EP3183079A1 - Modèle de coulée de boîtier, série de boîtier et procédé de fabrication d'un boîtier coulé d'une turbomachine à énergie fluidique radiale - Google Patents

Modèle de coulée de boîtier, série de boîtier et procédé de fabrication d'un boîtier coulé d'une turbomachine à énergie fluidique radiale

Info

Publication number
EP3183079A1
EP3183079A1 EP15763591.3A EP15763591A EP3183079A1 EP 3183079 A1 EP3183079 A1 EP 3183079A1 EP 15763591 A EP15763591 A EP 15763591A EP 3183079 A1 EP3183079 A1 EP 3183079A1
Authority
EP
European Patent Office
Prior art keywords
housing
model
casm
pressure
cast
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
Application number
EP15763591.3A
Other languages
German (de)
English (en)
Other versions
EP3183079B1 (fr
Inventor
Sebastian Huth
Dieter Nass
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.)
Siemens AG
Original Assignee
Siemens 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 Siemens AG filed Critical Siemens AG
Publication of EP3183079A1 publication Critical patent/EP3183079A1/fr
Application granted granted Critical
Publication of EP3183079B1 publication Critical patent/EP3183079B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22C—FOUNDRY MOULDING
    • B22C7/00—Patterns; Manufacture thereof so far as not provided for in other classes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22C—FOUNDRY MOULDING
    • B22C9/00—Moulds or cores; Moulding processes
    • B22C9/02—Sand moulds or like moulds for shaped castings
    • 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
    • F04D17/125—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 the casing being vertically split
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/20—Manufacture essentially without removing material
    • F05D2230/21—Manufacture essentially without removing material by casting

Definitions

  • the invention relates to a multi-part housing casting model for the production of the cast housing of Radialturbofluidenergiema- machine.
  • the invention relates to a housing series of a series of a radial turbofan energy machine.
  • the invention relates to a method for producing a cast housing of a radial turbofan energy machine comprising the steps:
  • Casing models due to the molding and casting - which corresponds to a copy of the mold - are identical to the mold casings except for differences that are immaterial to the invention.
  • Housing casting model, a housing series and method for producing a cast housing a radial turbofluid energy ⁇ machine employs. This is due to the fact that advantages in the radial turbofluid energy machine are due to the nature of the objects and methods according to the invention. This mental fusion is not always repeated in the following.
  • Radial turbo fluid energy machine for which the hergestell ⁇ th by means of the above presented objects and process housing are specified, as a turbo compressor often used in the form of pipeline compressors for production of natural gas.
  • Compressor stage must be specially adapted.
  • Radial Turbofluid energiemaschinen are usually provided as a compact unit with a drive or output on a ge ⁇ common platform. During maintenance or inspection of the radial turbo fluid energy machine an opening of a housing is usually required, and it is preferable to avoid an expense to the other is closed ⁇ aggregates. In particular, a drive or output of the radial turbofan energy machine should not have to be moved.
  • the casing to be produced by means of the initially defined objects and procedural ⁇ ren are preferred in pot design designed so that there is no parting line extending along the central axis or axis of rotation on the housing. Since the machines are usually placed horizontally on ⁇ , this type of parting joint is then also referred to as a horizontal parting line.
  • a parting line is accompanied by Loka ⁇ len, necessary in the region of the parting material concentrations that require space on the one hand, on the other hand, additional material and also cause changes in stiffness within the housing. Avoiding the horizontal parting joint also has the advantage in pot design that un ⁇ ter be no asymmetric in dealing direction deformations of the mechanical and thermal stresses on the housing, which can lead to alignment problems and leaks in the parting line.
  • the preferred application of the invention are the housings of radial turbocompressors, in particular designed as a pipeline compressor for the compression of natural gas.
  • the housing according to the invention a Radialturbofluidenergyma ⁇ machine can also be used for an expander. In essence, such a design is identical with reversal of the flow direction.
  • high pressure and "low pressure” are to be understood in the context of this document such that during normal operation of the machine according to the invention in the region of low pressure a lower pressure prevails than in the area of high pressure.
  • Low pressure does not necessarily mean that there mr ⁇ Schende pressure level in the order of atmospheric pressure or is below.
  • FIG. 5 shows a conventional Radialturbofluidenergyma- machine is in the form of a centrifugal compressor represented in longitudinal section-specific ⁇ automatically.
  • the illustrated radial turbofluid energy engine RFM comprises a rotor R which extends along an axis X and comprises the impellers IMP, specifically in the flow direction: a first impeller IMP1, a second impeller IMP 2 and a third impeller IMP3.
  • a process fluid PF passes through the inlet of a housing CAS in the interior of the machine and is by means of
  • Impeller IMP and compressed by means of stationary between the impellers arranged shelves to a final pressure.
  • the process fluid PF is collected in a high-pressure spiral HSP before it leaves the housing CAS radially through an outlet.
  • the housing CAS substantially comprises a housing casing CCV, on a low pressure side, a low-pressure cover LPC and on a high pressure side of a high pressure ⁇ lid HPC.
  • the high-pressure spiral HSP takes up so much radial
  • the housing CAS is bell-shaped with optimization of the material ⁇ requirement and the space requirement, wherein the larger outer and inner diameter is provided on the high pressure side due to the high-pressure spiral HSP.
  • large high-pressure cover of the HPC Gezzau ⁇ ses CAS must be particularly ⁇ det etcbil and sufficiently dimensioned due to the pressure with respect to its strength and complex fixed to the casing CCV in diameter.
  • the diameter of the high-pressure Spi ⁇ rale and thus the high-pressure lid shapes the overall size of the machine and causes high costs.
  • Due to the required bell shape of the housing CAS the lateral surface is also not nearly cylindrical and walls of the lateral surface are bent.
  • the likewise bell-shaped, because of the dimensions of the high pressure spiral HSP formed in ⁇ nenbündel IB can only along a first axial mounting direction DX1 in the housing CAS or the
  • Housing jacket CCV be introduced.
  • the introduction of the In ⁇ nenbündels IB is done through the opening of the housing shell by the high-pressure lid HPC. Due to the bell shape also to the inner diameter of the casing CAS is support of the inner beam IB in the housing shell does not mög ⁇ Lich during assembly of a waste, so that prolong a so-called horsetail the inner bundle IB along the rotor siege and outside the housing CAS on the low-pressure side or on the low-pressure cover the horsetail (eg Fig 3, 4, 5 EP 2 045 472 AI) is supported against the weight of the rotor, so that an axial introduction of the inner beam IB in the direction of the first mounting direction DX1 without obstructive contact of the inner beam IB on the inside of the
  • Housing jacket CCV can be done.
  • a further disadvantage of the conventional design of the radial turbofan energy machine RFM according to FIG. 5 is the enormous dimensions of the high pressure cover HPC, which is oriented in its diameter at the high pressure spiral HSP belonging to the inner bundle IB.
  • the large diameter be ⁇ dingt a massive thickness of the high-pressure lid HPC and requires particularly reliable stationary seals the high-pressure lid HPC to the housing jacket CCV, the
  • Casing jacket CCV is additionally weakened in the high-pressure area by fastening the HPC high-pressure lid by means of SCR screws.
  • the high weight of the HPC high-pressure cap calls in addition special measures also in the context of assembly for supporting and guiding the high-pressure lid HPC and a special care, so that the sealing of the high ⁇ pressure lid HPC is not destroyed in the joining process.
  • the invention has set itself the task, the
  • the invention proposes a method for producing a cast housing of the initially defined kind with the additional features of the method claim.
  • the invention proposes a novel housing series.
  • the particular advantage of the method according to the invention lies in the variability of the design of the housing required for the radial turbo fluid power machine, the housing being advantageously provided as a cast component in terms of flow and not the same number of complete ones for a large number of geometries for the high-pressure spiral
  • Low-pressure casing shell models only have to have an identical geometry or cross-sectional geometry at the end faces which are respectively opposite and which are to be joined, so that a largely smooth transition between see the assembled model parts is guaranteed.
  • Judging from the example shown in Figure 3 example shows that in an ultimate type variety of ten different geometries for the entire housing model coat only five high-pressure parts and two low-pressure parts must be be ⁇ riding provided. This saving is added to the special material savings resulting from the design of the housing as a cast component with integrated high-pressure Spira ⁇ le.
  • the special modularization on which the invention is based makes it possible not to provide the high-pressure spiral to an inner bundle to be introduced into the housing but to carry it out as an integral part of the housing.
  • High-pressure housing shell models can be selected which different high-pressure housing shell models fit to the same high-pressure model cover or the same opening vorse ⁇ hen, which is to close by means of the high-pressure model cover.
  • Low pressure housing shell models can be selected, which match different Niederbuchgephaseusemantel models to the sel ⁇ ben low pressure model cover or provide the same opening, which is to close ver ⁇ means of the low pressure model cover.
  • Another advantageous development of the invention provides that the housing model casing is designed such that the cast housing to be produced therewith is formed undivided in the axial direction.
  • the housing model jacket is formed such that the thus produced Gussge ⁇ housing is configured undivided and in the circumferential direction.
  • the undivided design of the housing model shell in the axial direction relates only to the design of the shell itself, wherein this is formed axially closable by means of the already described Hochtikde ⁇ ckels and low pressure lid.
  • at least the area of the Hochdruckmodellspi ⁇ rale is performed with stiffening rib models, so that the wall thickness of the high-pressure model spiral or the high-pressure spiral can be made smaller, because the high-pressure spiral is executed in this way rib-stiffened.
  • Housing cast model comprises at least one embarkstellfußmodell, by means of which at least one Aufstellfuß is model-technically formable to the other cast housing.
  • Housing cast model is provided for the outlet nozzle and an extension direction along a
  • Outlet nozzle axis results from the training and attachment and an inlet nozzle model is provided as a detachable stock ⁇ part of the housing casting model for the inlet nozzle, wherein the inlet nozzle extends along an extension direction of an inlet nozzle axis, where ⁇ in the housing casting model and the formation and attachment of the nozzle models such is trained that the When the radial turbofan energy-generating machine with a horizontal axis is installed, the inlet nozzle axis and the outlet nozzle axis essentially lie in an identical horizontal plane.
  • FIG. 5 shows a schematic longitudinal section through a radial turbo fluid energy machine of conventional type
  • Figure 1 shows a schematic representation of a longitudinal ⁇ section through a multi-part (ie not one-piece) Casegussussmodell CASM comprising a housing model jacket CCVM, a high pressure model cover HCVM and a low pressure model cover LCVM.
  • FIG. 2 shows a housing casting model of this housing in a schematic three-dimensional view according to FIG Invention.
  • the high-pressure model jacket CCVM extends along an axis X from a high-pressure side HPS to a low-pressure side LPS.
  • the housing model jacket CCVM is divided in an axial plane perpendicular to the axis X in a circumferentially extending parting line SPA into a high-pressure model jacket HPCVM and a low-pressure model jacket LPCVM.
  • the high-pressure model ⁇ HPCVM coat is formed in an axial range as a high pressure model spiral HSPM with an opening for an off ⁇ takes clip.
  • the low-pressure model jacket LPCVM has an inlet opening IOC for an inlet connection IFL into the cast housing CAS.
  • the inlet nozzle model IFLM and the outlet nozzle model OFLM are shown. Both that
  • Outlet nozzle model OFLM extend along an axis, namely an inlet nozzle axis IFX and an outlet nozzle axis OFX.
  • the housing casting model CASM is sawn vorzugt formed such that, for a setting up of a corresponding radial Turbo Power engine with a horizon ⁇ talen orientation of the axis X (which is also present as a rotation axis of a rotor R in fully compiled radial fluid turbo Power engine RFM), as well as in Fi - Gur 2 is shown, the inlet nozzle axis IFX and the outlet nozzle axis OFX are arranged in the same horizontal plane.
  • the high-pressure spiral HSP or the high-pressure spiral model HSPM must each be adapted in size. Therefore, the method according to the invention provides that, in a first step, a compilation of the housing casting model CASM takes place, before in a second step
  • Cast housing model CASM takes place and finally in a third step, a casting of the housing CAS takes place.
  • the To ⁇ sammen ein the housing casting model CASM is under ⁇
  • the Housing model jacket CCVM and its division into a high pressure model jacket HPCM and a low pressure model jacket LPCVM are already explained.
  • the combination of the housing model jacket CCVM takes place from a selection of different low-pressure housing model jackets LPCVM and a selection of a suitable high-pressure housing model jacket HPCVM from different models, as shown in FIG. Figure 3 shows the possibilities of five different
  • HPCVM High Pressure Casing Models HPCVM (HPCVM 1 to HPCVM 5) and two different LPCVM low pressure casings (LPCVM 1, LPCVM 2) assemble CASM casemate according to step a).
  • LPCVM 1 to HPCVM 5 High Pressure Casing Models HPCVM (HPCVM 1 to HPCVM 5) and two different LPCVM low pressure casings (LPCVM 1, LPCVM 2) assemble CASM casemate according to step a).
  • LPCVM 1 to HPCVM 5 High Pressure Casing Models HPCVM (HPCVM 1 to HPCVM 5) and two different LPCVM low pressure casings (LPCVM 1, LPCVM 2) assemble CASM casemate according to step a).
  • LPCVM 1 to HPCVM 5 High Pressure Casing Models HPCVM (HPCVM 1 to HPCVM 5) and two different LPCVM low pressure casings (LPCVM 1, LPCVM 2) assemble CASM casemate according to step
  • HPCVM high-pressure casing models are selected for optimum efficiency with the best expansion ratio, impeller outer diameter and spiral base circle.
  • the various high-pressure casing model Coats HPCVM under ⁇ the high pressure model spiral HSPM divorced particular by differently sized plenums SCL.
  • the high-pressure model spiral HSPM provides Versteifungsmodellrip ⁇ pen FINM, in particular, the casting of stiffening ribs for stiffening ⁇ the high-pressure spiral HSP shown in Figure 4 are used.
  • the high-pressure model spiral HSPM has a spiral inlet SPI pointing radially outwards into the collecting space.
  • the spiral collecting space SCL of the high-pressure model spiral HSPM extends radially outward from the spiral inlet SPI, annularly in the circumferential direction and in the axial direction, starting from the spiral inlet SPI toward the low-pressure side LPS.
  • the spiral outlet is secant-like - approximately tangential to the circumferentially enjoyedre ⁇ ckenden spiral collection space SCL.
  • the housing model casing CCVM is provided with foot support models SUPM, wherein the support foot models SUPM support the housing CAS in a first vertical orientation against the ground in a setup as already defined above with a horizontally extending axis X.
  • the support foot models SUPM support the housing CAS in a first vertical orientation against the ground in a setup as already defined above with a horizontally extending axis X.
  • the Aufstellfußmodelle SUPM on the housing model jacket CCVM also Aufstellfußmodelle are provided so that the resulting housing CAS embarkstellf fele for two possible verti ⁇ cal alignments with horizontal axis X has.
  • the radial turbofan energy machine RFM which is shown schematically in longitudinal section in FIG. 4, has a cast housing CAS which extends along an axis X.
  • the Gussgefeldu ⁇ se CAS has a housing jacket CCV formed undivided in the circumferential direction.
  • the Radialturbofluidenergy ⁇ machine RFM is placed horizontally with horizontally extending axis X.
  • a rotor R which is axially guided out of the housing Ge ⁇ CAS extends.
  • the housing casing of the housing CCV CAS ⁇ means of a high pressure cap HCV is sealed from the environment.
  • the housing jacket CCV is closed off from the environment by means of a low-pressure cover LCV.
  • the rotor R is by means of a clutch CUP on the high pressure side HPS with a drive DRI torque transmitting verbun ⁇ the.
  • a radial bearing HBR On the high pressure side HPS is a radial bearing HBR, which is attached to the high pressure cover HCV.
  • a radial bearing LBR On the low pressure side LPS are a radial bearing LBR and a thrust bearing LBA, which are attached to the low pressure cover LCV.
  • Both on the high pressure side HPS and on the Nie ⁇ der horrseite LPS are each a shaft seal, namely, a high pressure shaft seal HSS and a low pressure shaft seal LSS to seal a circumferentially extending movement gap between the rotor R and the respective lid.
  • the housing jacket CCV is in an axial plane perpendicular to the axis X extending in egg ⁇ ner indicated by a dash-dotted line and extending in the circumferential direction along the housing shell CCV parting line SPA ( Figure 1) between a
  • the be ⁇ preferred alternative of the design of the housing shell CCV is that the housing shell CCV of the housing CAS in an axial plane perpendicular to the axis X (also shown here by means of the parting line SPA ( Figure 1)) extending in the circumferential direction extending transition between low pressure side LPS and high-pressure side HPS, wherein the housing shell is continuously integrally formed as a casting in the axial direction, as a result of a made prior to molding and casting in the casting process compilation of the housing casting model of a particular high-pressure model jacket and a certain low-pressure model jacket.
  • SPA Parting line
  • Low-pressure housing jackets are provided.
  • the high-pressure housing jacket HCV is provided with a high pressure spiral HSP comprising a collecting space SCL, wherein the collecting space SCL has a circumferentially tangetial and radially outwardly directed outlet opening OOC and a radially outwardly facing outlet nozzle OFL of the housing CAS or high-pressure housing jacket HPCV.
  • the low-pressure housing jacket LPCV On the low-pressure side LPS, the low-pressure housing jacket LPCV has a radial inlet opening IOP and an inlet connection piece IFL, which adjoins it against the flow direction, into the cast housing CAS.
  • inlet connection IFL is also the socket diametrically into two equal halves dividing flow rib GFI ( Figure 1), on the one hand stiffen the neck and ⁇ other hand, the incoming process fluid PF ( Figure 2) in two substantially identical volumetric flow rates for the two halves of the annular inflow ⁇ divides.
  • FIG. 2 also shows that radially extending stiffening ribs FIN on the outside of the cast housing CAS at least in the region of the high-pressure spiral HSP.
  • This Ver ⁇ steifungsrippen FIN go in a horizontal installation of the machine preferably both towards the bottom in mounting feet SUPM above and in the opposite direction, so that the machine can be placed in the opposite vertical orientation with horizontally extending axis X.
  • This option may be especially useful if the Strö ⁇ flow direction to be reversed with the same arrangement of the drive DRI.
  • FIG. 2 also shows that the outlet nozzle RFL has an extension direction along an outlet nozzle axis OFX, and the inlet nozzle IFL has an extension direction along a direction of extension
  • Inlet nozzle axis IFX identifies, wherein the cast housing CAS is formed such that the outlet nozzle axis OFX and the inlet nozzle axis IFX in a list of radial turbofan energy engine RFM with horizontally extending axis lie substantially in an identical horizontal plane.
  • a compensating piston BAP is provided on the rotor R which separates a high-pressure chamber HPC from a low-pressure chamber LPC by means of a compensating piston shaft seal BAS.
  • the balance piston BAP is arranged axially in the direction of the high pressure side HPS adjacent to an impeller IMP of the rotor R. This is adjacent to the balance piston BAP.
  • te impeller IMP is traversed by the process fluid PF on the highest in the radial turbofluid energy machine RFM pressure level.
  • a compensation line BAC connects the low ⁇ pressure chamber LPC with the inlet chamber INC downstream of the inlet opening IOP. This compensation line BAC is connected for this purpose only to openings in the housing jacket CCV.
  • the machine can be opened by removing the low-pressure cover LCV and a réellebün ⁇ del IBN consisting of the rotor and surrounding flow-guiding components can be axially removed from the housing CAS, without dismantling the compensation line BAC.
  • a method for assembling the radial turbofluid energy machine RFM comprises the following steps: a) setting up the housing jacket CCV with a substantially horizontal axis X,
  • the inner bundle IBN here comprises as stationary components the so-called return stages RRS or intermediate bottoms which respectively downstream of an impeller IMP the process fluid PF by 180 ° C from radially outward to radially inwardly diverting and the downstream befindli ⁇ chen stage axially in the forward following impeller.
  • a high-pressure spiral HSP is part of the housing CAS with a spiral inlet SPI opening radially inwardly from the high-pressure spiral HSP and viewed against the flow direction.
  • a spiral inlet SPI opening radially inwardly from the high-pressure spiral HSP and viewed against the flow direction.
  • downstream of the collecting space SCL extends substantially axially in the direction of the low pressure side LPS.
  • the collecting space SCL is located radially outward of the spiral inlet SPI.
  • FIG. 5 shows a schematic longitudinal section through a conventional radial turbofan energy machine. The essential features of this machine were already described in the introduction to the description.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

L'invention concerne un procédé de fabrication d'un boîtier coulé (CAS) d'une turbomachine à énergie fluidique radiale (RFM), comprenant les étapes suivantes : a) établissement d'un modèle de coulée de boîtier (CASM), b) moulage du modèle de coulée de boîtier (CASM) établi, et c) coulée du boîtier coulé (CAS). L'invention concerne également un modèle de coulée de boîtier en plusieurs parties pour la fabrication du boîtier de coulée de la turbomachine à énergie fluidique radiale. L'invention concerne également une série de boîtier d'une série d'une turbomachine à énergie fluidique radiale.
EP15763591.3A 2014-09-19 2015-09-16 Modèle de coulée de boîtier, série de boîtier et procédé de fabrication d'un boîtier coulé d'une turbomachine à énergie fluidique radiale Not-in-force EP3183079B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014218945.4A DE102014218945A1 (de) 2014-09-19 2014-09-19 Gehäusegussmodell, Gehäusebaureihe, Verfahren zur Erzeugung eines gegossenen Gehäuses einer Radialturbofluidenergiemaschine
PCT/EP2015/071151 WO2016042004A1 (fr) 2014-09-19 2015-09-16 Modèle de coulée de boîtier, série de boîtier et procédé de fabrication d'un boîtier coulé d'une turbomachine à énergie fluidique radiale

Publications (2)

Publication Number Publication Date
EP3183079A1 true EP3183079A1 (fr) 2017-06-28
EP3183079B1 EP3183079B1 (fr) 2018-08-01

Family

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EP15763591.3A Not-in-force EP3183079B1 (fr) 2014-09-19 2015-09-16 Modèle de coulée de boîtier, série de boîtier et procédé de fabrication d'un boîtier coulé d'une turbomachine à énergie fluidique radiale

Country Status (5)

Country Link
EP (1) EP3183079B1 (fr)
CN (1) CN107073561A (fr)
DE (1) DE102014218945A1 (fr)
RU (1) RU2669133C1 (fr)
WO (1) WO2016042004A1 (fr)

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DE102016217669A1 (de) 2016-09-15 2018-03-15 Siemens Aktiengesellschaft Verfahren zur Montage, Turbomaschine
DE102016217672A1 (de) 2016-09-15 2018-03-15 Siemens Aktiengesellschaft Einwellenturboverdichter
DE102018200287A1 (de) * 2018-01-10 2019-07-11 Siemens Aktiengesellschaft Turbomaschineninnengehäuse

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Publication number Publication date
WO2016042004A1 (fr) 2016-03-24
EP3183079B1 (fr) 2018-08-01
RU2669133C1 (ru) 2018-10-08
DE102014218945A1 (de) 2016-03-24
CN107073561A (zh) 2017-08-18

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