EP0265633A1 - Turbine axiale - Google Patents
Turbine axiale Download PDFInfo
- Publication number
- EP0265633A1 EP0265633A1 EP87112769A EP87112769A EP0265633A1 EP 0265633 A1 EP0265633 A1 EP 0265633A1 EP 87112769 A EP87112769 A EP 87112769A EP 87112769 A EP87112769 A EP 87112769A EP 0265633 A1 EP0265633 A1 EP 0265633A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- diffuser
- flow
- turbine according
- ribs
- turbine
- 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
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
- 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
-
- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
- Y10S415/914—Device to control boundary layer
Definitions
- the invention relates to an axially flow-through turbine with reaction blading, to the outlet rotor blades of which a high Mach number flows and which is followed by a diffuser with an axial outlet into an exhaust pipe.
- Systems of this type are used in particular in gas turbine construction.
- the axial exhaust pipe opens into a chimney through which the turbine exhaust gases are discharged into the open.
- both the inner boundary wall, ie the hub and the outer boundary wall, ie the cylinder can be inclined at a certain angle to the machine axis.
- the hub runs cylindrically with the corresponding angle adjustment of the cylinder. In machines with a high Mach number, the angle between the hub and the cylinder can easily reach 30 ° and more. The meridian streamlines at the blading outlet therefore run over this angular range.
- the diffuser for connects to this outlet the recovery of the kinetic energy. If the conicity were to be continued in a straight line, the above-mentioned angle of 30 ° would be completely unsuitable to delay the flow and to achieve the desired pressure increase. The current would detach from the walls.
- the turbine designer now knows that a diffuser angle of approx. 7 ° should not be exceeded. As a result, he will reduce the mentioned angle from 30 ° to 7 °, and connect the diffuser determined in this way according to practical considerations. Studies have now shown that such a diffuser with an axial outlet is unsuitable.
- the invention seeks to remedy this. It is based on the task of designing the diffuser for maximum pressure recovery, especially at partial load of the system. This is achieved according to the invention in that the articulation angles of the diffuser inlet both on the hub and on the cylinder are determined exclusively for the purpose of homogenizing the energy profile above the channel height at the outlet of the last row of blades, and that means for swirl removal of the swirled flow are provided within the deceleration zone.
- the advantage of the invention can be seen, inter alia, in the fact that a considerable length reduction can be achieved with such a diffuser.
- the diffuser for supporting the flow in the radial direction is divided into several partial diffusers by means of flow-guiding plates. This means that each individual partial diffuser can be optimally designed.
- Baffles of this type are known from the exhaust steam housings of steam turbines, in which the relaxed, axially escaping steam is transferred in a radial outflow direction.
- These known sheets thus do not limit part diffusers, but are usually only deflection aids.
- baffles are one-piece rings without a joint, which at least partially extend over the entire length of the diffuser.
- the free cross-section that can be flowed through is increased.
- the rotational symmetry of the guide plates has a very favorable effect on the vibration behavior of the system.
- the diffuser end part is designed as a Carnot diffuser, this measure can further shorten the overall diffuser without having to accept the disadvantages of the flow.
- the means for removing the swirl within the diffuser are at least three evenly arranged circumferential, non-curved or curved flow ribs with thick profiles, which extend over the entire height of the channel through which the flow passes. This configuration leads to the ribs being insensitive to oblique flow.
- the flow ribs have a cavity in their radial extension through which the hub interior of the diffuser can be reached. This means that the bearings and the internal tubes are accessible at all times without disassembling the diffuser.
- the flow ribs advantageously form support bodies for the guide rings, such that the correspondingly recessed rings are attached to the support body in the longitudinal direction of the profile, preferably welded on.
- the flowed leading edge of the flow ribs is at a distance from the exit plane of the turbine blading, at which a diffuser area ratio of at least 2, preferably 3, prevails.
- the first diffuser zone thus remains undisturbed due to total rotational symmetry, which leads to the greatest possible deceleration with the shortest overall length. Since the ribs only become effective in a plane in which a relatively low energy level already prevails, no interference effects between the rib and the blading are to be expected. The specific losses through the ribs are also small.
- a part of the guide rings extends in the machine longitudinal direction only up to the plane in which the support body has its greatest profile thickness. As a result, the personnel can penetrate to the narrowest point between the outer and / or inner boundary wall of the diffuser and the flow rib without impairment.
- the diffuser is supported in an exhaust gas housing which is screwed to the turbine housing, the hub-side, internal exhaust gas housing parts being connected to the external exhaust gas housing parts surrounding the diffuser by supporting ribs, which preferably penetrate the cavity of the flow ribs.
- the load-bearing structure can be kept at a lower and homogeneous temperature level, which has an effect on the deformation behavior, and thus ultimately enables smaller blade clearances.
- the system becomes particularly easy to maintain when the exhaust housing / diffuser unit can be moved axially into the exhaust pipe. If the machine has to be dismantled, the exhaust pipe, which is usually installed in the wall of the machine house, can be left in place.
- the inner ring channel formed by the inner exhaust gas housing part and the inner diffuser boundary wall are connected to one another via the cavities of the flow ribs with the outer channel by the outer exhaust gas housing part and the outer diffuser boundary wall. If an adequate coolant, for example suitably conditioned rotor cooling air, flows through the cooling channels formed in this way, the entire load-bearing structure can be kept at a low, homogeneous temperature level.
- the gas turbine of which only the last three axially flowed stages are shown in FIG. 1, essentially consists of the bladed rotor 1 and the blade carrier 2 equipped with guide blades.
- the blade carrier is suspended in the turbine housing 3.
- the rotor 1 lies in a support bearing 4, which in turn is supported in an exhaust gas housing 5.
- This exhaust housing 5 essentially consists of a hub-side, inner part 6 and an outside lying part 7. Both elements are one-piece pot housings without an axial parting plane. They are connected to each other by three welded supporting ribs 8, which are evenly distributed over the circumference.
- the supporting ribs 8 are hollow. This makes it possible to walk inside the hub 22 of the exhaust gas housing, as symbolically represented by the fitter in FIG. 1.
- the spatial conditions make it possible to carry out even larger storage work such as lifting off the bearing cover.
- the supply lines can also be led out of the system.
- the ribs have the function of transmitting the bearing forces from the inner housing part 6 to the outer housing part 7.
- the outer housing part 7 is connected to the turbine housing 3 via flange screw connections 20 (FIG. 4).
- the exhaust housing 5 is designed so that it is not in contact with the exhaust gas flow.
- the actual flow control is taken over by the diffuser, which is designed as an insert for the exhaust housing.
- the outer boundary wall 9 of the diffuser is supported on the turbine housing 3 together with the outer exhaust gas housing part 7 via sheets 19; the inner boundary wall 10, on the other hand, is suspended via struts 11 on the hub cap 12 of the inner exhaust gas housing part 6.
- the end of the diffuser opens into the exhaust pipe 13.
- the diffuser is designed, regardless of structural considerations, but solely on the basis of fluid dynamics.
- the two articulation angles must be determined based on the total flow in the blading and in the diffuser, possibly even taking into account the influence of the combustion chamber.
- the meridian curvature of the streamlines is primarily responsible for the extent of the pressure increase mentioned. This must be influenced primarily by adjusting the angle of attack in order to achieve a homogeneous energy distribution. In principle, this defines the kink angle of the inner boundary wall at the diffuser inlet. In the present case, this leads to an angle ⁇ N that rises from the horizontal in a positive direction. It can be seen that the angle is almost 20 °. This is due, among other things, to the influence of cooling air. As is known, the hub, ie the rotor surface and the blade roots, is generally cooled down to a tolerable level with cooling air.
- the total opening angle of the diffuser is in the range of the opening angle of the blading, and may even be greater than this, but in no case holds those values that would correspond to the purely constructive considerations.
- a diffuser with a 30 ° opening angle is unsuitable to delay the flow. It is therefore divided into partial diffusers in the radial direction by means of flow-guiding plates 15. These can now be dimensioned according to the known rules. In the present case this means that three baffles 15 are arranged in such a way that four partial diffusers 16, each with an opening angle of 7.5 °, result.
- these guide plates 15 are designed as one-piece rings or truncated cones. Because they are designed to be rotationally symmetrical and without separating flanges, they form the best prerequisites for the undisturbed pressure conversion in the flow, which at the time was still swirling. In order to achieve the best possible pressure recovery in this way, the guide rings 15 extend without any cross-sectional impairments to a level at which a diffuser area ratio of 3 is reached. This route is considered the first diffuser zone.
- baffles 15 must be suitably fastened in the diffuser and kept at a distance from one another.
- the classic ribs are ideal for this.
- the invention also provides for the best possible pressure recovery at partial load. This leads to the requirement to remove the adherent swirl from the flow, which in turn is feasible in the classic way by rectifying ribs.
- both functions can be combined with one and the same means, namely flow ribs 17.
- the baffles are attached to the three flow ribs 17 by welding.
- the guide plates of the rib profile shape are cut out accordingly. Due to the long weld seams, a stable attachment is guaranteed, which enables the baffles to protrude long over the entire first diffuser zone.
- FIG. 1 shows that only the middle baffle extends to the end of the diffuser.
- the lower part of FIG. 1 shows that the baffles arranged between the middle plate and the boundary walls end in the plane in which the flow ribs 17 have their greatest thickness. From its end, the diffuser can thus be walked so far that, for example, the last row of the gas turbine can be subjected to a direct optical examination without further notice.
- the first diffuser zone ends in the plane of the front edge of the flow ribs 17.
- a second zone now extends from the front edge to the greatest profile thickness of the ribs.
- the boundary walls 9 and 10 of the diffuser are adapted to the profile of the rib, that the flow in this second zone, in which most of the swirl is carried out, is largely without delay.
- the second zone is followed by a third zone, which in turn is decelerated.
- the middle baffle and the flow ribs also extend beyond this third zone.
- This is a predominantly straight diffuser. Since the flow is already largely swirl-free at this point in time, it must be ensured that the expansion does not run too much in order to avoid detachment of the flow at the boundary walls 9 running cylindrically in this zone. In order not to let the system length increase excessively, the inner boundary walls 10 of the diffuser are not allowed to run out completely, but are limited in their axial extent by a blunt section 23.
- the flow ribs 17 end in the same plane as the inner diffuser walls 10 also with a blunt section 18, which determines the trailing edges of the profile.
- a type of Carnot diffuser is formed here in a fourth zone due to the sudden expansion, which in turn contributes to shortening the overall length.
- the dotted surface which is composed of the blunt ends of the three ribs and the blunt end of the inner boundary walls, is less than 20% of the circular area of the exhaust pipe 13 is.
- the exhaust gas housing and diffuser elements which form a functional unit, are designed to be displaceable as a whole.
- the unit can be moved into the exhaust pipe 13 at least by the amount necessary to be able to lift the rotor 1 freely from the support bearing 4. Since that Support bearing in the fully assembled system is supported in the interior of the exhaust housing part 6 to be moved, for this purpose it is provided to support the rotor 1 preferably in the plane of the compressor diffuser, not shown.
- the cooling medium is introduced downstream of the blading into the annular channel 24 between the inner exhaust gas housing part 5 and the inner diffuser boundary wall 10.
- FIG. 4 it can be seen that the parts of the flow ribs 17 projecting beyond the flow-through channel are perforated both at their inner and at their outer end.
- the coolant enters the cavity 21 of the ribs through the inner cooling air openings 25 ⁇ (FIG. 6).
- the front part of this cavity is partitioned off from the end of the profile by a partition 27 which extends over the entire channel height.
- the supporting ribs 8 are located in an actual cooling space which is flowed through from the inside to the outside in the radial direction.
- the cooling air flows through the corresponding cooling air openings 25 ⁇ into the ring channel 26 (FIG. 7) between the outer exhaust gas housing part 7 and the outer diffuser boundary wall 9.
- the medium is directed back to the diffuser inlet, where it is directly behind the trailing edge of the blades 14 the gap flow and the main flow is mixed as aerodynamic ballast.
- this proportion of cooling air will also have to be taken into account when determining the articulation angle ⁇ Z.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
- Supercharger (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH3876/86 | 1986-09-26 | ||
CH3876/86A CH672004A5 (fr) | 1986-09-26 | 1986-09-26 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0265633A1 true EP0265633A1 (fr) | 1988-05-04 |
EP0265633B1 EP0265633B1 (fr) | 1991-02-06 |
Family
ID=4265384
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP87112769A Expired - Lifetime EP0265633B1 (fr) | 1986-09-26 | 1987-09-02 | Turbine axiale |
Country Status (6)
Country | Link |
---|---|
US (1) | US4802821A (fr) |
EP (1) | EP0265633B1 (fr) |
JP (1) | JP2820403B2 (fr) |
AU (1) | AU603136B2 (fr) |
CH (1) | CH672004A5 (fr) |
DE (1) | DE3767965D1 (fr) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014175763A1 (fr) * | 2013-04-25 | 2014-10-30 | Siemens Aktiengesellschaft | Turbomachine et dispositif d'utilisation de chaleur perdue |
EP3159501A1 (fr) * | 2015-10-21 | 2017-04-26 | Siemens Aktiengesellschaft | Moteur d'écoulement comprenant un agencement de sortie |
Families Citing this family (40)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0417433B1 (fr) * | 1989-09-12 | 1993-06-09 | Asea Brown Boveri Ag | Turbine axiale |
US5297930A (en) * | 1991-12-31 | 1994-03-29 | Cornell Research Foundation, Inc. | Rotating stall suppression |
EP0581978B1 (fr) * | 1992-08-03 | 1996-01-03 | Asea Brown Boveri Ag | Diffuseur à zones multiples pour turbomachine |
DE4422700A1 (de) * | 1994-06-29 | 1996-01-04 | Abb Management Ag | Diffusor für Turbomaschine |
US5494405A (en) * | 1995-03-20 | 1996-02-27 | Westinghouse Electric Corporation | Method of modifying a steam turbine |
US5743710A (en) * | 1996-02-29 | 1998-04-28 | Bosch Automotive Motor Systems Corporation | Streamlined annular volute for centrifugal blower |
AU1181199A (en) * | 1997-10-17 | 1999-05-10 | Zakrytoe Aktsionernoe Obschestvo "Entek" | Exhaust duct for a steam turbine |
DE19803161C2 (de) * | 1998-01-28 | 2000-03-16 | Alstom Energy Syst Gmbh | Gasturbinenschalldämpfer mit Diffusor |
DE19821889B4 (de) * | 1998-05-15 | 2008-03-27 | Alstom | Verfahren und Vorrichtung zur Durchführung von Reparatur- und/oder Wartungsarbeiten im Innengehäuse einer mehrschaligen Turbomaschine |
DE19846224A1 (de) * | 1998-10-07 | 2000-04-20 | Siemens Ag | Dampfturbine mit einem Abdampfgehäuse |
DE10037684A1 (de) | 2000-07-31 | 2002-02-14 | Alstom Power Nv | Niederdruckdampfturbine mit Mehrkanal-Diffusor |
DE10051223A1 (de) | 2000-10-16 | 2002-04-25 | Alstom Switzerland Ltd | Verbindbare Statorelemente |
US6807803B2 (en) * | 2002-12-06 | 2004-10-26 | General Electric Company | Gas turbine exhaust diffuser |
JP4040556B2 (ja) * | 2003-09-04 | 2008-01-30 | 株式会社日立製作所 | ガスタービン設備及び冷却空気供給方法 |
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 |
US7909569B2 (en) * | 2005-06-09 | 2011-03-22 | Pratt & Whitney Canada Corp. | Turbine support case and method of manufacturing |
US20110076146A1 (en) * | 2009-09-30 | 2011-03-31 | Falcone Andrew J | Wind turbine electrical generating system with combined structural support members and straightening vanes |
US8313286B2 (en) * | 2008-07-28 | 2012-11-20 | Siemens Energy, Inc. | Diffuser apparatus in a turbomachine |
US8628297B2 (en) * | 2010-08-20 | 2014-01-14 | General Electric Company | Tip flowpath contour |
US8591184B2 (en) | 2010-08-20 | 2013-11-26 | General Electric Company | Hub flowpath contour |
US20130091865A1 (en) * | 2011-10-17 | 2013-04-18 | General Electric Company | Exhaust gas diffuser |
US9267687B2 (en) | 2011-11-04 | 2016-02-23 | General Electric Company | Combustion system having a venturi for reducing wakes in an airflow |
US8899975B2 (en) | 2011-11-04 | 2014-12-02 | General Electric Company | Combustor having wake air injection |
DE102011118735A1 (de) | 2011-11-17 | 2013-05-23 | Alstom Technology Ltd. | Diffusor, insbesondere für eine axiale strömungsmaschine |
US20130180245A1 (en) * | 2012-01-12 | 2013-07-18 | General Electric Company | Gas turbine exhaust diffuser having plasma actuator |
PL221113B1 (pl) * | 2012-01-25 | 2016-02-29 | Gen Electric | Układy dyfuzora wydechowego turbiny |
EP2685054B1 (fr) * | 2012-07-09 | 2020-11-25 | ABB Schweiz AG | Diffuseur d'une turbine de gaz d'échappement |
EP2971614B1 (fr) * | 2013-03-14 | 2020-10-14 | Rolls-Royce Corporation | Amortisseur subsonique |
US9739201B2 (en) | 2013-05-08 | 2017-08-22 | General Electric Company | Wake reducing structure for a turbine system and method of reducing wake |
US9322553B2 (en) | 2013-05-08 | 2016-04-26 | General Electric Company | Wake manipulating structure for a turbine system |
US9435221B2 (en) | 2013-08-09 | 2016-09-06 | General Electric Company | Turbomachine airfoil positioning |
US20150059312A1 (en) * | 2013-08-29 | 2015-03-05 | General Electric Company | Exhaust stack having a co-axial silencer |
US9598981B2 (en) * | 2013-11-22 | 2017-03-21 | Siemens Energy, Inc. | Industrial gas turbine exhaust system diffuser inlet lip |
US9617873B2 (en) * | 2014-09-15 | 2017-04-11 | Siemens Energy, Inc. | Turbine exhaust cylinder / turbine exhaust manifold bolted stiffening ribs |
US10563543B2 (en) * | 2016-05-31 | 2020-02-18 | General Electric Company | Exhaust diffuser |
US20190145284A1 (en) * | 2017-11-13 | 2019-05-16 | National Chung Shan Institute Of Science And Technology | Exhaust channel of microturbine engine |
US11028778B2 (en) | 2018-09-27 | 2021-06-08 | Pratt & Whitney Canada Corp. | Engine with start assist |
KR102350377B1 (ko) * | 2020-03-20 | 2022-01-14 | 두산중공업 주식회사 | 유동박리 현상을 줄이는 배기 디퓨저의 허브 구조 |
CN113757021A (zh) * | 2021-09-24 | 2021-12-07 | 广西桂冠电力股份有限公司大化水力发电总厂 | 水轮机大轴中心测量方法 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
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CH352534A (fr) * | 1957-12-12 | 1961-02-28 | Napier & Son Ltd | Ensemble comprenant un conduit d'échappement annulaire et des paliers destinés à supporter un rotor de groupe moteur à turbine à gaz |
DE1227290B (de) * | 1959-11-04 | 1966-10-20 | Otto Schiele Dr Ing | Diffusoranordnung kurzer Baulaenge mit einem Profilgitter am Anfang und/oder am Endedes divergierenden Diffusorteiles |
CH512664A (de) * | 1969-08-04 | 1971-09-15 | Gen Electric | Verfahren zur Kühlung des Gehäuses einer Strömungsmaschine für kompressible Medien sowie Einrichtung zur Durchführung des Verfahrens |
DE2224249A1 (de) * | 1971-05-27 | 1972-11-30 | Westinghouse Electric Corp., Pittsburgh, Pa. (V.StA.) | Auspuffanlage für eine Gasturbine mit offenem Kreislauf und elastischem Treibmittel |
Family Cites Families (12)
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DE697997C (de) * | 1936-06-23 | 1940-10-29 | Siemens Schuckertwerke Akt Ges | Luftkanal hinter einem Axialgeblaese mit Diffusor |
US2538739A (en) * | 1946-03-27 | 1951-01-16 | Joy Mfg Co | Housing for fan and motor |
US2828939A (en) * | 1950-09-20 | 1958-04-01 | Power Jets Res & Dev Ltd | Support of turbine casings and other structure |
FR1104644A (fr) * | 1954-02-15 | 1955-11-22 | Thomson Houston Comp Francaise | Perfectionnements aux systèmes de commande de l'écoulement d'un fluide |
CH484358A (de) * | 1968-02-15 | 1970-01-15 | Escher Wyss Ag | Abströmgehäuse einer axialen Turbomaschine |
US4013378A (en) * | 1976-03-26 | 1977-03-22 | General Electric Company | Axial flow turbine exhaust hood |
FR2401311A1 (fr) * | 1977-08-25 | 1979-03-23 | Europ Turb Vapeur | Dispositif d'echappement pour turbine axiale a fluide condensable |
JPS5672206A (en) * | 1979-11-14 | 1981-06-16 | Nissan Motor Co Ltd | Diffuser with collector |
EP0035838B1 (fr) * | 1980-03-10 | 1985-02-06 | Rolls-Royce Plc | Diffuseur |
DE3206626A1 (de) * | 1982-02-24 | 1983-09-01 | Kraftwerk Union AG, 4330 Mülheim | Abgaskanal fuer gasturbinen |
IT1153351B (it) * | 1982-11-23 | 1987-01-14 | Nuovo Pignone Spa | Diffusore compatto perfezionato, particolarmente adatto per turbine a gas di grande potenza |
JPS60196414A (ja) * | 1984-03-16 | 1985-10-04 | Hitachi Ltd | ガスタ−ビンダクトの整流装置 |
-
1986
- 1986-09-26 CH CH3876/86A patent/CH672004A5/de not_active IP Right Cessation
-
1987
- 1987-09-02 DE DE8787112769T patent/DE3767965D1/de not_active Expired - Fee Related
- 1987-09-02 EP EP87112769A patent/EP0265633B1/fr not_active Expired - Lifetime
- 1987-09-21 AU AU78802/87A patent/AU603136B2/en not_active Ceased
- 1987-09-21 US US07/099,020 patent/US4802821A/en not_active Expired - Lifetime
- 1987-09-25 JP JP62239105A patent/JP2820403B2/ja not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH352534A (fr) * | 1957-12-12 | 1961-02-28 | Napier & Son Ltd | Ensemble comprenant un conduit d'échappement annulaire et des paliers destinés à supporter un rotor de groupe moteur à turbine à gaz |
DE1227290B (de) * | 1959-11-04 | 1966-10-20 | Otto Schiele Dr Ing | Diffusoranordnung kurzer Baulaenge mit einem Profilgitter am Anfang und/oder am Endedes divergierenden Diffusorteiles |
CH512664A (de) * | 1969-08-04 | 1971-09-15 | Gen Electric | Verfahren zur Kühlung des Gehäuses einer Strömungsmaschine für kompressible Medien sowie Einrichtung zur Durchführung des Verfahrens |
DE2224249A1 (de) * | 1971-05-27 | 1972-11-30 | Westinghouse Electric Corp., Pittsburgh, Pa. (V.StA.) | Auspuffanlage für eine Gasturbine mit offenem Kreislauf und elastischem Treibmittel |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014175763A1 (fr) * | 2013-04-25 | 2014-10-30 | Siemens Aktiengesellschaft | Turbomachine et dispositif d'utilisation de chaleur perdue |
EP3159501A1 (fr) * | 2015-10-21 | 2017-04-26 | Siemens Aktiengesellschaft | Moteur d'écoulement comprenant un agencement de sortie |
WO2017067774A1 (fr) * | 2015-10-21 | 2017-04-27 | Siemens Aktiengesellschaft | Moteur d'écoulement comportant un dispositif d'évacuation |
Also Published As
Publication number | Publication date |
---|---|
EP0265633B1 (fr) | 1991-02-06 |
JPS6390630A (ja) | 1988-04-21 |
JP2820403B2 (ja) | 1998-11-05 |
US4802821A (en) | 1989-02-07 |
CH672004A5 (fr) | 1989-10-13 |
DE3767965D1 (de) | 1991-03-14 |
AU603136B2 (en) | 1990-11-08 |
AU7880287A (en) | 1988-03-31 |
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