EP0721546B1 - Turbomachine a usure par abrasion reduite - Google Patents

Turbomachine a usure par abrasion reduite Download PDF

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Publication number
EP0721546B1
EP0721546B1 EP94927620A EP94927620A EP0721546B1 EP 0721546 B1 EP0721546 B1 EP 0721546B1 EP 94927620 A EP94927620 A EP 94927620A EP 94927620 A EP94927620 A EP 94927620A EP 0721546 B1 EP0721546 B1 EP 0721546B1
Authority
EP
European Patent Office
Prior art keywords
impeller
turbo
wall surface
machine according
ring
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
EP94927620A
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German (de)
English (en)
Other versions
EP0721546A1 (fr
Inventor
Sönke BRODERSEN
Peter Hergt
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
Priority claimed from DE4431947A external-priority patent/DE4431947A1/de
Application filed by KSB AG filed Critical KSB AG
Publication of EP0721546A1 publication Critical patent/EP0721546A1/fr
Application granted granted Critical
Publication of EP0721546B1 publication Critical patent/EP0721546B1/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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance
    • 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
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • 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
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous

Definitions

  • the invention relates to a turbomachine, for promotion of media loaded with solid particles, with one or several impellers arranged within a housing, the Impellers are provided with at least one wheel disc, a wheel side space is formed between the housing and the wheel disc and a gap seal between the wheel disc and the housing is arranged.
  • turbomachines which are pumps, Turbines, pump turbines or the like can be found in the most diverse areas of technology application. It is has long been the desire of the designers, for machines that exposed to material wear due to abrasive particles are to improve their service life.
  • the first measures in general are the use of particularly hard and wear-resistant materials.
  • particularly wear-sensitive areas for example Centrifugal pumps have the wheel side spaces and those in it Area seals are proven.
  • Kick through one Material wear an enlargement of the column of the seals on, there are increased hydraulic losses and as a result of which a reduced efficiency. Furthermore arise this causes strong vibrations in multi-stage machines, which up to can lead to failure of the unit.
  • a measure is known from EP-B 0 346 677 in which a a shaft seal receiving space and one Shaft seal itself should be protected from wear.
  • the room is behind the impeller and is through a Gap seal compared to the actual one, a higher pressure having wheel side space separately.
  • a centrifugal pump is known from DE-OS 22 10 556, at with the help of particularly wear-resistant Housing parts, such as the spiral space and the impeller side space limiting wear plates, the service life of the machine should be improved. Furthermore, this machine can by feeding in solid-free material Wheel side space and also the seal before wearing Particles are protected.
  • Another measure shows the DE-OS 23 44 576, whose Construction in the area of the gap seals additional Provides funding channels, the entrances of which are circulating Annular chamber is connected upstream.
  • DE-OS 38 08 598 tries with the help of a certain inclination the peripheral wall surface of the space downstream of an impeller to increase the stability.
  • US-A 1 634 317 is an axial thrust compensation device known for pump impellers.
  • Diameter split ring seals arranged.
  • a split ring seal is always on the outer circumference Cover plate and a second split ring seal interacting with it is on a smaller diameter at the other Cover plate arranged.
  • the suction mouth of the impeller is immersed Formation of a liquid-permeable gap in a paragraph of the housing.
  • the rotating wall surface parts of the Sealing gaps have additional blading. A flow generated with this affects the pressure at the impeller outlet opposite. This is supposed to reduce the pressure losses in the wheel space be kept low while being effective Axial thrust compensation.
  • the invention addresses the problem set out above described wear problems basically in their cause to reduce or eliminate.
  • the solution to this problem provides that the wheel side spaces delimiting stationary Wall surface in the direction of a flow near the wall in front of the Gap seal has an annular projection, the Form the flow near the wall along the stationary one Wall surface of a wheel side space in the direction of the rotating Wheel disc of an impeller and in areas higher Rotational movement of the flow medium conducts, the gap at least 2 mm between the projection and the wheel disc It has been recognized that the abrasive particles are always in close to the standing, d. H. of the non-rotating wall surfaces hike radially inwards.
  • Dependent on of the performance data of the turbomachine can Designs in relation to the impeller outer radius different, d. H. for the respective purpose most suitable radii.
  • This can e.g. B. in Area of an impeller outlet, immediately in front of one Gap seal or a shaft seal, in the area in between, but also in a wheel side space between the shaft and Gap seal can be arranged.
  • the wheel side spaces delimit stationary wall surface in the direction of a flow close to the wall has an annular recess in front of the gap seal, whose shape is the flow near the wall along the stationary one Wall surface of a wheel side space in the direction of the rotating Wheel disc of an impeller and in higher areas Rotational movement of the flow medium conducts, the depth the recess at least three times the local Boundary layer thickness corresponds.
  • an impeller 2 with an outer radius r 2 is arranged within a housing 1, the blades 3 of which are arranged between a pressure-side impeller cover plate 4 and a suction-side impeller cover plate 5. Opposite these are stationary housing wall surfaces, a pressure-side 6 and a suction-side housing wall surface 7.
  • the impeller 2 is surrounded by a spiral space 8 which is connected to a pressure connection 9. Due to the pressure gradient within the wheel side spaces, part of the medium located within the housing 1 flows to the gap seal 10 in the area of the impeller inlet or to the pressure-side gap seal 11 in the area of a shaft seal. As is known, the wheel-side friction on the impeller cover disks 4, 5 generates a flow in the pressure-side wheel side space 12 and in the suction-side wheel side space 13.
  • FIG. 2 shown another embodiment of a multi-stage Fluid machine. If they were operated as a pump, that would particle-laden medium through the suction nozzle 14.1, 14.2 den Flow impellers 2.1, 2.2. In contrast to the embodiment 1 have the wheels 2.1, 2.2 of the first stage only in the area of the shaft passage between the individual stages a gap seal on the pressure side.
  • FIGS. 3 to 14 and 18 to 23 uniformly in construction. It These are exemplary designs between one each on the left side as a stationary wall surface and a wall surface arranged to rotate on the right. According to Fig. 1, these would be designs that in Area of a suction side wheel side space 13 are used could. The axis of rotation for the rotating wall surface part is always below the respective display.
  • the representations shown here would be in correspondingly also for the pressure side wheel side space 12 apply, but then the presentation is reversed would be seen. For the sake of simplicity, this is limited Description on the above mentioned definition.
  • the width t 1 of the ring 17 should be greater than half the wheel side space width b, that is to say t 1 / b ⁇ 0.5.
  • the effectiveness can also be determined on other radii r 1 .
  • the difference between the wheel side space width b minus the width t 1 of the ring 17 is that it must not be less than 2 mm.
  • the gap has no function as a sealing gap; such would be destroyed by particles flowing through it.
  • the minimum gap width of 2 mm or larger prevents increased wear within the gap area. This also applies to the representations in the other figures below.
  • the rotating cover plate 5 is a ring 20 on the rotating cover plate 5 arranged, which is larger in diameter than that fixed housing ring 17 is located.
  • the fixed Ring 17 facing the bottom of the rotating ring 20 is with Buckets 19 equipped that a higher area Generate rotational movement and thus the particle-laden Deflect the flow near the wall to the outer diameter of the impeller.
  • the blades 19 can also have a promotional effect generating grooves are arranged, for example, in the Material of the impeller can be introduced.
  • a bevel of the Gap between the two advantageous the one radially outward directed forced movement of the particles causes.
  • the shovels or grooves can be both in the axial direction and perpendicular to Direction of rotation can be arranged as well as under a certain angle to the axis direction.
  • the rotating ring 20 is smaller Diameter than the fixed ring 17 arranged and has via grooves or blades 19 to produce a higher one Rotational movement to deflect the particles flow close to the wall.
  • the grooves or blades 19 are relative their capacity so that their energy the Slightly influenced flow near the wall. But they are like that small that there is no amplifying circular flow inside of the wheel side space 13 produce what with the previously known outer auxiliary blades reinforced the case.
  • Buckets shown can also be wholly or partly of Cover disc-shaped elements in the manner of a closed Impeller be covered.
  • the housing ring 17 is included a radially outwardly facing disc 23 which the Deflection of the particle-laden flow near the wall reinforced. Furthermore, here are the rotating impeller cover plates 5 equipped with or without short blades 19. The disk 23 can be on the ring 17 both on its end face as well as be provided in the central area.
  • FIG. 13 and 14 show a plan view of the housing-fixed Ring 17, which according to FIG. 13 as a closed ring, 14 but also as a split ring can be trained.
  • the division can be chosen in this way be that several ring segments 17.2 have an arrangement, which has a shovel-shaped course relative to the housing wall 7 demonstrate.
  • the center or centers of the ring segments 17.2 are outside the center of the axis of rotation, however shifted in the associated vertical and / or horizontal Cutting plane.
  • the individual ring segments open here Direction of rotation of the - not shown - impeller Outside. Thus, a different job and thus an influence on the flow can be obtained.
  • the arrow shows the direction of rotation of the impeller.
  • the depth t 2 should be such that it corresponds to at least three times the local boundary layer thickness.
  • the boundary layer thickness results from the usual calculations (e.g. according to Schlichting: boundary layer theory, G. Braun, Düsseldorf 1982). The boundary layer thickness is largely dependent on the medium, the impeller speed, the radius r 1 or r 1 'and the width b of the wheel side space 13.
  • Another form of influencing the flow near the wall is 21 to 25.
  • this can be done in one stationary wall surface 7 incorporated grooves 27 or projecting blades 28, which are in the direction of rotation of the Impeller or the opposite rotating Develop the disk surface radially outwards. You lead the particles brought up by the flow near the wall at the radially outward contour of the grooves 27 or Scoops 28 along outward.

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

Claims (13)

  1. Turbomachine pour le transport de fluides chargés de particules solides, avec une ou plusieurs roues mobiles (3, 16, 2.1, 2.2) disposées à l'intérieur d'un corps (1), dans laquelle les roues mobiles (2.1, 2.2, 3, 16) sont pourvues d'au moins un disque de roue (5, 6), un espace (12, 13) latéral à la roue est formé entre le corps (1) et le disque de roue (5, 6), et une boíte à labyrinthe (10, 11, 11.1, 11.2) est disposée entre le disque de roue (5, 6) et le corps (1), caractérisée en ce que la surface de paroi fixe (6, 7) délimitant des espaces (12, 13) latéraux à la roue présente, avant la boíte à labyrinthe (5, 6, 11.1, 11.2) dans la direction d'un écoulement proche de la paroi, une saillie annulaire (17) dont la forme conduit l'écoulement proche de la paroi le long de la surface de paroi fixe (6, 7) d'un espace (12, 13) latéral à la roue en direction du disque de roue tournant (4, 6) d'une roue mobile (3, 2.1, 2.2) et dans des zones avec un mouvement de rotation plus élevé du fluide en écoulement, la fente (5) entre la saillie (17) et le disque de roue valant au moins 2 mm.
  2. Turbomachine suivant la revendication 1, caractérisée en ce qu'une surface annulaire saillante en direction axiale ou un anneau (17) est disposée sur les surfaces de paroi fixe (6, 7) du corps.
  3. Turbomachine suivant la revendication 2, caractérisée en ce que plusieurs aubes courtes ou des rainures (19) sont placées sur la surface de paroi tournante (4, 5) en face de la zone d'extrémité de la surface annulaire ou de l'anneau (17).
  4. Turbomachine suivant la revendication 2, caractérisée en ce que la surface annulaire ou l'anneau (17) coopère avec une surface annulaire (1) ou un anneau (20) garni(e) d'aubes ou de rainures, disposée sur la surface de paroi tournante (4, 5) à un diamètre plus grand ou plus petit.
  5. Turbomachine suivant l'une quelconque des revendications 1 à 4, caractérisée en ce que la surface annulaire ou l'anneau (17) est pourvue d'un élément de disque en saillie (23) s'étendant en direction radiale.
  6. Turbomachine suivant la revendication 5, caractérisée en ce que plusieurs aubes courtes (19) ou des rainures sont disposées sur la surface de paroi tournante (4, 5), en face de la zone de l'élément de disque (23).
  7. Turbomachine suivant la revendication 2, caractérisée en ce que la surface annulaire ou l'anneau (17) se compose de plusieurs segments (17.2), le point milieu de chaque segment (17.2) étant disposé à l'extérieur de l'axe de rotation.
  8. Turbomachine suivant la revendication 2, caractérisée en ce que les rainures ou les aubes (19) placées sur l'anneau tournant (20) sont orientées en oblique par rapport à l'axe de rotation.
  9. Turbomachine pour le transport de fluides chargés de particules solides, avec une ou plusieurs roues mobiles (2.1, 2.2, 3, 16) disposées à l'intérieur d'un corps (1), dans laquelle les roues mobiles (2.1, 2.2, 3, 16) sont pourvues d'au moins un disque de roue (5, 6), un espace (12, 13) latéral à la roue est formé entre le corps (1) et le disque de roue (5, 6), et une boíte à labyrinthe (10, 11, 11.1, 11.2) est disposée entre le disque de roue (5, 6) et le corps (1), caractérisée en ce que la surface de paroi fixe (6, 7) délimitant des espaces (12, 13) latéraux à la roue présente, avant la boíte à labyrinthe (5, 6, 11.1, 11.2) dans la direction d'un écoulement proche de la paroi, une cavité annulaire (25) dont la forme conduit l'écoulement proche de la paroi le long de la surface de paroi fixe (6, 7) d'un espace (12, 13) latéral à la roue en direction du disque de roue tournant (4, 6) d'une roue mobile (2.1, 2.2, 3) et dans des zones avec un mouvement de rotation plus élevé du fluide en écoulement, la profondeur (t2) de la cavité (25) correspondant au moins au triple de l'épaisseur locale de la couche limite.
  10. Turbomachine suivant la revendication 9, caractérisée en ce qu'une cavité annulaire (25) est formée dans la surface de paroi fixe (6, 7), la transition entre la cavité (25) et la surface de paroi fixe (6, 7) étant pourvue d'une arête d'échappement (26).
  11. Turbomachine suivant la revendication 10, caractérisée en ce que plusieurs aubes courtes (19) ou des rainures sont placées sur la surface de paroi tournante (4, 5), en face de l'arête d'échappement (26).
  12. Turbomachine suivant l'une quelconque des revendications 1 à 11, caractérisée en ce que plusieurs rainures (27) et ou aubes (28), qui se développent radialement vers l'extérieur, dans la direction de rotation de la surface de paroi tournante opposée, sont placées sur la surface de paroi fixe (6, 7).
  13. Turbomachine suivant l'une quelconque des revendications 1 à 12, caractérisée en ce que la surface de paroi fixe (6, 7) est pourvue de rainures se développant vers l'extérieur, qui présentent une surface plate montante (29).
EP94927620A 1993-09-25 1994-09-16 Turbomachine a usure par abrasion reduite Expired - Lifetime EP0721546B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE4332703 1993-09-25
DE4332703 1993-09-25
DE4431947A DE4431947A1 (de) 1993-09-25 1994-09-08 Strömungsmaschine mit verringertem abrasiven Verschleiß
DE4431947 1994-09-08
PCT/EP1994/003108 WO1995008714A1 (fr) 1993-09-25 1994-09-16 Turbomachine a usure par abrasion reduite

Publications (2)

Publication Number Publication Date
EP0721546A1 EP0721546A1 (fr) 1996-07-17
EP0721546B1 true EP0721546B1 (fr) 1998-12-02

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP94927620A Expired - Lifetime EP0721546B1 (fr) 1993-09-25 1994-09-16 Turbomachine a usure par abrasion reduite

Country Status (6)

Country Link
US (1) US5984629A (fr)
EP (1) EP0721546B1 (fr)
CN (1) CN1054418C (fr)
AU (1) AU7697094A (fr)
DE (1) DE59407403D1 (fr)
WO (1) WO1995008714A1 (fr)

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AU7697094A (en) 1995-04-10
CN1131978A (zh) 1996-09-25
CN1054418C (zh) 2000-07-12
EP0721546A1 (fr) 1996-07-17
DE59407403D1 (de) 1999-01-14
WO1995008714A1 (fr) 1995-03-30
US5984629A (en) 1999-11-16

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