EP0346677B1 - Liquid-displacement machine - Google Patents

Liquid-displacement machine Download PDF

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Publication number
EP0346677B1
EP0346677B1 EP89109759A EP89109759A EP0346677B1 EP 0346677 B1 EP0346677 B1 EP 0346677B1 EP 89109759 A EP89109759 A EP 89109759A EP 89109759 A EP89109759 A EP 89109759A EP 0346677 B1 EP0346677 B1 EP 0346677B1
Authority
EP
European Patent Office
Prior art keywords
ring element
shaft
turbomachine
impeller
end side
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
EP89109759A
Other languages
German (de)
French (fr)
Other versions
EP0346677A1 (en
Inventor
Karlheinz Becker
Karl-Heinz Bayer
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
Priority to AT89109759T priority Critical patent/ATE75818T1/en
Publication of EP0346677A1 publication Critical patent/EP0346677A1/en
Application granted granted Critical
Publication of EP0346677B1 publication Critical patent/EP0346677B1/en
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
    • F04D29/40—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
    • 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
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/126—Shaft sealings using sealing-rings 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 according to the preamble of the main claim.
  • the invention has for its object to provide a measure for a turbomachine which is supplied with a conveying medium containing solids of the aforementioned magnitude, by means of which a space surrounding the shaft seal and the shaft seal itself can be protected against erosion wear. This object is achieved in accordance with the characterizing part of the main claim.
  • Embodiments of the invention described in claims 4 to 8 have the effect that dangerous wear marks were not detectable either on the shaft seal or in the space surrounding the shaft seal.
  • the split ring seal was damaged within a very short time without the ring element. If an annular element according to the invention was instead arranged in the space receiving the shaft seal, no signs of wear were detectable even on the split ring seal after a long test period.
  • the configurations of claims 9 to 11 describe the different possibilities for producing the ring element.
  • FIG. 1 shows a housing (1) of a turbomachine, which is designed here as a centrifugal pump, and an impeller (2) arranged inside the housing (1).
  • the impeller is equipped with split ring seals (3, 4) on the suction and pressure side.
  • the impeller (2) is attached to a shaft (5) on which a shaft protection sleeve (6) and a shaft seal (7) designed as a mechanical seal are also attached.
  • the impeller (2) has axial thrust compensation bores (9) in the area of the impeller hub (8) in the impeller cover disk on the pressure side.
  • the ring element (12) fastened in the housing (1) is arranged within the space (10) surrounding the shaft seal (7), here a pressure-side housing cover (11). It extends in the area between the split ring (13) attached to the impeller and the impeller hub (8) and the shaft seal (7).
  • the free end face of the ring element (11) has a surface (14) running radially to the shaft, on the smallest diameter of which a nozzle (15) pointing in the axial direction to the shaft seal (7) is attached.
  • the ring element (12) formed here as a sheet metal part can also be designed as a solid part which would have a backward rotation on the side facing the shaft seal. Furthermore, it can be formed in one piece with the split ring (16) fixed to the housing.
  • FIG. 2 largely corresponds to that of FIG. 1. A difference is that the ring element (12) is provided on its free end face only with a surface (14) extending in the radial direction to the shaft.
  • Fig. 3 shows a truncated conical ring element (12) which runs diagonally to the shaft axis, its free end face (17) facing the shaft (5).
  • a nozzle (15) attached to it shown in FIGS. 1 and 2 Tear-off edge, with the help of which erosion wear can be prevented within the space (10).

Abstract

PCT No. PCT/EP89/00604 Sec. 371 Date Dec. 13, 1990 Sec. 102(e) Date Dec. 13, 1990 PCT Filed May 30, 1989 PCT Pub. No. WO89/12755 PCT Pub. Date Dec. 28, 1989.A centrifugal pump has a housing which defines an annular chamber disposed downstream of the impeller and surrounding the shaft seal. The chamber receives a hollow cylindrical or frustoconical shroud which surrounds the shaft seal with spacing and protects it from solid particles in the conveyed fluid. A non-contact type annular seal between the impeller and the housing surrounds the shroud.

Description

Die Erfindung betrifft eine Strömungsmaschine gemäß dem Oberbegriff des Hauptanspruches.The invention relates to a turbomachine according to the preamble of the main claim.

Bei Strömungsmaschinen, die mit einem Feststoffe enthaltenden Fördermedium beaufschlagt sind, besteht die Gefahr eines Erosionsverschleisses innerhalb der Strömungsmaschine. Dem kann zwar durch eine entsprechende Auskleidung des Gehäuses entgegengewirkt werden, jedoch existiert eine besonders gefährdete Stelle im Bereich der Wellenabdichtung. Im Fördermedium enthaltene Feststoffe, welche eine Körnung von bis zu 1 mm aufweisen können, sind in der Lage, die Wellenabdichtung selbst oder die Wellenabdichtung haltende Gehäuseteile zu zerstören. Ein vorzeitiger Ausfall der Strömungsmaschine wäre dadurch gegebenIn turbomachines which are supplied with a conveying medium containing solids, there is a risk of erosion wear within the turbomachine. This can be counteracted by appropriate lining of the housing, but there is a particularly vulnerable area in the area of the shaft seal. Solids contained in the pumped medium, which can have a grain size of up to 1 mm, are capable of destroying the shaft seal itself or housing parts holding the shaft seal. This would result in premature failure of the turbomachine

Aus der US-A 17 22 439 ist eine Gleitringdichtungspatrone, die mit Hilfe eines Flansches an einer einen Wellendurchtritt aufweisenden Gehäuseöffnung angeflanscht ist, bekannt. Der dem abzusperrenden Medium ausgesetzte Deckel von der Gleitringdichtungs-Patrone weist eine Eintrittsöffnung auf, in die eine Pumpenlaufradnabe dichtend hineinpaßt. Ein im druckseitigen Radseitenraum rotierendes feststoffhaltiges Fördermedium würde in kürzester Zeit den Deckel und danach den dichtenden Gummibalg der Gleitringdichtung zerstören. Es besteht auch die Gefahr, daß infolge der fehlenden Möglichkeit zum Flüssigkeitsaustausch innerhalb der Gleitringdichtung die Dichtringe wegen Trockenlaufes zerstört werden.From US-A 17 22 439 a mechanical seal cartridge is known which is flanged to a housing opening having a shaft passage by means of a flange. The cover of the mechanical seal cartridge which is exposed to the medium to be shut off has an inlet opening into which a pump impeller hub fits sealingly. A fluid-containing conveying medium rotating in the pressure-side wheel side space would destroy the cover in a very short time and then the sealing rubber bellows of the mechanical seal. There is also a risk that due to the lack of possibility to exchange fluid within the mechanical seal, the sealing rings are destroyed due to dry running.

Der Erfindung liegt die Aufgabe zugrunde, für eine Strömungsmaschine, die mit einem Feststoffe der vorgenannten Größenordnung enthaltenden Fördermedium beaufschlagt ist, eine Maßnahme vorzusehen, mit deren Hilfe ein die Wellenabdichtung umgebender Raum und die Wellenabdichtung selbst vor Erosionsverschleiß geschützt werden kann. Die Lösung dieser Aufgabe erfolgt gemäß dem kennzeichnenden Teil des Hauptanspruches.The invention has for its object to provide a measure for a turbomachine which is supplied with a conveying medium containing solids of the aforementioned magnitude, by means of which a space surrounding the shaft seal and the shaft seal itself can be protected against erosion wear. This object is achieved in accordance with the characterizing part of the main claim.

In praktischen Versuchen hat sich in überraschender Weise gezeigt, daß mit einem gemäß dem Hauptanspruch gestalteten Ringelement ein Erosionsverschleiß durch im Fördermedium enthaltene Feststoffe, wobei bis zu 100 mg Feststoffanteil pro dm³ gegeben war, ein Erosionsverschleiß abgestellt werden konnte. Die Unteransprüche 2 und 3 geben vorteilhafte Ausgestaltungen der Erfindung und die Lage der freien Stirnseite des Ringelementes an.Practical tests have shown, surprisingly, that with a ring element designed according to the main claim, erosion wear due to solids contained in the conveying medium, with up to 100 mg of solids content per dm 3, could prevent erosion wear. The subclaims 2 and 3 indicate advantageous embodiments of the invention and the position of the free end face of the ring element.

In den Ansprüchen 4 bis 8 beschriebene Ausgestaltungen der Erfindung bewirken, daß gefährdende Verschleißspuren weder an der Wellenabdichtung noch in dem die Wellenabdichtung umgebenden Raum feststellbar waren. Bei Versuchen mit einem Laufrad, welches auf der der Wellenabdichtung zugekehrten Seite mit einer Spaltringdichtung versehen war, wurde ohne das Ringelement die Spaltringdichtung innerhalb kürzester Zeit beschädigt. Wurde stattdessen in dem die Wellenabdichtung aufnehmenden Raum ein erfindungsgemäßes Ringelement angeordnet, dann waren nach langer Versuchszeit selbst an der Spaltringdichtung keine Verschleißspuren feststellbar. Die Ausgestaltungen der Ansprüche 9 bis 11 beschreiben die unterschiedlichen Möglichkeiten zur Herstellung des Ringelementes.Embodiments of the invention described in claims 4 to 8 have the effect that dangerous wear marks were not detectable either on the shaft seal or in the space surrounding the shaft seal. In tests with an impeller, which was provided with a split ring seal on the side facing the shaft seal, the split ring seal was damaged within a very short time without the ring element. If an annular element according to the invention was instead arranged in the space receiving the shaft seal, no signs of wear were detectable even on the split ring seal after a long test period. The configurations of claims 9 to 11 describe the different possibilities for producing the ring element.

Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden im folgenden näher beschrieben. DieEmbodiments of the invention are shown in the drawings and are described in more detail below. The

Fig. 1 bis 3 zeigen hierbei unterschiedlich geformte Ringelemente.1 to 3 show differently shaped ring elements.

Die Fig. 1 zeigt ein Gehäuse (1) einer Strömungsmaschine, welche hier als Kreiselpumpe ausgebildet ist sowie ein innerhalb des Gehäuses (1) angeordnetes Laufrad (2). Bei dem hier gewählten Ausführungsbeispiel ist das Laufrad mit saug- und druckseitigen Spaltringdichtungen (3, 4) ausgerüstet. Das Laufrad (2) ist auf einer Welle (5) befestigt, auf der weiterhin eine Wellenschutzhülse (6) und eine als Gleitringdichtung ausgebildete Wellenabdichtung (7) befestigt ist. Desweiteren weist das Laufrad (2) im Bereich der Laufradnabe (8) in der druckseitigen Laufraddeckscheibe angebracht Axialschubausgleichsbohrungen (9) auf.1 shows a housing (1) of a turbomachine, which is designed here as a centrifugal pump, and an impeller (2) arranged inside the housing (1). In the exemplary embodiment selected here, the impeller is equipped with split ring seals (3, 4) on the suction and pressure side. The impeller (2) is attached to a shaft (5) on which a shaft protection sleeve (6) and a shaft seal (7) designed as a mechanical seal are also attached. Furthermore, the impeller (2) has axial thrust compensation bores (9) in the area of the impeller hub (8) in the impeller cover disk on the pressure side.

Innerhalb des die Wellenabdichtung (7) umgebenden Raumes (10), hier einem druckseitigen Gehäusedeckel (11), ist das im Gehäuse (1) befestigte Ringelement (12) angeordnet. Es erstreckt sich im Bereich zwischen dem am Laufrad angebrachten Spaltring (13) sowie der Laufradnabe (8) und der Wellenabdichtung (7). Die freie Stirnseite des Ringelementes (11) weist eine radial zur Welle verlaufende Fläche (14) auf, an deren kleinsten Durchmesser ein in axialer Richtung zur Wellenabdichtung (7) weisender Stutzen (15) angebracht ist. Das hier als Blechformteil ausgebildete Ringelement (12) kann auch als massives Formteil ausgebildet sein, welches auf der zur Wellenabdichtung weisenden Seite eine Hinterdrehung aufweisen würde. Desweiteren kann es mit dem gehäusefesten Spaltring (16) einteilig ausgebildet sein.The ring element (12) fastened in the housing (1) is arranged within the space (10) surrounding the shaft seal (7), here a pressure-side housing cover (11). It extends in the area between the split ring (13) attached to the impeller and the impeller hub (8) and the shaft seal (7). The free end face of the ring element (11) has a surface (14) running radially to the shaft, on the smallest diameter of which a nozzle (15) pointing in the axial direction to the shaft seal (7) is attached. The ring element (12) formed here as a sheet metal part can also be designed as a solid part which would have a backward rotation on the side facing the shaft seal. Furthermore, it can be formed in one piece with the split ring (16) fixed to the housing.

Das Ausführungsbeispiel der Fig. 2 entspricht weitgehend dem der Fig. 1. Ein Unterschied besteht darin, daß das Ringelement (12) an seiner freien Stirnseite nur mit einer in radialer Richtung zur Welle verlaufenden Fläche (14) versehen ist.The embodiment of FIG. 2 largely corresponds to that of FIG. 1. A difference is that the ring element (12) is provided on its free end face only with a surface (14) extending in the radial direction to the shaft.

Die Fig. 3 zeigt ein im querschnitt kegelstumpfförmig ausgebildetes Ringelement (12), welches diagonal zur Wellenachse verläuft, wobei seine freie Stirnseite (17) der Welle (5) zugekehrt ist. Infolge der kegelstumpfförmigen Ausbildung des Ringelementes (12) existiert an seiner freien Stirnseite (17), ebenso wie an den daran angebrachten, in den Fig. 1 und 2 gezeigten kleinsten Durchmessern der Fläche (14) bzw. eines daran angebrachten Stutzens (15) eine Abreißkante, mit deren Hilfe innerhalb des Raumes (10) ein Erosionsverschleiß verhindert werden kann.Fig. 3 shows a truncated conical ring element (12) which runs diagonally to the shaft axis, its free end face (17) facing the shaft (5). As a result of the frustoconical design of the ring element (12), there is one on its free end face (17), as well as on the smallest diameters of the surface (14) or a nozzle (15) attached to it shown in FIGS. 1 and 2 Tear-off edge, with the help of which erosion wear can be prevented within the space (10).

Claims (11)

1. A turbomachine, more particularly a centrifugal pump with an impeller arranged within a housing, a shaft seal arranged downstream from the impeller, more particularly a mechanical seal, in the case of which the housing has a space surrounding the shaft seal, characterized in that within the space (10) a ring element (12) is arranged which partly or completely covers over the shaft seal (7) and is attached so that its one end side is in engagement with the wall of the space, in that the free other end side of the ring element (12) is turned towards the impeller (2), in that between the free end side and the shaft (5) and/or the hub (8) of the impeller an intermediate space is present and in that the ring element (12) extends approximately parallel or inclined towards the free end side in relation to the shaft.
2. The turbomachine as claimed in claim 1, characterized in that the ring element (12) is arranged so that its free end side is in the part between a gap ring (13), which is arranged on the impeller (2), and the shaft (5).
3. The turbomachine as claimed in claim 1, characterized in that the free end side of the ring element (12) is arranged in a diameter range occupied by axial thrust compensation holes (9) provided in the impeller (2).
4. The turbomachine as claimed in any one of the preceding claims 1 through 3, characterized in that the ring element (12) is frustoconical in cross section.
5. The turbomachine as claimed in claim 4, characterized in that a surface (14), which extends radially in relation to the shaft (5), is arranged on the free end side of the ring element (12).
6. The turbomachine as claimed in any one of the preceding claims 1 through 3, characterized in that the ring element (12) extends predominantly parallel to'the shaft (5), a surface (14) extending parallel to the shaft being arranged on the free end side of the ring element.
7. The turbomachine as claimed in any one or more of the preceding claims 1 through 6, characterized in that the distance between a ring element (12), which predominantly extends parallel to the shaft (5) and a gap ring (13), which rotates with the impeller (5) is many times greater than the distance within the gap ring seal (4).
8. The turbomachine as claimed in any one or more of the preceding claims 1 through 7, characterized in that a hollow stud (15) is arranged on the surface (14) which extends radially towards the shaft, on a minimum diameter, such stud extending in the axial direction in relation to the shaft seal (7).
9. The turbomachine as claimed in any one or more of the preceding claims 1 through 8, characterized in that the ring element (12) and a fixed gap ring (16), which is inserted into the housing (1 and 11), are integral.
10. The turbomachine as claimed in any one or more of the preceding claims 1 through 9, characterized in that the ring element (12) is in the form of a sheet metal pressing.
11. The turbomachine as claimed in any one or more of the preceding claims 1 through 9, characterized in that the ring element (12) is constituted by a solid component and is provided with an undercut on the side thereof turned away from the impeller (2).
EP89109759A 1988-06-13 1989-05-30 Liquid-displacement machine Expired - Lifetime EP0346677B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89109759T ATE75818T1 (en) 1988-06-13 1989-05-30 FLOW MACHINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3820062 1988-06-13
DE3820062A DE3820062A1 (en) 1988-06-13 1988-06-13 FLOWING MACHINE

Publications (2)

Publication Number Publication Date
EP0346677A1 EP0346677A1 (en) 1989-12-20
EP0346677B1 true EP0346677B1 (en) 1992-05-06

Family

ID=6356432

Family Applications (2)

Application Number Title Priority Date Filing Date
EP89906085A Pending EP0442883A1 (en) 1988-06-13 1989-05-30 Turbine
EP89109759A Expired - Lifetime EP0346677B1 (en) 1988-06-13 1989-05-30 Liquid-displacement machine

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP89906085A Pending EP0442883A1 (en) 1988-06-13 1989-05-30 Turbine

Country Status (10)

Country Link
US (1) US5171126A (en)
EP (2) EP0442883A1 (en)
JP (1) JPH0646037B2 (en)
AT (1) ATE75818T1 (en)
CA (1) CA1330908C (en)
DE (2) DE3820062A1 (en)
DK (1) DK171831B1 (en)
ES (1) ES2032073T3 (en)
GR (1) GR3005061T3 (en)
WO (1) WO1989012755A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4431947A1 (en) * 1993-09-25 1995-03-30 Klein Schanzlin & Becker Ag Fluid flow engine for particle containing medium - has wall surfaces formed to direct medium flow in regions of higher rotary fluid flow
US5984629A (en) * 1993-09-25 1999-11-16 Ksb Aktiengesellscaft Turbo-machine with reduced abrasive wear

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JPH04123387U (en) * 1991-04-22 1992-11-09 三菱重工業株式会社 slurry pump
AU662811B2 (en) * 1992-04-08 1995-09-14 Alexander Phillip Caldwell Improvements to pump assemblies
GB2290113B (en) * 1994-05-31 1998-07-15 Ingersoll Dresser Pump Co Centrifugal pump
DE19503318C2 (en) * 1995-02-02 1997-11-20 Kronos Titan Gmbh Rinsing the seal on a pump for pumping highly saline media
GB2307276A (en) * 1996-03-06 1997-05-21 Shell Int Research Multi-phase fluid compressor
DE50012259D1 (en) * 2000-01-11 2006-04-27 Sulzer Pumpen Ag Winterthur Turbomachine for a fluid with a radial sealing gap between stator and a rotor
FR2904038A1 (en) * 2006-07-19 2008-01-25 Snecma Sa Centrifugal compressor impeller downstream face cooling system for aircraft turbomachine e.g. turbojet and jet prop engines, has cylindrical passage and sheet guiding drawn ventilating air till neighborhood of downstream face of impeller
AP2015008293A0 (en) * 2008-05-27 2015-02-28 Weir Minerals Australia Ltd Improvements relating to centrifugal pump impellers
JP5384322B2 (en) * 2009-12-28 2014-01-08 株式会社荏原製作所 Pump impeller and submersible pump equipped with the impeller
CN208169144U (en) * 2018-02-05 2018-11-30 上海荣威塑胶工业有限公司 Pump with waterproof construction

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Publication number Priority date Publication date Assignee Title
DE4431947A1 (en) * 1993-09-25 1995-03-30 Klein Schanzlin & Becker Ag Fluid flow engine for particle containing medium - has wall surfaces formed to direct medium flow in regions of higher rotary fluid flow
US5984629A (en) * 1993-09-25 1999-11-16 Ksb Aktiengesellscaft Turbo-machine with reduced abrasive wear

Also Published As

Publication number Publication date
JPH0646037B2 (en) 1994-06-15
DE3820062A1 (en) 1989-12-21
EP0442883A1 (en) 1991-08-28
GR3005061T3 (en) 1993-05-24
DE58901311D1 (en) 1992-06-11
ATE75818T1 (en) 1992-05-15
DK171831B1 (en) 1997-06-23
US5171126A (en) 1992-12-15
WO1989012755A1 (en) 1989-12-28
JPH03501761A (en) 1991-04-18
CA1330908C (en) 1994-07-26
ES2032073T3 (en) 1993-01-01
DK294990A (en) 1990-12-12
DK294990D0 (en) 1990-12-12
EP0346677A1 (en) 1989-12-20

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