EP0480261B1 - Dispositif de guidage - Google Patents

Dispositif de guidage Download PDF

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Publication number
EP0480261B1
EP0480261B1 EP91116503A EP91116503A EP0480261B1 EP 0480261 B1 EP0480261 B1 EP 0480261B1 EP 91116503 A EP91116503 A EP 91116503A EP 91116503 A EP91116503 A EP 91116503A EP 0480261 B1 EP0480261 B1 EP 0480261B1
Authority
EP
European Patent Office
Prior art keywords
fitting
insert
guide device
larger diameter
fitting position
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.)
Expired - Lifetime
Application number
EP91116503A
Other languages
German (de)
English (en)
Other versions
EP0480261A1 (fr
Inventor
Jörg Urban
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.)
KSB AG
Original Assignee
KSB 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 KSB AG filed Critical KSB AG
Publication of EP0480261A1 publication Critical patent/EP0480261A1/fr
Application granted granted Critical
Publication of EP0480261B1 publication Critical patent/EP0480261B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • 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
    • 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
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid 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
    • F05D2230/60—Assembly methods
    • F05D2230/64—Assembly methods using positioning or alignment devices for aligning or centring, e.g. pins
    • F05D2230/642—Assembly methods using positioning or alignment devices for aligning or centring, e.g. pins using maintaining alignment while permitting differential dilatation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S277/00—Seal for a joint or juncture
    • Y10S277/931—Seal including temperature responsive feature

Definitions

  • the invention relates to a stator for centrifugal pumps according to the preamble of claim 1.
  • the invention has for its object to develop a heavy-duty guide device for centrifugal pumps that are exposed to temperature changes, wherein starting of the pump shaft and impermissible material stresses prevented as well as the tightness is guaranteed. This object is achieved in accordance with the characterizing part of the main claim.
  • the use of two different materials within the guide device may appear to be disadvantageous, especially since the flow-guiding insert made of austenitic material has a greater coefficient of thermal expansion than the pressure-loaded housing part made of ferritic material.
  • the supposed disadvantage a rapidly warming flow-carrying insert, which additionally has a larger coefficient of thermal expansion, is reversed in the opposite in the design according to the invention.
  • a precisely definable behavior of the guide device is possible. Due to the fact that the inner insert is only at one fit point depending on the temperature, tension between the components and thus material overloads are effectively avoided.
  • an austenitic material has higher toughness and wear resistance, which is why its use for flow-guiding applications ensures a long service life.
  • the flow-carrying insert lies only within one fit location within the flow-carrying housing or between the flow-carrying housings. In the cold operating state it is the fitting point arranged on a small diameter, while in the warm or hot operating state it is the fitting point located on a larger diameter. This measure prevents During the start-up phase, that is to say during the transition from the cold operating state to the warm or hot operating state and vice versa, the pump shaft starts up at the bearing points or the sealing bushes due to tension in the pump housing.
  • the unfavorable thermal expansions mean that the flow-guiding insert is without a guide within the pressure-loaded housing part and thus fails to a certain extent, and thus contact between the stationary and rotating part takes place again. At the same time, this prevents eccentricity between the impeller and stator, which prevents the creation of increased hydraulic radial forces on the impeller.
  • a further embodiment provides that in the warm operating state the mating surfaces of the fitting location located on a larger diameter center the flow-carrying insert within the pressure-loaded part. Depending on the operating temperature in each case, only one fit point is used to center the flow-carrying insert within the pressure-loaded housing part.
  • the mating surfaces located on a larger diameter are designed as conical outer surfaces. It is thus achieved in a system of the mating surfaces that forces are transmitted both in the radial and in the axial direction depending on the cone angle.
  • a thin coating is applied to a conical surface (preferably on the austenitic part) to prevent adhesive wear and to minimize friction.
  • another embodiment of the invention provides that the larger-diameter fitting surface of the flow-guiding insert is attached to an elastically resilient component. This ensures that the mating surface part, the component of the resilient, flow-guiding and austenitic insert is resiliently resilient when heated on the cooperating opposite mating surface of the ferritic pressure-loaded housing part.
  • the elastically resiliently arranged fitting surface can slide resiliently along the opposite fitting surface.
  • the operation of the invention can be illustrated as follows.
  • the fit points which usually consist of two circular ring surfaces pushed over one another, have a very specific configuration.
  • the flow-carrying insert In the cold operating state, under which you can usually see a room and unit temperature of around 20 ° C, the flow-carrying insert is only guided at one fitting point, and that is because it lies against the fitting point on the smaller diameter of the pressure-loaded housing part.
  • the fit has a tolerance field, according to which the dimensions result in a transition fit.
  • transition fits lie between the game fits and press fits. In practice, this means that there is no radial gap between the mating surfaces during assembly and in the cold operating state.
  • the fitting location which has a larger diameter, has a radial gap in the cold operating state.
  • the parts coming into contact with the medium expand.
  • the flow-carrying insert that is completely exposed to the medium will expand faster and more than that made of ferritic material Material existing pressure-loaded housing.
  • the radial gaps thus grow at the fitting points.
  • the mating surfaces located on a smaller diameter grow apart and form a radial gap, while the mating surfaces located on a larger diameter grow to a certain extent and close the existing gap. Since the thermal expansion coefficients of the materials are known, the appropriate gap dimensioning and gap configuration can be used to determine exactly at which temperature the radial gap of the fit point, which is located on a larger diameter, approaches zero or when elastic deformation takes place in this area.
  • Impellers (3, 4) are attached to a shaft (1) by means of a tongue and groove connection (2).
  • the pumped medium emerging from the impeller (3) flows into the flow-carrying insert (5), first into the guide channels (6), then reaches an annular space (7) which is delimited from the outside by the pressure-loaded housing (8) and flows from there through the return section (9) downstream impeller (4).
  • the flow-guiding insert (5) is formed here in two parts, the return section (9) and the guide channels (6) forming one part and a cover part (10) closing the guide channels (6) in the axial direction.
  • the cover part (10) and the flow-guiding insert (5) are made of the same austenitic material, so that a fit point possibly located between these parts remains without influence in the event of temperature fluctuations. If necessary, the cover part (10) and the flow-carrying insert can be soldered or welded together.
  • the flow-guiding insert (5) which is formed here in two parts, can also be designed as a one-part component. Within the pressure-loaded housing (8), the flow-guiding insert (5) is centered on the fitting point (11) or (12) which is on a smaller diameter and on a fitting point (13) which is on a larger diameter.
  • the fit points are marked here with dash-dotted lines as details X to Z.
  • the fitting points which consist of two cooperating fitting surfaces, are part of FIGS. 2 and 3 in an enlarged view.
  • a bolt (14) is used here to prevent the cover part (10) or the flow-guiding insert (5) from rotating.
  • Fig. 2 shows the behavior of the fitting point (13) under the influence of temperature.
  • the detail Y encircled in FIG. 1 is shown here in an enlarged representation and at three different operating temperatures above a coordinate diagram.
  • the system temperature from 0 to 200 ° C is shown on the abscissa and the gap size in millimeters on the ordinate.
  • the representation of the fit point (13) shows an elastically resilient component (15) of the cover part (10).
  • Its mating surface (16) like the mating surface (17) attached to and cooperating with the pressure-loaded housing (8), is designed as a conical surface.
  • the insert (5) and the cover part (10) expand further, as a result of which - due to the mating surfaces arranged on the conical surfaces and the resilient component (15) - the mating surface (16) on the mating surface (17) according to graphic representation can slide diagonally upwards along the right.
  • the fitting surface (16) is provided with a thin coating to reduce friction and prevent adhesive wear. In the right-hand illustration of FIG. 2, this is represented by a dash-dotted contour of the elastically flexible component (15).
  • the resilient component (15) is subjected to bending.
  • the 200 ° C given here as the final temperature in the abscissa does not represent a limit for the subject matter of the invention. According to the selected dimensions and gap sizes and the materials used, the subject matter of the invention can readily be used at system temperatures well above 200 ° C. It then represents an optimization task at which temperatures and which gap widths the most favorable load values are determined.
  • the cover part (10) made of austenitic material expands further in the radial direction than the pressure-loaded housing (8) made of ferritic material.
  • the straight line beginning at 20 ° on the abscissa and rising to the top right shows the gap size as a function of the temperature.
  • a radial gap of 0.1728 mm is created.
  • the 200 ° C do not represent an absolute limit, but are only to be understood as an example. Higher temperatures can readily be used in the subject matter of the invention. Due to the fact that the guide device is almost always guided by only one fit point, tension can be effectively prevented.
  • the fit point (12) encircled as detail Z in FIG. 1 largely corresponds in its behavior to the fit point (11). It can be used as an alternative to the fit point (11).
  • Essential to the invention is the fact that within of the stage housing, only two fitting points with different diameters are used. In the example shown here, this can be the fitting points (12) and (13) or the fitting points (11) and (13).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Massaging Devices (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (9)

  1. Dispositif de guidage pour pompes centrifuges à un ou plusieurs étages soumises à des charges thermiques dans lequel chaque dispositif de guidage est composé d'une partie externe de boîtier (8) soumise à la pression et d'un insert (5) interne guidant le courant, dans lequel l'insert (5) peut être accôté dans et/ou à la partie externe (8) du boîtier sur des points d'ajustement (11, 12, 13) placés sur des diamètres différents caractérisé par le fait que
    - que la partie externe du boîtier (8) est fabriqué dans un matériau ferritique et que l'insert (5) guidant le courant est fabriqué dans un matériau austénitique et que
    - l'insert interne (5) est accollé à un point d'ajustement changeant selon la température.
  2. Dispositif de guidage selon la revendication 1 caractérisé en ce que, à régime froid, les surfaces d'ajustement (18, 19) du point d'ajustement (11 ou 12) placé sur le plus petit diamètre sont accollées et en ce qu'une fente est formée entre les surfaces d'ajustements (16, 17) des points d'ajustement (13) placés sur le plus grand diamètre.
  3. Dispositif de guidage selon la revendication 1 caractérisé en ce que, à régime chaud, les surfaces d'ajustement (18, 19) du point d'ajustement (11 ou 12) placés sur le petit diamètre forment une fente qui grandit lorsque la température augmente et en ce que les surfaces d'ajustement (16, 17) du point d'ajustement (13) se trouvant sur le plus grand diamètre présentent une fente qui diminue jusqu'à se fermer lorsque la température augmente.
  4. Dispositif de guidage selon les revendications 1 à 3 caractérisé par le fait que, à régime chaud, les surface d'ajustement (16, 17) du point d'ajustement (13) situé sur le plus grand diamètre centrent l'insert (5) à l'intérieur du boîtier (8) soumis à la pression.
  5. Dispositif de guidage selon les revendications 1 à 4 caractérisé par le fait que les surfaces d'ajustement (16, 17) situées sur le plus grand diamètre ont la forme d'une aire latérale de cône.
  6. Dispositif de guidage selon les revendications 1 à 5 caractérisé par le fait que les surfaces d'ajustement (16) situées sur le plus grand diamètre sont placées sur un composant (15) déformable et élastique de l'insert (5) qui guide le courant.
  7. Dispositif de guidage selon les revendications 1 à 6 caractérisé par le fait que l'insert (5) a la forme d'un composant austénitique en une ou plusieurs parties.
  8. Dispositif de guidage selon une ou plusieurs des revendications 1 à 7 caractérisé par le fait que l'insert (5) guidant le courant est muni d'une partie de couvercle (10) limitant latéralement des canaux de guidage dans le sens axial et de points d'ajustement (16, 17) placés sur cette partie de couvercle et situés sur le plus grand diamètre.
  9. Dispositif de guidage selon une ou plusieurs des revendications 1 à 7 caractérisé par le fait qu'une des aires latérales de cône (16, 17) est recouverte d'une fine couche.
EP91116503A 1990-10-09 1991-09-27 Dispositif de guidage Expired - Lifetime EP0480261B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4031936A DE4031936A1 (de) 1990-10-09 1990-10-09 Leiteinrichtung
DE4031936 1990-10-09

Publications (2)

Publication Number Publication Date
EP0480261A1 EP0480261A1 (fr) 1992-04-15
EP0480261B1 true EP0480261B1 (fr) 1996-03-27

Family

ID=6415886

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91116503A Expired - Lifetime EP0480261B1 (fr) 1990-10-09 1991-09-27 Dispositif de guidage

Country Status (4)

Country Link
US (1) US5207560A (fr)
EP (1) EP0480261B1 (fr)
AT (1) ATE136098T1 (fr)
DE (2) DE4031936A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2466148A1 (fr) 2010-12-15 2012-06-20 KSB Aktiengesellschaft Agencement d'étanchéité pour pompes centrifuges

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DE4241406C2 (de) * 1992-12-09 2001-10-18 Bosch Gmbh Robert Gebläsegehäuse
JP3299638B2 (ja) * 1994-09-20 2002-07-08 株式会社日立製作所 ターボ流体機械
FR2831637B1 (fr) * 2001-10-25 2004-01-30 Snecma Moteurs Joint d'etancheite a deux levres concentriques
US8579603B2 (en) * 2004-07-13 2013-11-12 Energy Recovery, Inc. Centrifugal pump
WO2006018591A1 (fr) 2004-08-19 2006-02-23 Honeywell International, Inc. Carter de roue de compresseur
US8371811B2 (en) * 2007-10-03 2013-02-12 Schlumberger Technology Corporation System and method for improving flow in pumping systems
WO2013120549A1 (fr) * 2012-02-14 2013-08-22 Sulzer Pumpen Ag Système d'étanchéité et pompe équipée d'un système d'étanchéité
EP3055514B1 (fr) 2013-10-07 2020-04-08 United Technologies Corporation Système de régulation thermique d'élément d'étanchéité à l'air extérieur d'aube de moteur à turbine à gaz
US9945248B2 (en) 2014-04-01 2018-04-17 United Technologies Corporation Vented tangential on-board injector for a gas turbine engine
DE102015202417A1 (de) 2015-02-11 2016-08-11 Ksb Aktiengesellschaft Stömungsführendes Bauteil
EP3173587B1 (fr) * 2015-11-30 2021-03-31 MTU Aero Engines GmbH Carter de turbomachine, element de verrouillage et turbomachine
US9816519B2 (en) * 2015-12-03 2017-11-14 Summit Esp, Llc Press-fit bearing locking system, apparatus and method
EP3228837B1 (fr) * 2016-04-08 2019-08-28 Ansaldo Energia Switzerland AG Ensemble de composants de moteur turbomachine
US10683868B2 (en) 2016-07-18 2020-06-16 Halliburton Energy Services, Inc. Bushing anti-rotation system and apparatus
SG10201707225UA (en) * 2016-09-23 2018-04-27 Sulzer Management Ag Centrifugal pump for conveying a fluid
US10359045B2 (en) 2017-04-05 2019-07-23 Halliburton Energy Services, Inc. Press-fit thrust bearing system and apparatus
US11118594B2 (en) * 2017-05-16 2021-09-14 Dresser-Rand Company Seal apparatus for a turbomachine casing
US11286950B2 (en) * 2019-11-27 2022-03-29 Sulzer Management Ag Bridged stage piece
DE102020119914A1 (de) * 2020-07-28 2022-02-03 KSB SE & Co. KGaA Gehäuse für strömungsführende Bauteile

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2466148A1 (fr) 2010-12-15 2012-06-20 KSB Aktiengesellschaft Agencement d'étanchéité pour pompes centrifuges
DE102010063108A1 (de) 2010-12-15 2012-06-21 Ksb Aktiengesellschaft Dichtungsanordnung für Kreiselpumpen

Also Published As

Publication number Publication date
US5207560A (en) 1993-05-04
ATE136098T1 (de) 1996-04-15
DE59107613D1 (de) 1996-05-02
DE4031936A1 (de) 1992-04-16
EP0480261A1 (fr) 1992-04-15

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