EP0417433A1 - Turbine axiale - Google Patents
Turbine axiale Download PDFInfo
- Publication number
- EP0417433A1 EP0417433A1 EP90113994A EP90113994A EP0417433A1 EP 0417433 A1 EP0417433 A1 EP 0417433A1 EP 90113994 A EP90113994 A EP 90113994A EP 90113994 A EP90113994 A EP 90113994A EP 0417433 A1 EP0417433 A1 EP 0417433A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- guide vanes
- flow
- turbine according
- blades
- ribs
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000011084 recovery Methods 0.000 abstract description 16
- 239000007789 gas Substances 0.000 description 12
- 238000010586 diagram Methods 0.000 description 5
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- 238000002485 combustion reaction Methods 0.000 description 3
- 230000002829 reductive effect Effects 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000002245 particle Substances 0.000 description 2
- UJCHIZDEQZMODR-BYPYZUCNSA-N (2r)-2-acetamido-3-sulfanylpropanamide Chemical compound CC(=O)N[C@@H](CS)C(N)=O UJCHIZDEQZMODR-BYPYZUCNSA-N 0.000 description 1
- 241001669680 Dormitator maculatus Species 0.000 description 1
- 230000001154 acute effect Effects 0.000 description 1
- 238000009530 blood pressure measurement Methods 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000009792 diffusion process Methods 0.000 description 1
- 230000003628 erosive effect Effects 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000011835 investigation Methods 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 210000002435 tendon Anatomy 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- 239000013598 vector Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 238000009736 wetting Methods 0.000 description 1
Images
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
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
- F01D17/162—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for axial flow, i.e. the vanes turning around axes which are essentially perpendicular to the rotor centre line
-
- 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
Definitions
- the invention relates to an axially flow-through turbine, to the outlet rotor blades of which a diffuser is connected, means within the deceleration zone being provided for swirl removal of the swirled flow
- Such a turbine is known from EP-A 265 633.
- a rectifying grid is provided within the diffuser, which extends over the entire height of the flowed channel.
- These means for swirl removal are three flow ribs with thick profiles which are arranged uniformly over the circumference and which are designed according to the knowledge of turbomachine construction and which should be as insensitive as possible to oblique flow. The flowed leading edge of these ribs is located relatively far behind the trailing edge of the last blades in order to avoid excitation of the last row of blades caused by the pressure field of the ribs.
- This distance is dimensioned such that the front edge of the ribs is in a plane in which a diffuser area ratio of preferably three predominates.
- the diffuser zone between the blading and the flow ribs should therefore remain undisturbed due to total rotational symmetry.
- the fact that no interference effects between the ribs and the blades are to be expected is due to the fact that the Ribs only become effective on a level in which a relatively low energy level already prevails.
- the diffuser is flowed at at idle under a speed ratio c t / c n of approximately 1.2, where c t means the tangential speed and c n the axial speed of the medium.
- This oblique flow leads to a drop in the pressure recovery C p , as can be seen from FIG. 2 to be described later (curve A).
- the pressure behind blading can usually be 0.98 at full load at 40% volume flow rise up to 1.15 bar. This back pressure means that at 40% volume flow, significantly more drive power has to be applied to the machine than if a well-acting diffuser is available.
- the object of the invention is to design the diffusion zone in axially flow-through turbines of the type mentioned at the outset in such a way that the part-load behavior of the machine is further improved.
- At least one row with adjustable guide vanes is arranged between the means for swirl removal and the outlet blades.
- the guide blades have a straight skeleton line with a symmetrical profile.
- the well-known properties of such grids on insensitivity in the inflow can be used for low-loss deflection.
- the known gas turbine of which only the last three axially flowed stages are shown in FIG. 1, consists essentially of the bladed rotor 1 'and the blade carrier 2' equipped with guide vanes.
- the blade carrier is suspended in the turbine housing 3 '.
- the rotor is in a support bearing 4 ', which in turn is supported in an exhaust housing 5'.
- This exhaust housing 5 ' consists essentially of a hub-side, inner part 6' and an outer part 7 ', which limit the diffuser 13'.
- Both elements 6 'and 7' can be one-piece pot housings without an axial parting plane. They are interconnected by several welded supporting flow ribs 8 ', which are arranged evenly distributed over the circumference and whose profile is indicated by 9'. It can be seen that for the reasons mentioned at the outset, the flow ribs 8 'are arranged at a suitable distance from the blading.
- the pressure recovery C p is plotted on the ordinate, which in a first approximation corresponds to the ratio (p A -p E ) / p * E -p E ), where p A is the static pressure at the outlet of the diffuser, p E is the static pressure at Entry of the diffuser and p * E mean the total pressure at the inlet of the diffuser and thus at the outlet of the blading.
- Curve A shows the pressure recovery in a diffuser which is equipped with flow ribs which have a pitch to chord ratio of approximately 0.5. It can be seen that the drop is somewhat acceptable up to a c t / c n value, but that the pressure recovery deteriorates dramatically as the volume flow decreases.
- Curve B shows the completely unreasonable course when flow ribs with a pitch to chord ratio of approximately 1 are used.
- FIG. 3 The structure of the gas turbine shown there corresponds to that of FIG. 1, which is why the structure is not described again.
- the same elements as in Fig. 1 are designated in Fig. 3 with the same reference numerals without (').
- Evenly distributed over the circumference are the same Straightening flow ribs 8 with a straight skeleton line and with a ratio of division to tendon of 0.5. This ratio occurs in the middle section of the flow-through channel of the flow ribs, which run conically in the radial direction.
- the guide vanes 11 are also symmetrical profiles with a straight skeleton line, as are known for example under the term NACA 0010.
- these guide blades have a pitch to chord ratio of 0.5 in the middle section of the channel through which the flow passes.
- Such blades are to a certain extent insensitive to inclined flow, (see article by N. Scholz, "Investigations on blade grids of turbomachines", Journal of Flight Sciences, No. 3, 1955).
- the guide vanes 11 are tapered in the radial direction and are preferably twisted.
- the adjustment of the guide vanes 11 in the grating takes place via actuating means, not shown, as are known, for example, from compressor construction.
- the actual adjustment is preferably carried out automatically as a function of the operating parameters such as load, speed, etc.
- the greatest pressure recovery is achieved when the guide vanes are adjusted so that the shaft power assumes the greatest possible value under all operating conditions. A permanent performance measurement is therefore suitable.
- the greatest pressure recovery can also be achieved if the adjustment of the guide vanes takes place in such a way that the static pressure in front of the guide vanes 11, ie behind the outlet rotor blades 12, takes the smallest possible value.
- a permanent differential pressure measurement p A -p E is therefore suitable.
- the cylinder section in FIG. 4 shows, on an enlarged scale, the blade plan in the gas turbine zone under consideration.
- the characters c in each case mean the absolute speed, w the relative speed and u the peripheral speed of the machine.
- the individual grids have, for example, the following in order to indicate the order of magnitude in an executed example Data:
- the chord of the guide vanes 11 is 125 mm, that of the flow ribs is approximately 700 mm.
- the ratio of profile thickness to chord is 0.1 for the guide vanes and for the flow ribs.
- the flow towards the guide vanes 11 is approximately the same under which they leave the outlet rotor vanes 12, i.e. with the speed c and an angle ⁇ of 60 °.
- the exhaust gases thus leave the guide vane at an angle of approximately 40 °, with which they strike the front edges of the flow ribs 8, which are also insensitive to oblique flow, where they enter the axial, i.e. be aligned to 0 °.
- Curve C in FIG. 2 now shows the effect of an optimally adjusted guide blading.
- the pressure recovery is almost constant and only then drops to a modest extent, compared to the diffuser configuration without guide vanes.
- the diagram also shows that at full load, ie in the range c t / c n between -0.1 and +0.1 (depending on the design of the blading), the diffuser configurations which are state of the art achieve a somewhat better pressure recovery. This is because the area around which the diffuser flows is less than that with guide vanes.
- the new measure also makes it possible to allow a certain counter-swirl at the outlet from the last rotor blades 12, since an axial alignment takes place downstream in the diffuser through the guide blades and the flow ribs.
- This counter-swirl would have the following advantages: - The step work can be increased with constant efficiency; or - The efficiency can be increased with constant step work; - The blades of the last row could be made less twisted, which leads to a reduction in price; - The deflection in the last turbine stage can be reduced, which is particularly important in the case of fluidized-bed-fired gas turbines because of the particle separation.
- the invention is not limited to the exemplary embodiment shown and described, which relates to a diffuser with an axial outlet and thus greatly facilitates the arrangement of the flow ribs. It is also particularly applicable to steam turbines or the turbines of exhaust gas turbochargers, both of which generally have a so-called axial-radial exit from the blading. In such machines, the means for swirl removal are represented by the radial part of the outlet housing itself.
- the skeleton shape of the guide vanes can also be curved, which would of course lead to a significant increase in the cost of this additional measure.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH332289 | 1989-09-12 | ||
CH3322/89 | 1989-09-12 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0417433A1 true EP0417433A1 (fr) | 1991-03-20 |
EP0417433B1 EP0417433B1 (fr) | 1993-06-09 |
Family
ID=4253475
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP90113994A Expired - Lifetime EP0417433B1 (fr) | 1989-09-12 | 1990-07-21 | Turbine axiale |
Country Status (4)
Country | Link |
---|---|
US (1) | US5102298A (fr) |
EP (1) | EP0417433B1 (fr) |
JP (1) | JP3162363B2 (fr) |
DE (1) | DE59001693D1 (fr) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0581978A1 (fr) * | 1992-08-03 | 1994-02-09 | Asea Brown Boveri Ag | Diffuseur à zones multiples pour turbomachine |
EP0589215A1 (fr) * | 1992-09-25 | 1994-03-30 | Asea Brown Boveri Ag | Turbine à gaz avec carter d'échappement et conduit d'échappement |
WO1999020874A1 (fr) * | 1997-10-17 | 1999-04-29 | Zakrytoe Aktsionernoe Obschestvo 'entek' | Conduit d'evacuation pour turbine a vapeur |
EP1245784A3 (fr) * | 2001-03-30 | 2009-05-13 | General Electric Company | Aube de guidage variable |
US8893511B2 (en) | 2009-07-24 | 2014-11-25 | General Electric Company | Systems and methods for a gas turbine combustor having a bleed duct |
EP3147458A1 (fr) * | 2015-09-25 | 2017-03-29 | Siemens Aktiengesellschaft | Système basse pression pour une turbine à vapeur et turbine à vapeur |
Families Citing this family (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5279110A (en) * | 1992-06-12 | 1994-01-18 | Lin Abraham S | Double-rotor rotary engine and turbine |
DE4232385A1 (de) * | 1992-09-26 | 1994-03-31 | Asea Brown Boveri | Gasturbine mit angeflanschtem Abgasgehäuse |
JP3070401B2 (ja) * | 1994-08-23 | 2000-07-31 | 株式会社日立製作所 | ガスタービン排気構造 |
US5494405A (en) * | 1995-03-20 | 1996-02-27 | Westinghouse Electric Corporation | Method of modifying a steam turbine |
JPH11247605A (ja) | 1997-12-26 | 1999-09-14 | United Technol Corp <Utc> | タ―ボマシ―ンコンポ―ネントの振動緩衝方法及び装置 |
US6866479B2 (en) * | 2003-05-16 | 2005-03-15 | Mitsubishi Heavy Industries, Ltd. | Exhaust diffuser for axial-flow turbine |
US20050200080A1 (en) * | 2004-03-10 | 2005-09-15 | Siemens Westinghouse Power Corporation | Seal for a turbine engine |
US8757965B2 (en) * | 2004-06-01 | 2014-06-24 | Volvo Aero Corporation | Gas turbine compression system and compressor structure |
US20110176917A1 (en) * | 2004-07-02 | 2011-07-21 | Brian Haller | Exhaust Gas Diffuser Wall Contouring |
US7100358B2 (en) * | 2004-07-16 | 2006-09-05 | Pratt & Whitney Canada Corp. | Turbine exhaust case and method of making |
JP2009531593A (ja) * | 2006-03-31 | 2009-09-03 | アルストム テクノロジー リミテッド | 流体機械、特に蒸気タービンの案内ブレード |
US7731475B2 (en) * | 2007-05-17 | 2010-06-08 | Elliott Company | Tilted cone diffuser for use with an exhaust system of a turbine |
GB201002642D0 (en) * | 2010-02-16 | 2010-03-31 | Beachy Head Michael A | Engine for thrust and or shaft output |
EP2441918A1 (fr) | 2010-10-18 | 2012-04-18 | Siemens Aktiengesellschaft | Diffuseur annulaire d'une turbine à gaz |
US20120198810A1 (en) * | 2011-02-04 | 2012-08-09 | General Electric Company, A New York Corporation | Strut airfoil design for low solidity exhaust gas diffuser |
US9284853B2 (en) * | 2011-10-20 | 2016-03-15 | General Electric Company | System and method for integrating sections of a turbine |
US20140314549A1 (en) * | 2013-04-17 | 2014-10-23 | General Electric Company | Flow manipulating arrangement for a turbine exhaust diffuser |
US11028778B2 (en) | 2018-09-27 | 2021-06-08 | Pratt & Whitney Canada Corp. | Engine with start assist |
US11047314B2 (en) | 2019-03-12 | 2021-06-29 | Pratt & Whitney Canada Corp. | Systems and methods for control of engine variable geometry mechanism |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2047820A (en) * | 1978-11-27 | 1980-12-03 | Kh Polt I Im V I Lenina | Exhaust pipe of turbine |
US4398865A (en) * | 1978-11-10 | 1983-08-16 | Garkusha Anatoly V | Exhaust pipe of turbine |
EP0265633B1 (fr) * | 1986-09-26 | 1991-02-06 | BBC Brown Boveri AG | Turbine axiale |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2682363A (en) * | 1950-12-08 | 1954-06-29 | Rolls Royce | Gas turbine engine |
US2674845A (en) * | 1951-05-02 | 1954-04-13 | Walter D Pouchot | Diffuser apparatus with boundary layer control |
US2815770A (en) * | 1954-05-11 | 1957-12-10 | Westinghouse Electric Corp | Diffuser |
FR1502832A (fr) * | 1966-09-26 | 1967-11-24 | Nord Aviation | Hélice carénée à diffusion |
DE1925172B2 (de) * | 1969-05-17 | 1977-07-14 | Daimler Benz Ag, 7000 Stuttgart | Nachleitgitter eines axialverdichters, insbesondere eines ueberschall- axialverdichters |
US4116584A (en) * | 1973-10-12 | 1978-09-26 | Gutehoffnungshutte Sterkrade Ag | Device for extending the working range of axial flow compressors |
US4950129A (en) * | 1989-02-21 | 1990-08-21 | General Electric Company | Variable inlet guide vanes for an axial flow compressor |
US4995786A (en) * | 1989-09-28 | 1991-02-26 | United Technologies Corporation | Dual variable camber compressor stator vane |
-
1990
- 1990-07-21 DE DE9090113994T patent/DE59001693D1/de not_active Expired - Fee Related
- 1990-07-21 EP EP90113994A patent/EP0417433B1/fr not_active Expired - Lifetime
- 1990-08-23 US US07/571,153 patent/US5102298A/en not_active Expired - Lifetime
- 1990-09-11 JP JP23914590A patent/JP3162363B2/ja not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4398865A (en) * | 1978-11-10 | 1983-08-16 | Garkusha Anatoly V | Exhaust pipe of turbine |
GB2047820A (en) * | 1978-11-27 | 1980-12-03 | Kh Polt I Im V I Lenina | Exhaust pipe of turbine |
EP0265633B1 (fr) * | 1986-09-26 | 1991-02-06 | BBC Brown Boveri AG | Turbine axiale |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0581978A1 (fr) * | 1992-08-03 | 1994-02-09 | Asea Brown Boveri Ag | Diffuseur à zones multiples pour turbomachine |
US5338155A (en) * | 1992-08-03 | 1994-08-16 | Asea Brown Boveri Ltd. | Multi-zone diffuser for turbomachine |
EP0589215A1 (fr) * | 1992-09-25 | 1994-03-30 | Asea Brown Boveri Ag | Turbine à gaz avec carter d'échappement et conduit d'échappement |
DE4232088A1 (de) * | 1992-09-25 | 1994-03-31 | Asea Brown Boveri | Gasturbine mit Abgasgehäuse und Abgaskanal |
US5346365A (en) * | 1992-09-25 | 1994-09-13 | Asea Brown Boveri Ltd. | Gas turbine with exhaust gas casing and exhaust gas duct |
WO1999020874A1 (fr) * | 1997-10-17 | 1999-04-29 | Zakrytoe Aktsionernoe Obschestvo 'entek' | Conduit d'evacuation pour turbine a vapeur |
EP1245784A3 (fr) * | 2001-03-30 | 2009-05-13 | General Electric Company | Aube de guidage variable |
US8893511B2 (en) | 2009-07-24 | 2014-11-25 | General Electric Company | Systems and methods for a gas turbine combustor having a bleed duct |
EP3147458A1 (fr) * | 2015-09-25 | 2017-03-29 | Siemens Aktiengesellschaft | Système basse pression pour une turbine à vapeur et turbine à vapeur |
Also Published As
Publication number | Publication date |
---|---|
JP3162363B2 (ja) | 2001-04-25 |
US5102298A (en) | 1992-04-07 |
JPH03100302A (ja) | 1991-04-25 |
DE59001693D1 (de) | 1993-07-15 |
EP0417433B1 (fr) | 1993-06-09 |
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