EP2906785A1 - Joint de redondance à faible encombrement, destiné à un carter de turbomachine - Google Patents

Joint de redondance à faible encombrement, destiné à un carter de turbomachine

Info

Publication number
EP2906785A1
EP2906785A1 EP13811882.3A EP13811882A EP2906785A1 EP 2906785 A1 EP2906785 A1 EP 2906785A1 EP 13811882 A EP13811882 A EP 13811882A EP 2906785 A1 EP2906785 A1 EP 2906785A1
Authority
EP
European Patent Office
Prior art keywords
housing
sealing element
pot
sealing
radially
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Withdrawn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
EP13811882.3A
Other languages
German (de)
English (en)
Inventor
Jan Weule
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 EP2906785A1 publication Critical patent/EP2906785A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • F04D29/08—Sealings
    • F04D29/086—Sealings especially adapted for liquid pumps
    • 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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/003—Preventing or minimising internal leakage of working-fluid, e.g. between stages by packing rings; Mechanical seals
    • 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/083—Sealings especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/002—Sealings comprising at least two sealings in succession
    • F16J15/004—Sealings comprising at least two sealings in succession forming of recuperation chamber for the leaking fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/062—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces characterised by the geometry of the seat
    • 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
    • F05D2240/00—Components
    • F05D2240/40—Use of a multiplicity of similar components
    • 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
    • F05D2260/00—Function
    • F05D2260/60—Fluid transfer
    • F05D2260/602—Drainage
    • F05D2260/6022—Drainage of leakage having past a seal

Definitions

  • the invention relates to a housing of a turbomachine, in particular a compressor, with a housing pot and egg ⁇ nem via a common contact surface on the housing pot ⁇ parent housing cover and arranged in the common contact surface seal for sealing the common contact surface with a first sealing element and a radially offset from the first sealing element, second sealing element.
  • Compressors or fluid compressing devices are used in various industries for various applications involving compression or compression of fluids, especially (process) gases.
  • turbo compressors in mobile industrial applications, such as in exhaust gas turbochargers or in jet engines, or even in stationary industrial applications, such as gear turbo compressors for air separation.
  • a plurality of such compressor stages can be connected in series.
  • turbocompressors a distinction is made between radial and axial compressors.
  • the fluid to be compressed for example a process gas
  • the centrifugal compressor the gas flows axially into the impeller of
  • Pinion shafts arranged turbochargers wear, are driven by a large, mounted in the housing drive gear, a large wheel.
  • volute casing in cup-shaped design also referred to as pot spiral casing
  • a spiral insert used in such a way that in the cylindrical bore (of the (housing) pot) axially at the end of the spiral insert a trapped by the spiral housing and the spiral insert ⁇ ner space, a so-called annulus, remains over which the fluid - coming from the impeller - flows radially over the one hand, he ⁇ -expanding cross-section.
  • a plant piping such as a arranged on the volute casing or (housing) bottom pressure nozzle tube with a Druckstutzenflansch arranged thereon, the fluid then flows from the annular space further from the compressor stage.
  • a pot spiral intake flange which is designed as an (axially frontal) housing cover (or else only as a cover), which - via a common "radial”, ie radially extending, axial contact surface (briefly below) also only “radial” contact surface) by means of a (housing) Deckelverschraubung with the pot spiral housing or the (housing) pot screwed - the pot spiral housing or the (Ge ⁇ housing) pot closes axially.
  • Such a transmission compressor a transmission compressor from Siemens called STC-GC, used for air separation, is out
  • a so-called gap monitoring is provided in the lid of the cup spiral housing between the two Dichtele- elements. That is, the sealing effect of the radially inner sealing element is controlled by the gap monitoring.
  • a further, radially tungsnuten between the two dense axially in the end face of the cover is interrupted ⁇ te / inturned circumferential (monitoring) ut is provided wel ⁇ che a monitoring at the interval in the common radial contact surface between the lid and the pot, ie radially formed in the common radial bearing surface between the two seals / sealing grooves.
  • a Connection between the monitoring space to be monitored "made to the outside."
  • a connection flange is welded or screwed to the lid, which in turn egg- ner monitoring device, such as a sensor for detecting leakage, is connected.
  • the invention has for its object to provide a Topfspiralge- housing for a turbomachine, which allows a com ⁇ pact and yet pressure-safe design of the housing and thus also the turbomachine.
  • the housing of the turbomachine has a housing pot as well as a common contact surface on the
  • Housing pot arranged, in particular via the common bearing surface against the housing pot by means of a
  • the seal is configured as a double / tandem seal with a first sealing element and a second sealing element (double / tandem seal) arranged radially offset from one another and radially adjacent to one another.
  • Sealing element - in addition to or in addition to the radial Ver Settlement - also axially offset from each other or axiallychiei ⁇ nander in the common contact surface are arranged.
  • the double / tandem seal with the two (otherwise only) radially juxtaposed sealing elements offset both radially and axially, i. "Obliquely” or “nested” to each other, are arranged.
  • the sealing elements of the seal can thus be arranged compactly (-er) relative to one another - and thus a compact and yet pressure-resistant housing of the turbomachine can be realized.
  • the first sealing element is arranged in a first sealing element receptacle and the second sealing element in a second sealing element receptacle, wherein the first and second sealing element ⁇ receptacle ⁇ in the housing cover and / or in the housing pot, but in particular in the housing cover , are formed.
  • first and / or the second sealing element receptacle are used as circumferential fende chamfer / bevels, in particular on the housing cover, ⁇ out forms / is.
  • first sealing element receptacle is designed as a circumferential chamfer and the second sealing element receptacle is designed as a circumferential, rectangular groove or circumferential, rectangular recess, in particular on the housing cover.
  • a sealing element recording as (triangular) chamfer ie in simplified terms, radial um ⁇ running rooms (sealing element recording) are placed on bevel (short also, triangular cross-sectional shape of the chamfer replaced - in the case of a rectangular groove - rectangular cross-sectional shape of the groove), can even more compact inventive sealing ⁇ arrangements - and thus more compact and pressure-resistant Strö ⁇ tion engine housing or turbomachines realized ⁇ the.
  • the housing cover screw connection can therefore be even closer to the sealing elements and to the pressure surface - and can be even smaller. Also, the residual clamping force of
  • Housing cover screw connection is further improved. Further reduced wall thicknesses in the housing or in the housing pot are possible.
  • such chamfers can be easily produced, for example, by machining activity.
  • the housing cover is referred to only as a suction flange or Topfspiralsaugflansch (in hat shape).
  • the sealing elements are 0-rings, Cupseals, profile seals or other similar sealing ⁇ elements - or combinations thereof -, in particular of plastic, such as PTFE, are.
  • O-rings, Cupseals, profile seals or similar sealing elements, in particular made of plastic, such as PTFE, are - in diversi ⁇ ger embodiment - sufficiently known from the prior art, tested and available inexpensively.
  • the first sealing element is radially ⁇ arranged outside the second sealing member and the first sealing element is an O-ring and the second sealing element are a Cupseal.
  • the radially outer sealing element is an O-ring and the radially inner sealing element is a
  • Cupseal sit in a rectangular groove in the housing cover and the O-ring in a chamfer in the housing cover.
  • an interspace monitoring for the seal in particular for a in the common contact surface formed radially between the first and the second sealing element monitoring space is provided.
  • Surveillance space limiting circumferential chamfer which is formed on the housing pot such that it is arranged radially and axially between the first and the second sealing element in the common bearing surface.
  • the housing cover screw connection can here also be closer to the sealing elements and to the pressure surface - and can be even smaller.
  • the residual clamping force of the housing cover screw connection is further improved here. Further reduced wall thicknesses in the housing or in the housing pot are thus possible.
  • the interstitial monitoring has a bore opening into the area of the chamfer in the monitoring space, wherein the bore is formed quite right to the chamfer.
  • the gap monitoring further comprises at an outer peripheral surface of the housing pot formed, in particular milled, Screw plate for screwing on a ⁇ circuit elements for the gap at the monitoring
  • Housing pot has.
  • a sensor can be connected, which detects leakage into the space to be monitored - and thus controls the sealing effect of the radially inner sealing element.
  • a arranged in the housing pot, a common radial pawflä ⁇ che with the housing pot and the housing cover having Direction spiral insert is provided.
  • this spiral insert in the housing pot is extended axially beyond the housing pot - and thus offers - via its axially verlän ⁇ siege outer peripheral surface - a radial bearing surface both with the housing pot as well as for the housing cover.
  • Housing cover (or even a realized together with the housing cover (Topfspiral-) suction flange) is thereby possible.
  • the radially inner sealing element is arranged on the outer peripheral surface of the spiral attachment.
  • Housing cover / suction flange serves the radial system as "carrier” for the radially inner sealing element.
  • the fit number can be reduced in the housing, which greatly simplifies its processing.
  • the housing is used in a compressor, in particular a compressor for carbon dioxide applications.
  • the compressor can be a single-shaft compressor. Also, the compressor may be a Gereteturbover participatr.
  • a further preferred Wide Erbil ⁇ dung is the inventive housing - as a receptacle for an impeller of a compressor stage and a flow guide for a fluid in the compressor stage - installed in a Gereteturbo- compressor.
  • the housing is used in an expander or a turbine.
  • FIG. 1 shows a detail of FIG. 1 with a section of the gearbox compressor with a pot spiral housing according to the invention with a backup seal in a compact design
  • FIG. 3 shows a detail view of Figure 1 with a cut off of the transmission ⁇ compressor with a inventions to the invention pot spiral housing with backup seal in compact structure
  • FIG. 4 shows a plan view of a gear compressor with a cup spiral housing according to the invention with Bacup seal in a compact design
  • FIG. 5 shows a detail view of Figure 1 with an off ⁇ section of the compressor with a transmission OF INVENTION ⁇ to the invention pot spiral housing with backup seal in a compact design.
  • FIG. 1 shows a longitudinal section through an illustrated part of a compressor stage 18 of a gear compressor 10 with a pot spiral housing 1 according to the invention, which accommodates the compressor stage.
  • the pot spiral housing 1 (hereinafter only housing 1) has a housing pot 2 (in the following only pot 2) and one against the Pot 2 via a common contact surface 6 (between pot 2 and housing cover 8) by means of a screw 19 ver ⁇ screwed housing cover 8 (hereinafter only lid 8 or even (pot spiral) suction flange 8).
  • the compressor stage 18 is formed by a about an axis of rotation 22 rotating and in an axial bore 15 in the pot 2 ⁇ taken - not shown for clarity - rotor or pinion shaft formed at one end, located in the pot 2 (also not shown) impeller is mounted.
  • the impeller is by an axial inflow 12 of a - formed in the housing cover 8, axial flange 24 (which is why the housing cover 8 also referred to as Topfspiralsaugflansch 8) in the pot 2 entering - fluid 11 (axially) flows and promotes the compressed fluid 11 radially outward into an annular space 23 (shown only schematically), wherein the fluid is also compressed.
  • the spiral insert 7 is fitted into the pot 2 in such a way that an enclosed space forming the annular space 23 remains axially at the end of the spiral insert 7.
  • a backup seal 3 is introduced in a compact design in the common contact surface 6 between the pot 2 and the lid 8, the tightness is monitored or controlled by means of a gap monitoring 13.
  • Figures 2 and 3 show this backup seal 2 (also FIG 5) with their gap monitoring 13 in detail.
  • the backup seal 3 is in the form of a double / tandem seal with a first, radially outer sealing element 4, an O-ring, and a first seal. element 4 radially disposed inside, second sealing ⁇ element 5, a Cupseal, designed.
  • Both sealing elements / seals 4, 5, i. the O-ring and the Cupseal are arranged in corresponding sealing element receptacles 14 and 15 in the lid 8.
  • the two sealing element receptacles 14 and 15 are, as the FI Gen 1 - 3 and 5 also show, introduced into the cover 8 in such a way that the two sealing elements 4 and 5 offset both radially and axially, i. "Obliquely” or “nested” to each other, in the cover 8 and in the common bearing surface 6 are arranged.
  • Cupseal 14 and 15 are arranged or introduced.
  • Cupseal 5 realized what a compact design of the backup seal 3 and thereby of the housing 1 and the
  • Compressor 18 / the turbomachine 10 allows.
  • the spiral insert 7, which has been inserted in the pot 2 is extended axially in such a way (axia ⁇ le extension 30) that it - over its axially extended by the axial extension 30 - Fangsisation 31 - forms a common radial bearing surface 21 so ⁇ well with the pot 2 and with the lid 8.
  • This radial outer circumferential surface 31 of the spiral insert 7 is, like the Figs 1-3 and 5, as Shinflä ⁇ surface for the radially inner sealing element 5 or for the Cupseal. 5
  • the radial contact on the common radial abutment surface 21 between the spiral insert 7 and the housing 1, ie the pot 2 and the lid 8, is used several times. Ne ⁇ ben the centering 33 of spiral insert 7 and cover 8, the radial contact also serves as a "support" for the radially inner sealing element. 5
  • the fitting number in the housing 1 can be reduced, which considerably simplifies its machining.
  • the gap monitoring 13, as shown in FIGS. 1 to 3, provides for a monitoring space 26 arranged radially and axially between the first and the second sealing element 4, 5 in the common contact surface 6.
  • This - radially encircling - monitoring space 26 is formed by a bevel 27 on the pot 2, ie there in the range of (complementary) "counterstep" of the pot 2 to the step 25 on De ⁇ claw 8.
  • a drilling during the production of the bore 28 is simplified - and - due to a characterized realizable short bore and a standing at an angle to the sealing surface of the radially inner sealing element 5
  • Anbohr construction in Boh ⁇ tion 28 - damage to the sealing surface of the radially inne ⁇ ren sealing element 5 largely excluded.
  • the second bore 29 extends radially outwardly in the pot wall 35, approximately at an angle of 45 °, where, on a milled surface 17 (see also FIG of the pot 2 to outside of the pot 2 occurs.
  • This milled surface 17 on the outer contour of the pot 2 is used for screw 20 of a connection component (not shown) for the gap monitoring 13th
  • a sensor may be connected, which detects in the space to be monitored 27 penetrating leakage - and thus the sealing effect of ra ⁇ dial inner sealing element 5 and the Cupseal 5 controlled.
  • FIG 5 also shows, there is a mounting fuse 32 of the spiral insert 7 in the pot 2 by means of a stud
  • a corresponding Gewindeboh ⁇ tion 32 in the spiral insert 7 and a corresponding bore 32 in the pot 2 is provided.
  • the backup takes place before the cover 8 or the suction flange 8 presses the spiral insert 7 in the pot 2.
  • This backup seal 3 with their slanted two sealing elements 4, 5 and the laying on chamfer (14, 27) radially encircling spaces in the backup seal 3 as well as in the gap monitoring 26 allow such a compact design, easy to manufacture and pressure-resistant housing 1, at the wall thicknesses 35 are reduced as well as the
  • Housing cover screw 19 closer to the sealing elements 4, 5 and so on the pressure surface sit - and so may be smaller.
  • the residual clamping force of the Gescousedeckelverschraubung 19 is improved.
  • this also reduces the number of fits in the housing 1 and centerings 33 in pot 2, lid 8 and spiral insert 7 easily and efficiently - because multiple uses - are designed.
  • the disassembly of the housing 1 is also easier because the interim ⁇ rule room monitoring 26 during disassembly of the lid
  • suction flange 8 does not have to be dismantled.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)

Abstract

L'invention concerne un carter de turbomachine, pourvu d'un corps creux de carter et d'un couvercle de carter qui est disposé sur le corps creux de carter au niveau d'une surface de contact commune, et qui est notamment vissé contre le corps creux de carter au niveau de la surface de contact commune, ainsi que d'un joint disposé dans la surface de contact commune pour ainsi étanchéifier la surface de contact commune et composé d'un premier élément d'étanchéité et d'un second élément d'étanchéité présentant un décalage radial par rapport au premier élément d'étanchéité. Afin de réaliser un carter à la fois compact et résistant à la pression, le premier et le second élément d'étanchéité sont disposés dans la surface de contact commune de manière à présenter également un décalage axial l'un par rapport à l'autre.
EP13811882.3A 2012-12-17 2013-12-17 Joint de redondance à faible encombrement, destiné à un carter de turbomachine Withdrawn EP2906785A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012223462A DE102012223462B3 (de) 2012-12-17 2012-12-17 Backup Dichtung in Kompaktbauweise bei einem Gehäuse einer Strömungsmaschine
PCT/EP2013/076875 WO2014095843A1 (fr) 2012-12-17 2013-12-17 Joint de redondance à faible encombrement, destiné à un carter de turbomachine

Publications (1)

Publication Number Publication Date
EP2906785A1 true EP2906785A1 (fr) 2015-08-19

Family

ID=48794828

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13811882.3A Withdrawn EP2906785A1 (fr) 2012-12-17 2013-12-17 Joint de redondance à faible encombrement, destiné à un carter de turbomachine

Country Status (5)

Country Link
EP (1) EP2906785A1 (fr)
CN (1) CN104884742A (fr)
DE (1) DE102012223462B3 (fr)
RU (1) RU2015129034A (fr)
WO (1) WO2014095843A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014203466B4 (de) * 2014-02-26 2017-03-30 Siemens Aktiengesellschaft Gehäuse einer Fluidenergiemaschine
EP3594506A1 (fr) 2018-07-12 2020-01-15 Siemens Aktiengesellschaft Bague de contour pour un compresseur
DE102018215280B4 (de) 2018-09-07 2023-03-16 Volkswagen Aktiengesellschaft Anordnung eines fluidführenden Elements unmittelbar oder mittelbar an einem Gehäuse eines Verdichters
DE102018128255A1 (de) * 2018-11-12 2020-05-14 Ebm-Papst Landshut Gmbh Gebläsevorrichtung

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3144035A (en) * 1963-02-01 1964-08-11 Nat Res Corp High vacuum system
IT955877B (it) * 1972-05-26 1973-09-29 Nuovo Pignone Spa Sistema di chiusura ermetica di un corpo cilindrico soggetto ad alte pressioni interne in particolare della cassa di un compressore cen trifugo ad elevata pressione
CH662865A5 (de) * 1984-03-19 1987-10-30 Sulzer Ag Topfgehaeuse fuer eine kreiselpumpe.
DE4127300A1 (de) * 1991-06-15 1993-02-25 Albrecht Dipl Ing Kayser Kombinierter-gleit-und spiralnuten-axial-wellendichtring
DK0723143T3 (da) * 1995-01-12 1999-03-01 Endress Hauser Gmbh Co Indretning til måling af tryk eller differenstryk
DE10200579B4 (de) * 2002-01-09 2013-06-06 Hilge Gmbh & Co. Kg Selbstansaugende Kreiselpumpe
FR2877036B1 (fr) * 2004-10-27 2006-12-22 Snecma Moteurs Sa Dispositif de lubrification d'un composant dans une turbomachine
US7918215B2 (en) * 2006-05-08 2011-04-05 Honeywell International Inc. Compressor stage assembly lock
DE102009012038B4 (de) * 2009-03-10 2014-10-30 Siemens Aktiengesellschaft Wellendichtung für eine Strömungsmaschine
DE102009058411A1 (de) * 2009-12-16 2011-06-22 BorgWarner Inc., Mich. Abgasturbolader
WO2011076704A1 (fr) * 2009-12-22 2011-06-30 Basf Se Ensemble d'étanchéité pour un turbocompresseur de gaz de procédé
CN201771836U (zh) * 2010-07-07 2011-03-23 上海连成（集团）有限公司 一种新型泵壳体密封结构

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2014095843A1 *

Also Published As

Publication number Publication date
RU2015129034A (ru) 2017-01-25
CN104884742A (zh) 2015-09-02
WO2014095843A1 (fr) 2014-06-26
DE102012223462B3 (de) 2013-08-08

Similar Documents

Publication Publication Date Title
DE102011003525A1 (de) Gestufte Teilfuge an einem Getriebegehäuse
EP2906785A1 (fr) Joint de redondance à faible encombrement, destiné à un carter de turbomachine
WO2016062549A1 (fr) Joint de séparation à gradins installé au niveau d'un carter d'engrenage
EP2704813B1 (fr) Plaque d'extrémité pour un élément filtrant, élément filtrant et filtre correspondants
US20160115943A1 (en) Oil discharging system for main shaft bearing of wind turbine generator
EP3587739A1 (fr) Agencement d' anneau de carter pour une turbomachine
EP2906828B1 (fr) Étanchéification d'un rotor de compresseur
DE212012000091U1 (de) Pumpenrotor
EP2826958A1 (fr) Rotor pour une turbomachine thermique
EP2201250B1 (fr) Élément de pompe
EP2002123B1 (fr) Pompe a fluide
EP0290664B1 (fr) Pompe à deux arbres
EP2772652B1 (fr) Paroi intermédiaire pour isoler de façon étanche l'espace arrière d'un compresseur radial
EP3198149A1 (fr) Boîtier de transmission séparable à élément d'étanchéité pour jonction étagée
EP3356678B1 (fr) Pompe à palettes multicellulaire
DE10344718B3 (de) Seitenkanalverdichter
DE102017106779A1 (de) Zentrifugalkompressor
EP2867509A1 (fr) Agencement spécial d'un alésage de raccordement d'un canal de refroidissement
EP3571380A1 (fr) Carter de turbine et procédé de montage d'une turbine comprenant un carter
EP2885544B1 (fr) Carter à volute de pot sans soudure
EP3084229B1 (fr) Carter d'une machine à fluide énergétique
WO2015063252A1 (fr) Ventilateur à pistons rotatifs possédant un système d'étanchéité
DE102015009900B4 (de) Verfahren zum Prüfen eines Abgasturboladers sowie Verfahren zum Prüfen einer Brennkraftmaschine
EP3204651B1 (fr) Pompe centrifuge
DE102016106049A1 (de) Verdrängermaschine

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

17P Request for examination filed

Effective date: 20150511

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20161028