EP2394029A2 - Turbomachine comprenant un piston d'équilibrage - Google Patents

Turbomachine comprenant un piston d'équilibrage

Info

Publication number
EP2394029A2
EP2394029A2 EP10703824A EP10703824A EP2394029A2 EP 2394029 A2 EP2394029 A2 EP 2394029A2 EP 10703824 A EP10703824 A EP 10703824A EP 10703824 A EP10703824 A EP 10703824A EP 2394029 A2 EP2394029 A2 EP 2394029A2
Authority
EP
European Patent Office
Prior art keywords
cavity
seal
turbomachine
stator
pressure
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Withdrawn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
EP10703824A
Other languages
German (de)
English (en)
Inventor
Patrick Van Der Span
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 EP2394029A2 publication Critical patent/EP2394029A2/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Withdrawn legal-status Critical Current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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/051—Axial thrust balancing
    • F04D29/0516—Axial thrust balancing balancing pistons
    • 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
    • F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
    • F01D3/04—Machines or engines with axial-thrust balancing effected by working-fluid axial thrust being compensated by thrust-balancing dummy piston or the like
    • 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0416—Axial thrust balancing balancing pistons

Definitions

  • the invention relates to a turbomachine with a balancing piston, which compensating piston has at least one shaft shoulder on a rotor extending along a machine axis and a seal, which seal seals a gap between the rotor and a stator, so that a cavity adjacent to a first side of the seal may have a different pressure in the operation by a differential pressure on the seal than on the other side of the seal, wherein the shaft shoulder adjacent to the cavity.
  • turbomachinery such as steam turbines, gas turbines or compressors, in particular axial and radial compressors, arises as a result of relaxation or compression of the process fluid above the impeller, a pressure difference, which causes an axial thrust of the rotor adjacent to adjacent surfaces of the rotor.
  • This axial thrust is dependent on the operating conditions of the turbomachine and can also act in different directions depending on the operating conditions.
  • differential pressure the differential pressure and the
  • turbo machine regularly have a so-called balance piston, which of the
  • Thrust compensation is used. This is regularly designed so that a small thrust remains in a certain direction under all operating conditions, so that no load change reactions take place and the rotor is not moved back and forth in any axial play.
  • Balancing pistons regularly have at least one shaft shoulder, often being considered to be radial extending disc are formed on the rotor and a shaft seal adjacent to the at least one shaft shoulder seals the rotor to a stator.
  • the most common design is the mentioned disc shape, so that on the two flanks or wave heels, which are defined by the disc different pressures produce the required axial thrust for compensation.
  • Adjacent to the shaft shoulder or the shaft seal and the stator a cavity is formed, in which a first pressure of a process fluid prevails, which differs from a second pressure on the other side of the cavity and a differential pressure across the shaft seal differently from the first pressure.
  • the first pressure acting on the shaft shoulder results with the surface of the shaft shoulder in a force which, correspondingly dimensioned, at least partially compensates for the axial thrust and accordingly facilitates the axial bearing of the shaft by the amount of the compensating force.
  • a system for compensating axial thrust is already known from the European patent EP 1 418 341 Bl with a compensating piston, which is acted upon only in case of need with pressure for thrust compensation, wherein in normal operation the thrust balance by means of the possible shaft seals at the passages through the housing , so that in normal operation no supply of the balance piston with process fluid is required.
  • the object of the invention on the basis of the abovementioned problems, is to reduce the loss of process fluid occurring at the compensating piston and thus to improve the efficiency of the machine.
  • the invention proposes that the stator is designed to be movable in such a way that the gap can be increased and decreased. Due to the guided moveable design of the stator, a gap width adapted to the current operating conditions of the turbomachine can be set which is lower than that required under other operating conditions so that the difference in amount of process fluid flowing through the balance piston is saved an improvement in efficiency.
  • This embodiment opens up the possibility of realizing a gap width of the gasket on the balance piston which is automatically adapted to the pressure in the cavity without any further actuators moving the stator or a complicated regulation.
  • the stator may have an elastic element which, depending on the position within the scope of the guided, preferably axial displaceability, generates a restoring force which counteracts the pressure in the cavity.
  • the force from the elastic element acts on the stator in the same or opposite direction of the force from the pressure in the cavity to the stator.
  • this elastic element may be designed such that adjusts to each operating pressure in the cavity a matching to the operating condition, which belongs to this pressure, matching gap.
  • the gap widening or gap reduction can be produced particularly simply by the fact that the annular space of the gap extending in the circumferential direction about the machine axis does not extend parallel to the machine axis in the axial direction, but is guided obliquely thereto and the displaceability of the stator in the axial direction.
  • This design has the advantage that the gap can be changed without a variation of the components involved in terms of their circumferential dimensions.
  • the gap limiting surfaces of the rotor and the stator are each formed as a cone. The cone of the rotor and the stator can be different from each other
  • a compensation line to the cavity for the supply or discharge of process fluid to adjust an advantageous for the operating pressure in the cavity.
  • this compensation line can open into a pressure reservoir of the process fluid or a pressure sink or suction, and particularly advantageously a control valve is provided in the equalization line, by means of which a defined pressure difference across the control valve is applicable.
  • the control valve allows the regulation of the pressure in the cavity via a control of the inflowing or outflowing amount of process fluid.
  • the efficiency of a turbomachine in particular of a compressor, can be increased in a particularly advantageous manner by virtue of the quantity flowing through the equalizing line after starting the turbomachine in steady-state operation
  • Process fluid is reduced by the control valve as far as it allows the remaining clearance of the seal on the balance piston.
  • the elastic Element, the stator and the inclination of the seal coordinated so that a reduction of the flowing through the equalization line and the seal amount of process fluid by means of the control valve has a reduction in the gap width of the seal result.
  • Figure 1 is a schematic representation of the turbomachine according to the invention with balancing piston in a longitudinal section.
  • FIG. 1 shows a compressor or a turbomachine T with a housing CAS and a rotor R which extends along a machine axis X.
  • the rotor R has an impeller IMP - here the impeller of a centrifugal compressor - by means of which a process fluid PF is compressed under a rotation with the rotational speed n of the rotor R from a first pressure pl to a higher second pressure p2.
  • Process fluid PF enters for this purpose in the housing CAS by an inflow IN and leaves the housing by an outflow EX. Before the process fluid PF leaves the housing CAS through the outflow EX, it partially collects in a pressure chamber PCH. Adjacent to the pressure chamber, the rotor R is provided with a balancing piston BP.
  • the balance piston BP has a substantially disc shape, which with the flat Aussteckung perpendicular to Machine axis X thus extends, accordingly, a first shaft shoulder RS1, which here adjoins the pressure chamber PCH, and a second shaft shoulder RS2, which adjoins a cavity CH.
  • a gap between the compensating piston BP and an axially movable stator ST in the housing CAS is sealed by means of a seal SS designed as a shaft seal - in this case as a labyrinth seal, so that a pressure difference arises between the pressure p 2 in the
  • a compensation line BPL is provided for discharge overflowing process fluid PF, which flows from the pressure chamber PCH to the cavity CH via the seal SS.
  • the compensation line BPL is connected to a pressure sink, which here is the inlet IN into the housing CAS.
  • Compensation line is connected to a pressure reservoir, if the pressure difference .DELTA.PBD on the balance piston BP is reversely oriented (for example, in a different orientation of the impeller).
  • the equalizing line BPL is provided with a control valve CF via which a pressure difference ⁇ PCV is generated depending on the position of the control valve CF.
  • a part of the seal SS is attached to the stator ST, which is guided guided axially movable, wherein the gap to be sealed GP to the machine axis X is inclined.
  • the spatial geometry defined by the gap GP forms a cone that extends concentrically circumferentially about the machine axis X.
  • the turbomachine T of this embodiment is a centrifugal compressor, and the balancing piston BP is on the higher pressure side of FIG Impeller IMP is arranged so that the pressure chamber PCH with respect to the cavity CH has a higher pressure, it is advantageous if a displacement of the stator ST in the direction of the chamber with the lower pressure (here cavity CH or p3) an enlargement of the gap GP or the gap width H causes and consequently causes a higher permeability of the seal SS.
  • the stator ST is biased by means of an elastic element EE such that the restoring force of the elastic element EE acts in the direction of a reduction of the gap width H. Will be in stationary

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)

Abstract

L'invention concerne une turbomachine (T) comprenant un piston d'équilibrage (BP) qui est rendu étanche vis-à-vis d'un stator (ST) au moyen d'un joint (SS). Les pistons d'équilibrage classiques nécessitent d'importantes quantités de fluide de traitement (PF), ce qui peut entraîner une perte de rendement considérable. L'invention permet de résoudre ce problème du fait que le stator (ST) qui porte partiellement le joint (SS) est conçu mobile axialement dans le carter (CAS) de sorte que le joint (SS) soit plus ou moins lâche.
EP10703824A 2009-02-05 2010-01-20 Turbomachine comprenant un piston d'équilibrage Withdrawn EP2394029A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009007713 2009-02-05
PCT/EP2010/050643 WO2010089198A2 (fr) 2009-02-05 2010-01-20 Turbomachine comprenant un piston d'équilibrage

Publications (1)

Publication Number Publication Date
EP2394029A2 true EP2394029A2 (fr) 2011-12-14

Family

ID=42542444

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10703824A Withdrawn EP2394029A2 (fr) 2009-02-05 2010-01-20 Turbomachine comprenant un piston d'équilibrage

Country Status (4)

Country Link
US (1) US20110286835A1 (fr)
EP (1) EP2394029A2 (fr)
CN (1) CN102308098A (fr)
WO (1) WO2010089198A2 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014222057A1 (de) * 2014-10-29 2016-05-04 Siemens Aktiengesellschaft Turbine mit Axialdruckausgleich
US10247029B2 (en) 2016-02-04 2019-04-02 United Technologies Corporation Method for clearance control in a gas turbine engine
US11353036B2 (en) * 2017-12-01 2022-06-07 Nuovo Pignone Tecnologie Srl Balancing system and method for turbomachine
CN112368481B (zh) 2018-09-14 2023-09-01 开利公司 构造成控制抵靠磁性马达推力轴承的压力的压缩机

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1528719A1 (de) * 1965-07-24 1971-11-04 Halbergerhuette Gmbh Entlastungseinrichtung fuer mehrstufige Kreiselpumpen
CH686525A5 (de) * 1992-07-02 1996-04-15 Escher Wyss Ag Turbomaschine .
DE29500744U1 (de) * 1995-01-18 1996-05-15 Sihi Ind Consult Gmbh Strömungsmaschine mit Entlastungskolben
US6309174B1 (en) * 1997-02-28 2001-10-30 Fluid Equipment Development Company, Llc Thrust bearing for multistage centrifugal pumps
ITMI20011348A1 (it) * 2001-06-27 2002-12-27 Nuovo Pignone Spa Pistone di bilanciamento per compressori centrifughi con tenuta a cellette a gioco divergente
GB2393766A (en) * 2002-10-03 2004-04-07 Alstom A sealing arrangement for a turbine
ITMI20022337A1 (it) 2002-11-05 2004-05-06 Nuovo Pignone Spa Assieme di bilanciamento di spinta assiale per un
US6957945B2 (en) * 2002-11-27 2005-10-25 General Electric Company System to control axial thrust loads for steam turbines

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2010089198A2 *

Also Published As

Publication number Publication date
WO2010089198A2 (fr) 2010-08-12
US20110286835A1 (en) 2011-11-24
WO2010089198A3 (fr) 2010-10-21
CN102308098A (zh) 2012-01-04

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