CN113833540B - Diffuser structure with axially adjustable outer ring end wall - Google Patents
Diffuser structure with axially adjustable outer ring end wall Download PDFInfo
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- CN113833540B CN113833540B CN202111078707.0A CN202111078707A CN113833540B CN 113833540 B CN113833540 B CN 113833540B CN 202111078707 A CN202111078707 A CN 202111078707A CN 113833540 B CN113833540 B CN 113833540B
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- diffuser
- outer ring
- end wall
- ring end
- endwall
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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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/30—Exhaust heads, chambers, or the like
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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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
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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
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
The invention provides a diffuser structure with an axially adjustable outer ring end wall, wherein the diffuser outer ring end wall can move forwards and backwards along the axial direction, so that the axial length of the profile of the diffuser outer ring end wall and the area of an outlet of the diffuser are changed. The diffuser end wall structure of the present invention serves as two: firstly, the exhaust system is suitable for the requirements of the gas turbine and the steam turbine on the exhaust system due to the working condition change; and the device is suitable for a circumferentially uneven flow field caused by a single-side exhaust/steam structure. The adjusting condition of the axial adjustable diffuser provided by the invention is as follows: when the unit runs at full load or overload, the outer ring end wall of the diffuser moves towards the upstream turbine direction, so that the axial length of the diffuser is reduced, and the flow passage area and the inlet-outlet area ratio of the diffuser outlet are increased under the condition that the inner ring end wall is unchanged, thereby improving the pressure expansion capability; and when the low-load operation is performed, the diffuser moves away from the turbine, so that the axial length of the end wall of the outer ring of the diffuser is increased, the area ratio of the outlet flow channel to the inlet and outlet area of the diffuser is reduced, and the flow separation of an exhaust system is avoided.
Description
Technical Field
The invention belongs to the technical field of gas turbines and steam turbines, relates to an outer ring end wall axial adjustable diffuser structure, and in particular relates to an outer ring end wall axial adjustable diffuser structure suitable for a single-side radial exhaust/steam system.
Background
The exhaust/steam system at the downstream of the turbine plays a role in recovering the kinetic energy of the last-stage turbine residual speed and guiding the airflow, and is an important component of a gas turbine and a steam turbine unit. When the exhaust gas/steam is radially exhausted from one side, the airflow is overturned from the axial direction to the radial direction while the airflow is diffused and flows in the exhaust gas/steam system, so that a non-axisymmetric flow field is generated on the section of the turbine outlet, and the airflow speeds at different circumferential positions of the inlet of the exhaust gas/steam diffuser are different. In addition, the flow field distribution of the section of the turbine outlet also affects the flow field in the exhaust system, so that the diffuser of the exhaust system is subjected to flow separation, the recovery capability of the diffuser of the exhaust system on the residual speed kinetic energy of the final turbine outlet is reduced or even completely lost, and meanwhile, the flow loss is increased.
The system is a marine gas engine or a gas engine with a deep flexibility peak regulation function in a power grid, and in the actual working process, the working condition changes frequently, and the conditions of partial load and small flow are normalized. Under partial load and low flow conditions, various forms of flow separation are more likely to occur in the turbine and exhaust/steam system. On the one hand, the flow separation in the exhaust gas/steam diffuser can significantly deteriorate the aerodynamic performance in the turbine and the exhaust gas/steam system, the output power of the turbine is reduced, and even the working state of the final turbine is changed into a blasting state (the output power is negative); on the other hand, the dynamic stress in the blade can be obviously increased, the vibration amplitude of the blade is increased, the self-excited vibration of the turbine blade can be possibly caused, the flutter phenomenon similar to that of the compressor blade can be generated, and the operation safety of the blade is greatly influenced.
In the past, the integrated pneumatic optimization design of the turbine and the exhaust/steam system is carried out at a certain operating condition point, and the performance of the turbine and the exhaust/steam system can be improved to a certain extent, but as the load and the flow are reduced, the original design cannot adapt to the change of the flow condition, so that obvious flow separation still occurs in the turbine and the exhaust/steam system, and the performance of the turbine and the exhaust/steam system is deteriorated.
Chinese patent application CN112302741a discloses a diffuser with adjustable end wall, the annular end wall of the diffuser is formed by splicing multiple sections of sectors, and the tangential direction and the axial direction of each section of sector can be adjusted to make the annular end wall deflect or zoom. The diffuser has the advantages of being applicable to the change of the operation condition, improving the flow separation of a turbine and an exhaust system under the variable condition, reducing the back pressure of a turbine outlet, improving the pneumatic performance of the turbine outlet and the turbine system under the non-design condition, improving the efficiency of a unit, being beneficial to adapting to the non-axisymmetric structure of a volute of a single-side radial exhaust (steam) system, weakening the non-axisymmetric degree of the back pressure of the final-stage turbine outlet section caused by the single-side radial exhaust (steam) and the low-frequency aerodynamic force caused by a movable blade table, and the like, but having more movable parts, leading the processing to the actual adjustment operation to be more complicated and being difficult to realize. And the end wall only rotates along the circumference of the root, and the axial adjustment range is limited.
Disclosure of Invention
In order to overcome the defects and shortcomings in the prior art, the invention aims to provide an axially adjustable diffuser structure of an outer ring end wall of a single-side radial exhaust/steam system, which is different from the diffuser design thought and structural form of the existing fixed end wall, wherein the outer ring end wall of the diffuser can move forwards and backwards along the axial direction, the axial moving distances of the outer ring end wall at different circumferential positions can be the same or different, the diffuser structure can adapt to the requirement of a circumferentially uneven flow field produced by a non-axial symmetrical exhaust/steam volute, can adapt to different operation conditions, improves the thermal efficiency and the operation safety of turbine blades of a turbine unit, is suitable for a gas turbine of the single-side radial exhaust/steam and a diffuser in the turbine exhaust/steam system, and is relatively simple in processing, mounting and using operation, and has a large axial adjustment range.
In order to achieve the above purpose, the technical solution of the present invention is:
the diffuser structure with axially adjustable outer ring end wall is arranged at the flat-penetrating outlet of a single-side radial exhaust/steam system, and comprises a diffuser outer ring end wall and a diffuser inner ring end wall which are arranged in a volute, wherein the diffuser inner ring end wall is fixedly arranged in the volute, a circumferential space between the diffuser outer ring end wall and the diffuser inner ring end wall is formed into a diffuser runner,
the outer ring end wall of the diffuser comprises a cylindrical section with a constant diameter and an expansion section arranged at the downstream end of the cylindrical section;
the diffuser outer ring end wall can move forwards and backwards along the axial direction, so that the axial length L of the diffuser outer ring end wall molded surface is adjusted, the axial length L is the axial distance between the outlet edge of the diffuser outer ring end wall molded surface and the through flat outlet, and when the diffuser outer ring end wall moves along the axial direction, the inlet area A of the diffuser runner 0 Remain unchanged, outlet area A 1 Gradually shrinking or increasing;
the axial length L increases as the diffuser outer ring endwall moves axially downstream, the diffuser outer ring endwall gradually approaching the diffuser inner ring endwall in an axial direction, the diffuser flow passage outlet area A 1 The inlet-outlet area ratio of the diffuser flow passage is reducedAnd the gradient of the change of the flow area in the diffuser flow channel is reduced;
the axial length L decreases as the diffuser outer ring endwall moves axially upstream, the diffuser outer ring endwall gradually moving axially away from the diffuser inner ring endwall, the diffuser flow passage outlet area A 1 Increasing the inlet-outlet area ratio of the diffuser flow passageAnd the gradient of the change of the flow area in the diffuser flow channel is increased.
The diffuser structure with the axially adjustable outer ring end wall, which is applicable to a single-side radial exhaust/steam system, can be in any form and any structural shape with axial symmetry and non-axial symmetry, and the geometric parameter of the axial length of the diffuser is changed by adjusting the axial position of the outer ring end wall of the diffuser, so that the flow passage area of the diffuser is reduced or increased.
Preferably, the diffuser outer ring end wall has an axial length adjustment value that may be the same or different along a circumference, thereby forming an axisymmetric or non-axisymmetric diffuser structure.
Preferably, the adjusting value of the axial length of the end wall of the outer ring of the diffuser is determined according to the turbine outlet flow field under the working condition of the adjusting value; under the design working condition, when the flow rate of an inlet of an exhaust/steam system is increased, the end wall of the outer ring of the diffuser moves towards the upstream direction close to the turbine, so that the axial length of the end wall of the outer ring of the diffuser is reduced, and the flow passage area of the diffuser is increased; under the low flow condition, when the flow speed of an inlet of an exhaust system is reduced, the end wall of the outer ring of the diffuser moves towards the downstream direction far away from the turbine, so that the axial length of the diffuser is increased, and the flow passage area of the diffuser is reduced.
Preferably, the adjusting value of the axial length of the outer ring end wall of the diffuser is according to a circumferential uneven flow field of the diffuser inlet along a circumferential variation rule.
Preferably, the adjusting value of the axial length of the outer ring end wall of the diffuser ensures that the expansion coefficient of the outer ring end wall of the diffuser is maximum at each working point, and the circumferential uneven coefficient of the inlet is minimum, namely the aerodynamic performance of the exhaust system is optimal.
Preferably, the axial length of the end wall of the outer ring of the diffuser changes the axial position of the end wall of the outer ring of the diffuser under the condition of non-design working condition, and the change range of the flow passage area of the diffuser is required to be 0.923-1.786 times of the flow passage area of the diffuser under the design working condition, and the specific value is determined according to the actual design.
Compared with the prior art, the diffuser structure with the axially adjustable outer ring end wall has the advantages that:
1. the method is suitable for the actual flow field change of the final turbine outlet under different working conditions, ensures that the steam exhaust system has good pressure expansion capability under the wide operating conditions of the unit, reduces the back pressure of the turbine outlet, increases the turbine output and improves the thermal efficiency of the unit.
2. The turbine blade is suitable for the steam exhaust volute of the single-side radial steam exhaust, weakens the circumferential non-uniformity degree of the flow in the single-side radial steam exhaust system, reduces the fluctuation of the final turbine blade load and aerodynamic force in a circle, and improves the running safety of the unit.
3. The diffuser structure with the axially adjustable outer ring end wall is suitable for a single-side radial exhaust/steam system, and the adjustable end wall is self-integrated, and is simple in structure and convenient to operate. The circumferential change of the end wall has continuity, uniform transition, wider axial adjustment range and stronger adaptability to different operation conditions.
Drawings
FIG. 1 is a schematic cross-sectional view of an inner and outer ring end wall of a diffuser and a typical single-sided exhaust system. 1 is the diffuser outer ring end wall and 2 is the diffuser inner ring end wall.
Fig. 2 is geometric parameters of the diffuser outer ring endwall: axial length L, initial divergence angle alpha, outlet area A 1 Inlet area A 0 。
FIG. 3 shows diffuser outer ring end wall axial length full circumference adjustment values being the sameSchematic diagram and geometric parameters on vertical bisection plane. 3 is a diffuser outer ring end wall indication in an initial state, and the outer ring end wall parameter is L 1 、α、A 1 (outlet area), 4 is a representation of the diffuser outer ring end wall after the diffuser outer ring end wall moves away from the turbine under specific conditions, and the outer ring end wall parameter is L 1 ’、α、A 1 ’。
FIG. 4 is a schematic illustration of diffuser outer ring endwall axial length circumferential adjustment values that are not identical. 5 is a diffuser outer ring end wall schematic under design conditions, the profile of which is the dashed line in fig. 4 (right), and the outer ring end wall parameter is L 1 、α、A 1 (exit area); 6 is an indication of the outer ring end wall of the asymmetric diffuser generated when the diffuser outer ring end wall moves along the direction far away from the turbine under the specific working condition and the full circumferential axial length adjustment values are different, the molded lines of the asymmetric diffuser outer ring end wall are solid lines in the figure 4 (right), and the asymmetric diffuser outer ring end wall is respectively formed by L 11 ’、L 12 ’、L 13 The' …, a plurality of different axial lengths are circumferentially formed into a plurality of different diffuser profiles forming an asymmetric diffuser outer ring endwall.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is apparent that the described embodiments are some embodiments of the present invention, but not all embodiments of the present invention. All other embodiments, which can be made by one of ordinary skill in the art without undue burden from the present disclosure, are within the scope of the present disclosure.
The terminology used in the embodiments of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. Unless defined otherwise, technical or scientific terms used herein should be given the ordinary meaning as understood by one of ordinary skill in the art to which this invention belongs.
The invention provides an axially adjustable pressure expander structure suitable for an outer ring end wall of a single-side radial exhaust/steam system. FIG. 1 is a schematic illustration of a diffuser in position in an exhaust system. The diffuser is composed of inner and outer ring end walls, as shown in fig. 1, 1 is the diffuser outer ring end wall and profile, and 2 is the diffuser inner ring end wall and profile. The air flow enters the diffuser from the turbine outlet, and flows into the volute after the diffuser outlet is turned 90 degrees.
The invention provides an adjustable diffuser, which is used for adjusting the end wall of an outer ring of the diffuser. As shown in FIG. 2, the geometric parameters of the outer ring end wall of the diffuser such as axial length L, initial diffusion angle alpha, and outlet area A 1 The geometry of the end wall of the outer ring is determined, and the gist of the invention is that the diffuser can be adjusted by changing the axial length L of the end wall of the outer ring through pushing or stretching.
FIG. 3 is a schematic view of an outer diffuser ring endwall with equal circumferential axial length adjustment, with an axial length L when the outer diffuser ring endwall is in an initial condition 1 An initial diffusion angle alpha and an outlet area A 1 The formed outer ring end wall can maximize the diffusion capacity of the exhaust system under the design working condition.
According to the axial adjustable diffuser structure with the outer ring end wall, when the operation condition of a unit is changed, the outer ring end wall of the diffuser can be adjusted along the axial direction, and the diffuser flow passage is changed due to the change of the axial length, so that the flow state in the diffuser is improved. As shown in FIG. 3, when the load of the unit drops to a particular operating condition, the flow decreases, axially increasing (or decreasing) the axial length of the diffuser outer ring end wall to L 1 ' the diffuser outlet cross-sectional area becomes A 1 ’，L 1 The value of' is preset by the optimal design under the specific working condition, and after the change, the value is changed by the axial length L 1 ' initial diffusion angle alpha, exit area A 1 The diffuser outer ring end wall with the 'composition' can realize the maximum diffusion capability of an exhaust system under specific working conditions.
According to the diffuser structure with the axially adjustable outer ring end wall, according to the actual unit operation working conditions, the diffuser outer ring end wall axial length L' of the unit when operated under specific working conditions is preset, and for the unit with a larger operation working condition range, a plurality of diffuser outer ring end wall axial lengths L can be preset 1 ’、L 2 ’、 L 3 ' … to achieve good aerodynamic performance of the exhaust system over a wide range of operating conditions.
FIG. 4 is a schematic view of an outer ring endwall of a diffuser with different circumferential length adjustment values. The axial adjustable diffuser structure of the outer ring end wall provided by the invention can realize different adjustment values of the axial length of diffusers at different positions around the circumference. The outer ring end wall of the asymmetric diffuser designed on the basis of the same whole-circumference adjusting value can realize that an exhaust system has good pressure expansion capability under specific working conditions, and can obviously weaken the non-uniformity of a flow field in the exhaust system. The axial length of the outer ring end wall of the asymmetric diffuser is preset according to the axial length of the outer ring end wall of the symmetric diffuser, and the axial length L of the outer ring end wall of the diffuser is preset under specific working conditions 1 ' as a base, different diffuser outer ring end wall axial lengths L are preset at different circumferential positions 11 ’、L 12 ’、L 13 ’、L 14 The asymmetric pressure expander generated by different regulating values of the positions of the … whole circumference can obviously weaken the asymmetry of the flow field in the exhaust system. The axial length L of the end wall of the outer ring of the diffuser at different positions of the whole circumference under a plurality of working conditions can be preset according to different operation working conditions of the unit mn The axial length L of the outer ring end wall of the diffuser is changed in real time according to the actual flow field state, so that the axial direction of the diffuser is adjustable, and the aerodynamic performance of the exhaust system under the variable working condition is improved.
The axial length L mn ' are all preset values, and are defined by the axial length L mn ' initial diffusion angle alpha, outlet area A mn The diffuser formed by the method can enable the exhaust system to have good pressure expansion capability under specific working conditions, and meanwhile, the asymmetric flow field in the exhaust system can be weakened.
The object of the present invention is fully effectively achieved by the above-described embodiments. Those skilled in the art will appreciate that the present invention includes, but is not limited to, those illustrated in the drawings and described in the foregoing detailed description. While the invention has been described in connection with what is presently considered to be the most practical and preferred embodiment, it is to be understood that the invention is not limited to the disclosed embodiment, but on the contrary, is intended to cover various modifications and equivalent arrangements included within the scope of the appended claims.
Claims (5)
1. The diffuser structure with axially adjustable outer ring end wall is arranged at the turbine outlet of a single-side radial exhaust system and comprises a diffuser outer ring end wall and a diffuser inner ring end wall which are arranged in a volute, wherein the diffuser inner ring end wall is fixedly arranged in the volute, a circumferential space between the diffuser outer ring end wall and the diffuser inner ring end wall is formed into a diffuser runner,
the outer ring end wall of the diffuser comprises a cylindrical section with a constant diameter and an expansion section arranged at the downstream end of the cylindrical section;
the diffuser outer ring end wall can move forwards and backwards along the axial direction, so that the axial length L of the diffuser outer ring end wall molded surface is adjusted, the axial length L is the axial distance between the outlet edge of the diffuser outer ring end wall molded surface and the turbine outlet, and when the diffuser outer ring end wall moves along the axial direction, the inlet area A of the diffuser runner 0 Remain unchanged, outlet area A 1 Gradually shrinking or increasing;
the axial length L increases as the diffuser outer ring endwall moves axially downstream, the diffuser outer ring endwall gradually approaching the diffuser inner ring endwall in an axial direction, the diffuser flow passage outlet area A 1 The inlet-outlet area ratio of the diffuser flow passage is reducedAnd the gradient of the change of the flow area in the diffuser flow channel is reduced;
the axial length L decreases as the diffuser outer ring endwall moves axially upstream, the diffuser outer ring endwall gradually moving axially away from the diffuser inner ring endwall, the diffuser flow passage outlet area A 1 Increasing the inlet-outlet area ratio of the diffuser flow passageAnd the gradient of the change of the flow area in the diffuser flow channel is increased;
inlet-outlet area ratio of the diffuser flow passageThe adjustable range is 0.923-1.786.
2. The axially adjustable outer ring endwall diffuser structure of claim 1, wherein the diffuser outer ring endwall axial length adjustment is the same or different throughout the circumference to adapt the diffuser flow passage to its radially exhausting non-axisymmetric volute structure.
3. The axially adjustable outer ring endwall diffuser structure of claim 1, wherein an axial length of the diffuser outer ring endwall is increased to reduce an outlet area a of the diffuser flow passage when an exhaust system inlet flow rate is reduced 1 Thereby reducing the inlet-outlet area ratio of the diffuser flow passageAnd a gradient of flow area variation within the diffuser flow path.
4. The axially adjustable outer ring endwall diffuser structure of claim 1, wherein the axial length of the diffuser outer ring endwall is reduced to increase the outlet area a of the diffuser flow passage as the exhaust system inlet flow rate increases 1 Thereby reducing the inlet-outlet area ratio of the diffuser flow passageAnd a gradient of change in the flow area of the diffuser.
5. The axially adjustable diffuser structure of any one of claims 1-4, wherein the axial length L of the outer ring endwall profile of the diffuser is such that when adjusted according to the operating conditions, the geometry of the outer ring endwall of the diffuser is guaranteed to be a certain matching value, so as to optimize the aerodynamic performance of the exhaust system during operation under the design operating conditions.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111078707.0A CN113833540B (en) | 2021-09-15 | 2021-09-15 | Diffuser structure with axially adjustable outer ring end wall |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202111078707.0A CN113833540B (en) | 2021-09-15 | 2021-09-15 | Diffuser structure with axially adjustable outer ring end wall |
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| CN113833540A CN113833540A (en) | 2021-12-24 |
| CN113833540B true CN113833540B (en) | 2023-08-18 |
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103244209A (en) * | 2012-02-06 | 2013-08-14 | 中国科学院工程热物理研究所 | Diffuser end wall of turbine single-side exhaust system |
| CN107061321A (en) * | 2017-03-15 | 2017-08-18 | 清华大学 | The compressor of variable asymmetric vaned diffuser is coupled using established angle and denseness |
| CN111927582A (en) * | 2020-09-10 | 2020-11-13 | 杭州汽轮机股份有限公司 | Exhaust casing of industrial steam turbine |
| CN112302741A (en) * | 2019-07-25 | 2021-02-02 | 中国科学院工程热物理研究所 | Diffuser with adjustable end wall |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102011003522B4 (en) * | 2011-02-02 | 2013-03-14 | Siemens Aktiengesellschaft | Coupled outlet diffuser angle adjustment |
| US20190170010A1 (en) * | 2017-12-04 | 2019-06-06 | General Electric Company | Methods, systems and apparatus relating to turbine engine exhaust diffusers |
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2021
- 2021-09-15 CN CN202111078707.0A patent/CN113833540B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103244209A (en) * | 2012-02-06 | 2013-08-14 | 中国科学院工程热物理研究所 | Diffuser end wall of turbine single-side exhaust system |
| CN107061321A (en) * | 2017-03-15 | 2017-08-18 | 清华大学 | The compressor of variable asymmetric vaned diffuser is coupled using established angle and denseness |
| CN112302741A (en) * | 2019-07-25 | 2021-02-02 | 中国科学院工程热物理研究所 | Diffuser with adjustable end wall |
| CN111927582A (en) * | 2020-09-10 | 2020-11-13 | 杭州汽轮机股份有限公司 | Exhaust casing of industrial steam turbine |
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| CN113833540A (en) | 2021-12-24 |
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