CN114483210A - Steam seal structure between dynamic and static parts of radial flow turbine - Google Patents
Steam seal structure between dynamic and static parts of radial flow turbine Download PDFInfo
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- CN114483210A CN114483210A CN202111612423.5A CN202111612423A CN114483210A CN 114483210 A CN114483210 A CN 114483210A CN 202111612423 A CN202111612423 A CN 202111612423A CN 114483210 A CN114483210 A CN 114483210A
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- steam seal
- steam
- dynamic
- flow turbine
- teeth
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- 230000003068 static effect Effects 0.000 title claims abstract description 39
- 210000004907 gland Anatomy 0.000 claims abstract description 51
- 238000007789 sealing Methods 0.000 claims description 13
- 238000000034 method Methods 0.000 abstract description 12
- 208000035874 Excoriation Diseases 0.000 abstract description 8
- 238000005299 abrasion Methods 0.000 abstract description 8
- 238000009434 installation Methods 0.000 description 7
- 229920001971 elastomer Polymers 0.000 description 6
- 239000000806 elastomer Substances 0.000 description 6
- 230000005284 excitation Effects 0.000 description 6
- 238000004519 manufacturing process Methods 0.000 description 4
- 206010040007 Sense of oppression Diseases 0.000 description 3
- 230000005489 elastic deformation Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
Images
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
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
- F01D11/04—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type using sealing fluid, e.g. steam
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
The invention discloses a steam seal structure between dynamic and static parts of a radial-flow turbine, which comprises a rotating impeller and a stator part, wherein a dynamic and static gap is formed between the rotating impeller and the stator part, and the steam seal structure is characterized in that: the stator component is provided with a mounting groove, and a gland seal body facing the rotating impeller is arranged in the mounting groove; a plurality of annular steam seal grooves are formed in a rotating plane of the rotating impeller opposite to the steam seal body; the steam seal body is provided with inclined steam seal teeth, and the steam seal teeth extend into the steam seal groove to be matched with the rotary impeller for steam seal. By adopting the steam seal structure between the moving and static parts of the radial flow turbine, the collision and abrasion risk between the moving and static parts in the starting and stopping process is reduced, and the steam leakage in the design working condition and variable working condition operation is reduced.
Description
Technical Field
The invention relates to a steam seal structure between a moving part and a static part of a radial-flow turbine, belonging to the technical field of radial-flow turbines.
Background
With the development of the power industry, working media are diversified, and media parameters are extended to a lower direction. The radial-flow turbine has the characteristics of simple and compact structure, simple manufacturing process, convenience in installation, high efficiency, high single-stage expansion ratio and the like. In the fields of new energy and turbines with small flow and high expansion ratio, the radial-flow turbine has certain advantages compared with an axial-flow turbine, and is widely applied to the fields of small and medium-sized gas turbines, new energy turbines and the like.
When the radial-flow turbine runs in practice, steam leakage can occur in a gap between the rotating impeller and the adjacent stator side, the leakage steam not only influences the working environment of a generator set, but also influences the economic efficiency of the generator set, and the influence is more intensified on the application occasions of small flow and large expansion ratio. Meanwhile, when the unit is started or stopped, the metal parts are deformed due to the change of heating conditions, so that relative displacement of the movable parts and the static parts is generated, and the movable and static gaps are changed. The change of the dynamic and static gaps generated by thermal expansion increases the possibility that the dynamic and static parts of the steam seal structure in the prior design collide and grind in the starting and stopping process of the radial-flow turbine, thereby influencing the smooth starting of the turbine. Meanwhile, the axial clearance is increased, and the leakage amount of the steam seal after the turbine stably operates is increased relative to the original design value, so that the economical efficiency is reduced. In addition, when the system operates under variable working conditions, the thermal parameters of the radial turbine level change, gaps between the rotating impeller and the adjacent stator side change along with the thermal parameters, the generated steam leakage is more obvious, the economic efficiency of the unit is seriously influenced, the variable working condition performance of the unit is more difficult to guarantee under the conditions of small flow and large expansion ratio, and the safety of the unit is also greatly influenced. In order to meet the design requirements of a turbine with smaller flow and higher expansion ratio and ensure the economy and safety under the design working condition and the variable working condition of the turbine, a steam seal structure between a dynamic part and a static part of a radial-flow turbine is provided.
Disclosure of Invention
The invention aims to: aiming at the existing problems, the invention provides the steam seal structure between the moving and static parts of the radial flow turbine, which can reduce the collision and abrasion risk between the moving and static parts in the starting and stopping process and reduce the steam leakage in the design working condition and variable working condition operation.
The technical scheme adopted by the invention is as follows:
a steam seal structure between a moving part and a static part of a radial-flow turbine comprises a rotating impeller and a stator part, wherein a moving gap and a static gap are formed between the rotating impeller and the stator part, the stator part is provided with an installation groove, and a steam seal body facing the rotating impeller is arranged in the installation groove;
a plurality of annular steam seal grooves are formed in a rotating plane of the rotating impeller opposite to the steam seal body;
the steam seal body is provided with inclined steam seal teeth, and the steam seal teeth extend into the steam seal groove to be matched with the rotary impeller for steam seal.
In the invention, the steam seal teeth are obliquely inserted into the steam seal teeth, so that the leakage amount and steam leakage loss of the dynamic and static gaps are not increased, and a steam path with a zigzag and multidirectional direction is formed, thereby increasing the flow resistance, reducing the steam leakage amount and effectively ensuring the economical efficiency of a unit; and because rotating impeller is at the rotation in-process, rotating impeller can be to radial expansion, under the condition in the clearance of the same gland tooth and rotating impeller, through setting up the cooperation of inclined gland tooth and gland groove, increase the radial distance in gland tooth and gland groove to when rotating impeller and static part emergence relative movement, can reduce the risk that gland tooth and rotating impeller bump the mill greatly.
Preferably, an elastic body is arranged in the mounting groove, and the elastic body is positioned between the steam seal body and the stator component.
Preferably, the elastic body is elastic plastic or a spring.
In the above scheme, through setting up the elastomer, when comparatively abominable operation condition appears in the miniwatt turbine, the gland casing takes place the mutual contact with the rotation impeller, rotates impeller oppression gland casing and can transmit the elastomer and make the elastomer take place elastic deformation to can offset most oppression, thereby effectively alleviate the bump between gland tooth and the rotation impeller and grind the risk, the production of the dangerous operating mode of greatly reduced unit effectively guarantees the safe operation of unit.
Preferably, the steam seal groove is a tooth-shaped groove consisting of two inclined planes.
Preferably, the gland teeth are perpendicular to the corresponding inclined plane of the gland groove.
Preferably, the steam seal groove comprises a first inclined surface and a second inclined surface, and the steam seal tooth is perpendicular to the first inclined surface and parallel to the second inclined surface.
In the above scheme, the radial distance between the steam seal groove and the rotating impeller can be further increased under the condition of ensuring the clearance between the steam seal teeth and the steam seal groove through vertical arrangement, the collision and abrasion risk is reduced, and the steam flow excitation is weakened.
Preferably, the included angle of the steam seal groove is alpha, the inclination angles of the two inclined planes of the steam seal groove are beta 1 and beta 2, and the inclination angle of the steam seal tooth is beta 3, then
In the scheme, the two inclined planes of the steam seal groove are perpendicular to each other, the two inclined planes are the same in length, and the steam seal tooth is perpendicular to the corresponding inclined plane of the steam seal tooth and parallel to the other inclined plane, so that the distance between the steam seal groove and the other inclined plane is ensured.
Preferably, the gland sealing teeth are plate-shaped.
Preferably, the steam seal teeth are arranged obliquely to the steam inlet side.
In the above scheme, to the steam admission side slope, can flow to the gland seal tooth bottom and receive the hindrance after steam gets into the sound clearance, receive the gland seal tooth to block back steam and pass through from the clearance between gland seal tooth and the gland seal groove again, further increased the tortuous multidirectional flow of leak vapour direction, increase the flow resistance, reduce the volume of leaking vapour.
Preferably, the plurality of gland grooves are connected in sequence.
In the scheme, the steam seal grooves and the steam seal teeth are arranged as many as possible in the limited range of the steam seal body through sequential connection, so that the steam seal performance is improved.
Preferably, the number of the steam seal teeth is the same as that of the steam seal grooves, and the steam seal teeth correspond to the steam seal grooves one to one.
Preferably, the joint of the gland sealing tooth and the gland sealing body is flush with the end part of the gland sealing groove on the rotating plane.
In the scheme, one steam seal tooth corresponds to one steam seal groove, and the steam seal teeth are in one-to-one correspondence, so that the steam seal performance is ensured.
The steam seal structure between the moving and static parts of the radial flow type turbine can reduce the collision and abrasion risks of the moving and static parts in the processes of starting, loading and stopping of the radial flow type turbine, ensure smooth starting, weaken steam flow excitation and ensure safe and reliable operation of a unit; the steam leakage amount of the designed clearance between the steam seal teeth and the rotating impeller is ensured when the unit operates under the designed working condition and the variable working condition, and the economy of the unit is effectively improved.
In summary, due to the adoption of the technical scheme, the invention has the beneficial effects that:
1. in the starting, loading and stopping processes of the low-power turbine, although relative motion exists between the rotating impeller and the stator component, the dynamic and static gaps of the steam seal teeth, which are vertical to the corresponding inclined planes of the steam seal grooves, can basically keep the design values unchanged, the risk of collision and abrasion of the steam seal teeth and the rotating impeller is greatly reduced, the steam flow excitation is weakened, and the smooth starting of a unit is ensured;
2. when the low-power turbine operates under the design condition, the dynamic and static gaps of the steam seal teeth, which are perpendicular to the corresponding inclined planes of the steam seal grooves, keep the design value unchanged, so that the leakage amount and the steam leakage loss between the dynamic and static parts are not increased, the flow direction flows in a zigzag multi-way manner, the flow resistance is increased, the steam leakage amount is reduced, and the economical efficiency of a unit is effectively ensured.
3. When the low-power unit has comparatively abominable operating mode, the elastomer between gland casing and the stator part can effectively alleviate the collision and abrasion risk of gland casing tooth and rotation impeller, and the production of the dangerous operating mode of greatly reduced unit effectively guarantees the safe operation of unit.
4. When the unit operates under variable working conditions, although relative motion exists between the rotating impeller and the stator component, the dynamic and static gaps of the steam seal teeth, which are vertical to the corresponding inclined planes of the steam seal grooves, can basically keep unchanged the design values, and the variable working condition performance of the unit is ensured.
Drawings
The invention will now be described, by way of example, with reference to the accompanying drawings, in which:
FIG. 1 is a schematic view of a vapor seal configuration;
FIG. 2 is an enlarged view of a portion of FIG. 1;
FIG. 3 is an enlarged view of a portion of FIG. 2;
FIG. 4 is a schematic view of a gland tooth and the angle of the gland tooth.
The labels in the figure are: the method comprises the following steps of 1-rotating an impeller, 2-stator parts, 3-steam seal bodies, 4-elastic bodies, 5-steam seal teeth, 11-steam seal grooves, 11 a-first inclined planes, 11 b-second inclined planes, 21-dynamic and static gaps and 22-installation grooves.
Detailed Description
All of the features disclosed in this specification, or all of the steps in any method or process so disclosed, may be combined in any combination, except combinations of features and/or steps that are mutually exclusive.
Any feature disclosed in this specification may be replaced by alternative features serving equivalent or similar purposes, unless expressly stated otherwise. That is, unless expressly stated otherwise, each feature is only an example of a generic series of equivalent or similar features.
As shown in fig. 1, the steam seal structure between the moving and static parts of the radial flow turbine of the present embodiment includes a rotating impeller 1 and a stator part 2, a moving and static gap 21 is formed between the rotating impeller 1 and the stator part 2, the stator part 2 is provided with an installation groove 22, a steam seal body 3 facing the rotating impeller 1 is arranged in the installation groove 22, the steam seal body 3 is in an "i" shape, one end of the steam seal body is positioned in the installation groove 22 for assembly, and the other part of the steam seal body is opposite to the rotating impeller 1;
a plurality of annular tooth-shaped steam seal grooves 11 are formed in the rotating plane of the rotating impeller 1 opposite to the steam seal body 3;
the steam seal body 3 is provided with a plurality of steam seal teeth 5 which incline to the steam inlet side, and the steam seal teeth 5 extend into the steam seal groove 11 to be matched with the rotating impeller 1 for steam seal.
In the embodiment, firstly, the steam seal tooth 5 is obliquely inserted into the steam seal tooth 5 towards the steam inlet side, so that the leakage amount and the steam leakage loss of the dynamic and static gaps 21 are not increased; and a steam path with a zigzag and multidirectional direction is formed, so that the flow resistance of the steam is increased, the steam leakage is reduced, and the economical efficiency of the unit is effectively ensured; the steam enters the dynamic and static gap 21 and then flows to the bottom of the steam seal tooth 5 to be blocked, and the steam after being blocked by the steam seal tooth 5 passes through the gap between the steam seal tooth 5 and the steam seal groove 11, so that the tortuous multi-directional flow in the steam leakage direction is further increased;
secondly under the condition in the clearance of same gland tooth 5 and rotating impeller 1, through setting up the cooperation of inclined gland tooth 5 and profile of tooth gland groove 11, can increase the radial distance between gland tooth 5 and the rotating impeller 1 to when rotating impeller 1 radial expansion, can reduce the risk that gland tooth 5 and rotating impeller 1 bump the mill greatly.
As an alternative to the above embodiment, in other embodiments, the elastic body 4 is disposed in the mounting groove 22, the elastic body 4 is located between the gland casing 3 and the stator component 2, and the elastic body 4 is made of elastic plastic; when comparatively abominable operation operating mode appears in the miniwatt turbine, gland casing 3 takes place the mutual contact with rotating impeller 1, and rotating impeller 1 oppresses gland casing 3 and can transmit elastomer 4 and make elastomer 4 take place elastic deformation to can offset most oppression, thereby effectively alleviate the bump between gland tooth 5 and the rotating impeller 1 and grind the risk, the production of the dangerous operating mode of greatly reduced unit effectively guarantees the safe operation of unit.
As an alternative to the above embodiments, in other embodiments, as shown in fig. 4, the gland teeth 5 are perpendicular to the corresponding inclined surfaces of the gland groove 11, and the axial distance is increased under the condition of a certain clearance, so that the collision and abrasion risk is reduced, and the steam flow excitation is weakened.
As an alternative to the above embodiment, in another embodiment, the included angle of the gland groove 11 is α, the inclination angles of the two inclined surfaces of the gland groove 11 are β 1 and β 2, and the inclination angle of the gland tooth 5 is β 3, so that β 1 ═ β 2 ═ β 3 ═ 1/2 α, and the optimum design effect can be ensured under this setting.
As an alternative to the above-described embodiment, in other embodiments, the gland teeth 5 are plate-shaped.
As an optional manner of the above embodiment, in other embodiments, a plurality of the steam seal grooves 11 are sequentially connected, so that the steam seal grooves 11 and the steam seal teeth 5 are arranged as many as possible within a limited range of the steam seal body 3, and the steam seal performance is improved.
As an optional way of the above embodiment, in other embodiments, the number of the gland sealing teeth 5 is the same as that of the gland sealing grooves 11, the gland sealing teeth 5 correspond to the gland sealing grooves 11 one to one, and the joint of the gland sealing teeth 5 and the gland sealing body 3 is flush with the end of the gland sealing groove 11 on the rotation plane, so as to ensure the gland sealing performance.
Of course, in the above embodiment, the number of the gland teeth 5 and the gland grooves 11 may be set as required.
Through the arrangement of the invention, as shown in fig. 3, the distance between the steam seal tooth 5 and the first inclined plane 11a is the gap between the steam seal tooth 5 and the rotating impeller 1, the gap between the steam seal tooth 5 and the second inclined plane 11b is the radial distance, when the design is carried out, under the condition that the gap between the steam seal tooth 5 and the first inclined plane 11a is not changed, the larger gap between the steam seal tooth 5 and the second inclined plane 11b is set according to the situation, when the rotating impeller 1 is radially expanded, the gap between the steam seal tooth 5 and the first inclined plane 11a can not be changed, the gap between the steam seal tooth 5 and the second inclined plane 11b can be changed, as long as the proper gap between the steam seal tooth 5 and the second inclined plane 11b is set, the steam seal tooth 5 and the rotating impeller 1 can not be collided with each other, and the risk of the impeller tooth 5 and the rotating impeller 1 being collided with each other is greatly reduced, and the steam flow excitation is weakened.
In conclusion, by adopting the steam seal structure between the moving and static parts of the radial-flow turbine, the collision and abrasion risks of the moving and static parts in the starting, loading and stopping processes of the radial-flow turbine can be reduced, the smooth starting is ensured, the steam excitation is weakened, and the safe and reliable operation of a unit is ensured; the steam leakage amount of the designed clearance between the steam seal teeth and the rotating impeller is ensured when the unit operates under the designed working condition and the variable working condition, and the economy of the unit is effectively improved.
The invention is not limited to the foregoing embodiments. The invention extends to any novel feature or any novel combination of features disclosed in this specification and any novel method or process steps or any novel combination of features disclosed.
Claims (10)
1. The utility model provides a vapor seal structure between radial-flow type turbine sound part, includes impeller (1) and stator part (2) of rotating, has sound clearance (21) between impeller (1) and stator part (2) its characterized in that: the stator component (2) is provided with a mounting groove (22), and a gland sealing body (3) facing the rotary impeller (1) is arranged in the mounting groove (22);
a plurality of annular steam seal grooves (11) are arranged on a rotating plane of the rotating impeller (1) opposite to the steam seal body (3);
the steam seal body (3) is provided with inclined steam seal teeth (5), and the steam seal teeth (5) extend into the steam seal groove (11) to be matched with the rotating impeller (1) for steam seal.
2. The steam seal structure between the dynamic and static parts of radial flow turbine as claimed in claim 1, wherein: an elastic body (4) is arranged in the mounting groove (22), and the elastic body (4) is positioned between the steam seal body (3) and the stator component (2).
3. The steam seal structure between the dynamic and static parts of radial flow turbine as claimed in claim 2, wherein: the elastic body (4) is elastic plastic or a spring.
4. The steam seal structure between the dynamic and static parts of radial flow turbine as claimed in claim 1, wherein: the steam seal groove (11) is a tooth-shaped groove consisting of two inclined planes.
5. The steam seal structure between the dynamic and static parts of radial flow turbine as claimed in claim 4, wherein: the steam seal teeth (5) are vertical to the corresponding inclined planes of the steam seal grooves (11).
6. The steam seal structure between the dynamic and static parts of radial flow turbine as claimed in claim 4, wherein: the included angle of the steam seal groove (11) is alpha, the inclination angles of two inclined planes of the steam seal groove (11) are beta 1 and beta 2, the inclination angle of the steam seal tooth (5) is beta 3, and then beta 1 ═ beta 2 ═ beta 3 ═ 1/2 alpha.
7. The steam seal structure between the dynamic and static parts of radial flow turbine as claimed in claim 1, wherein: the steam seal teeth (5) are plate-shaped.
8. The steam seal structure between the dynamic and static parts of radial flow turbine as claimed in claim 1, wherein: the steam seal teeth (5) are obliquely arranged towards the steam inlet side.
9. The steam seal arrangement between moving and stationary parts of a radial flow turbine as claimed in claim 1, wherein: the steam seal grooves (11) are connected in sequence.
10. The steam seal structure between the dynamic and static parts of radial flow turbine as claimed in claim 1, wherein: the number of the steam seal teeth (5) is the same as that of the steam seal grooves (11), and the steam seal teeth (5) correspond to the steam seal grooves (11) one to one.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111612423.5A CN114483210B (en) | 2021-12-27 | 2021-12-27 | Steam seal structure between dynamic and static parts of radial turbine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111612423.5A CN114483210B (en) | 2021-12-27 | 2021-12-27 | Steam seal structure between dynamic and static parts of radial turbine |
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| CN114483210A true CN114483210A (en) | 2022-05-13 |
| CN114483210B CN114483210B (en) | 2024-02-13 |
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| CN114483210B (en) | 2024-02-13 |
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