CN107420135B - T-shaped blade root of turbine blade and matched rim groove thereof - Google Patents
T-shaped blade root of turbine blade and matched rim groove thereof Download PDFInfo
- Publication number
- CN107420135B CN107420135B CN201710680683.3A CN201710680683A CN107420135B CN 107420135 B CN107420135 B CN 107420135B CN 201710680683 A CN201710680683 A CN 201710680683A CN 107420135 B CN107420135 B CN 107420135B
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- 230000007704 transition Effects 0.000 claims abstract description 9
- 125000006850 spacer group Chemical group 0.000 claims description 4
- 229910003460 diamond Inorganic materials 0.000 claims description 2
- 239000010432 diamond Substances 0.000 claims description 2
- 238000000034 method Methods 0.000 abstract description 8
- 230000007547 defect Effects 0.000 abstract description 2
- 238000006243 chemical reaction Methods 0.000 description 4
- 238000007789 sealing Methods 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 3
- 238000005452 bending Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000003750 conditioning effect Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 239000000109 continuous material Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
Classifications
-
- 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
- F01D5/3007—Fixing blades to rotors; Blade roots ; Blade spacers of axial insertion type
-
- 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
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/03—Annular blade-carrying members having blades on the inner periphery of the annulus and extending inwardly radially, i.e. inverted rotors
Abstract
The invention relates to a T-shaped blade root of a turbine blade, which comprises a T-shaped head, a neck, a blade root and a blade body connecting section, and is characterized in that: viewed from a meridian plane sectional view, the bearing surface of the blade root T-shaped head part matched with the rim groove is an inclined surface, and the bearing surface of the blade root T-shaped head part forms an included angle theta with the axial direction of the steam turbine to form an inclined T-shaped head blade root structure; the bearing surface of the inclined T-shaped head of the blade root and the neck of the blade root are in fillet transition. The included angle is more than or equal to 25 degrees and less than or equal to 30 degrees, and is preferably 25 degrees. The invention solves the technical defects of the traditional T-shaped blade root, and provides the novel oblique T-shaped blade root of the turbine blade and the matched rim groove thereof, which avoid the larger stress concentration of the round angle of the T-shaped blade root and the round angle of the rim groove, and have the advantages of higher safety, lower process difficulty, compact structure and convenient assembly.
Description
Technical Field
The invention relates to a turbine rotor blade, in particular to a blade root for a reaction turbine rotor blade and a matched rim groove thereof.
Background
Reaction turbines typically employ a rotary drum rotor with continuous material between the rim grooves of adjacent stages as opposed to a disk rotor. The blade root forms of the rotor blade commonly used on the drum rotor are: t-root, double T-root, fork-root, fir-tree root, etc., which are mainly characterized by the following features.
T-shaped blade root: simple structure, reliable operation and convenient processing. The blade root is assembled circumferentially, and the rim groove for fixing the blade root is provided with at least one notch, so that the blades are sequentially and radially arranged in the rim groove from the notch, and the sealing blades are fixed at the notch position through radial seam riding screws. The T-shaped blade root has smaller bearing capacity and is suitable for blades with smaller centrifugal force.
Double T-shaped blade root: compared with the T-shaped blade root, the bearing surfaces are additionally provided, so that the bearing surfaces are uniformly stressed, the dimensional tolerance requirements of the bearing surfaces of the blade root and the rim groove are higher, and the processing difficulty is higher. Similar to the T-shaped blade root, the double T-shaped blade root is also assembled circumferentially, and a notch is formed in a rim groove for fixing the blade root, so that the blades are sequentially and radially arranged in the rim groove from the notch. Because the radial dimension of the double T-shaped blade root is generally larger, radial riding seam screw holes for locking and sealing blades are deeper, and the processing difficulty is also higher. In addition, due to the relatively large blade root volume, the centrifugal force of the blade root part accounts for the relatively large specific gravity of the total centrifugal force of the blade, so that the bearing capacity of the blade root is weakened to a certain extent, and the double-T-shaped blade root is relatively large in bearing capacity and suitable for the blade with the relatively large centrifugal force.
Fork-shaped blade root: the processing is more convenient, and the blade root fork radially inserts in the groove that the rim corresponds, fixes through axial pin. The more the fork number is, the stronger the bearing capacity is, and the method is suitable for the final stage blade which can process the axial pin holes or the regulating stage blade with larger root diameter.
Fir-tree root: the bearing surfaces are more, the processing precision requirement is higher, and the process is more complicated. She Genyou is axially received in the root slot and, in addition to the final and conditioning stages, more axial space is reserved between stages for assembly when the fir tree root is used for other stages. Compared with other blade roots of several types, the fir-tree blade root has the highest bearing capacity under the same blade body size, and is suitable for the last stage blade or the regulating stage blade with higher load.
For the rotary drum rotor of the reaction turbine, the fork-shaped blade root and the fir-shaped blade root have larger bearing capacity, but are limited by the assembly space, the processing precision and the cost, so that the use of the rotary drum rotor is restricted; the double T-shaped blade root is inconvenient to use due to the factors of process and assembly. From the standpoint of blade machining and assembly, the use of a T-root is preferred for stages other than the final and conditioning stages. When the T-blade root is used for medium-height blades or for low-pressure blades of the last stage, where the centrifugal forces are large, the bearing capacity has to be increased, and the stress level has to be reduced, by increasing the blade root size, due to its limited bearing capacity. However, as the blade root size increases, on one hand, the proportion of the centrifugal force of the blade root part to the total centrifugal force of the blade increases, and the stress of the blade root and the rim may not decrease and rise; on the other hand, the diameters and the depths of the saddle joint screw holes for locking the sealing blades are correspondingly increased, and the processing difficulty is increased. These two factors adversely affect the use of T-blade roots for medium-height blades or for low-pressure blades of the last stage where centrifugal forces are greater.
Disclosure of Invention
The invention aims to solve the problems that: if a T-shaped blade root is adopted, larger stress concentration is easily generated on a blade root fillet and a rim groove fillet, and the safe operation of the blade is influenced; if the double T-shaped blade root is adopted, although the stress concentration of the blade root fillet and the rim groove fillet is reduced, the process requirements of the blade root and the rim groove are higher, and the assembly of the tail blade is inconvenient; if the fork-shaped blade root is adopted, pin holes cannot be processed in a limited space except the final stage and the adjusting stage; if the fir-type blade root is adopted, more axial space is reserved between the stages for assembly except the final stage and the regulating stage, and the process requirement is high.
The T-shaped blade root structure is selected as the blade root of the medium-height blade or the last-stage low-pressure blade with larger centrifugal force on the rotary drum rotor of the reaction turbine by comprehensively considering the blade root structures under the conditions of meeting the requirements of limited assembly space, convenient assembly and processing technology difficulty.
On this basis, solve traditional T type blade root technical defect, provide one kind and avoid the great stress concentration of T type blade root fillet and rim groove fillet to have the novel steam turbine blade oblique T type blade root and the complex rim groove of security higher, the technology degree of difficulty is lower, compact structure, convenient assembly.
The invention provides a T-shaped blade root of a turbine blade, which comprises a T-shaped head, a neck, a blade root and a blade body connecting section, and is characterized in that: as seen in a sectional view through the meridian plane,
1) The bearing surface of the blade root T-shaped head part matched with the rim groove is an inclined surface, and an included angle theta is formed between the bearing surface of the blade root T-shaped head part and the axial direction of the steam turbine, so that an inclined T-shaped head blade root structure is formed; the bearing surface of the inclined T-shaped head of the blade root and the neck of the blade root are in fillet transition.
2) The inclination angle theta of the bearing surfaces at the left side and the right side of the T-shaped head of the blade root is equal.
3) The included angle is 25 degrees or more and θ or less than 30 degrees, and 25 degrees is the optimal angle.
4) The axial width of the inclined T-shaped head part is smaller than that of the connecting section of the blade root and the blade body.
5) The axial width of the blade root and blade body connecting section and the axial width of the rim groove of the blade root and blade body connecting section adopt clearance fit tolerance, so that the blade is axially positioned.
6) The bearing surface of the inclined T-shaped head of the blade root and the neck of the blade root are transited by a round angle, and a larger round angle radius is preferably adopted on the premise of ensuring that the bearing surface has a certain effective contact area.
The further improvement is that: the blade root is a circumferentially mounted blade root.
The further improvement is that: the blade root is suitable for both rectangular blade roots and diamond blade roots.
The further improvement is that: blade roots of adjacent stages of blades of the steam turbine can be adopted.
The invention provides a rim groove matched with a T-shaped blade root, which is characterized in that: as seen in a sectional view through the meridian plane,
1) The bearing surface of the rim groove matched with the bearing surface of the inclined T-shaped head forms an included angle theta with the axial direction of the steam turbine to form an inclined T-shaped rim groove structure; the bearing surface of the rim groove and the side wall of the bottom of the rim groove are in round corner transition.
2) The inclination angles of the bearing surfaces at the left side and the right side of the rim groove are equal;
3) The included angle is more than or equal to 25 degrees and less than or equal to 30 degrees, and is preferably 25 degrees.
4) The axial width of the blade root and blade body connecting section and the axial width of the rim groove of the blade root and blade body connecting section adopt clearance fit tolerance, so that the blade is axially positioned;
5) The bearing surface of the rim groove and the side wall of the bottom of the rim groove are transited by a round angle, and a larger round angle radius is preferably adopted on the premise of ensuring that the bearing surface has a certain effective contact area;
6) The side wall of the bottom of the rim groove and the bottom surface of the rim groove are transited by a round angle, and a larger round angle radius is preferably adopted on the premise of ensuring that the blade root and the rim groove do not interfere;
7) And a spacer strip is arranged between the bottom of the blade root and the bottom of the rim groove.
Compared with the prior art, the invention has the following beneficial effects:
1. because of the inclined T-shaped blade root structure, the positive pressure F applied to the bearing surface can be decomposed into radial force F r With axial force F a Meanwhile, the included angle between the blade root bearing surface and the side wall of the blade root neck and the included angle between the rim bearing surface and the side wall of the bottom of the rim groove are increased from right angles to obtuse angles, so that the stress concentration of a fillet is effectively reduced, the stress level of the blade root and the rim is reduced, and the safety of the blade is improved. When the blade root size is the same, the inclined T-shaped blade root has larger bearing capacity than the T-shaped blade root.
2. The blade root size is reduced properly, the proportion of the centrifugal force of the blade root part to the total centrifugal force of the blade is reduced, the material strength performance of the blade root and the rim is fully exerted, and the blade root and the blade rim are suitable for the blades with the heights above medium level and with larger centrifugal force.
3. The two bearing surfaces are insensitive to radial dimension deviation and angle deviation, and have good tolerance adaptability.
4. The axial structure is compact.
5. The method has good manufacturability, is suitable for most of circumferentially-installed turbine blades, and is beneficial to popularization.
Drawings
FIG. 1 is a meridian plane cross-sectional view of a blade root and rim groove assembly of a skewed T-blade root.
Figure 2 is a meridian plane cross-sectional view of a blade root and a rim channel split of a skewed T-blade root.
Figure 3 is a meridian plane cross-sectional view of the root and the rim channel of the T-root taken apart.
FIG. 4 is a schematic diagram of the bearing surface stress of adjacent beveled T-rims.
Fig. 5 shows the variation rule of the maximum stress of the blade root fillet and the maximum stress of the rim groove fillet according to the inclination angle of the bearing surface obtained by finite element calculation.
Detailed Description
The invention will be described in detail below with reference to the attached drawings:
as shown in figure 1, the T-shaped blade root of the turbine blade and the rim groove matched with the T-shaped blade root of the turbine blade comprise an inclined T-shaped blade root 1 of the turbine blade, a spacer strip 2 and a rim groove 3, wherein the spacer strip is arranged between the bottom of the inclined T-shaped blade root and the bottom of the rim groove. The oblique T-shaped blade root of the turbine blade comprises a T-shaped head, a neck, a blade root and a blade body connecting section.
As shown in fig. 1 and 2, the inclined T-shaped blade root 1 has an inclined T-shaped head, so that the inclined T-shaped head bearing surface 101 and the rim groove bearing surface 301 matched with the inclined T-shaped head bearing surface form an included angle theta with the axial direction of the turbine. After assembly, the inclined T-shaped blade root 1 is jacked up by the cushion gap strip 2 at the bottom of the inclined T-shaped blade root, so that the inclined T-shaped head bearing surface 101 and the rim groove bearing surface 301 are mutually attached. The blade root is in contact with the blade body connecting section end face 103 and the rim groove end face 303.
In the working state, the blade root inclined T-shaped head bearing surface 101 and the rim groove bearing surface 301 bear centrifugal force and bending moment load of the blade, and radial displacement of the blade root is restrained. The axial force load of the blade is borne by the blade root, the blade body connecting section end face 103 and the rim groove end face 303, and the axial displacement of the blade root is restrained.
As shown in fig. 2, the bearing surface of the inclined T-shaped head of the blade root and the neck of the blade root are in fillet transition, and a larger fillet radius is preferably adopted on the premise of ensuring that the bearing surface has a certain effective contact area. The rim groove bearing surface and the side wall of the bottom of the rim groove are in fillet transition, and a larger fillet radius is preferably adopted on the premise of ensuring that the bearing surface has a certain effective contact area. And the side wall at the bottom of the rim groove and the bottom surface of the rim groove are in fillet transition, and a larger fillet radius is preferably adopted on the premise of ensuring that the blade root and the rim groove do not interfere.
Therefore, compared with the traditional T-shaped blade root structure shown in fig. 3, the fillet radii of the blade root fillet 102 and the rim groove fillet 302 of the inclined T-shaped blade root are larger than those of the blade root fillet 105 and the rim groove fillet 305 of the T-shaped blade root with the same size, and the included angle between the blade root bearing surface and the side wall of the blade root neck and the included angle between the rim bearing surface and the side wall of the rim groove bottom are increased from right angles to obtuse angles, so that the stress concentration of the fillet is effectively reduced, and the stress level of the blade root and the rim is reduced. When the blade root size is the same, the inclined T-shaped blade root has larger bearing capacity than the T-shaped blade root.
As shown in fig. 4, due to the bearing surface of the oblique T-shaped blade rootPositive pressure F can be decomposed into radial force F r With axial force F a The inclined T-shaped blade root is adopted in the adjacent stage adopting the inclined T-shaped blade root structure as much as possible, so that the bending moment born by the inclined T-shaped rim can be effectively counteracted, and the safety of the rim is improved.
As shown in FIG. 5, the change rule of the maximum stress of the blade root fillet and the maximum stress of the rim groove fillet along with the inclination angle of the bearing surface is obtained through finite element calculation, and therefore, when the value range of the included angle theta is 25 degrees or more and less than or equal to 30 degrees, the maximum stress values of the blade root fillet and the rim groove fillet are comprehensively considered to be relatively low, wherein 25 degrees is taken as the preferred value of the included angle theta.
As shown in fig. 2, due to the oblique bearing surface, when the following tolerances exist simultaneously or partially, 1) radial height tolerance of the left and right sides of the blade root bearing surface 101, 2) angular tolerance of the included angle θ of the left and right sides of the blade root, 3) radial height tolerance of the left and right sides of the rim groove bearing surface 301, and 4) angular tolerance of the included angle θ of the left and right sides of the rim groove are not caused to significantly increase average stress of the oblique T-shaped blade root structure, and also are not caused to cause larger local stress concentration. The two bearing surfaces are insensitive to radial dimension deviation and angle deviation, and have good tolerance adaptability.
The sealing blade of the inclined T-shaped blade root structure is fixed by adopting a radial seam-riding screw rod. The inclined T-shaped blade root has compact axial structure and good manufacturability and universality.
Claims (7)
1. The utility model provides a steam turbine blade T type blade root, includes T type head, neck, blade root and blade body linkage segment, characterized by: the blade root is a circumferentially mounted blade root, a bearing surface of the T-shaped head of the blade root, which is matched with the rim groove, is an inclined surface as seen from a meridian plane sectional view, an included angle theta is formed between the bearing surface of the T-shaped head of the blade root and the axial direction of the steam turbine, and the included angle theta is more than or equal to 25 degrees and less than or equal to 30 degrees, so that an inclined T-shaped head blade root structure is formed; the bearing surfaces of the inclined T-shaped head of the blade root and the neck of the blade root are in fillet transition, and the inclination angles of the bearing surfaces on the left side and the right side of the T-shaped head of the blade root are equal.
2. A T-root according to claim 1, wherein the included angle θ is 25 °.
3. The T-root of claim 1, wherein the angled T-head has an axial width that is less than an axial width of a blade root-blade connection section.
4. The T-root of claim 1, wherein the root is for a rectangular root or a diamond root.
5. A mounting structure for a steam turbine blade comprising a T-blade root as claimed in any one of claims 1 to 4, characterized in that: the radial cross-sectional view shows that the bearing surface of the rim groove matched with the bearing surface of the inclined T-shaped head forms an included angle with the axial direction of the steam turbine, so as to form an inclined T-shaped rim groove structure; the bearing surface of the rim groove and the side wall of the bottom of the rim groove are in round corner transition.
6. The mounting structure for turbine blades as claimed in claim 5, wherein the bearing surfaces on the left and right sides of the rim groove are inclined at equal angles.
7. The mounting structure for a turbine blade according to claim 5, wherein the axial width of the blade root and blade body connecting section and the axial width of the rim groove portion corresponding to the blade root and blade body connecting section are subjected to clearance fit tolerance to axially position the blade; the side wall of the bottom of the rim groove is in fillet transition with the bottom surface of the rim groove; and a spacer strip is arranged between the bottom of the blade root and the bottom of the rim groove.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710680683.3A CN107420135B (en) | 2017-08-10 | 2017-08-10 | T-shaped blade root of turbine blade and matched rim groove thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710680683.3A CN107420135B (en) | 2017-08-10 | 2017-08-10 | T-shaped blade root of turbine blade and matched rim groove thereof |
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| Publication Number | Publication Date |
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| CN107420135A CN107420135A (en) | 2017-12-01 |
| CN107420135B true CN107420135B (en) | 2023-09-19 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201710680683.3A Active CN107420135B (en) | 2017-08-10 | 2017-08-10 | T-shaped blade root of turbine blade and matched rim groove thereof |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112372451B (en) * | 2020-11-05 | 2022-11-08 | 中国航发哈尔滨东安发动机有限公司 | High-precision rotor blade and rim size control method thereof |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19705323A1 (en) * | 1997-02-12 | 1998-08-27 | Siemens Ag | Turbo-machine blade |
| US6033185A (en) * | 1998-09-28 | 2000-03-07 | General Electric Company | Stress relieved dovetail |
| CN1607319A (en) * | 2003-10-16 | 2005-04-20 | Snecma发动机公司 | Apparatus for mounting blade on turbine rotor plate in turbo machine |
| CN201103425Y (en) * | 2007-12-03 | 2008-08-20 | 哈尔滨汽轮机厂有限责任公司 | T blade root used for high pressure cylinder blade of macrotype full rotary speed turbine |
| CN101769172A (en) * | 2008-12-31 | 2010-07-07 | 通用电气公司 | Dovetail rotor blade assembly |
| CN105863742A (en) * | 2014-12-31 | 2016-08-17 | 通用电气公司 | Flowpath boundary and rotor assemblies in gas turbines |
| CN207332951U (en) * | 2017-08-10 | 2018-05-08 | 杭州汽轮动力集团有限公司 | A kind of T-shaped blade root of turbine blade and its flangeway of cooperation |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7594799B2 (en) * | 2006-09-13 | 2009-09-29 | General Electric Company | Undercut fillet radius for blade dovetails |
| US8047797B2 (en) * | 2007-07-16 | 2011-11-01 | Nuovo Pignone Holdings, S.P.A. | Steam turbine and rotating blade |
-
2017
- 2017-08-10 CN CN201710680683.3A patent/CN107420135B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19705323A1 (en) * | 1997-02-12 | 1998-08-27 | Siemens Ag | Turbo-machine blade |
| US6033185A (en) * | 1998-09-28 | 2000-03-07 | General Electric Company | Stress relieved dovetail |
| CN1607319A (en) * | 2003-10-16 | 2005-04-20 | Snecma发动机公司 | Apparatus for mounting blade on turbine rotor plate in turbo machine |
| CN201103425Y (en) * | 2007-12-03 | 2008-08-20 | 哈尔滨汽轮机厂有限责任公司 | T blade root used for high pressure cylinder blade of macrotype full rotary speed turbine |
| CN101769172A (en) * | 2008-12-31 | 2010-07-07 | 通用电气公司 | Dovetail rotor blade assembly |
| CN105863742A (en) * | 2014-12-31 | 2016-08-17 | 通用电气公司 | Flowpath boundary and rotor assemblies in gas turbines |
| CN207332951U (en) * | 2017-08-10 | 2018-05-08 | 杭州汽轮动力集团有限公司 | A kind of T-shaped blade root of turbine blade and its flangeway of cooperation |
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| Publication number | Publication date |
|---|---|
| CN107420135A (en) | 2017-12-01 |
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Address after: No. 357, Shiqiao Road, Xiacheng District, Hangzhou, Zhejiang 310000 Patentee after: Hangzhou Steam Turbine Holding Co.,Ltd. Address before: No. 357, Shiqiao Road, Xiacheng District, Hangzhou, Zhejiang 310000 Patentee before: HANGZHOU TURBINE POWER GROUP CO.,LTD. |