EP0104413A1 - Machine rotative d'un ou de plusieurs étages de haute pression pour les fluides agressifs ou chauds - Google Patents

Machine rotative d'un ou de plusieurs étages de haute pression pour les fluides agressifs ou chauds Download PDF

Info

Publication number
EP0104413A1
EP0104413A1 EP83108202A EP83108202A EP0104413A1 EP 0104413 A1 EP0104413 A1 EP 0104413A1 EP 83108202 A EP83108202 A EP 83108202A EP 83108202 A EP83108202 A EP 83108202A EP 0104413 A1 EP0104413 A1 EP 0104413A1
Authority
EP
European Patent Office
Prior art keywords
housing
insulation
blades
segments
insulating
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.)
Withdrawn
Application number
EP83108202A
Other languages
German (de)
English (en)
Inventor
Christian O. Schön
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0104413A1 publication Critical patent/EP0104413A1/fr
Withdrawn legal-status Critical Current

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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/28—Selecting particular materials; Particular measures relating thereto; Measures against erosion or corrosion
    • F01D5/284—Selection of ceramic materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/03—Annular blade-carrying members having blades on the inner periphery of the annulus and extending inwardly radially, i.e. inverted rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/06—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being hot or corrosive, e.g. liquid metals

Definitions

  • the invention relates to a single-stage or multi-stage high-performance centrifugal machine for aggressive and / or hot media, with a rotor having a housing and with a feed and an outlet line for the medium, the rotor being designed as a rotationally symmetrical hollow body, on the inner wall of which blades are essentially are supported radially inwards and the blades consist of a chemical and / or heat-resistant material.
  • a gas turbine is also known in which the rotor blades and a ring surrounding them consist of ceramic material (GB-PS 867 716). Although this material is highly heat-resistant, it generally conducts heat well and can also only absorb very low tensile forces. For this reason, in this known turbine the turbine housing is provided with an annular space surrounding the rotor which can be pressurized in such a way that the effect of the centrifugal forces on the rotor and rotor blades is completely or partially eliminated. Such a design results in extremely complicated design problems with regard to sealing between rotating and fixed parts and the removal of the ceramic parts into the annular space dissipated heat.
  • the invention is therefore based on the object of creating a device of the type mentioned at the outset which enables economical operation at media temperatures of up to over 1600.degree. C. and at very high speeds and pressures of 2000 mm AC and more.
  • the invention solves the problem in that an encompassing insulation made of heat-insulating and highly heat-resistant material is present on the inner wall of the rotor housing.
  • the outer casing of the rotor housing is made of a material with high tensile strength (steel, carbon fiber, or the like), the blades are made of a highly heat-resistant material that especially when simple plate-shaped blades are used, is essentially suitable for absorbing only compressive stresses, such as ceramic, and the insulation layer on the inside of the rotor housing is made of a material which has high thermal insulation, but which does not need to absorb tensile or substantial compressive forces and can be relatively soft and amorphous. It only has to absorb centrifugal forces without solidifying too much.
  • the inner contour of the housing can be conical or cylindrical.
  • the conical configuration can be achieved, for example, by the housing widening in steps and the steps being filled on the inside by the lining in such a way that a cone is formed on the inside.
  • the blades need not be held by pins on the housing, 'but they are supported on the steps.
  • the conical shape par excellence can be of particular advantage, particularly in the case of single-stage blowers or compressors, because of the better conveyance of the gases.
  • ceramic wool or rock wool can be introduced between the blades attached to the inner wall of the housing as thermal insulation, which densifies when the housing rotates.
  • a cover for example a mesh screen; kept at a standstill.
  • loose packing elements can also be introduced, such as so-called Raschig rings, which can be made of metal, glass or ceramic and which are pressed together and fixed by the centrifugal forces.
  • Raschig rings can be made of metal, glass or ceramic and which are pressed together and fixed by the centrifugal forces.
  • a honeycomb-like insert can also be used here, for example made of very thin sheet metal. The honeycomb-shaped cavities extend axially. The gas enclosed in the honeycomb provides a high level of insulation since it cannot circulate.
  • thermal insulation between the blades according to the invention is that radially extending, spaced-apart fixed plates made of a high-temperature-resistant material, e.g. cast porous ceramic plates, and that the plates are held at least in their radially outer region by insulating wool pressed between them, i.e. the blades and the insulation need not be screwed.
  • the whole system remains elastic in itself and the production is simplified since screwing requires a more precise production.
  • the outer layer can be elastic and ceramic insulation rests on this elastic layer. Tensions are absorbed in the outer layer, while the rigid high-temperature part can expand.
  • a very advantageous further training possibility consists in the fact that the radially extending plates which are fixed to the inner wall of the housing and are arranged at a distance from one another serve as insulation between the blades, whose mutually facing surfaces have axially extending step-shaped projections or recesses, each of which forms a radially extending labyrinth channel between two plates.
  • This training is suitable for relatively large plants. If everything is lined with ceramic, the ceramic could blow up the case. In the outer area of the labyrinths, the specifically heavier cooled gas remains by centrifugal force, while the specifically much lighter hot gas cannot escape to the outside. No swirling can take place either.
  • the housing end wall has an insulation on the inside, which consists of individual circular segments leaving a gap between them. Since the insulating material, for. B. porous ceramic material, more than steel, is thereby avoided that at the high temperatures n the insulation in the relatively cool steel housing expands so that it is blown up.
  • the insulation preferably consists of at least two layers of segments arranged axially one behind the other, the segments of the individual layers being offset from one another.
  • the segments can be provided with grooves or projections projecting into them, which engage in a contactless manner to form labyrinths.
  • the arrangement can be such that the labyrinths run either radially or in the direction of rotation. They can be completely or partially filled with deformable insulating materials.
  • loose insulating fillers e.g. densified glass wool, rock wool or the like. or a plurality of hollow bodies of cylindrical or polygonal (honeycomb-shaped) cross section with axes essentially parallel to the housing axis.
  • These hollow bodies can consist of steel or an insulating material. The air enclosed in the hollow body has a high insulating effect.
  • the insulating effect is created by the respective substance itself and / or by the gases enclosed in each case.
  • porous ceramic material e.g. fireclay or other suitable materials can also be used.
  • it can have notches arranged at a distance in several axially perpendicular radial planes or it can be axially divided into several sections.
  • the gas guide tube ends directly at or shortly behind the free blade edge and penetrates the gas outlet tube which is designed as a bend and which has a substantially larger diameter corresponding to the housing diameter on the open end face, preferably in the case of a multi-stage configuration for higher pressures, the housing is on both Sides open for axial flow and a guide blade is fastened in front of each rotor blade to a fixed holder which penetrates the housing within the inner blade circle diameter.
  • This type of fan can be flowed through in both directions. But it can also be in Strömüngs direction, a standing baffle and a rotating baffle are provided in front of each fixed guide vane. These fans can only be flowed through in one direction.
  • a very important advantage of the device according to the invention is that if it works in a closed system, no sealing is required on the pressure side. The device then works as a suction fan. However, if the device is operated as a pressure system, a seal is required.
  • a non-contact labyrinth seal which overlaps one of the two parts and is formed from annular disks and is attached to both parts, is arranged between the housing and the respective fixed gas guide tube adjoining the housing wall.
  • a cold gas can be fed into these labyrinths in order to cool the housing jacket.
  • the gas pressure can be regulated depending on the temperature measured outside in the gap area.
  • the ring disks forming the labyrinths are preferably designed as rotating or standing axial blades.
  • the pressure forced by the blades counteracts the gap pressure acting outwards due to the centrifugal forces and the overpressure generated. Ideally, all pressures in the gap cancel each other out.
  • the labyrinths can also be formed on opposite radial annular disks attached to the ends of the respective circumferential and fixed part, wherein they are formed by a ceramic coating applied to the circumferential annular disk with concentric annular grooves introduced therein, into which corresponding ones are located engage the fixed washer arranged concentric rings without contact.
  • the circumferential housing consists of a cylindrical sheet steel jacket 1, which is closed on one end by a steel sheet washer 2, which carries a shaft journal 3, which is mounted and can be driven in a manner known per se .
  • Plate-shaped blades 4 made of ceramic are supported and fastened to the latter within the cylindrical housing 1, e.g. by means of cast-in bolts.
  • the space between the blades 4 and the inner sides of the disk 2 are covered by means of corresponding segments 5 or an insulating compound, e.g. Ceramic insulating compound, existing pane 6 covered.
  • any other suitable heat-insulating material can also be used.
  • the jacket including the cladding can also be designed as a cone.
  • FIGS. 4-8 show still other possibilities for the insulation for the steel sheet jacket.
  • loose insulation 11 is shown between the respective blades, e.g. Rock wool, which condenses on rotation.
  • the blades 4 are held here by stud bolts 12.
  • a sieve 13 is provided radially on the inside.
  • anchors 14 fastened in the steel jacket 1 can also serve to hold the insulation 11.
  • raster or porous ceramic plates 15 are arranged at a distance from one another between the blades 4 and are held by caulked insulating wool 16 or the like.
  • the blades 1 and the plates 15 need not be screwed in this case.
  • Figure 6 shows an embodiment in which a layer of low-temperature insulation 17, e.g. a foam, and inside a layer 18 high temperature insulation are introduced.
  • the blades 4 are screwed together by means of stud bolts 12.
  • a gap 19 is left between each blade 4 and the high-temperature insulation 18 in order to allow this layer to expand. If necessary, a soft insert can be introduced into the gap.
  • the insulating plates 20 labyrinths 21 arranged between the blades 4 and screwed to the housing 1 have projections and recesses. Centrifugal force throws cold and therefore heavy gas to the outside, while the specifically much lighter gas cannot escape due to the labyrinths and the lower centrifugal force.
  • the plates 2o which are preferably made of fired porous ceramic, can expand freely when heated.
  • the blades 4 are also provided with corresponding projections 22 in order to likewise form a labyrinth with the respectively adjacent plate 20.
  • the insulating plates 2o can be cast over a common shell 23 abutting the housing 1.
  • the multi-stage compressor design according to FIG. 9 corresponds essentially to the design according to FIGS. 1 and 2, with the exception that the fixed feed pipe 7 'extends close to the closed end of the cylindrical housing 1 and carries fixed guide vanes 24 which protrude between the guide vanes 4 .
  • the formed as a manifold outlet conduit 27 opens just before the housing 1.
  • a labyrinth seal 28 is provided, which essentially consists of two parts attached to annular discs 29 and 3 0 the interdigitated and non-contact, exists.
  • a cold gas is fed into the resulting labyrinth via line 31, which counteracts the total pressure formed by centrifugal forces and gap pressure and cools the housing at this point.
  • the temperature of the cold gas supplied can be regulated by measuring the temperature at 32.
  • a cold gas shown here it is possible to design the annular disks 29 and 3o as small, short axial blades, by means of which cool atmospheric air is forced into the gap 10.
  • the multi-stage compressor according to Figure 1o is designed as a flow compressor.
  • the circumferential housing 1 is mounted at 25 in a manner known per se by means of roller bearings, slide bearings, magnetic bearings or the like. by means of V-belts .., magnetically or the like. Also driven in a known manner.
  • the fixed guide vanes 24 are held by means of a fixed holder 26.
  • pipes 33 and 34 serving as supply or outlet lines are arranged, each of which is sealed off from the rotating housing cylinder 1 by means of a labyrinth seal, as described in connection with FIG. 9.
  • the compressors according to FIGS. 9 and 10 can be operated in both directions, the terms supply and outlet lines each having to be exchanged.
  • FIG. 13 A multi-stage version is shown schematically in FIG. 13, in which the housing 1 widens in steps and a rotor blade 4 is arranged on each stage.
  • the insulation 5 forms a continuously conical extension on the inner contour.
  • FIG. 14 schematically shows yet another sealing option between the peripheral housing part 1 and the fixed outlet line 27.
  • Both parts have ring disks 37 and 38, which are firmly connected to them at the free ends facing one another.
  • the ring disk 37 goes back into one at its radially outer end short zy Lindric ring 39 over.
  • the insulation 5 is also drawn in the form of an annular disk over the annular disk 37 and in this part 40 is provided with concentric annular grooves 41, into which concentric rings 42 attached to the fixed annular disk 38 protrude and form a layout.
  • the concentric rings 42 can be designed as small, short blades for conveying cool air inwards.
  • the insulation shown in Figure 1 on the inside of the end wall 2 - shown there for example as a porous ceramic disk 6 - is, as shown in Figures 15 and 16, here divided into segments 43 and 44, which are arranged in two layers offset from each other and between them leave radial column 45. More than two layers can also be provided.
  • the two layers 43 and 44 are arranged at a small distance from one another and, as shown only in FIG. 16, can have circumferential grooves and projections 46 and 47 on the facing end faces, which form a labyrinth 48.
  • the segments 43 and 44 are screwed to the housing jacket 1.
  • the grooves 49 and projections 50 forming the labyrinths can also run radially on the opposite end faces of the segments 45 and 44, respectively.
  • labyrinths 51 can also be formed on the radial edges of the segments 52, which are narrower here than in the previous examples.
  • flat closing segments 53 are arranged which cover the gaps and which make it more difficult for hot gases to enter the labyrinths 51.
  • loose fillers such as glass wool, rock wool, ceramic wool or the like can also be introduced between the end wall 2 and the end segments 53.
  • foamed materials such as foam glass, foam ceramic or porous ceramic infage.
  • honeycomb-shaped or cylindrical hollow bodies made of steel or an insulating material can also be introduced, in which the air enclosed in the hollow bodies has an insulating effect.
  • the mutually facing surfaces of the segments 43 and 44 have small-area projections 54 or depressions 55, the projections 54 engaging in the depressions 55 without contact.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Ceramic Engineering (AREA)
  • Materials Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP83108202A 1982-09-01 1983-08-19 Machine rotative d'un ou de plusieurs étages de haute pression pour les fluides agressifs ou chauds Withdrawn EP0104413A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3232433 1982-09-01
DE3232433 1982-09-01
DE3235585A DE3235585C2 (de) 1982-09-01 1982-09-25 Hochleistungsgebläse oder -verdichter für aggressive und/oder heiße Medien
DE3235585 1982-09-25

Publications (1)

Publication Number Publication Date
EP0104413A1 true EP0104413A1 (fr) 1984-04-04

Family

ID=25804148

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83108202A Withdrawn EP0104413A1 (fr) 1982-09-01 1983-08-19 Machine rotative d'un ou de plusieurs étages de haute pression pour les fluides agressifs ou chauds

Country Status (4)

Country Link
US (1) US4541776A (fr)
EP (1) EP0104413A1 (fr)
CA (1) CA1217172A (fr)
DE (1) DE3235585C2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0173803A1 (fr) * 1984-09-05 1986-03-12 Latimer N.V. Machine d'écoulement
GB2174757A (en) * 1985-05-07 1986-11-12 Nuaire Ltd Fan

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0791660B2 (ja) * 1989-08-30 1995-10-04 株式会社日立製作所 環境遮断用耐熱壁を備えた地上機器
US5288205A (en) * 1990-09-26 1994-02-22 The United States Of America As Represented By The Secretary Of The Navy India-stabilized zirconia coating for composites
GB0206136D0 (en) * 2002-03-15 2002-04-24 Rolls Royce Plc Improvements in or relating to cellular materials
EP1980715A1 (fr) * 2007-04-13 2008-10-15 Siemens Aktiengesellschaft Amortissement de vibrations dans des aubes mobiles et fixes par granulat
TR201819956T4 (tr) 2014-03-21 2019-02-21 Exergy Spa Radyal turbo maki̇ne.
US9945258B2 (en) * 2014-10-10 2018-04-17 Ford Global Technologies, Llc Sheet metal turbine housing with cellular structure reinforcement
GB201616239D0 (en) * 2016-09-23 2016-11-09 Intelligent Power Generation Limited Axial Turbine
DE102020121030A1 (de) * 2020-08-10 2022-02-10 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Luftfahrzeug und dessen Herstellung

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB867716A (en) * 1959-05-26 1961-05-10 Klaus William Mikael Kerppola Improvements in or relating to turbines
DE3016817A1 (de) * 1980-05-02 1981-11-05 Hans-Peter Dipl.-Ing. 4800 Bielefeld Böddeker Gasturbinenrotor mit extrem hoher warmfestigkeit

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR339962A (fr) * 1904-01-27 1904-06-23 Jean Marcel Aubert Genre de turbine motrice pouvant tourner dans les deux sens et à vitesse variable
US3312389A (en) * 1964-05-04 1967-04-04 Fukuo Saeki Air blower device with silencer
GB1043089A (en) * 1964-06-30 1966-09-21 Shelley Electric Furnaces Ltd Improved kilns and similar heat treatment apparatus
DE7029967U (de) * 1970-08-10 1971-06-03 Willig Kurt Neuartige gasturbine.
US3778184A (en) * 1972-06-22 1973-12-11 United Aircraft Corp Vane damping
CA994246A (en) * 1973-09-27 1976-08-03 Harold Tai Vane damping
FR2330276A5 (fr) * 1973-12-05 1977-05-27 United Aircraft Corp Amortisseur pour aubes de turbine
US4083180A (en) * 1976-10-01 1978-04-11 Caterpillar Tractor Co. Gas turbine engine internal insulation

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB867716A (en) * 1959-05-26 1961-05-10 Klaus William Mikael Kerppola Improvements in or relating to turbines
DE3016817A1 (de) * 1980-05-02 1981-11-05 Hans-Peter Dipl.-Ing. 4800 Bielefeld Böddeker Gasturbinenrotor mit extrem hoher warmfestigkeit

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0173803A1 (fr) * 1984-09-05 1986-03-12 Latimer N.V. Machine d'écoulement
GB2174757A (en) * 1985-05-07 1986-11-12 Nuaire Ltd Fan

Also Published As

Publication number Publication date
DE3235585A1 (de) 1984-03-08
CA1217172A (fr) 1987-01-27
US4541776A (en) 1985-09-17
DE3235585C2 (de) 1985-11-14

Similar Documents

Publication Publication Date Title
DE2406277C2 (de) Kühllufteinlaß
DE2518919C2 (de) Gasturbinenanlage
DE10303088B4 (de) Abgasgehäuse einer Wärmekraftmaschine
EP2787168B1 (fr) Rotor pour une turbomachine avec un arbre creux
DE2907769C2 (de) Turbinenschaufel-Mantelhalterung
DE69018338T2 (de) Gasturbine.
EP1451450B1 (fr) Ensemble turbine a gaz
EP0104413A1 (fr) Machine rotative d'un ou de plusieurs étages de haute pression pour les fluides agressifs ou chauds
DE1300346B (de) Gasturbine
DE2842410C2 (fr)
WO2015022222A1 (fr) Écran thermique comportant un résonateur de helmholtz
DE1286333B (de) Ringfoermige Leitvorrichtung fuer Gasturbinentriebwerke mit axialer Stroemung
DE19757945B4 (de) Rotor für thermische Turbomaschine
DE2728750A1 (de) Geblaeseschlaegermuehle
DE2140337B2 (de) Gasturbinentriebwerk mit wärmebeweglich gelagerter Welle
DE1476771B1 (de) Gasturbinentriebwerk fuer Strassenfahrzeuge
DE2201730C3 (de) Vorrichtung zum Kühlen von gebranntem oder geeinterem Gut
DE8224628U1 (de) Hochleistungsgeblaese oder -verdichter fuer aggressive und/oder heisse gase
DE972115C (de) Axialdurchstroemte Turbine fuer heisse Treibmittel, insbesondere Gasturbine
DE915088C (de) Kuehlung fuer Turbomaschinenanlagen
DE3000614A1 (de) Turbomaschine
EP2159380A1 (fr) Dispositif de turbine à gaz avec carter poreux et son procédé de fabrication
DE102007005010A1 (de) Abgasturbine mit thermischer Isolation
DE2009140C3 (de) Querstromgebläse für einen industriellen Warmbehandlungsofen
CH639171A5 (en) Stator for at least one part of a multi-stage axial flow turbo-engine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

17P Request for examination filed

Effective date: 19840912

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19880429