EP0224764B1 - Dispositif compensateur de force axiale pour pompes à fluide - Google Patents

Dispositif compensateur de force axiale pour pompes à fluide Download PDF

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Publication number
EP0224764B1
EP0224764B1 EP86115684A EP86115684A EP0224764B1 EP 0224764 B1 EP0224764 B1 EP 0224764B1 EP 86115684 A EP86115684 A EP 86115684A EP 86115684 A EP86115684 A EP 86115684A EP 0224764 B1 EP0224764 B1 EP 0224764B1
Authority
EP
European Patent Office
Prior art keywords
sleeve
bores
gap
equalizer
equalizer according
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
Application number
EP86115684A
Other languages
German (de)
English (en)
Other versions
EP0224764A1 (fr
Inventor
Johann Guelich
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.)
Sulzer AG
Original Assignee
Gebrueder Sulzer 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 Gebrueder Sulzer AG filed Critical Gebrueder Sulzer AG
Publication of EP0224764A1 publication Critical patent/EP0224764A1/fr
Application granted granted Critical
Publication of EP0224764B1 publication Critical patent/EP0224764B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/04—Antivibration arrangements
    • 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 an axial thrust compensation device for a liquid pump, which essentially consists of a fixed sleeve and a relief piston rotating in this sleeve and firmly connected to the impeller shaft, and to the use of such an axial thrust compensation device.
  • Such devices are used in liquid pumps, in particular in multi-stage high-performance radial pumps, and have the purpose and the task of neutralizing or reducing large axial thrust forces.
  • the patent specification DE-C 611 232 describes a device for axle thrust relief, in which the working fluid flowing through the gap between the relief piston and the bushing is discharged via drain openings in the bushing and relief holes.
  • the published patent application DE-A 1 940 555 describes an encapsulated centrifugal pump in which an intermediate wall is arranged on both sides of the rotor in the rotor space of the housing.
  • the partition wall and the housing wall form a second channel for the working fluid.
  • the rotor each has a groove which, when the rotor is displaced in the axial direction, changes the flow in the rotor space in such a way that the centering forces acting on the rotor are increased.
  • the construction is self-centering.
  • French patent FR-A 1 276 208 describes a centrifugal pump in which the actual pump wheel lies between unevenly sized pressure surfaces of the axial thrust compensation device.
  • An axial thrust compensation device consists of a rotating pressure compensation or relief piston which is firmly connected to the pump impeller and which runs in a fixed sleeve without contact.
  • the sleeve can be designed as a separate part that is firmly connected to the housing.
  • the relief piston itself can be designed as part of the pump rotor shaft or can be rigidly connected to the rotor shaft as a separate part.
  • the axial thrust compensation device is arranged downstream of the last stage in the direction of the following pump stages.
  • the pressure conditions in the area of the axial thrust compensating device in the liquid are such that, in the operating state, working liquid constantly flows from the impeller side space to and through the gap between the bushing and the relief piston.
  • This liquid is set in rotation in the impeller side space, the intensity of which increases with the flow rate through the gap.
  • the working medium therefore enters the gap with a peripheral component. This rotation of the working fluid can interfere with the maximum performance of the pump by increasing the tendency of the rotor to natural vibrations.
  • the object of the invention is to completely prevent the penetration of liquid on the pump wheel side with pre-rotation into the gap and to supply liquid without pre-rotation to the gap without complex additional devices.
  • the invention as characterized in the claims, solves this problem with the aid of the flowing partial flow from the gap into the impeller side space. Since only pre-rotation-free liquid is fed into the gap via the channels, the rotational movement of the liquid through the gap into the gap space facing away from the pump wheel is reduced, which in turn reduces the tendency of the pump rotor to natural vibrations in the limit load range and thus permits higher pump outputs with the same dimensions of the pump rotor shaft .
  • a device according to the invention has particular advantages for multi-stage, high-speed high-pressure radial pumps such as Boiler feed pumps.
  • the figure shows schematically in section a part of the last two stages of a radial pump with an axial thrust compensation device.
  • the schematic section through the housing and rotor of the last two stages of a radial pump shows the one-part or multi-part, fixed pump housing 1 and the two pump wheels 2, 3, which are rigidly connected to the pump wheel shaft 4.
  • the direction of flow of the liquid in the channels 22, 23 of the pump wheels 2, 3, in the pump wheel adjoining rooms 12, 21, 31 and in the main flow channels 11 is indicated by arrows.
  • the axial thrust compensation device consists of the bush 5, which is fixedly connected to the housing, and the relief piston 6, which is rigidly connected to the rotor shaft 4 and rotates in the bush 5.
  • the sleeve 5 has bores 51, only one of which is shown, which open into an internal groove 52, which in turn opens into the gap 56 between the sleeve 5 and the relief piston 6.
  • the bores in the recess 15 are connected to the wheel side space 31 on the outside of the bush 5.
  • the outer and inner diameter (D 2 , Di) of the sleeve 5 and the outer diameter (Ds) of the relief piston 6 are the flows conditions in this area as shown by the arrows.
  • the embodiment of the invention suitable for a particular type of pump can be determined by a pump specialist without any problems.
  • the groove 52 has the task of uniformly supplying the working fluid to the gap 56 over the circumference of the compensating piston 6 and thus, seen over the circumference, to create pressure conditions which are as balanced as possible. However, it is also conceivable that the groove 52 is completely absent and the bores 51 open directly into the gap 56.
  • the working fluid is supplied to the bores 51 via the recess 15.
  • the recess 15 is missing and the bores 51 are connected directly to the pump wheel side space 31 through lateral bores in the bushing 5 (not shown here) or inclined bores in the housing 1.
  • the rotation of the pump wheel 3 generates a rotating flow of the working fluid in the wheel side space 31 and thus an outward radial pressure gradient.
  • the ratios must now be selected so that in the operating state the radial pressure difference in the side space 31 between the sleeve outer and inner diameter (D 2 , D 1 ) is greater than the pressure loss in the bores 51 and groove 52 with a flow rate (Qi) alone, ie that part of the flow (Q) which flows in the gap 56 towards the end of the gap 56 facing the pump wheel. If this condition is met, a ram flow (Q 2 ) flows from the mouth to the end of the pump impeller end into the impeller side space 31, which at the same time completely prevents the penetration of working fluid with pre-rotation into the gap 56.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Rotary Pumps (AREA)

Claims (10)

1. Dispositif de compensation de la pousée axiale (5, 6) destiné à une pompe à liquide, qui est constitué pour l'essentiel d'un fourreau (5) fixe et d'un piston compensateur (6) tournant dans ce fourreau (5) et relié de manière fixe à l'arbre de roue de la pompe, caractérisé en ce que le fourreau (5) présente des conduits (51, 52) destinés à guider un écoulement (Q) de liquide de travail, dirigé dans la direction du piston compensateur (6) et provenant du volume côté roue (31) adjacent au dispositif de compensation de la poussée axiale (5, 6), de telle sorte que l'écoulement (Q) se divise, à l'embouchure (53) des conduits (51, 52) dans la fente (56) située entre le fourreau (5) et le piston compensateur (6), en écoulements (01, Q2) dirigés vers les deux extrémités de la fente.
2. Dispositif selon la revendication 1, caractérisé en ce que les conduits situés dans le fourreau sont des perçages (51) pratiqués dans l'enveloppe du fourreau et qui sont uniformément répartis sur le pourtour du bossage (5).
3. Dispositif selon la revendication 1, caractérisé en ce que les conduits (51) situés dans le fourreau sont des perçages uniformément répartis dans l'enveloppe du fourreau (5) et une rainure (52), les perçages (51) débouchant dans la rainure (52) qui, à son tour, débouche dans l'espace de la fente (56).
4. Dispositif selon la revendication 2 ou 3, caractérisé en ce que les perçages (51) pratiqués dans l'enveloppe du fourreau (5) sont des perçages radiaux.
5. Dispositif selon la revendication 1, 2 ou 3, caractérisé en ce que les perçages (51) sont inclinés sous un certain angle par rapport au sens de rotation de l'arbre de roue (4) de la pompe.
6. Dispositif selon l'une des revendications précédentes 3, 4 ou 5, caractérisé en ce que les axes de symétrie des perçages (51) se situent dans un plan qui est perpendiculaire à l'axe de l'arbre de roue (4) de la pompe et en ce que la rainure est une rainure périphérique (52).
7. Dispositif selon l'une des revendications 1 à 6, caractérisé en ce que le quotient du diamètre extérieur et du diamètre intérieur du fourreau (Di/D2) est supérieur ou égal à 1,25 et en ce que le rapport entre la somme des sections transversales des perçages et la section transversale de la fente est supérieur ou égal à 3.
8. Dispositif selon l'une des revendications 1 à 7, caractérisé en ce que le fourreau (5) comporte 24 perçages radiaux (51) uniformément répartis sur le pourtour du fourreau, dont l'écartement angulaire radial est de 15°.
9. Dispositf selon l'une des revendications 1 à 8, caractériseé en ce que les conduits (51, 52) sont placés à proximité de la surface frontale (50) du fourreau (5), côté roue de la pompe.
10. Utilisation d'un dispositif de compensation de la poussée axiale selon l'une des revendications 1 à 9, dans une pompe radiale à haute pression de liquide, à plusieurs étages et à grande vitesse.
EP86115684A 1985-11-27 1986-11-12 Dispositif compensateur de force axiale pour pompes à fluide Expired EP0224764B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH5066/85 1985-11-27
CH5066/85A CH669241A5 (de) 1985-11-27 1985-11-27 Axialschub-ausgleichsvorrichtung fuer fluessigkeitspumpe.

Publications (2)

Publication Number Publication Date
EP0224764A1 EP0224764A1 (fr) 1987-06-10
EP0224764B1 true EP0224764B1 (fr) 1989-05-03

Family

ID=4287365

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86115684A Expired EP0224764B1 (fr) 1985-11-27 1986-11-12 Dispositif compensateur de force axiale pour pompes à fluide

Country Status (5)

Country Link
US (1) US4892459A (fr)
EP (1) EP0224764B1 (fr)
CH (1) CH669241A5 (fr)
DE (1) DE3663165D1 (fr)
FI (1) FI93259C (fr)

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US8869531B2 (en) 2009-09-17 2014-10-28 Echogen Power Systems, Llc Heat engines with cascade cycles
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WO2013055391A1 (fr) 2011-10-03 2013-04-18 Echogen Power Systems, Llc Cycle de réfrigération du dioxyde de carbone
BR112015003646A2 (pt) 2012-08-20 2017-07-04 Echogen Power Systems Llc circuito de fluido de trabalho supercrítico com uma bomba de turbo e uma bomba de arranque em séries de configuração
US9341084B2 (en) 2012-10-12 2016-05-17 Echogen Power Systems, Llc Supercritical carbon dioxide power cycle for waste heat recovery
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Also Published As

Publication number Publication date
DE3663165D1 (en) 1989-06-08
FI93259B (fi) 1994-11-30
US4892459A (en) 1990-01-09
CH669241A5 (de) 1989-02-28
FI864381A (fi) 1987-05-28
EP0224764A1 (fr) 1987-06-10
FI93259C (fi) 1995-03-10
FI864381A0 (fi) 1986-10-28

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