496mm. The blade root is a fork-shaped blade root, the fork number is 4, and the axial length is 187mm. The center of the boss hole is 341.9mm away from the bottom of the blade body, the diameter of the boss hole is 21mm, the diameters of two ends of the double-cone rod are 16.6mm, and the double-cone rod is limited by the boss holes of two adjacent blade bodies and can move but cannot move out. The vane can safely run under the conditions of back pressure of 5kPa-40kPa and rotation speed of 2400rpm-4000rpm, and the variable-rotation-speed high-flow high-load final stage vane has the characteristics of high variable-rotation-speed 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 variable rotation speeds.
Description
Technical Field
The invention relates to a moving blade of an industrial turbine for driving, in particular to a final moving blade of the industrial turbine for driving at a variable rotation speed and a large flow.
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 operation condition of the final stage blade is severe, and the operation from the blocking condition to the blowing condition needs to be satisfied, and the operation condition of the final stage blade is very severe under the conditions of low back pressure, blocking condition or high back pressure and blowing; the enthalpy drop of the final-stage blade is large, and a high-efficiency molded line is needed to improve the efficiency of the unit and reduce the energy consumption. The design difficulty of the final stage blade is high, and the final stage blade relates to multiple disciplines such as thermodynamics, theoretical mechanics, hydrodynamics, material mechanics, materials and the like, has high technical content and belongs to core technology in the design of a steam turbine.
The large part of the variable-speed industrial steam turbine has small steam discharge area, poor variable working condition performance, low pneumatic efficiency and high energy consumption, and cannot meet the operation requirement aiming at the operation working condition of large load, so that the high-load variable-speed industrial steam turbine with larger steam discharge area needs to be developed, and the final stage blade is important.
Disclosure of Invention
The invention aims to solve the defects of the technology and provide a final-stage moving blade of an industrial steam turbine with variable rotation speed and large flow rate, wherein the steam discharge area of the blade is 2.9m 2 The blade has good aerodynamic efficiency, variable working condition performance and strength performance, reasonable structure and convenient assembly.
The invention relates to a variable-rotation-speed high-flow industrial turbine last-stage moving blade which consists of a blade root, a blade body, a boss with holes on the blade body and a biconical rod. The blade root and the blade body are manufactured into a whole; the boss with the hole is positioned at the middle upper part of the blade body and is made into a whole with the blade body; the blade body is a variable-section torsion blade, two adjacent sections are twisted relatively along the height direction of the blade, and the area of the section of the blade body is gradually reduced from the bottom to the top.
The blade body is relative to the blade height L d From 0% to 100%, the pitch-chord ratio T/b change rule from blade root section to blade top section is: t/b is more than or equal to 0.54 and less than or equal to 1.25; the change rule of the axial width ratio T/B of the pitch and the blade profile section is as follows: T/B is more than or equal to 0.54 and less than or equal to 2.57; pitch and maximum blade profile thicknessRatio of degree T/D max The change rule is as follows: T/D of 2.98 ≡ max Less than or equal to 25.78; radius R of leading edge of blade 0 The change rule is as follows: r is more than or equal to 2.38mm 0 Not less than 1.73mm; radius R of blade trailing edge 1 The change rule is as follows: r is more than or equal to 1.58mm 1 Not less than 1.10mm; the change rule of the installation angle beta is as follows: 81.59 DEG is more than or equal to beta is more than or equal to 28.63 DEG; the change rule of the inlet angle alpha is as follows: 48.89 degrees is more than or equal to alpha and less than or equal to 155.54 degrees; the change rule of the outlet angle theta is as follows: 37.53 DEG.gtoreq.theta.gtoreq.31.60 deg.
As preferable:
the She Shengao degrees is 496mm;
the blade root is a fork-shaped blade root, the fork number is 4, the axial width of the blade root is 187mm, and the radial height of the blade root is 160mm;
the boss with holes is a round table, the center of each boss hole is 341.9mm away from the bottom of the blade body, the diameter of each boss hole is 21mm, and boss holes of two adjacent blade bodies respectively accommodate two ends of the biconical rod;
the diameters of two ends of the double-cone rod are 16.6mm, the diameter of the middle of the double-cone rod is 24mm, the taper is 4 degrees, the displacement of the double-cone rod is limited by boss holes of two adjacent blade bodies, and the double-cone rod can move but cannot move out.
The invention has the beneficial effects that:
the invention relates to a final-stage moving blade of an industrial turbine with variable rotation speed and large flow, which is designed by adopting an advanced full three-dimensional pneumatic design method and a finite element analysis method. The width, thickness and cross section area of the cross section gradually decrease from root to top, monotonically and smoothly transition, and the blade body has a certain distortion rule along the blade height direction, so that the static strength requirement of the blade is considered, and the distribution rule of each thermal parameter along the blade body is reasonable, so that the blade has good aerodynamic performance. Proved by professional computational fluid dynamics software CFX, numeca and the like, under the working condition that the back pressure is 0.1bar outlet Mach number 0.5, the pneumatic efficiency of the low-pressure stage group is about 93%, the maximum flow is more than 550t/h, and meanwhile, the variable working condition performance is good; the middle upper part of the blade body is provided with a boss with holes and a double cone rod, under the action of centrifugal force and steam flow force in a working state, the double cone rod and the boss with holes collide with each other to form damping, so that the vibration resistance of the blade is improved, and the dynamic stress of the blade is reduced; the blade root adopts a fork blade root, so that the processing cost is low, and the assembly technology is mature;
the final stage blade has the advantages of high pneumatic efficiency, good strength performance, large steam exhaust area and the like, and has the characteristics of low processing and manufacturing cost, convenience in assembly and stable structure. Can safely run under the condition of the back pressure of 5kPa-40Pa and the rotating speed of 2400rpm-4000rpm, can be widely applied to industrial turbines for ultra-large air separation devices with the grade of more than one hundred thousand, industrial turbines for ethylene devices with the grade of 150 ten thousand/year, and the like, and has wide market application prospect.
Drawings
FIG. 1 is a schematic view of the structure of a blade of the present invention.
Fig. 2 is an axial view of a blade of the present invention.
Fig. 3 is a top view of a blade of the present invention.
FIG. 4 is a schematic view of various cross-sectional profiles of a blade of the present invention.
FIG. 5 is a schematic view of the profile geometry of a blade of the present invention.
Fig. 6 is a schematic diagram of a double tapered rod connection of adjacent 3 blades.
Fig. 7 is a cross-sectional view of a double tapered rod connection of adjacent 3 blades.
In the figure, a blade root 1, a blade body 2, a perforated boss 3 and a biconical rod 4 are shown.
Detailed Description
The invention is described in further detail below with reference to the attached drawing figures:
as shown in fig. 1 to 7, the final stage moving blade of the industrial turbine with variable rotational speed and large flow rate described in this embodiment is a variable cross-section torsion blade, which comprises a blade root 1, a blade body 2, a perforated boss 3 and a biconical stick 4. The blade body 2 is relative to the blade height L d From 0% to 100%, the pitch-chord ratio T/b change rule from blade root section to blade top section is: t/b is more than or equal to 0.54 and less than or equal to 1.25; the change rule of the axial width ratio T/B of the pitch and the blade profile section is as follows: T/B is more than or equal to 0.54 and less than or equal to 2.57; pitch and blade profile section maximum thickness ratio T/D max The change rule is as follows: T/D of 2.98 ≡ max Less than or equal to 25.78; the change rule of the installation angle beta is as follows: 81.59 DEG is more than or equal to beta is more than or equal to 28.63 DEG; the change rule of the inlet angle alpha is as follows: 48.89 degrees is more than or equal to alpha and less than or equal to 155.54 degrees; the change rule of the outlet angle theta is as follows: 37.53 degree or moreθ≥31.60°。
The blade root 1 is a fork-shaped blade root, the fork number is 4, the axial width of the blade root 1 is 187mm, and the radial height of the blade root 1 is 160mm.
The boss 3 with holes is a round table, the center of the boss hole is 341.9mm away from the bottom of the vane body, the diameter of the boss hole is 21mm, and the boss holes of two adjacent vane bodies respectively accommodate two ends of the biconical rod 4. The diameters of the two ends of the double-cone rod 4 are 16.6mm, the middle diameter is 24mm, the taper is 4 degrees, the displacement of the double-cone rod 4 is limited by boss holes of two adjacent blade bodies and can move, but the double-cone rod cannot move out.
The blade body 2 is designed by adopting an advanced full three-dimensional pneumatic design method and a finite element analysis method. The blade has the advantages that the blade is designed by the technology, the width, the thickness and the cross section area of the cross section gradually decrease from the root to the top, the cross section is in monotone smooth transition, the blade body has a certain distortion rule along the blade height direction, the static strength requirement of the blade is considered, and the distribution rule of all thermal parameters along the blade body is reasonable, so that the blade has good aerodynamic performance. Proved by professional computational fluid dynamics software CFX, numeca and the like, under the working condition that the back pressure is 0.1bar outlet Mach number 0.5, the pneumatic efficiency of the low-pressure stage group is about 93%, the maximum flow is more than 550t/h, and meanwhile, the variable working condition performance is good; the middle upper part of the blade body 2 is provided with a boss 3 with holes and a double-cone rod 4, and under the action of centrifugal force and steam flow force in a working state, the double-cone rod 4 collides with the boss 3 with holes to form damping, so that the vibration resistance of the blade is improved, and the dynamic stress of the blade is reduced; the blade root 1 adopts a fork-shaped blade root, so that the processing cost is low, and the assembly technology is mature; the blade can safely run under the conditions of back pressure of 5kPa-40kPa and rotation speed of 2000rpm-4000rpm, and has wide market application prospect.
The heights of the blade bodies 2 are respectively 0mm, 87mm, 174mm, 261mm, 348mm, 435mm and 522mm, and the corresponding sectional areas are respectively 3834.81mm 2 、2662.84mm 2 、2129.28mm 2 、1270.32mm 2 、929.2mm 2 、724.18mm 2 、749.32mm 2 。
The corresponding pitch chord ratios of the blade bodies 2 are respectively: 0.54, 0.64, 0.77, 0.9, 1.03, 1.14, 1.25, the corresponding pitch width ratios are respectively: 0.54, 0.68, 0.87, 1.13, 1.54, 2.07, 2.57, the corresponding pitch thicknesses are respectively: 2.98, 4.51, 5.67, 12.22, 17.7, 24.41, 25.78, the corresponding mounting angles are respectively: 81.59, 71.74, 62.72, 53.02, 41.47, 33.07, 28.63, the corresponding inlet angles are: 48.89, 64.81, 71.38, 71.36, 105.71, 136.84, 155.54, the corresponding outlet angles are: 37.53, 33.19, 34.85, 33.33, 32.1, 33.24, 31.6.
The specific parameters of each section of the blade body 2 are shown in the following table.
Claims (1)
1. Variable-rotation-speed high-flow industrial turbine last-stage moving blade with exhaust area of 2.9m 2 The blade has the advantages that the running rotating speed of the blade is 2400rpm-4000rpm, the maximum flow is 550T/h, the blade comprises a blade root (1) and a blade body (2), and a perforated boss (3) and a biconical rod (4) on the blade body (2), the blade body (2) is a variable-section torsion blade, two adjacent sections are relatively twisted along the blade height direction, the blade body (2) gradually reduces in section area from bottom to top, the relative blade height Ld of the blade body (2) is monotonically increased to 100% from 0% from the blade root section to the blade top section, and the change rule of the pitch to chord length ratio T/b is as follows: t/b is more than or equal to 0.54 and less than or equal to 1.25; the change rule of the axial width ratio T/B of the pitch and the blade profile section is as follows: T/B is more than or equal to 0.54 and less than or equal to 2.57; the change rule of the maximum thickness ratio T/Dmax of the pitch and the blade profile section is as follows: T/Dmax is less than or equal to 2.98 and less than or equal to 25.78; the change rule of the radius R0 of the blade-shaped front edge is as follows: r0 is more than or equal to 2.38mm and more than or equal to 1.73mm; the change rule of the radius R1 of the blade-shaped trailing edge is as follows: r1 is more than or equal to 1.58mm and more than or equal to 1.10mm; the change rule of the installation angle beta is as follows: 81.59 DEG is more than or equal to beta is more than or equal to 28.63 DEG; the change rule of the inlet angle alpha is as follows: 48.89 degrees is more than or equal to alpha and less than or equal to 155.54 degrees; the change rule of the outlet angle theta is as follows: 37.53 DEG or more, and theta or more than 31.60 DEG;
the heights of the blade bodies (2) are respectively 0mm, 87mm, 174mm, 261mm, 348mm, 435mm and 522mm, and the corresponding sectional areas are respectively 3834.81mm 2 、2662.84mm 2 、2129.28mm 2 、1270.32mm 2 、29.2 mm 2 、724.18mm 2 、 749.32 mm 2 ；
The corresponding pitch chord length ratios of the blade bodies (2) are respectively as follows: 0.54, 0.64, 0.77, 0.9, 1.03, 1.14, 1.25, the corresponding pitch width ratios are respectively: 0.54, 0.68, 0.87, 1.13, 1.54, 2.07, 2.57, the corresponding pitch thicknesses are respectively: 2.98, 4.51, 5.67, 12.22, 17.7, 24.41, 25.78, the corresponding mounting angles are respectively: 81.59 °, 71.74 °, 62.72 °, 53.02 °, 41.47 °, 33.07 °, 28.63 °, the corresponding inlet angles are: 48.89 °, 64.81 °, 71.38 °, 71.36 °, 105.71 °, 136.84 °, 155.54 °, the corresponding outlet angles are: 37.53 °, 33.19 °, 34.85 °, 33.33 °, 32.1 °, 33.24 °, 31.6 °;
the blade root (1) is a fork-shaped blade root, the fork number is 4, the axial width of the blade root (1) is 187mm, and the radial height of the blade root (1) is 160mm;
the hole bosses (3) are round tables, the centers of the holes of the hole bosses (3) are 341.9mm away from the bottom of the blade body, the hole diameters of the hole bosses (3) are 21mm, and the holes of the hole bosses (3) of two adjacent blade bodies (2) respectively accommodate two ends of the biconical rod (4); the diameters of two ends of the double-cone rod (4) are 16.6mm, the middle diameter is 24mm, the taper is 4 degrees, and the double-cone rod (4) is limited by the perforated bosses (3) of two adjacent blade bodies (2).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810141411.0A CN108374691B (en) | 2018-02-11 | 2018-02-11 | Variable-rotation-speed high-flow industrial turbine last-stage moving blade |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810141411.0A CN108374691B (en) | 2018-02-11 | 2018-02-11 | Variable-rotation-speed high-flow industrial turbine last-stage moving blade |
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| Publication Number | Publication Date |
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| CN108374691A CN108374691A (en) | 2018-08-07 |
| CN108374691B true CN108374691B (en) | 2024-03-29 |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102536328A (en) * | 2011-12-13 | 2012-07-04 | 杭州汽轮机股份有限公司 | Last-stage blade in low-pressure stage group of variable-rotation-speed air-cooling industrial steam turbine |
| CN102926821A (en) * | 2012-11-07 | 2013-02-13 | 哈尔滨汽轮机厂有限责任公司 | 900mm last stage moving blade for combined cycle steam turbine |
| CN103628926A (en) * | 2013-10-30 | 2014-03-12 | 杭州汽轮机股份有限公司 | 3m<2>-steam-exhaust-area low-pressure stage set last stage blade of variable speed industrial steam 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 |
| CN206458508U (en) * | 2016-12-20 | 2017-09-01 | 上海汽轮机厂有限公司 | Variable speed last-stage moving blade of air-cooled steam turbine |
| CN207847702U (en) * | 2018-02-11 | 2018-09-11 | 杭州汽轮机股份有限公司 | A kind of variable speed big flow industrial steam turbine final stage moving blade |
-
2018
- 2018-02-11 CN CN201810141411.0A patent/CN108374691B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102536328A (en) * | 2011-12-13 | 2012-07-04 | 杭州汽轮机股份有限公司 | Last-stage blade in low-pressure stage group of variable-rotation-speed air-cooling industrial steam turbine |
| CN102926821A (en) * | 2012-11-07 | 2013-02-13 | 哈尔滨汽轮机厂有限责任公司 | 900mm last stage moving blade for combined cycle steam turbine |
| CN103628926A (en) * | 2013-10-30 | 2014-03-12 | 杭州汽轮机股份有限公司 | 3m<2>-steam-exhaust-area low-pressure stage set last stage blade of variable speed industrial steam 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 |
| CN206458508U (en) * | 2016-12-20 | 2017-09-01 | 上海汽轮机厂有限公司 | Variable speed last-stage moving blade of air-cooled steam turbine |
| CN207847702U (en) * | 2018-02-11 | 2018-09-11 | 杭州汽轮机股份有限公司 | A kind of variable speed big flow industrial steam turbine final stage moving blade |
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Country or region after: China Address after: 310022 Building 1, No. 608, Kangxin Road, Linping District, Hangzhou, Zhejiang Applicant after: Hangzhou Turbine Power Group Co.,Ltd. Address before: 357 Shiqiao Road, Xiacheng District, Hangzhou City, Zhejiang Province Applicant before: HANGZHOU STEAM TURBINE Co.,Ltd. Country or region before: China |
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