US20100098538A1 - Casing for a fluid flow machine - Google Patents

Casing for a fluid flow machine Download PDF

Info

Publication number
US20100098538A1
US20100098538A1 US12/565,309 US56530909A US2010098538A1 US 20100098538 A1 US20100098538 A1 US 20100098538A1 US 56530909 A US56530909 A US 56530909A US 2010098538 A1 US2010098538 A1 US 2010098538A1
Authority
US
United States
Prior art keywords
casing
coil
casings
tensioning
cable
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.)
Abandoned
Application number
US12/565,309
Other languages
English (en)
Inventor
Ferenc Bajay
Martin Reigl
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.)
General Electric Technology GmbH
Original Assignee
Alstom Technology AG
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 Alstom Technology AG filed Critical Alstom Technology AG
Assigned to ALSTOM TECHNOLOGY LTD reassignment ALSTOM TECHNOLOGY LTD ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: REIGL, MARTIN, BAJAY, FERENC
Publication of US20100098538A1 publication Critical patent/US20100098538A1/en
Abandoned 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
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • F01D21/04—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for responsive to undesired position of rotor relative to stator or to breaking-off of a part of the rotor, e.g. indicating such position
    • F01D21/045—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for responsive to undesired position of rotor relative to stator or to breaking-off of a part of the rotor, e.g. indicating such position special arrangements in stators or in rotors dealing with breaking-off of part of rotor
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F04D1/063—Multi-stage pumps of the vertically split casing type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/02—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/628—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/64—Mounting; Assembling; Disassembling of axial pumps
    • F04D29/644—Mounting; Assembling; Disassembling of axial pumps especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/64—Mounting; Assembling; Disassembling of axial pumps
    • F04D29/648—Mounting; Assembling; Disassembling of axial pumps especially adapted for liquid pumps

Definitions

  • the present invention refers to a casing for a fluid flow machine, especially for a turbomachine.
  • the invention also refers to an installation device for attaching a coil on such a casing.
  • Fluid flow machines especially turbomachines such as steam turbines, gas turbines, compressors, hydroturbines or hydropumps, are exposed to very high pressure loads during operation.
  • turbomachines such as steam turbines, gas turbines, compressors, hydroturbines or hydropumps
  • additional loads are added as a result of high temperatures.
  • These loads have to be able to be absorbed by corresponding casings or casings of the fluid flow machines.
  • casings as a rule are assembled from two half-shells which abut against each other in the region of an axial parting plane of the casing.
  • the axial orientation of the casing is determined in this case by the orientation of a rotor of such a fluid flow machine, the rotational axis of which defines the axial direction.
  • the two casing half-shells or half-casings have to be fastened to each other with a comparatively large force in order to be able to meet the demands which exist during operation.
  • a type of construction with a single casing and a type of construction with a double casing, which comprises an inner casing and an outer casing, are known.
  • shrink rings can be attached on the casing on the outside.
  • the casing must have a relatively large wall thickness.
  • the shrink rings have a relatively large dimension in the radial direction, as a result of which the casing is altogether relatively large in construction. Creep deformations, which occur in the course of operation of the fluid flow machine, in this case are comparatively large since the temperature gradient is correspondingly large across the relatively large wall thickness. This especially applies to an inner casing since this is exposed to intense heat from the inside and at the same time is cooled from the outside.
  • the outer casing must also be dimensioned correspondingly larger.
  • An uneven pressure distribution can develop along the parting plane since the bolted connections enable only singular force transmission.
  • the loads of the casing are limited by temperature and pressure.
  • a very large material thickness prevails, as a result of which the temperature gradient can trigger comparatively large plastic deformations.
  • the fixing of the half-casings along the fastening flanges can bring about deformation of the casing in the case of high pressures and/or in the case of high thermal loads. Therefore, the per se circular interior of the casing becomes slightly elliptical as a result of these loads.
  • the invention should provide a remedy for this.
  • the invention as is characterized in the claims, deals with the problem of disclosing an improved embodiment for a casing of the type referred to in the introduction, which is especially characterized by reduced deformation of the casing during operation and/or by reduced weight and/or by reduced production and maintenance costs.
  • the invention is based on the general idea of fastening the two half-casings to each other by means of a coil which wraps around the half-casings on the outside and which is formed with at least one tensionally-loaded cable which comprises at least one wire.
  • the coil can be almost optimally adapted to the rotational symmetry of the casing, which enables an optimum force distribution along the casing.
  • the casing can be designed comparatively thin on account of the homogeneous force distribution, as a result of which the weight of the casing and the production costs can also be reduced.
  • a thin wall thickness of the casing reduces the temperature sensitivity and especially reduces creep deformations due to temperature gradients.
  • the coil as such requires comparatively little installation space in the radial direction, as a result of which the space requirement can be reduced in addition to the reduced wall thickness.
  • the tension cable which can be loaded under tension and can especially be formed by means of a wire cable formed from a plurality of wires, has a significantly higher stability and creep strength in its tensioning direction than the cast material of the half-casings. This also applies when the tension cable and the half-casings are produced from the same material. This is attributable to the different sizes. By the same token, this is attributable to the cold processing of the tension cable which contributes to an advantageous internal material structure, especially with regard to fiber orientation.
  • fastening flanges can be dispensed with as can highly-loadable pretensioning bolts.
  • the outer casing can also be designed correspondingly smaller. The comparatively homogeneous force distribution along the sealing face in the parting plane, in which the two half-casings abut against each other, enables a higher pressure loading and/or temperature loading of the casing even during transient operating conditions, which reduces the susceptibility of the casing to plastic deformations of the sealing face.
  • the tension cable is exposed to altogether considerably lower temperatures than for example the tensioning bolts of a fastening flange, because such tensioning bolts extend inside the respective fastening flange and are consequently arranged comparatively close to the inner surface of the respective casing which especially delimits a hot gas path of a gas turbine or a hot high-pressure region of a steam turbine.
  • the tension cable is located on the outer side of the respective casing and can also be directly exposed to cooling.
  • an installation device for attaching a coil on a casing is characterized in that provision is made for an abutment device which can be attached, or is attached, in a fixed manner on the casing and upon which at least one tensioning device can be supported, which serves for introducing a tensioning force into the tension cable.
  • the forces which are required for the tensioning can therefore be borne directly on the casing which reduces the equipment cost for producing the desired pretensioned coil.
  • FIG. 1 shows a partially sectioned side view of a casing
  • FIG. 2 shows a half cross section of the casing from FIG. 1 corresponding to lines of intersection A
  • FIG. 3 shows a half cross section of the casing from FIG. 1 corresponding to lines of intersection B
  • FIG. 4 shows a non-sectioned side view of a casing with casing diameters which increase in one direction
  • FIG. 5 shows a non-sectioned side view of a casing with casing diameters which vary in the axial direction
  • FIG. 6 shows a non-sectioned plan view of a casing with a combination of conventional bolted connection (on the left) and cable coil (on the right),
  • FIG. 7 shows a non-sectioned side view of a casing with a combination of conventional shrink ring connection (on the left) and cable coil (on the right),
  • FIG. 8 shows a half axial section of the casing with installation device attached thereupon
  • FIG. 9 shows a plan view of the casing in the region of the installation device according to FIG. 8 .
  • FIG. 10 shows a view as in FIG. 8 , but in the case of another embodiment of the installation device,
  • FIG. 11 shows an axial view of the casing with an installation device, wherein the casing is rotated in the cable coil
  • FIG. 12 shows an installation device as in FIG. 11 , but additionally with springs on the axial slide.
  • a casing 1 of a fluid flow machine which is not otherwise shown, comprises two half-casings 2 , 3 , specifically especially an upper half-casing 2 and a lower half-casing 3 .
  • the two half-casings 2 , 3 abut against each other in an axial parting plane 4 , as a result of which the casing 1 is closed in the circumferential direction.
  • the casing 1 comprises a fastening device 5 which is designed so that with this the two half-casings 2 , 3 can be fastened to each other and can be pretensioned against each other.
  • the said fastening device 5 has at least one coil 6 which is formed by at least one tension cable 7 .
  • the coil 6 wraps around the two half-casings 2 , 3 on their outer side. The wrapping is carried out in this case in the circumferential direction, or helically.
  • the helically configured coil 6 in this case expediently has a pitch 8 which corresponds to a cable thickness or to a cable diameter 9 .
  • Other pitches 8 are also conceivable.
  • the tension cable 7 can be formed by a single wire so that it can also be referred to as a tension wire 7 .
  • An embodiment in which the tension cable comprises a plurality of wires which together form a wire cable is also possible.
  • a steel wire is preferably used. At very high temperatures, for example in the case of steam turbines with steam inlet temperatures above 700 degrees C., as are currently designed, a nickel-based material wire can also be used instead of a steel wire.
  • the casing 1 of which is equipped with such a coil 6 it is preferably a turbomachine such as a steam turbine, a gas turbine, a compressor or charger, a hydroturbine and a hydropump.
  • the casing 1 in the case of such a fluid flow machine or turbomachine can form a single casing or an inner casing of a double casing or an outer casing of a double casing.
  • the casing 1 can also form a stator blade carrier or a seal carrier of such a fluid flow machine or turbomachine.
  • the casing 1 is preferably designed in an rotationally symmetrical manner at least in a region which is provided with the coil 6 .
  • the outer sides of the two abutting half-casings 2 , 3 preferably have an outer contour 10 which corresponds to a shell of an rotationally symmetrical body and is therefore circular in cross section.
  • the casing 1 has a constant cross section and is cylindrically designed accordingly.
  • Casings 1 which have a cross section which varies in the axial direction are also conceivable.
  • Conical or frustoconical-shaped casings 1 or casing sections are especially conceivable.
  • Casings 1 with their outside diameter altering in steps are shown in FIG. 4 and FIG. 5 .
  • the cylindricity of the external surfaces of the casing sections which are identified by 42 for example has the advantage that the tension cable 7 cannot slip sideways and that the pretensioning is not consequently lost.
  • the casing sections 42 are axially delimited by means of casing collars 43 .
  • the casing 1 according to FIG. 6 can be equipped with a conventional bolted flange connection 33 in one longitudinal section, and in another longitudinal section, which is preferably associated with the hotter side of the casing 1 , can be provided with a wire coil connection 34 of the previously described type.
  • the casing 1 can be equipped with a conventional shrink ring connection 35 in one longitudinal section, and in another longitudinal section, which is preferably associated with the hotter side of the casing 1 , can be equipped with a wire coil connection 34 of the aforementioned type.
  • the bolted flange connection 33 from FIG. 6 comprises flanges 47 with flange holes 44 for connecting bolts.
  • the shrink ring connection 35 from FIG. 7 comprises bearing surfaces 45 for shrink rings 46 .
  • Each tension cable 7 inevitably has two ends which are not identified here in more detail. These ends of the respective tension cable 7 can be fastened on the casing 1 via corresponding anchor points, which are not shown here. These anchor points for example can be attached on a casing collar 11 or on the cylindrical wire bearing surface. One cable end, however, can also be connected to another cable end of the same cable or of another cable. For example, two wire ends can be welded to each other. Also, an eye can be attached on each cable end, wherein the eyes are then connected by means of a preferably retensionable clamp.
  • the respective tension cable 7 is loaded under tension.
  • the tension can be introduced into the casing 1 or into the half-casings 2 , 3 via the anchor points 11 .
  • the pretensioning of the coil 6 or of the respective tension cable 7 can therefore be dissipated inside the casing 1 .
  • at least one of the anchor points 11 can be designed so that retensioning of the respective tension cable 7 can be carried out with it.
  • the coil 6 can basically be configured with a single layer. This means that the individual windings of the respective tension cable 7 are arranged next to each other exclusively in the axial direction.
  • a multilayer configuration of the coil 6 is also possible.
  • FIG. 1 exemplarily shows a double-layer configuration of the coil 6 , as a result of which individual windings are adjacently arranged in the radial direction as well.
  • Coils 6 with more than two coil layers are also conceivable. To configure the coil 6 so that each coil layer is produced from only a single tension cable 7 is especially conceivable, wherein each winding layer preferably comprises a separate tension cable 7 of its own in each case.
  • the coil 6 is constructed from a plurality of different tension cables 7 , provision can basically be made to configure individual tension cables 7 differently with regard to cable thickness or cable diameter and/or with regard to the wire material which is used. As a result of this, it is especially possible to reduce the cable thickness 9 in higher-loaded regions in order to increase the winding density or to increase the cable thickness in just these regions in the case of a single-layer construction. Wire materials of different strengths corresponding to the strength requirements can also be used. For example, an embodiment is conceivable in which a plurality of winding layers are provided, wherein different tension cables 7 are used in different winding layers. Also, different axial regions, which are enwrapped by different tension cables 7 , can be formed along the casing 1 .
  • the wire material in the colder regions can be produced from less expensive material and in the hotter regions produced from material which is more resistant to heat.
  • the wire material in the hotter first inner winding layers can be produced from material which is more resistant to heat and in the colder outer winding layers produced from less expensive material.
  • centering pins 12 it can be expedient to position the two half-casings 2 , 3 relative to each other by means of centering pins 12 .
  • These centering pins 12 in this case are arranged in the region of the contact plane 4 and are inserted in corresponding centering holes 13 which are preferably formed in each case in a boundary region of the respective half-casings 2 , 3 .
  • the centering holes 13 or the centering pins 12 in this case are oriented perpendicularly to the parting plane 4 .
  • the centering pins 12 enable the locating of a desired relative position between the two half-casings 2 , 3 .
  • centering pins 12 are attached on the half-casings 2 , 3 so that they are located entirely inside the outer contour 10 of the casing 1 in each case, as a result of which a completely recessed arrangement for the centering pins 12 is created. As a result of this, interference of the coil 6 by means of the centering pins 12 does not occur.
  • securing screws 14 in this case serve essentially only for securing the relative position between the half-casings 2 , 3 which is located by means of the centering pins 12 .
  • the securing screws 14 in particular are not able to apply the retaining forces between the two half-casings 2 , 3 which are necessary for the operation of the fluid flow machine which is equipped with the casing 1 . They therefore serve only for facilitating installation.
  • each half-casing 2 , 3 is provided with through-holes or through-bores 15 , as a result of which it is possible to insert the respective securing screw 14 and to form a threaded connection with a complementary securing nut 16 .
  • the securing screws 14 including the associated securing nuts 16 , are attached on the half-casings 2 , 3 so that they are arranged entirely inside the outer contour 10 . As a result of this, a completely recessed arrangement of the securing screws 14 or of the securing nuts 16 can be achieved, which simplifies the attaching of the coil 6 .
  • FIGS. 8 to 12 show installation devices 17 by means of which such a coil 6 can be attached on such a casing 1 .
  • the respective installation device 17 in this case comprises an abutment device 18 which is attached in a fixed manner on the respective casing 1 , or can be at least temporarily attached in a fixed manner on the casing 1 , for installation or for removal.
  • each installation device 17 comprises at least one tensioning device 19 which is designed so that it is either permanently supported on the abutment device 18 or can be at least temporarily supported on the abutment device 18 .
  • the respective tensioning device 19 is designed so that a tensioning force can be introduced into the respective tension cable 7 with it.
  • the abutment device 18 comprises a plurality of insertion holes 20 which for example are incorporated radially into the half-casings or into a corresponding collar on the outside and which are arranged adjacent to each other in the circumferential direction.
  • the respective tensioning device 19 in this case comprises a tensioning lever 21 which can be inserted by a foot 22 into the insertion holes 20 and can therefore be anchored on the abutment device 18 or on the casing 1 .
  • the tensioning lever 21 is pivotably mounted by its foot 22 on a pivot 23 .
  • a clamp fitting 25 is pivotably mounted on the tensioning lever 21 at 24 .
  • the clamp fitting 25 is designed so that it can be connected to the tension cable 7 for introducing tensioning force.
  • the clamping action can be created for example by screws, which are not shown here, clamping the clamping jaws of the clamp fitting 25 .
  • the clamping effect can also be carried out by the clamping jaws being designed in the shape of a wedge and automatically being clamped as a result of the friction between the clamping jaws and the cable and the applied cable tensioning force. This principle is frequently applied for example when clamping test pieces in universal tension testing machines.
  • the non-essential, but helpful, tension spring 26 enables a large displacement movement of the clamping lever 21 to be possible and the cable tension to be able to be accurately adjusted since as a result of the displacement movement of the tensioning lever 21 the tension spring 26 is stretched and a cable tensioning force is created which is adjustable by selection of the spring compliance.
  • the tensioning lever 21 in this case serves for actuating the clamp fitting 25 .
  • This installation device 17 operates for example with two such tensioning devices 19 which, displaced in the circumferential direction, are applied one after the other so that for example with the first tensioning device 19 a tensioning force can be introduced and maintained in the tension cable 7 , while at the same time the second tensioning device 19 can be applied at another position on the tension cable 7 in order to undertake the introduction of the tensioning force so that the first tensioning device 19 can subsequently be removed again for repositioning.
  • the tensioning devices 19 can therefore be displaced in the circumferential direction along the abutment device 18 corresponding to the spacing of the insertion holes 20 .
  • the tensioning lever 21 can be configured in the shape of a Y and via two feet 22 can be supported in each case at two positions on the abutment device 18 .
  • the abutment device 18 comprises a rail 27 which is anchored in a fixed manner to the casing 1 via supports 32 .
  • a slide 28 which forms a component part of the tensioning device 19 , interacts with the rail 27 .
  • the slide 28 in this case is adjustable along the rail 27 , that is to say in the circumferential direction with regard to the casing 1 .
  • the tensioning device 19 can be equipped with a drive, which is not shown, which enables the tensioning device 19 or the tensioning lever 21 to be adjusted along the abutment device 18 or along the rail 27 , that is to say in the circumferential direction of the casing 1 .
  • the tensioning device 19 in the case of the embodiment which is shown here can have a further drive 30 which ensures unwinding of the tension cable 7 , while maintaining the desired tension, during the adjusting movement of the tensioning device 19 in the circumferential direction of the casing 1 .
  • Such an embodiment can include a slide 29 which can be displaced in the axial direction of the casing by a drive, which is not shown here, and as a result can achieve the pitch 8 (see FIG. 1 ) of a helical cable coil.
  • the drives for the circumferential movement of the slide 28 and for the axial movement of the slide 29 are preferably matched to each other in order to maintain the desired helical shape of the cable coil 6 .
  • the tension cable 7 is initially wound on a reel 36 which is provided with a rotational drive, wherein the rotational drive is fastened on a slide 37 which is movable in the axial direction of the casing and provided with a drive, wherein a rail 38 of this slide 37 is connected to the floor 39 in a fixed manner.
  • the casing 1 in turn is rotatably mounted around the axis of the casing, wherein the rotational movement is also implemented by a drive.
  • Corresponding casing bearings 40 are also connected to the floor 39 in a fixed manner.
  • the cable coil is created by the casing 1 being rotated after fastening the tension cable 7 on the casing 1 , while the rotational drive of the reel 36 unwinds the cable 7 from this reel 36 , in fact so that the cable tensioning force corresponds to the predetermined value, i.e. the rotational drive of the reel 36 is load-controlled and not distance-controlled.
  • the axial slide 37 is moved by means of its drive so that the desired pitch 8 of the winding helical shape is achieved.
  • 48 identifies the direction of rotation of the casing 1 , 49 the winding-up direction of the cable 7 , 50 the direction of rotation of the reel 36 , 51 the direction of force of the reel 36 , and 52 the bearing of the reel 36 .
  • FIG. 12 includes the same tensioning device as FIG. 11 , but with the difference that a spring 41 is additionally installed on the axial slide 37 .
  • this spring 41 it is simpler to adjust the tension of the tension cable 7 since a small rotational movement of the reel 37 then brings about only a small change of the tensioning force in the tension cable 7 . Without this spring 41 , the change of the tension force would be much greater and controlling the drive of the reel 37 would be therefore more difficult.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Hydraulic Turbines (AREA)
US12/565,309 2007-03-30 2009-09-23 Casing for a fluid flow machine Abandoned US20100098538A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH00512/07 2007-03-30
CH5122007 2007-03-30
PCT/EP2008/053159 WO2008119654A1 (de) 2007-03-30 2008-03-17 Gehäuse für eine strömungsmaschine

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/053159 Continuation WO2008119654A1 (de) 2007-03-30 2008-03-17 Gehäuse für eine strömungsmaschine

Publications (1)

Publication Number Publication Date
US20100098538A1 true US20100098538A1 (en) 2010-04-22

Family

ID=38162238

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/565,309 Abandoned US20100098538A1 (en) 2007-03-30 2009-09-23 Casing for a fluid flow machine

Country Status (5)

Country Link
US (1) US20100098538A1 (de)
EP (1) EP2129877A1 (de)
JP (1) JP2010523872A (de)
CN (1) CN101680309A (de)
WO (1) WO2008119654A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105531461A (zh) * 2013-09-25 2016-04-27 三菱重工业株式会社 压缩机及增压器
EP4219953A1 (de) * 2022-01-28 2023-08-02 Hamilton Sundstrand Corporation Rotoreindämmungsstruktur

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013013571B4 (de) * 2013-08-14 2023-12-07 Man Energy Solutions Se Abgasturbolader

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US976260A (en) * 1910-04-12 1910-11-22 Charles E Hicks Turbine.
US2199595A (en) * 1939-05-11 1940-05-07 Murray Iron Works Company Turbine

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB702487A (en) * 1951-08-28 1954-01-20 Clayton Manufacturing Co Improvements in or relating to devices for supporting engines or like power sources
EP1293681A1 (de) * 2001-09-14 2003-03-19 ABB Turbo Systems AG Befestigungsvorrichtung für eine Strömungsmaschine

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US976260A (en) * 1910-04-12 1910-11-22 Charles E Hicks Turbine.
US2199595A (en) * 1939-05-11 1940-05-07 Murray Iron Works Company Turbine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105531461A (zh) * 2013-09-25 2016-04-27 三菱重工业株式会社 压缩机及增压器
EP3009634A4 (de) * 2013-09-25 2016-09-14 Mitsubishi Heavy Ind Ltd Verdichter und auflader
EP4219953A1 (de) * 2022-01-28 2023-08-02 Hamilton Sundstrand Corporation Rotoreindämmungsstruktur
US11846199B2 (en) 2022-01-28 2023-12-19 Hamilton Sundstrand Corporation Rotor containment structure

Also Published As

Publication number Publication date
EP2129877A1 (de) 2009-12-09
WO2008119654A1 (de) 2008-10-09
JP2010523872A (ja) 2010-07-15
CN101680309A (zh) 2010-03-24

Similar Documents

Publication Publication Date Title
US8128353B2 (en) Method and apparatus for matching the thermal mass and stiffness of bolted split rings
JP5225695B2 (ja) タービンロータ支持装置及びシステム
JP5706003B2 (ja) ガスタービンのロータ及びシャフト延長部分から軸受本体を引き抜くための方法
EP2500519B1 (de) Turbinenlaufschaufel
US9334738B2 (en) Gas turbine including belly band seal anti-rotation device
US20090188258A1 (en) Altering a natural frequency of a gas turbine transition duct
US8584514B2 (en) Axial loading device and method for magnetically-supported rotor systems
JPH02218824A (ja) ガスタービンエンジン用フレーム組立体
EP2601384B1 (de) Gasturbinenmotor mit einem spannungsbolzen
US20100098538A1 (en) Casing for a fluid flow machine
CN107030449A (zh) 用于空气循环机压缩机壳体的焊料修补
EP3073056B1 (de) Drahtplombe
US20090010760A1 (en) Method of correcting balance of gas turbine
JP6219129B2 (ja) ガスタービンのタービン区画を組み立て及び分解するためのシステム
KR20010014988A (ko) 터빈 노즐의 저 사이클 피로 수명을 증가시키는 방법 및가스 터빈용 노즐
JP6614576B2 (ja) 車室の製造方法、及び回転機械の製造方法
US7861435B1 (en) Method and system for adjusting a turbomachine gland seal
KR20230120982A (ko) T-페어링 설치 툴링 조립체
JP6740466B2 (ja) ターボ機械のホイールを拘束する固定具
JP2024072794A (ja) 水平に配置された機器を操作するためのアセンブリ及び方法
CN113864006A (zh) 一种汽轮机膨胀滑销系统及汽轮机
US20180087383A1 (en) Fixture for restraining a turbine wheel
US20170067362A1 (en) Gas turbine rotor cover
JP2012090397A (ja) 発電機の軸シール装置

Legal Events

Date Code Title Description
AS Assignment

Owner name: ALSTOM TECHNOLOGY LTD,SWITZERLAND

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BAJAY, FERENC;REIGL, MARTIN;SIGNING DATES FROM 20091205 TO 20091208;REEL/FRAME:023723/0874

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO PAY ISSUE FEE