CN107420135A - A kind of T-shaped blade root of turbine blade and its flangeway of cooperation - Google Patents
A kind of T-shaped blade root of turbine blade and its flangeway of cooperation Download PDFInfo
- Publication number
- CN107420135A CN107420135A CN201710680683.3A CN201710680683A CN107420135A CN 107420135 A CN107420135 A CN 107420135A CN 201710680683 A CN201710680683 A CN 201710680683A CN 107420135 A CN107420135 A CN 107420135A
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- Prior art keywords
- blade root
- blade
- flangeway
- root
- loading end
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- 230000007704 transition Effects 0.000 claims abstract description 12
- 238000009434 installation Methods 0.000 claims description 3
- 238000005516 engineering process Methods 0.000 abstract description 4
- 230000007812 deficiency Effects 0.000 abstract description 2
- 238000000034 method Methods 0.000 description 7
- 238000006243 chemical reaction Methods 0.000 description 5
- 230000004308 accommodation Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000007373 indentation Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000035945 sensitivity Effects 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
The present invention relates to a kind of T-shaped blade root of turbine blade, including T connector portion, neck, blade root and blade linkage section, it is characterized in that：From meridian plane sectional view, loading end that blade root T connector portion and flangeway coordinate be inclined plane, and blade root T connector portion's loading end and steam turbine axis direction have angle θ, form oblique T connector portion leaf and root structure；With round-corner transition between the oblique T connector portion loading end of blade root and blade neck.The span of the angle is 25 °≤θ≤30 °, is preferred with 25 °.The present invention solves the technological deficiency of the T-shaped blade root of tradition, one kind is provided and avoids the larger stress concentration of T-shaped blade root fillet and flangeway fillet, and with the oblique flangeway of T-shaped blade root and its cooperation of the novel steam turbine blade that security is higher, technology difficulty is relatively low, compact-sized, convenient for assembly.
Description
Technical field
The present invention relates to a kind of steam turbine blade, especially a kind of blade root for reaction turbine movable vane piece and its
The flangeway of cooperation.
Background technology
Reaction turbine generally use rotary drum rotor, compared with Wheel-type rotor, the adjacent level of rotary drum rotor
Material is continuous between flangeway.The movable vane piece blade root form commonly used on rotary drum rotor has：T-shaped blade root, double-T shaped blade root, fork
Type blade root, fir-tree root etc., the blade root of this several form mainly have following characteristics.
T-shaped blade root：Simple in construction, reliable operation is easy to process.Blade root is circumferentially assembled, and the flangeway of fixed blade root is at least
A breach need to be opened up, so that blade radially loads flangeway successively from indentation, there, and leaf will be sealed by radial direction junction of the edges of two sheets of paper screw rod
Piece is fixed on gap position.T-shaped blade root bearing capacity is smaller, suitable for the less blade of centrifugal force.
Double-T shaped blade root：More T-shaped blade root increases by a pair of loading ends, to ensure loading end uniform force, blade root and flangeway
The size tolerance requirements of loading end are higher, and difficulty of processing is larger.It is similar with T-shaped blade root, double-T shaped blade root also circumferentially assembling, it is necessary to
Breach is opened up in the flangeway of fixed blade root, so that blade radially loads flangeway successively from breach.Due to double-T shaped blade root radially
Size is generally large, and the radial direction junction of the edges of two sheets of paper screw for locking sealing blade is deeper, and difficulty of processing is also larger.Further, since blade root
Volume is relatively large, and the proportion that the centrifugal force of leaf root part accounts for the total centrifugal force of blade is larger, weakens blade root to a certain extent
Bearing capacity, in general, double-T shaped blade root bearing capacity are larger, suitable for the blade that centrifugal force is larger.
Multifork root：Process it is more convenient, blade root fork be inserted radially into groove corresponding to wheel rim, fixed by axial pin.Fork
Number is more, and bearing capacity is stronger, the larger regulating stage blade of the exhaust stage blade or root footpath suitable for that can process axial pin nail.
Fir-tree root：Loading end is more, and requirement on machining accuracy is higher, and technique is more complicated.Blade root is by axially loading blade root
Groove, in addition to final stage and governing stage, when fir-tree root is used for other grade, more axial space need to be reserved between level for assembling
With.Compared with the blade root of other several types, under same blade size, the bearing capacity highest of fir-tree root, it is applicable
In last several grade blades or regulating stage blade that load is larger.
For reaction turbine rotary drum rotor, although the bearing capacity of multifork root and fir-tree root is larger,
But limited by assembly space, machining accuracy and cost, constrain its use；And double-T shaped blade root is also because of technique and assembling aspect
Factor made troubles to use.From the point of view of blade processing, assembling, other levels in addition to final stage and governing stage, using T
Type blade root is preferred.When T-shaped blade root is used for medium altitude blade or larger what low pressure blade of end of centrifugal force, because it holds
Loading capability is limited, it has to improves bearing capacity by increasing blade root size, reduces stress level.But with blade root size
Increase, on the one hand, the proportion that the centrifugal force of leaf root part accounts for the total centrifugal force of blade increases, and the stress of blade root and wheel rim may not drop
It is anti-to rise；On the other hand, the diameter of the junction of the edges of two sheets of paper screw of blade is sealed for locking, depth all accordingly increases, difficulty of processing rising.This
Both sides factor last what low pressure blade larger to medium altitude blade or centrifugal force brings unfavorable shadow using T-shaped blade root
Ring.
The content of the invention
Problem to be solved by this invention is：Medium altitude blade or centrifugal force on reaction turbine rotary drum rotor
What larger last low pressure blade, according to T-shaped blade root, easily produces larger stress collection in blade root fillet and flangeway fillet
In, influence blade safe operation；According to double-T shaped blade root, reduce although blade root fillet and flangeway crankshaft fillets stress are concentrated,
But blade root and flangeway technological requirement are higher, and last years assembling inconvenience；According to multifork root, in addition to final stage and governing stage, nothing
Method processes pin hole in the confined space；According to fir-tree root, in addition to final stage and governing stage, need to be reserved between level more
Axial space is for assembling, and technological requirement is higher.
Consider above-mentioned several leaf and root structures, can meet that limited fit-ting space, easy to assembly and processing technology are difficult simultaneously
Under conditions of degree, exclude other several leaf and root structures and select T-shaped leaf and root structure as on reaction turbine rotary drum rotor
Medium altitude blade or larger what the last low pressure blade of centrifugal force blade root.
On this basis, solves the T-shaped blade root technological deficiency of tradition, there is provided one kind avoids T-shaped blade root fillet and flangeway from justifying
The larger stress concentration in angle, and with the novel steam turbine leaf that security is higher, technology difficulty is relatively low, compact-sized, convenient for assembly
The oblique flangeway of T-shaped blade root and its cooperation of piece.
The present invention provides a kind of T-shaped blade root of turbine blade, including T connector portion, neck, blade root and blade linkage section, its
It is characterized in：From meridian plane sectional view,
1) loading end that blade root T connector portion coordinates with flangeway is inclined plane, blade root T connector portion's loading end and turbine shaft
Line direction has angle θ, forms oblique T connector portion leaf and root structure；With fillet between the oblique T connector portion loading end of blade root and blade neck
Transition.
2) tilt angle theta of loading end is equal in magnitude at left and right sides of blade root T connector portion.
3) span of the angle is 25 °≤θ≤30 °, with 25 ° for optimal angle.
4) tiltedly the axial width in T connector portion is small compared with blade root and the axial width of blade linkage section.
5) blade root uses gap fit tolerance with blade linkage section axial width with this section of flangeway axial width, makes blade
Axially position.
6) have necessarily in guarantee loading end with round-corner transition between the oblique T connector portion loading end of blade root and blade neck
On the premise of effective contact area, preferably using larger radius of corner.
Further improve is：The blade root is the blade root circumferentially installed.
Further improve is：The blade root is not only suitable for rectangle blade root, is applied to rhombus blade root again.
Further improve is：Steam turbine adjacent level blade root can use the blade root.
The present invention provides a kind of flangeway coordinated with T-shaped blade root, it is characterized in that：From meridian plane sectional view,
1) have angle θ with the flangeway loading end and steam turbine axis direction of the cooperation of oblique T connector portion loading end, is formed oblique
T-shaped wheel rim slot structure；With round-corner transition between flangeway loading end and flangeway bottom sidewall.
2) angle of inclination of loading end is equal in magnitude at left and right sides of flangeway；
3) span of the angle is 25 °≤θ≤30 °, is preferred with 25 °.
4) blade root uses gap fit tolerance with blade linkage section axial width with this section of flangeway axial width, makes blade
Axially position；
5) have between flangeway loading end and flangeway bottom sidewall with round-corner transition in guarantee loading end with certain
On the premise of imitating contact area, preferably using larger radius of corner；
6) ensureing what blade root was not interfered with flangeway between flangeway bottom sidewall and wheel rim groove bottom with round-corner transition
Under the premise of, preferably using larger radius of corner；
7) installation pad gap bar between blade root bottom and wheel rim groove bottom.
Relative to prior art, the invention has the advantages that：
1st, due to oblique T-shaped leaf and root structure, normal pressure F suffered by its loading end is made to can be analyzed to radial load FrWith axial force Fa, together
When, blade root loading end and the angle, wheel rim loading end and the angle of flangeway bottom sidewall of blade neck side wall are increased by right angle
For obtuse angle, concentrated so as to effectively reduce crankshaft fillets stress, reduce the stress level of blade root and wheel rim, improve blade security.When
When blade root size dimension is identical, the oblique T-shaped more T-shaped blade root of blade root possesses bigger bearing capacity.
2nd, be advantageous to suitably reduce blade root size, the centrifugal force for reducing leaf root part accounts for the proportion of the total centrifugal force of blade, fills
The strength of materials performance of blade root and wheel rim is waved in distribution, suitable for the medium level above blade that centrifugal force is larger.
3rd, two loading ends are insensitive to radial direction dimensional discrepancy, angular deviation, have preferable tolerance accommodation.
4th, axial arrangement is compact.
5th, there is good manufacturability, suitable for most of turbine blades circumferentially installed, be advantageous to promote.
Brief description of the drawings
Fig. 1 is blade root and the meridian plane sectional view of flangeway assembling of oblique T-shaped blade root.
The meridian plane sectional view that Fig. 2 is the blade root of oblique T-shaped blade root and flangeway is split.
The meridian plane sectional view that Fig. 3 is the blade root of T-shaped blade root and flangeway is split.
Fig. 4 is adjacent tiltedly T-shaped wheel rim loading end stress diagram.
Fig. 5 is that the blade root fillet maximum stress that is obtained through FEM calculation and flangeway fillet maximum stress incline with loading end
The changing rule of rake angle.
Embodiment
Detailed introduction is done to the present invention below in conjunction with accompanying drawing：
As shown in figure 1, the flangeway of a kind of T-shaped blade root of turbine blade and its cooperation, including the oblique T-shaped leaf of turbine blade
Root 1, pad gap bar 2, flangeway 3, tiltedly gap bar is padded in installation between T-shaped blade root bottom and wheel rim groove bottom.The oblique T-shaped leaf of turbine blade
Root includes T connector portion, neck, blade root and blade linkage section.
As shown in Figure 1 and Figure 2, tiltedly T-shaped blade root 1 has oblique T connector portion, therefore forms oblique T connector portion loading end 101 and its
The flangeway loading end 301 of cooperation has angle θ with steam turbine axis direction.After assembling, oblique T-shaped blade root 1 is by its bottom
Pad gap bar 2 jacks up, and oblique T connector portion loading end 101, flangeway loading end 301 is mutually adjacent to.Blade root and blade linkage section end face
103rd, flangeway end face 303 contacts with each other.
Under working condition, the oblique T connector portion loading end 101 of blade root, flangeway loading end 301 bear the centrifugal force of blade and curved
Square load, constrain the radial displacement of blade root.Blade root bears the axle of blade with blade linkage section end face 103, flangeway end face 303
To power load, the axial displacement of blade root is constrained.
Such as Fig. 2, with round-corner transition between the oblique T connector portion loading end of blade root and blade neck, ensureing loading end with one
On the premise of fixed effective contact area, preferably using larger radius of corner.Flangeway loading end and flangeway bottom sidewall it
Between with round-corner transition, on the premise of ensureing that loading end has certain effective contact area, preferably using larger radius of corner.
And with round-corner transition between flangeway bottom sidewall and wheel rim groove bottom, in the premise that guarantee blade root is not interfered with flangeway
Under, preferably using larger radius of corner.
Therefore, contrasted with traditional T-shaped leaf and root structure as shown in Figure 3, blade root fillet 102, the flangeway circle of oblique T-shaped blade root
The radius of corner at angle 302 is big compared with the radius of corner of the blade root fillet 105 of the T-shaped blade root of same size, flangeway fillet 305, and
And blade root loading end and the angle, wheel rim loading end and the angle of flangeway bottom sidewall of blade neck side wall are increased to by right angle
Obtuse angle, concentrated so as to effectively reduce crankshaft fillets stress, reduce the stress level of blade root and wheel rim.When blade root size dimension is identical
When, the oblique T-shaped more T-shaped blade root of blade root possesses bigger bearing capacity.
As shown in figure 4, because normal pressure F suffered by oblique T-shaped blade root loading end can be analyzed to radial load FrWith axial force Fa, should
So can effectively it be offset suffered by oblique T-shaped wheel rim also using oblique T-shaped blade root in the adjacent level using oblique T-shaped leaf and root structure as far as possible
Moment of flexure, so as to increase the security of wheel rim.
As shown in figure 5, blade root fillet maximum stress and flangeway fillet maximum stress are obtained with carrying through FEM calculation
The changing rule at face angle of inclination, it is seen that when the span of angle theta is 25 °≤θ≤30 °, consider blade root fillet and
The maximum stress value of flangeway fillet is relatively low, wherein, 25 ° of preferred values as angle theta.
As shown in Fig. 2 due to loading end is tilting, when following tolerance simultaneously or partially in the presence of, 1) blade root carrying
The left and right sides radial height tolerance of face 101,2) angle tolerance of angle theta, 3) flangeway loading end 301 or so at left and right sides of blade root
The angle tolerance of both sides radial height tolerance, 4) flangeway left and right sides angle theta, it is unlikely to cause the flat of oblique T-shaped leaf and root structure
Equal stress substantially rises, and does not also cause bigger stress raisers.Two loading ends to radial direction dimensional discrepancy, angular deviation not
Sensitivity, there is preferable tolerance accommodation.
The sealing blade of oblique T-shaped leaf and root structure is fixed using radial direction junction of the edges of two sheets of paper screw rod.Oblique T-shaped blade root axial arrangement is compact, tool
There are good manufacturability and versatility.
Claims (10)
1. a kind of T-shaped blade root of turbine blade, including T connector portion, neck, blade root and blade linkage section, it is characterized in that：From meridian
Face sectional view, the loading end that blade root T connector portion coordinates with flangeway is inclined plane, blade root T connector portion's loading end and steamer
Machine axis direction has angle θ, forms oblique T connector portion leaf and root structure；Between the oblique T connector portion loading end of blade root and blade neck with
Round-corner transition.
2. T-shaped blade root according to claim 1, it is characterised in that at left and right sides of blade root T connector portion the inclination angle of loading end
It is equal in magnitude to spend θ.
3. T-shaped blade root according to claim 1, it is characterised in that the span of the angle theta is 25 °≤θ≤30 °.
4. T-shaped blade root according to claim 3, it is characterised in that the angle theta is preferred with 25 °.
5. T-shaped blade root according to claim 1, it is characterised in that the axial width in the tiltedly T connector portion is compared with blade root and leaf
The axial width of body linkage section is small；Blade root is coordinated with blade linkage section axial width with this section of flangeway axial width using gap
Tolerance, make blade axially position.
6. T-shaped blade root according to claim 1, it is characterised in that the blade root is the blade root circumferentially installed, described
Blade root is not only suitable for rectangle blade root, is applied to rhombus blade root again.
7. according to any described T-shaped blade roots of claim 1-6, it is characterised in that steam turbine adjacent level can use the knot
Structure blade root.
8. a kind of flangeway coordinated with T-shaped blade root, it is characterized in that：From meridian plane sectional view,
Flangeway loading end and the steam turbine axis direction coordinated with oblique T connector portion loading end has angle θ, forms tiltedly T-shaped wheel
Edge slot structure；With round-corner transition between flangeway loading end and flangeway bottom sidewall.
9. flangeway according to claim 8, it is characterised in that the angle of inclination size of loading end at left and right sides of flangeway
It is equal；The span of the angle is 25 °≤θ≤30 °.
10. flangeway according to claim 8, it is characterised in that blade root and blade linkage section axial width and the section wheel
Edge groove axial width uses gap fit tolerance, makes blade axially position；Between flangeway bottom sidewall and wheel rim groove bottom with
Round-corner transition；Installation pad gap bar between blade root bottom and wheel rim groove bottom.
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 |
|---|---|
| CN107420135A true CN107420135A (en) | 2017-12-01 |
| CN107420135B CN107420135B (en) | 2023-09-19 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| 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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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112372451A (en) * | 2020-11-05 | 2021-02-19 | 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 |
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| 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 |
| US20080063529A1 (en) * | 2006-09-13 | 2008-03-13 | General Electric Company | Undercut fillet radius for blade dovetails |
| 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 |
| US20090022595A1 (en) * | 2007-07-16 | 2009-01-22 | Lorenzo Cosi | Steam turbine and rotating blade |
| 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 |
-
2017
- 2017-08-10 CN CN201710680683.3A patent/CN107420135B/en active Active
Patent Citations (9)
| 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 |
| US20080063529A1 (en) * | 2006-09-13 | 2008-03-13 | General Electric Company | Undercut fillet radius for blade dovetails |
| US20090022595A1 (en) * | 2007-07-16 | 2009-01-22 | Lorenzo Cosi | Steam turbine and rotating blade |
| 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 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112372451A (en) * | 2020-11-05 | 2021-02-19 | 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 |
| 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107420135B (en) | 2023-09-19 |
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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. |
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