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EP2643595B1 - Self cleaning radial flow pump with recirculation behind the impeller - Google Patents

Self cleaning radial flow pump with recirculation behind the impeller Download PDF

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Publication number
EP2643595B1
EP2643595B1 EP11796936.0A EP11796936A EP2643595B1 EP 2643595 B1 EP2643595 B1 EP 2643595B1 EP 11796936 A EP11796936 A EP 11796936A EP 2643595 B1 EP2643595 B1 EP 2643595B1
Authority
EP
European Patent Office
Prior art keywords
screw
centrifugal wheel
type centrifugal
cover plate
hole
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.)
Active
Application number
EP11796936.0A
Other languages
German (de)
French (fr)
Other versions
EP2643595A1 (en
Inventor
Robles Ciro
Carl STÄHLE
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.)
Frideco AG
Original Assignee
Frideco 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 Frideco AG filed Critical Frideco AG
Priority to EP11796936.0A priority Critical patent/EP2643595B1/en
Priority to EP17152843.3A priority patent/EP3179112B1/en
Priority to DK17152843.3T priority patent/DK3179112T3/en
Publication of EP2643595A1 publication Critical patent/EP2643595A1/en
Application granted granted Critical
Publication of EP2643595B1 publication Critical patent/EP2643595B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw 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
    • F04D29/44—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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
    • F04D29/708—Suction grids; Strainers; Dust separation; Cleaning specially 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
    • F05D2250/00—Geometry
    • F05D2250/10—Two-dimensional
    • F05D2250/15—Two-dimensional spiral

Definitions

  • the invention relates to a synchronenzentrifugalradpumpe and a method for operating a synchronenzentrifugalradpumpe.
  • the document CH 662 864 discloses a fferenzentrifugalradpumpe, wherein the fferenzentrifugalrad is rotatably mounted on a rotational axis.
  • the fferenzentrifugalradpumpe has in the region of the connection between ringenzentrifugalrad and axis of rotation on a cavity.
  • This per se very well-proven embodiment of a screw centrifugal pump has the disadvantage that can deposit and accumulate impurities within the cavity. This results in increased wear and / or increased maintenance.
  • EP 1 041 320 A a centrifuge pump with a recirculation behind the fan wheel
  • a screw centrifugal wheel pump comprising a pump housing with a pump inlet opening and a pump inlet arranged opposite housing rear wall comprising a rotatably disposed within the pump housing fferenzentrifugalrad with a hub and a blade, and comprising a rotatable drive shaft which is connected to the fferenzentrifugalrad, and comprising a cover plate which is arranged between the fferenzentrifugalrad and the housing rear wall, wherein the cover plate has a central opening through which the hub or the drive shaft wherein an inner space is formed between the cover plate and the rear wall of the housing, wherein the cover plate has a front side oriented towards the pump inlet opening, and wherein the front side has a partial surface whose profile is adapted to the rear side of the screw centrifugal wheel such that between the front side of the cover plate and the back of the fferenzentrifugalrades a gap of up to 3 mm is formed, wherein between the center opening of the cover plate
  • the screw centrifugal wheel pump according to the invention and the method according to the invention have the advantage that during the pumping operation a partial flow is formed, which flows from the front side to the rear side of the cover plate and then flows along a center opening of the cover plate back to the front side of the cover plate, so that a cleaning stream is formed, which is possibly located in the cavity behind the cover plate or at least partially recycle accumulated impurities to the front of the cover plate, so that these impurities can be conveyed away via the main flow of the fferenzentrifugalradpumpe.
  • the screw centrifugal pump comprises a rotatably mounted screw centrifugal wheel and a cover plate arranged directly next to the screw centrifugal wheel with a central opening, wherein a hub or a drive shaft of the screw centrifugal wheel preferably extends through the central opening. Between the center opening and the hub or the drive shaft, a fluid-conducting gap is formed.
  • Rotating the helical centrifugal wheel in the direction of rotation causes a fluid to be conveyed along a main flow, causing a partial flow of the fluid to flow to the rear of the cover plate via an aperture spaced from the center opening, and thereafter, passing this partial flow across the fluid conducting gap flows again to the main flow, due to the prevailing between the aperture and the fluid gap gap pressure difference.
  • This partial flow forms a purifying fluid flow, which in particular flows through the rear space of the cover plate and supplies any impurities present therein to the skin flow.
  • the cover plate preferably extends on the side facing the screw centrifugal wheel or the partial surface facing the screw centrifugal wheel in accordance with the course of the rear side of the screw centrifugal wheel, so that the partial surface preferably frusto-conical or even, wherein the partial surface could also have a different shape, for example, a curved or polygonal course.
  • the object is further achieved in particular with a method for self-cleaning a fferenzentrifugalradpumpe comprising a rotatably mounted SSenzentrifugalrad and arranged to form a gap on the back of fferenzentrifugalrades cover plate having a central opening, wherein the cover plate has an opening which is spaced with respect to the center opening, wherein a hub or a drive shaft of the fferenzentrifugalrades passes through the central opening, so that forms a fluid-conducting gap between the center opening and the hub or the drive shaft, wherein the fferenzentrifugalrad and the arrangement of the aperture are configured so adapted to each other that the back of the fferenzentrifugalrades the opening during rotation of the fferenzentrifugalrades seen in the axial direction is not covered or only during a partial angle ⁇ is covered, wherein the fferenzentr Ifugalrad is rotated in the direction of rotation and thereby a fluid is conveyed along a main
  • a cover plate for a screw centrifugal pump wherein the cover plate has a front side and a rear side, and wherein the cover plate has a central opening in the center thereof, wherein the center opening adapted to pass through a rotational axis of the fferenzentrifugalrades and extends in the direction of the axis of rotation, and wherein the cover plate has at least one aperture which is spaced from the center opening, and wherein the aperture forms a fluid-conducting connection between the front and the back of the cover plate, and wherein the opening has an inlet opening to the front, and wherein the front side has a recess, wherein the inlet opening is arranged in this recess, and wherein the inlet opening forms an inlet surface which is substantially parallel to the axis of rotation A.
  • FIG. 1 shows a known from the prior art, in the document CH 662 864 disclosed embodiment of a synchronenzentrifugalradpumpe.
  • FIG. 1 shows an axial section through the sortedenzentrifugalradpumpe 1 comprising a fferenzentrifugalrad 20 with a hub 21 and a blade 25, comprising a drive shaft 33 which is fixedly connected to the hub 21, and comprising a housing rear wall 23 arranged behind the SSenzentrifugalrad 20, and a fferenzentrifugalrad 20 circumferentially surrounding housing outer wall 3.
  • a Outlet opening 36 is provided so that gases can escape, which are carried in the fluid and excrete against the Laufradrotations scholar and pass through the impeller back gap between the impeller hub 21 and rear wall 23 in the interior 37.
  • the gap between the impeller hub 21 and the housing rear wall 23 is formed as a labyrinth, wherein both the hub-side and the rear wall-side labyrinth structure is interrupted by a transverse groove 38, so that a self-cleaning effect and no conveyed solids in the interior 37 and the outlet opening 36th reach.
  • contaminants can enter the interior 37, whereby these contaminants can deposit in the interior 37 and accumulate, so that cleaning of the screw centrifugal pump is required at certain time intervals.
  • FIG. 1a shows a side view of in FIG. 1 shown centrifugal centrifugal pump 1 at away broken outer housing.
  • FIG. 1b shows a plan view of an embodiment of a fferenzentrifugalrades 20, which is not in the document so CH 662864 is disclosed, which, however, for those in the Figures 1 and 1a illustrated centrifugal centrifugal pump 1 would be suitable, therefore the Figures 1, 1a and 1b be declared together.
  • the fferenzentrifugalrad 20 of the bobenzentrifugalradpumpe 1 comprises a hub 21 with a crescent-shaped base member 30 to which a blade 25 is connected, wherein an axis 33, the pressure-side, designed as a truncated housing wall 23 penetrates and is connected to the hub 21.
  • the housing wall 23 having a cone angle ⁇ between 5 ° and 70 ° is swept over by the end edge 28 of the pressure-side blade edge 27 with a small clearance 24.
  • the blade 25 also includes a suction side flank 39.
  • the crescent-shaped base portion 30 extends from the blade exit tip 35 into which the end edge 26 terminates, helically over a relatively long distance about the pump axis, to a point 31 at which Hub 21 has a relatively small radius R2.
  • the hub 21 has the largest radius R1.
  • a relatively large area of the housing wall 23 is exposed over a relatively large arc ⁇ , which is expediently approximately 120 °, between the blade outlet tip 35 and the aforementioned hub point 31.
  • the exposure of the housing wall 23 by reducing the wheel hub radius R1 can go as far as allow the material parameters to ensure the screw centrifugal 20 still a sufficient strength.
  • FIG. 2 1 shows a pump housing 3 with inlet opening 3a or pump inlet opening 3a, outlet 3b and housing interior 3c, and further comprises a hub 21, which is connected to a blade 25 shown only diagrammatically and dashed is and a Schaufelzentrifugalrad 20th forms, and which is rotatably mounted about a rotatable about an axis A drive shaft 33.
  • the connection between the drive shaft 33 and the hub 21 is shown only schematically.
  • the bucket 25 and the hub 21 are preferably as in FIG. 1a and 1b represented as a single, common part or as Schaufelzentrifugalrad 20 designed.
  • the ringenzentrifugalradpumpe 1 also comprises a conical inner housing 4 with inlet opening 4a and a Abstandhaltering 5.
  • the fferenzentrifugalradpumpe 1 also comprises a housing rear wall 23 with an outlet opening 36 and a seal 6.
  • the outlet opening 36 is for maintenance purposes and is during operation of the fferenzentrifugalradpumpe 1 usually closed with a plug from the outside.
  • a main flow F is generated, which leads to the outlet 3b via the inlet opening 3a.
  • the conveyed mainstream F comprises a fluid, preferably water and possibly gases such as water vapor, the helical centrifugal pump 1 is used in a preferred use for conveying polluted water, so that the main flow F may also include solids, such as feces, sand, gravel, textiles, Fibers, plastic parts etc.
  • the screw centrifugal pump 1 also comprises a cover plate 2, which is arranged in the direction of the axis A directly behind the hub 21 and the SSenzentrifugalrades 20.
  • the cover plate 2 has a front side 2h and a rear side 2i, wherein the front side 2h comprises a partial surface 2k whose course is adapted to the rear side 25a of the screw centrifugal wheel 20 such that between the front side 2h of the cover plate 2 and the rear side 25a of the screw centrifugal wheel 20, a gap 24 is formed of a maximum of up to 3 mm.
  • the gap 24 has a width in the range between 0.5 mm and 2 mm.
  • the gap 24 is designed to be so narrow that solids, for example fabrics that occur in sewage, such as women's stockings, can not penetrate into the gap 24 or can even wrap around the hub.
  • the narrow gap 24 also produces a shearing action on solids located within the gap 24, so that they are mechanically comminuted and conveyed to the main flow F out.
  • at least one of the surfaces directed towards the gap 24 is structured, rough or designed, for example, with protruding teeth, in order to improve mechanical comminution of solids present in the gap 24.
  • a gap 24 wider than 3mm, for example 5mm or wider, would have several disadvantages. On the one hand, due to the wide gap 24, the mechanical comminution of solids would no longer be guaranteed.
  • the front side 2h in the illustrated embodiment comprises a substantially frusto-conical extending part surface 2k, the course of the rear side is adapted to a fferenzentrifugalrad 20, wherein the partial surface 2k in the center has a central opening 2g, wherein the central opening 2g extends parallel to the axis A.
  • the hub 21 extends through the central opening 2g, so that between the center opening 2g and the hub 21, a gap 2b extending in the direction of the axis A is formed.
  • the hub 21 also has a projection which partially covers the partial surface 2k, so that between the hub 21 and the sub-surface 2k, a gap 24 running transversely with respect to the axis A is formed.
  • the cover plate 2 has at least one opening 2a which is arranged at a distance from the center opening 2g, wherein the opening 2a forms a fluid-conducting connection between the front side 2h and the rear side 2i of the cover plate 2.
  • the fluid in the region of the opening 2a has a higher pressure than in the region of the central opening 2g, whereby a partial flow F1 is generated by a part of the main flow F as part of flow F1 flows through the opening 2a to the back 2i of the cover plate 2 in the interior 37, and then flows through the gap 2b and the gap 24 back into the main flow F.
  • This partial flow F1 causes contaminants, which are located in the interior 37, are conveyed out of this and the skin flow F are supplied.
  • the fferenzentrifugalrad 20 and the arrangement of the opening 2a are configured such that the rear side 25a of the fferenzentrifugalrades 20, the aperture 2a is not covered or covered by a rotation of the fferenzentrifugalrades 20 by 360 ° only during a partial angle ⁇ .
  • FIG. 12 shows a pump housing 3 in which a cover plate 2 and a fferenzentrifugalrad 20 is arranged.
  • the hub 21 is connected to a circular base part 30, wherein the blade 25 is connected via the end edge 28 with the base part 30.
  • the fferenzentrifugalrad 20 includes an end edge 26, a pressure-side blade edge 27, and a suction-side edge 39 and a blade outlet tip 35th
  • FIG. 13 shows the fferenzentrifugalrad 20 in a plan view, wherein the base member 30 is circular and with respect to the axis A has a maximum radius R1.
  • FIG. 13 shows an example of a possible arrangement of an opening or an opening 2a with respect to the SSenzentrifugalrad 20.
  • the opening 2a is not covered by the fferenzentrifugalrad 20 and by the back 25a of the fferenzentrifugalrades 20 so that the opening 2a is constantly open.
  • a flow in the direction of rotation R of the helical centrifugal wheel 20 is advantageously generated in order to hinder or prevent the entry of solid contaminants into the opening 2a.
  • a fluid-conducting connection between the front side 2h and the interior 37 is formed via the opening 2a in order to generate a fluid flow F1, which flows into the interior space 37 via the opening 2a and flows out of the interior space 37 via the gap 2b.
  • the ringenzentrifugalrad 20 could as in the FIGS. 1a and 1b be configured represented.
  • the hub 21 of the fferenzentrifugalrades 20 includes a crescent-shaped base portion 30, wherein the blade 25 is disposed on the crescent-shaped base portion 30 and the crescent-shaped base portion 30 with respect to the rotation axis A has a maximum radius R1 and a minimum radius R2.
  • the crescent-shaped base part 30 is extending with respect to the opening 2a in such a way designed such that the rear side 25a of the fferenzentrifugalrades 20, the aperture 2a at the minimum radius R2 is not covered, wherein the back 25a of the fferenzentrifugalrades 20, the aperture 2a covered during rotation of the fferenzentrifugalrades 20 by 360 ° during a partial angle ⁇ .
  • the opening 2a is thus briefly covered during each rotation of the fferenzentrifugalrades 20.
  • This embodiment has the advantage that in the region of the opening 2a advantageously a flow in the direction of rotation R of the fferenzentrifugalrades 20 is generated to complicate the entry of solid impurities in the opening 2a or prevent.
  • a further advantage is the fact that solid impurities, which accumulate at the inlet opening of the opening 2a, are mechanically removed by the hub 2a moving through the opening 2a, if the impurities protrude beyond the front side 2h.
  • the drive shaft 33 could also be further advanced, so that the gap 2 b is formed at least partially or exclusively between the cover plate 2 and the drive shaft 33.
  • the cover plate 2 has at least one opening 2a and preferably at least two openings 2a.
  • the openings 2a are arranged symmetrically with respect to the axis A in the partial surface 2k.
  • the openings 2a can be configured in a variety of ways. In the FIG. 2 shown below opening 2a is in FIG. 3 shown enlarged.
  • the opening 2 comprises an inlet opening 21 whose cross section has an entrance surface 2m formed.
  • the partial flow F1 flows through the opening 2a to the rear 2i of the cover plate 2.
  • the partial flow F1 is deflected when flowing into the opening 2a, which has the advantage that in the flow F2 located solids difficult to flow into the opening 2a.
  • the partial flow F1 is thereby at least partially cleaned of solids because the solids remain at least partially in the flow F2 and be carried away by this.
  • the cover plate 2 could, similar to those in FIG. 1a shown housing rear wall, have a cone angle ⁇ in the range between 5 ° and 70 °.
  • FIG. 4 shows a further embodiment of an opening 2a.
  • the embodiment shown in FIG. 4 represented opening 2a arranged such that the partial flow F1 is deflected with respect to the occurring at the front side 2h of the cover plate 2 flow F2 such that it undergoes a partial flow reversal.
  • the opening 2a extends as in FIG. 4 represented at least partially opposite to the direction of rotation R of the fferenzentrifugalrades 20.
  • the thus extending aperture 2a has the advantage that solids can get through the opening 2a to the back 2i of the cover plate 2 less well.
  • FIG. 2 The opening 2a shown above is in FIG. 5 shown enlarged.
  • a recess 2c is arranged, which opens to the opening 2a, wherein the opening 2a forms an inlet opening 21 with inlet surface 2m, so that the inlet opening 21 in the Recess 2c is arranged.
  • the inlet opening 21 or the inlet surface 2m can be arranged in various ways, but advantageously as in FIG. 5 represented such that the partial flow F1 is deflected and undergoes an at least partial flow reversal with respect to the occurring at the front 2h of the cover plate 2 flow F2.
  • the inlet opening 21 arranged in this way has the advantage that solids can pass through the opening 2a to the back 2i of the cover plate 2 less effectively.
  • the entrance surface 2m is arranged in an advantageous embodiment such that it is parallel or substantially parallel to the axis A.
  • the entrance surface 2m preferably arranged facing away from the direction of rotation R arranged. In FIG. 5 is not the axis A per se, but the course of the axis A is shown.
  • the entrance surface 2m is arranged in a further advantageous embodiment such that it is perpendicular or substantially perpendicular to the rotational direction R of the drive shaft 33, wherein the entrance surface 2m facing away from the rotation direction R is arranged.
  • FIGS. 6, 7 and 8th show an embodiment of a cover plate 2 in plan view, in perspective view and in a section along the section line BB.
  • the recess 2c, as in the FIGS. 6 and 7 are at least partially formed by a substantially perpendicular or perpendicular to the axis A extending bore.
  • FIG. 6 shows the course of the axis A and the preferred direction of rotation R. Off FIG. 6 is thus seen that the entrance surface 2m parallel to the axis A and perpendicular to Rotation direction R runs.
  • FIG. 8 shows in section the cover plate 2 with front 2h, back 2i and center opening 2g.
  • the openings 2a are arranged, wherein the openings 2a are always arranged at a distance from the central opening 2g.
  • the openings 2a could also, as in FIG. 3 shown, perpendicular or substantially perpendicular with respect to the partial surface 2k run, or as in FIG. 4 shown, transverse to the part surface 2k run.
  • a differently sized partial surface 2k is covered by the rear side 25a of the screw centrifugal wheel 20.
  • Screw centrifugal wheel 20 shown could, for example, the in FIG. 6 Covered with 2k part surface of the front 2h are covered on the with FIG. 1a and 1b described way.
  • Screw centrifugal wheel 20 shown could, for example, the in FIG. 6 2k2 designated partial surface of the front 2h are permanently covered.
  • the cover plate 2 as in the FIGS. 6 to 8 illustrated, a recess extending in the circumferential direction, in particular a spiral-shaped recess 2d, which advantageously extends in the region of the central opening 2g along the partial surface 2h to the outside.
  • the depression 2d extends as in FIG FIG. 6 shown in the direction of rotation R spiral from inside to outside.
  • the hub 21 rotating in the direction of rotation R over the part surface 2k or the screw centrifugal wheel 20 rotating in the direction of rotation R helps to move the dirt in the direction of rotation R in the depression 2d or on the part surface 2k and to move it towards the outside with respect to the part surface 2k the pollution reaches the skin stream F, and is detected by this and carried away.
  • an arrangement of the aperture 2a is particularly advantageous as in the FIGS. 6 to 8 shown. In particular from FIG.
  • the contamination is moved substantially in the direction of rotation R, wherein the aperture 2a is arranged in a recess 2c and the inlet surface 2m facing away from the direction of rotation R is aligned so that dirt, even if they flow over the recess 2c, due to Flow conditions and the direction of movement of the contaminants hardly or not at all flow through the opening 2a but the main stream F are supplied.
  • the cover plate 2 can, as in the FIGS. 7 and 8th shown, in addition, a running along the edge region recesses 2f, which is provided in particular for receiving an O-ring and thus for sealing.
  • FIG. 9 shows in a section a further embodiment of a cover plate 2, which in contrast to the in FIG. 8 However, shown section has a flat extending part surface 2k and 2k2. Otherwise, the cover plate 2 is configured similar to the in FIG. 8 illustrated embodiment by the cover plate 2 according to FIG. 9 also has a recess 2c, which opens into an opening 2a. If the spiraling depression 2d is thought away, discloses FIG. 6 a top view of the in FIG. 9 shown cover plate 2. The in FIG. 9 However, shown cover plate 2 could also have a spiral extending recess 2d, so that a plan view of this embodiment as in FIG. 6 would look like. In the FIG.
  • cover plate 2 also has a central opening 2g and a front side 2h and a back 2i.
  • the front side 2h or the partial surface 2k can run in a variety of ways, such as curved, as in FIG. 10 shown schematically in a section, or edged, as in FIG. 11 shown schematically in a section.
  • the sub-surface is as shown in FIG FIG. 8 shown, frustoconical.
  • the cover plate 2 is designed as a casting, wherein the recess 2c and advantageously also the opening 2a or the inlet opening 21 already form part of the still unprocessed casting. For the completion of the cover plate 2, it is then still essentially necessary to machine the front side 2h, in particular by removing machining machining.
  • a cover plate 2 made of a casting designed in this way has the advantage that there are no or only very small additional costs during production, since the chip-removing machining of the cover plate 2 is required anyway.
  • the casting may have a thickness between 2 and 10 mm.
  • the cover plate 2 could also be made of a metal sheet.
  • the inventive method allows self-cleaning a fferenzentrifugalradpumpe 1.
  • the fferenzentrifugalradpumpe 1 has a rotatably mounted SSenzentrifugalrad 20 and arranged immediately adjacent to or behind the SSenzentrifugalrad 20 cover plate 2 with a central opening 2g, wherein a hub 21 of the fferenzentrifugalrades 20 or the SSenzentrifugalrad 15th
  • the bearing axis 33 passes through the central opening 2g, so that between the center opening 2g and the hub 21 or the axis 33, a fluid-conducting gap 2b is formed.
  • the cover plate 2 on the front side 2h on the part surface 2k has a spiral recess 2d, wherein the spirally extending recess 2d in the direction of rotation R from inside extends to the outside, so that the outgoing from the gap 2b partial flow F1 and possibly located therein impurities on the spiraling depression 2d is supplied to the main flow F.
  • cover plate 2 and the housing rear wall 23 are always shown as separate parts.
  • the cover plate 2 and the housing rear wall 23 could also be designed in one piece, for example by being made of a single part, for example a cast part.
  • Such a single casting, comprising both the cover plate 2 and the housing rear wall 23, has the advantage that this is inexpensive to produce, and that between the cover plate 2 and the housing rear wall 23 no seal is required. This allows a particularly low-maintenance embodiment.
  • FIG. 14 shows in a plan view another embodiment of the already in FIG. 6 shown.
  • Cover plate 2 The opening 2a and the entrance surface 2m again runs parallel to the axis A, wherein the opening 2a and the inlet surface 2m, in contrast to FIG. 6 , with respect to a radially extending through the axis A extending straight line L inclined at an angle ⁇ , wherein the angle ⁇ preferably has a value in the range of +/- 60 degrees.

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

Description

Die Erfindung betrifft eine Schraubenzentrifugalradpumpe sowie ein Verfahren zum Betrieb einer Schraubenzentrifugalradpumpe.The invention relates to a Schraubenzentrifugalradpumpe and a method for operating a Schraubenzentrifugalradpumpe.

Stand der TechnikState of the art

Das Dokument CH 662 864 offenbart eine Schraubenzentrifugalradpumpe, wobei das Schraubenzentrifugalrad an einer Drehachse drehbar gelagert ist. Die Schraubenzentrifugalradpumpe weist im Bereich der Verbindung zwischen Schraubenzentrifugalrad und Drehachse einen Hohlraum auf. Diese an sich sehr bewährte Ausführungsform einer Schraubenzentrifugalradpumpe weist den Nachteil auf, dass sich innerhalb des Hohlraumes Verunreinigungen ablagern und aufakkumulieren können. Dies hat einen erhöhten Verschleiss und/oder einen erhöhten Wartungsaufwand zur Folge.The document CH 662 864 discloses a Schraubenzentrifugalradpumpe, wherein the Schraubenzentrifugalrad is rotatably mounted on a rotational axis. The Schraubenzentrifugalradpumpe has in the region of the connection between Schraubenzentrifugalrad and axis of rotation on a cavity. This per se very well-proven embodiment of a screw centrifugal pump has the disadvantage that can deposit and accumulate impurities within the cavity. This results in increased wear and / or increased maintenance.

Des Weiteren offenbart EP 1 041 320 A eine zentrifagale Pumpe mit einer Rezirkulation hinter dem LanfradFurther disclosed EP 1 041 320 A a centrifuge pump with a recirculation behind the fan wheel

Darstellung der ErfindungPresentation of the invention

Es ist Aufgabe der vorliegenden Erfindung eine Schraubenzentrifugalradpumpe auszubilden sowie ein Verfahren zum Reinigen einer Schraubenzentrifugalradpumpe vorzuschlagen, die bezüglich der Anlagerung von Verunreinigungen vorteilhaftere Eigenschaften aufweisen.It is an object of the present invention to form a Schraubenzentrifugalradpumpe and to propose a method for cleaning a Schraubenzentrifugalradpumpe, which have more advantageous properties with respect to the attachment of impurities.

Diese Aufgabe wird gelöst mit einer Schraubenzentrifugalradpumpe aufweisend die Merkmale von Anspruch 1. Die Unteransprüche 2 bis 17 beziehen sich auf weitere, vorteilhafte Ausführungsformen. Die Aufgabe wird weiter gelöst mit einem Verfahren zur Selbstreinigung einer Schraubenzentrifugalradpumpe aufweisend die Merkmale von Anspruch 18. Die Ansprüche 19 und 20 beziehen sich auf weitere, vorteilhafte Verfahrensschritte.This object is achieved with a Schraubenzentrifugalradpumpe comprising the features of claim 1. The dependent claims 2 to 17 relate to further advantageous embodiments. The object is further achieved with a method for self-cleaning a Schraubenzentrifugalradpumpe having the features of claim 18. The claims 19 and 20 relate to further advantageous method steps.

Die Aufgabe wird insbesondere gelöst mit einer Schraubenzentrifugalradpumpe umfassend ein Pumpengehäuse mit einer Pumpeneinströmöffnung und einer der Pumpeneinströmöffnung gegenüberliegend angeordneten Gehäuserückwand, umfassend ein innerhalb des Pumpengehäuses drehbar angeordnetes Schraubenzentrifugalrad mit einer Nabe sowie einer Schaufel, sowie umfassend eine drehbare Antriebswelle welche mit dem Schraubenzentrifugalrad verbunden ist, sowie umfassend eine Deckplatte welche zwischen dem Schraubenzentrifugalrad und der Gehäuserückwand angeordnet ist, wobei die Deckplatte eine Mittenöffnung aufweist durch welche die Nabe oder die Antriebswelle verläuft, und wobei zwischen der Deckplatte und der Gehäuserückwand ein Innenraum ausgebildet ist, wobei die Deckplatte eine zur Pumpeneinströmöffnung hin ausgerichtete Vorderseite aufweist, und wobei die Vorderseite eine Teiloberfläche umfasst deren Verlauf derart der Rückseite des Schraubenzentrifugalrades angepasst ausgestaltet ist, dass zwischen der Vorderseite der Deckplatte und der Rückseite des Schraubenzentrifugalrades ein Spalt von maximal bis zu 3 mm ausgebildet ist, wobei zwischen der Mittenöffnung der Deckplatte und der Nabe oder der Antriebswelle ein Spalt ausgebildet ist, der Fluid leitend mit dem Innenraum sowie dem Spalt verbunden ist, wobei die Deckplatte zumindest eine Durchbrechung aufweist welche beabstandet zur Mittenöffnung angeordnet ist, wobei das Schraubenzentrifugalrades und die Anordnung der Durchbrechung derart gegenseitig angepasst ausgestaltet sind, dass die Rückseite des Schraubenzentrifugalrades die Durchbrechung in Axialrichtung gesehen nicht bedeckt oder bei einer Rotation des Schraubenzentrifugalrades um 360° nur während eines Teilwinkels bedeckt, und wobei die Durchbrechung eine Fluid leitende Verbindung zwischen der Vorderseite und dem Innenraum ausbildet, um einen Fluidstrom zu erzeugen, der über die Durchbrechung in den Innenraum hinein strömt und über den Spalt wieder aus dem Innenraum hinaus strömt.The object is achieved in particular with a screw centrifugal wheel pump comprising a pump housing with a pump inlet opening and a pump inlet arranged opposite housing rear wall comprising a rotatably disposed within the pump housing Schraubenzentrifugalrad with a hub and a blade, and comprising a rotatable drive shaft which is connected to the Schraubenzentrifugalrad, and comprising a cover plate which is arranged between the Schraubenzentrifugalrad and the housing rear wall, wherein the cover plate has a central opening through which the hub or the drive shaft wherein an inner space is formed between the cover plate and the rear wall of the housing, wherein the cover plate has a front side oriented towards the pump inlet opening, and wherein the front side has a partial surface whose profile is adapted to the rear side of the screw centrifugal wheel such that between the front side of the cover plate and the back of the Schraubenzentrifugalrades a gap of up to 3 mm is formed, wherein between the center opening of the cover plate and the hub or the drive shaft, a gap is formed, the fluid is conductively connected to the interior and the gap, wherein the cover plate at least one Opening which has spaced apart from the center opening, wherein the Schraubenzentrifugalrades and the arrangement of the aperture are configured so adapted to each other that the back of the Schraubenzentrifugalrades the aperture not seen in the axial direction covered or covered in a rotation of the Schraubenzentrifugalrades 360 ° only during a partial angle, and wherein the aperture forms a fluid-conducting connection between the front and the interior to produce a fluid flow which flows through the opening into the interior and over the Gap flows out of the interior again.

Die erfindungsgemässe Schraubenzentrifugalradpumpe sowie das erfindungsgemässe Verfahren weisen den Vorteil auf, dass sich währen dem Pumpbetrieb ein Teilstrom ausbildet, der von der Vorderseite zur Rückseite der Deckplatte strömt und danach entlang einer Mittenöffnung der Deckplatte wieder zur Vorderseite der Deckplatte strömt, sodass sich ein Reinigungsstrom ausbildet, der in der Lage ist allfällig im Hohlraum hinter der Deckplatte befindliche oder angelagerte Verunreinigungen zumindest teilweise wieder zur Vorderseite der Deckplatte zu fördern, sodass diese Verunreinigungen über den Hauptstrom der Schraubenzentrifugalradpumpe weggefördert werden können.The screw centrifugal wheel pump according to the invention and the method according to the invention have the advantage that during the pumping operation a partial flow is formed, which flows from the front side to the rear side of the cover plate and then flows along a center opening of the cover plate back to the front side of the cover plate, so that a cleaning stream is formed, which is possibly located in the cavity behind the cover plate or at least partially recycle accumulated impurities to the front of the cover plate, so that these impurities can be conveyed away via the main flow of the Schraubenzentrifugalradpumpe.

Die erfindungsgemässe Schraubenzentrifugalradpumpe umfasst ein drehbar gelagertes Schraubenzentrifugalrad sowie eine unmittelbar neben dem Schraubenzentrifugalrad angeordnete Deckplatte mit einer Mittenöffnung, wobei eine Nabe oder eine Antriebswelle des Schraubenzentrifugalrades vorzugsweise durch die Mittenöffnung verläuft. Zwischen der Mittenöffnung und der Nabe beziehungsweise der Antriebswelle ist ein Fluid leitender Spalt ausgebildet. Das Rotieren des Schraubenzentrifugalrades in Drehrichtung bewirkt, dass ein Fluid entlang eines Hauptstromes gefördert wird, was zur Folge hat, dass ein Teilstrom des Fluides über eine bezüglich der Mittenöffnung beabstandete Durchbrechung zur Rückseite der Deckplatte strömt, und dass dieser Teilstrom danach über den Fluid leitenden Spalt wieder zum Hauptstrom strömt, auf Grund der zwischen der Durchbrechung und dem Fluid leitenden Spalt herrschenden Druckdifferenz. Dieser Teilstrom bildet ein reinigender Fluidstrom, der insbesondere den rückseitigen Raum der Deckplatte durchströmt und darin allfällig vorhandene Verunreinigungen dem Hautstrom zuführt.The screw centrifugal pump according to the invention comprises a rotatably mounted screw centrifugal wheel and a cover plate arranged directly next to the screw centrifugal wheel with a central opening, wherein a hub or a drive shaft of the screw centrifugal wheel preferably extends through the central opening. Between the center opening and the hub or the drive shaft, a fluid-conducting gap is formed. Rotating the helical centrifugal wheel in the direction of rotation causes a fluid to be conveyed along a main flow, causing a partial flow of the fluid to flow to the rear of the cover plate via an aperture spaced from the center opening, and thereafter, passing this partial flow across the fluid conducting gap flows again to the main flow, due to the prevailing between the aperture and the fluid gap gap pressure difference. This partial flow forms a purifying fluid flow, which in particular flows through the rear space of the cover plate and supplies any impurities present therein to the skin flow.

Die Deckplatte verläuft auf der dem Schraubenzentrifugalrad zugewandten Seite beziehungsweise der dem Schraubenzentrifugalrad zugewandten Teilfläche vorzugsweise entsprechend dem Verlauf der Rückseite des Schraubenzentrifugalrades, sodass die Teilfläche vorzugsweise kegelstumpfförmig oder eben verläuft, wobei die Teilfläche auch eine andere Verlaufsform aufweisen könnte, beispielsweise einen gekrümmten oder mehrkantigen Verlauf.The cover plate preferably extends on the side facing the screw centrifugal wheel or the partial surface facing the screw centrifugal wheel in accordance with the course of the rear side of the screw centrifugal wheel, so that the partial surface preferably frusto-conical or even, wherein the partial surface could also have a different shape, for example, a curved or polygonal course.

Die Aufgabe wird weiter insbesondere gelöst mit einem Verfahren zur Selbstreinigung einer Schraubenzentrifugalradpumpe aufweisend ein drehbar gelagertes Schraubenzentrifugalrad sowie eine unter Ausbildung eines Spaltes auf der Rückseite des Schraubenzentrifugalrades angeordnete Deckplatte mit einer Mittenöffnung, wobei die Deckplatte eine Durchbrechung aufweist, welche bezüglich der Mittenöffnung beabstandet ist, wobei eine Nabe oder eine Antriebswelle des Schraubenzentrifugalrades durch die Mittenöffnung verläuft, sodass sich zwischen der Mittenöffnung und der Nabe oder der Antriebswelle ein Fluid leitender Spalt ausbildet, wobei das Schraubenzentrifugalrad und die Anordnung der Durchbrechung derart gegenseitig angepasst ausgestaltet sind, dass die Rückseite des Schraubenzentrifugalrades die Durchbrechung während dem Rotieren des Schraubenzentrifugalrades in Axialrichtung gesehen nicht bedeckt wird oder nur während eines Teilwinkels Δ bedeckt wird, wobei das Schraubenzentrifugalrad in Drehrichtung rotiert wird und dadurch ein Fluid entlang eines Hauptstromes gefördert wird, wobei ein Teilstrom F1 des Fluides über die Durchbrechung zur Rückseite der Deckplatte strömt, und wobei dieser Teilstrom danach über die Spalten wieder zum Hauptstrom strömt, auf Grund der zwischen der Durchbrechung und dem Spalt herrschenden Druckdifferenz.The object is further achieved in particular with a method for self-cleaning a Schraubenzentrifugalradpumpe comprising a rotatably mounted Schraubenzentrifugalrad and arranged to form a gap on the back of Schraubenzentrifugalrades cover plate having a central opening, wherein the cover plate has an opening which is spaced with respect to the center opening, wherein a hub or a drive shaft of the Schraubenzentrifugalrades passes through the central opening, so that forms a fluid-conducting gap between the center opening and the hub or the drive shaft, wherein the Schraubenzentrifugalrad and the arrangement of the aperture are configured so adapted to each other that the back of the Schraubenzentrifugalrades the opening during rotation of the Schraubenzentrifugalrades seen in the axial direction is not covered or only during a partial angle Δ is covered, wherein the Schraubenzentr Ifugalrad is rotated in the direction of rotation and thereby a fluid is conveyed along a main flow, wherein a partial flow F1 of the fluid flows through the opening to the back of the cover plate, and wherein this partial flow then flows through the gaps back to the main flow, due to the between the opening and the gap prevailing pressure difference.

Hier weiter offenbart wird eine Deckplatte für eine Schraubenzentrifugalradpumpe, wobei die Deckplatte eine Vorderseite und eine Rückseite aufweist, und wobei die Deckplatte in deren Zentrum eine Mittenöffnung aufweist, wobei die Mittenöffnung zum Durchtritt einer Rotationsachse des Schraubenzentrifugalrades angepasst ausgestaltet ist und in Richtung der Rotationsachse verläuft, und wobei die Deckplatte zumindest eine Durchbrechung aufweist welche beabstandet zur Mittenöffnung angeordnet ist, und wobei die Durchbrechung eine Fluid leitende Verbindung zwischen der Vorderseite und der Rückseite der Deckplatte ausbildet, und wobei die Durchbrechung zur Vorderseite hin eine Eintrittsöffnung aufweist, und wobei die Vorderseite eine Vertiefung aufweist, wobei die Eintrittsöffnung in dieser Vertiefung angeordnet ist, und wobei die Eintrittsöffnung eine Eintrittsfläche ausbildet, die im Wesentlichen parallel zur Rotationsachse A verläuft.Further disclosed herein is a cover plate for a screw centrifugal pump, wherein the cover plate has a front side and a rear side, and wherein the cover plate has a central opening in the center thereof, wherein the center opening adapted to pass through a rotational axis of the Schraubenzentrifugalrades and extends in the direction of the axis of rotation, and wherein the cover plate has at least one aperture which is spaced from the center opening, and wherein the aperture forms a fluid-conducting connection between the front and the back of the cover plate, and wherein the opening has an inlet opening to the front, and wherein the front side has a recess, wherein the inlet opening is arranged in this recess, and wherein the inlet opening forms an inlet surface which is substantially parallel to the axis of rotation A.

Die Erfindung wird nachfolgend an Hand von Ausführungsbeispielen im Detail beschrieben.The invention will be described below with reference to exemplary embodiments in detail.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Die zur Erläuterung der Ausführungsbeispiele verwendeten Zeichnungen zeigen:

  • Fig. 1 einen Axialschnitt einer aus dem Stand der Technik bekannten Schraubenzentrifugalradpumpe;
  • Fig. la eine Seitenansicht der in Figur 1 dargestellten Schraubenzentrifugalradpumpe bei weg gebrochenem Aussengehäuse;
  • Fig. 1b eine Draufsicht auf ein Laufrad;
  • Fig. 2 in einem Längsschnitt eine Teilansicht einer Schraubenzentrifugalradpumpe mit einem Ausführungsbeispiel einer Deckscheibe;
  • Figuren 3 bis 5 unterschiedlich verlaufende Durchbrechungen;
  • Fig. 6 eine Draufsicht auf eine Deckscheibe;
  • Fig. 7 eine perspektivische Ansicht der in Figur 6 dargestellten Deckscheibe;
  • Fig. 8 einen Schnitt durch die Deckscheibe gemäss Figur 6 entlang der Linie B-B;
  • Fig. 9 einen Schnitt durch ein weiteres Ausführungsbeispiel einer Deckscheibe;
  • Fig. 10, 11 schematisch einen Schnitt durch zwei weitere Ausführungsbeispiele von Deckscheiben:
  • Fig. 12 eine Seitenansicht eines weiteren Ausführungsbeispiels eines Laufrades einer Schraubenzentrifugalradpumpe bei weg gebrochenem Aussengehäuse;
  • Fig. 13 eine Draufsicht auf das Laufrad der in Figur 12 dargestellten Schraubenzentrifugalradpumpe;
  • Fig. 14 eine Draufsicht auf ein weiteres Ausführungsbeispiel einer Deckscheibe.
The drawings used to explain the embodiments show:
  • Fig. 1 an axial section of a known from the prior art Schraubenzentrifugalradpumpe;
  • Fig. La is a side view of in FIG. 1 shown centrifugal centrifugal pump with wegbruchem outside housing;
  • Fig. 1b a plan view of an impeller;
  • Fig. 2 in a longitudinal section a partial view of a Schraubenzentrifugalradpumpe with an embodiment of a cover plate;
  • FIGS. 3 to 5 differently extending openings;
  • Fig. 6 a plan view of a cover plate;
  • Fig. 7 a perspective view of in FIG. 6 illustrated cover plate;
  • Fig. 8 a section through the cover plate according FIG. 6 along the line BB;
  • Fig. 9 a section through a further embodiment of a cover plate;
  • 10, 11 schematically a section through two further embodiments of cover plates:
  • Fig. 12 a side view of another embodiment of an impeller of a Schraubenzentrifugalradpumpe with away broken outer housing;
  • Fig. 13 a plan view of the impeller of in FIG. 12 illustrated centrifugal centrifugal pump;
  • Fig. 14 a plan view of another embodiment of a cover plate.

Grundsätzlich sind in den Zeichnungen gleiche Teile mit gleichen Bezugszeichen versehen.Basically, the same parts are given the same reference numerals in the drawings.

Wege zur Ausführung der ErfindungWays to carry out the invention

Fig. 1 zeigt eine aus dem Stand der Technik bekannte, im Dokument CH 662 864 offenbarte Ausführungsform einer Schraubenzentrifugalradpumpe. Figur 1 zeigt einen Axialschnitt durch die Schraubenzentrifugalradpumpe 1 umfassend ein Schraubenzentrifugalrad 20 mit einer Nabe 21 und einer Schaufel 25, umfassend eine Antriebswelle 33, welche fest mit der Nabe 21 verbunden ist, sowie umfassend eine hinter dem Schraubenzentrifugalrad 20 angeordnete Gehäuserückwand 23, sowie eine das Schraubenzentrifugalrad 20 in Umfangsrichtung umgebende Gehäuseaussenwand 3. In der Gehäuserückwand 23 ist in der Nähe der Antriebswelle 33 eine Auslassöffnung 36 vorgesehen, damit Gase entweichen können, welche im Fördermedium mitgeführt werden und sich gegen das Laufradrotationszentrum ausscheiden und durch den laufradrückseitigen Spalt zwischen Laufradnabe 21 und Gehäuserückwand 23 in den Innenraum 37 gelangen. Der Spalt zwischen der Laufradnabe 21 und der Gehäuserückwand 23 ist als ein Labyrinth ausgebildet, wobei sowohl die nabenseitige als auch die gehäuserückwandseitige Labyrinthstruktur mittels einer Quernute 38 unterbrochen ist, damit eine selbst reinigende Wirkung entsteht und keine mitgeförderten Festteile in den Innenraum 37 und die Auslassöffnung 36 gelangen. Es hat sich jedoch gezeigt, dass trotz dieser Massnahme Verunreinigungen in den Innenraum 37 gelangen können, wobei sich diese Verunreinigungen im Innenraumes 37 ablagern und aufakkumulieren können, sodass in gewissen Zeitabständen eine Reinigung der Schraubenzentrifugalradpumpe erforderlich ist. Fig. 1 shows a known from the prior art, in the document CH 662 864 disclosed embodiment of a Schraubenzentrifugalradpumpe. FIG. 1 shows an axial section through the Schraubenzentrifugalradpumpe 1 comprising a Schraubenzentrifugalrad 20 with a hub 21 and a blade 25, comprising a drive shaft 33 which is fixedly connected to the hub 21, and comprising a housing rear wall 23 arranged behind the Schraubenzentrifugalrad 20, and a Schraubenzentrifugalrad 20 circumferentially surrounding housing outer wall 3. In the housing rear wall 23 is in the vicinity of the drive shaft 33 a Outlet opening 36 is provided so that gases can escape, which are carried in the fluid and excrete against the Laufradrotationszentrum and pass through the impeller back gap between the impeller hub 21 and rear wall 23 in the interior 37. The gap between the impeller hub 21 and the housing rear wall 23 is formed as a labyrinth, wherein both the hub-side and the rear wall-side labyrinth structure is interrupted by a transverse groove 38, so that a self-cleaning effect and no conveyed solids in the interior 37 and the outlet opening 36th reach. However, it has been shown that, despite this measure, contaminants can enter the interior 37, whereby these contaminants can deposit in the interior 37 and accumulate, so that cleaning of the screw centrifugal pump is required at certain time intervals.

Figur 1a zeigt eine Seitenansicht der in Figur 1 dargestellten Schraubenzentrifugalradpumpe 1 bei weg gebrochenem Aussengehäuse 3. Figur 1b zeigt in einer Draufsicht ein Ausführungsbeispiel eines Schraubenzentrifugalrades 20, welches derart nicht im Dokument CH 662864 offenbart ist, welches jedoch für die in den Figuren 1 und 1a dargestellte Schraubenzentrifugalradpumpe 1 geeignet wäre, deshalb die Figuren 1, 1a und 1b gemeinsam erklärt werden. Das Schraubenzentrifugalrad 20 der Schraubenzentrifugalradpumpe 1 umfasst eine Nabe 21 mit einem sichelförmigen Basisteil 30, mit welcher eine Schaufel 25 verbunden ist, wobei eine Achse 33 die druckseitige, als Kegelstumpf ausgebildete Gehäusewand 23 durchdringt und mit der Nabe 21 verbunden ist. Die einen Kegelwinkel γ zwischen 5° und 70° aufweisende Gehäusewand 23 wird von der Stirnkante 28 der druckseitigen Schaufelflanke 27 mit kleinem Spiel 24 überstrichen. Die Schaufel 25 umfasst zudem eine saugseitige Flanke 39. Das sichelförmige Basisteil 30 erstreckt sich von der Schaufelaustrittspitze 35, in welche die Endkante 26 ausläuft, sichel- bzw. spiralförmig über eine relativ grosse Strecke um die Pumpenachse bis zu einer Stelle 31, an der die Nabe 21 einen relativ kleinen Radius R2 aufweist. An der Schaufelaustrittsspitze 35 weist die Nabe 21 den grössten Radius R1 auf. Dadurch ist über einen relativ grossen Bogen δ, der zweckmässig etwa 120° beträgt, zwischen Schaufelaustrittsspitze 35 und der genannten Nabenstelle 31 eine relativ grosse Fläche der Gehäusewand 23 freigelegt. Die Freilegung der Gehäusewand 23 durch Reduzierung des Laufradnabenradius R1 kann soweit gehen, wie es die materialtechnischen Parameter erlauben, um dem Schraubenzentrifugalrad 20 noch eine genügen grosse Festigkeit zu gewährleisten. FIG. 1a shows a side view of in FIG. 1 shown centrifugal centrifugal pump 1 at away broken outer housing. 3 FIG. 1b shows a plan view of an embodiment of a Schraubenzentrifugalrades 20, which is not in the document so CH 662864 is disclosed, which, however, for those in the Figures 1 and 1a illustrated centrifugal centrifugal pump 1 would be suitable, therefore the Figures 1, 1a and 1b be declared together. The Schraubenzentrifugalrad 20 of the Schraubenzentrifugalradpumpe 1 comprises a hub 21 with a crescent-shaped base member 30 to which a blade 25 is connected, wherein an axis 33, the pressure-side, designed as a truncated housing wall 23 penetrates and is connected to the hub 21. The housing wall 23 having a cone angle γ between 5 ° and 70 ° is swept over by the end edge 28 of the pressure-side blade edge 27 with a small clearance 24. The blade 25 also includes a suction side flank 39. The crescent-shaped base portion 30 extends from the blade exit tip 35 into which the end edge 26 terminates, helically over a relatively long distance about the pump axis, to a point 31 at which Hub 21 has a relatively small radius R2. At the blade outlet tip 35, the hub 21 has the largest radius R1. As a result, a relatively large area of the housing wall 23 is exposed over a relatively large arc δ, which is expediently approximately 120 °, between the blade outlet tip 35 and the aforementioned hub point 31. The exposure of the housing wall 23 by reducing the wheel hub radius R1 can go as far as allow the material parameters to ensure the screw centrifugal 20 still a sufficient strength.

Figur 2 zeigt in einem Längsschnitt ein Ausführungsbeispiel einer erfindungsgemässen Schraubenzentrifugalradpumpe 1. Die Schraubenzentrifugalradpumpe 1 umfasst ein Pumpengehäuse 3 mit Einlassöffnung 3a bzw. Pumpeneinströmöffnung 3a, Auslass 3b sowie Gehäuseinnenraum 3c, und umfasst weiter eine Nabe 21, welche mit einem nur schematisch und strichliert dargestellten Schaufel 25 verbunden ist und dabei ein Schaufelzentrifugalrad 20 ausbildet, und welche über eine um eine Achse A drehbare Antriebswelle 33 drehbar gelagert ist. Die Verbindung zwischen der Antriebswelle 33 und der Nabe 21 ist nur schematisch dargestellt. Die Schaufel25 sowie die Nabe 21 sind vorzugsweise, wie in Figur 1a und 1b dargestellt, als einziges, gemeinsames Teil bzw. als Schaufelzentrifugalrad 20 ausgestaltet. Im dargestellten Ausführungsbeispiel umfasst die Schraubenzentrifugalradpumpe 1 zudem ein konusförmiges Innengehäuse 4 mit Einlassöffnung 4a sowie einen Abstandhaltering 5. Die Schraubenzentrifugalradpumpe 1 umfasst zudem eine Gehäuserückwand 23 mit einer Auslassöffnung 36 sowie eine Dichtung 6. Die Auslassöffnung 36 dient zu Wartungszwecken und ist während dem Betrieb der Schraubenzentrifugalradpumpe 1 üblicherweise mit einem Stopfen von Aussen verschlossen. Während dem Rotieren des Schaufelzentrifugalrades 20 wird ein Hauptstrom F erzeugt, der über die Einlassöffnung 3a zum Auslass 3b führt. Der geförderte Hauptstrom F umfasst ein Fluid, vorzugsweise Wasser und eventuell Gase wie Wasserdampf, wobei die Schraubenzentrifugalradpumpe 1 in einem bevorzugten Verwendungszweck zum Fördern von verschmutztem Wasser verwendet wird, sodass der Hauptstrom F auch Feststoffe umfassen kann, beispielsweise Fäkalien, Sand, Kies, Textilien, Fasern, Kunststoffteile usw. FIG. 2 1 shows a pump housing 3 with inlet opening 3a or pump inlet opening 3a, outlet 3b and housing interior 3c, and further comprises a hub 21, which is connected to a blade 25 shown only diagrammatically and dashed is and a Schaufelzentrifugalrad 20th forms, and which is rotatably mounted about a rotatable about an axis A drive shaft 33. The connection between the drive shaft 33 and the hub 21 is shown only schematically. The bucket 25 and the hub 21 are preferably as in FIG FIG. 1a and 1b represented as a single, common part or as Schaufelzentrifugalrad 20 designed. In the illustrated embodiment, the Schraubenzentrifugalradpumpe 1 also comprises a conical inner housing 4 with inlet opening 4a and a Abstandhaltering 5. The Schraubenzentrifugalradpumpe 1 also comprises a housing rear wall 23 with an outlet opening 36 and a seal 6. The outlet opening 36 is for maintenance purposes and is during operation of the Schraubenzentrifugalradpumpe 1 usually closed with a plug from the outside. During the rotation of the vane centrifugal wheel 20, a main flow F is generated, which leads to the outlet 3b via the inlet opening 3a. The conveyed mainstream F comprises a fluid, preferably water and possibly gases such as water vapor, the helical centrifugal pump 1 is used in a preferred use for conveying polluted water, so that the main flow F may also include solids, such as feces, sand, gravel, textiles, Fibers, plastic parts etc.

Die Schraubenzentrifugalradpumpe 1 umfasst zudem eine Deckplatte 2, welche in Verlaufsrichtung der Achse A unmittelbar hinter der Nabe 21 beziehungsweise des Schraubenzentrifugalrades 20 angeordnet ist. Die Deckplatte 2 weist eine Vorderseite 2h und eine Rückseite 2i auf, wobei die Vorderseite 2h eine Teiloberfläche 2k umfasst deren Verlauf derart der Rückseite 25a des Schraubenzentrifugalrades 20 angepasst ausgestaltet ist, dass zwischen der Vorderseite 2h der Deckplatte 2 und der Rückseite 25a des Schraubenzentrifugalrades 20 ein Spalt 24 von maximal bis zu 3 mm ausgebildet ist. Vorzugsweise weist der Spalt 24 eine Breite im Bereich zwischen 0,5 mm und 2 mm auf. Der Spalt 24 ist unter anderem derart schmal ausgestaltet, damit sich Feststoffe, zum Beispiele im Abwasser vorkommende Gewebe wie Damenstrümpfe, nicht in den Spalt 24 eindringen können oder sich gar um die Nabe wickeln können. Der schmale Spalt 24 erzeugt zudem eine Scherwirkung auf sich innerhalb des Spaltes 24 befindende Feststoffe, sodass diese mechanisch zerkleinert werden und zum Hauptstrom F hin gefördert werden. In einer bevorzugten Ausgestaltung ist zumindest eine der zum Spalt 24 hin ausgerichteten Oberflächen strukturiert, rau oder zum Beispiel mit vorstehenden Zähnen verstehen ausgestaltet, um eine Mechanische Zerkleinerung von sich im Spalt 24 befindlichen Feststoffen zu verbessern. Ein Spalt 24, der breiter als 3 mm wäre, zum Beispiel 5 mm oder breiter, hätte mehrere Nachteile. Einerseits wäre auf Grund des breiten Spaltes 24 die mechanische Zerkleinerung von Feststoffen nicht mehr gewährleistet. Zudem würde ein breiter Spalt 24 den Wirkungsgrad der Schraubenzentrifugalradpumpe 1 erheblich reduzierten. Die Vorderseite 2h im dargestellten Ausführungsbeispiel umfasst eine im Wesentlichen kegelstumpfförmig verlaufende Teiloberfläche 2k, deren Verlauf der Rückseite einem Schraubenzentrifugalrad 20 angepasst ausgestaltet ist, wobei die Teiloberfläche 2k in deren Zentrum eine Mittenöffnung 2g aufweist, wobei die Mittenöffnung 2g parallel in Richtung der Achse A verläuft. Die Nabe 21 verläuft durch die Mittenöffnung 2g, sodass sich zwischen der Mittenöffnung 2g und der Nabe 21 ein in Richtung der Achse A verlaufender Spalt 2b ausbildet. Die Nabe 21 weist zudem eine Auskragung auf, welche teilweise die Teiloberfläche 2k bedeckt, sodass sich zwischen der Nabe 21 und der Teiloberfläche 2k ein im dargestellten Ausführungsbeispiel bezüglich der Achse A quer verlaufender Spalt 24 ausbildet. Die Deckplatte 2 weist zumindest eine Durchbrechung 2a auf, welche beabstandet zur Mittenöffnung 2g angeordnet ist, wobei die Durchbrechung 2a eine Fluid leitende Verbindung zwischen der Vorderseite 2h und der Rückseite 2i der Deckplatte 2 ausbildet. Während dem Pumpbetrieb, beziehungsweise während der Rotation des Schaufelzentrifugalrades 20 in Drehrichtung R, weist das Fluid im Bereich der Durchbrechung 2a einen höheren Druck auf als im Bereich der Mittenöffnung 2g, wodurch ein Teilstrom F1 erzeugt wird, indem ein Teil des Hauptstromes F als Teilstrom F1 durch die Öffnung 2a zur Rückseite 2i der Deckplatte 2 in den Innenraum 37 strömt, und danach über den Spalt 2b und den Spalt 24 wieder in den Hauptstrom F strömt. Dieser Teilstrom F1 bewirkt, dass Verschmutzungen, die sich im Innenraum 37 befinden, aus diesem herausgefördert werden und dem Hautstrom F zugeführt werden.The screw centrifugal pump 1 also comprises a cover plate 2, which is arranged in the direction of the axis A directly behind the hub 21 and the Schraubenzentrifugalrades 20. The cover plate 2 has a front side 2h and a rear side 2i, wherein the front side 2h comprises a partial surface 2k whose course is adapted to the rear side 25a of the screw centrifugal wheel 20 such that between the front side 2h of the cover plate 2 and the rear side 25a of the screw centrifugal wheel 20, a gap 24 is formed of a maximum of up to 3 mm. Preferably, the gap 24 has a width in the range between 0.5 mm and 2 mm. Among other things, the gap 24 is designed to be so narrow that solids, for example fabrics that occur in sewage, such as women's stockings, can not penetrate into the gap 24 or can even wrap around the hub. The narrow gap 24 also produces a shearing action on solids located within the gap 24, so that they are mechanically comminuted and conveyed to the main flow F out. In a preferred embodiment, at least one of the surfaces directed towards the gap 24 is structured, rough or designed, for example, with protruding teeth, in order to improve mechanical comminution of solids present in the gap 24. A gap 24 wider than 3mm, for example 5mm or wider, would have several disadvantages. On the one hand, due to the wide gap 24, the mechanical comminution of solids would no longer be guaranteed. In addition, a wide gap 24 would significantly reduce the efficiency of the Schraubenzentrifugalradpumpe 1. The front side 2h in the illustrated embodiment comprises a substantially frusto-conical extending part surface 2k, the course of the rear side is adapted to a Schraubenzentrifugalrad 20, wherein the partial surface 2k in the center has a central opening 2g, wherein the central opening 2g extends parallel to the axis A. The hub 21 extends through the central opening 2g, so that between the center opening 2g and the hub 21, a gap 2b extending in the direction of the axis A is formed. The hub 21 also has a projection which partially covers the partial surface 2k, so that between the hub 21 and the sub-surface 2k, a gap 24 running transversely with respect to the axis A is formed. The cover plate 2 has at least one opening 2a which is arranged at a distance from the center opening 2g, wherein the opening 2a forms a fluid-conducting connection between the front side 2h and the rear side 2i of the cover plate 2. During the pumping operation, or during the rotation of the Schaufelzentrifugalrades 20 in the direction of rotation R, the fluid in the region of the opening 2a has a higher pressure than in the region of the central opening 2g, whereby a partial flow F1 is generated by a part of the main flow F as part of flow F1 flows through the opening 2a to the back 2i of the cover plate 2 in the interior 37, and then flows through the gap 2b and the gap 24 back into the main flow F. This partial flow F1 causes contaminants, which are located in the interior 37, are conveyed out of this and the skin flow F are supplied.

Das Schraubenzentrifugalrad 20 und die Anordnung der Durchbrechung 2a sind derart gegenseitig angepasst ausgestaltet sind, dass die Rückseite 25a des Schraubenzentrifugalrades 20 die Durchbrechung 2a nicht bedeckt oder bei einer Rotation des Schraubenzentrifugalrades 20 um 360° nur während eines Teilwinkels Δ bedeckt.The Schraubenzentrifugalrad 20 and the arrangement of the opening 2a are configured such that the rear side 25a of the Schraubenzentrifugalrades 20, the aperture 2a is not covered or covered by a rotation of the Schraubenzentrifugalrades 20 by 360 ° only during a partial angle Δ.

In einer vorteilhaften Ausgestaltung könnte das Schraubenzentrifugalrad 20 wie in den Figuren 12 und 13 dargestellt ausgestaltet sein. Figur 12 zeigt ein Pumpengehäuse 3 in welchem eine Deckplatte 2 sowie ein Schraubenzentrifugalrad 20 angeordnet ist. Die Nabe 21 ist mit einem kreisförmigen Basisteil 30 verbunden, wobei die Schaufel 25 über deren Stirnkante 28 mit dem Basisteil 30 verbunden ist. Das Schraubenzentrifugalrad 20 umfasst eine Endkante 26, eine druckseitige Schaufelflanke 27, sowie eine saugseitige Flanke 39 und eine Schaufelaustrittsspitze 35. Figur 13 zeigt das Schraubenzentrifugalrad 20 in einer Draufsicht, wobei das Basisteil 30 kreisförmig ausgebildet ist und bezüglich der Achse A einen maximalen Radius R1 aufweist. Figur 13 zeigt beispielhaft eine mögliche Anordnung einer Öffnung bzw. eine Durchbrechung 2a bezüglich dem Schraubenzentrifugalrad 20. Bei dieser Anordnung wird die Durchbrechung 2a nicht durch das Schraubenzentrifugalrad 20 beziehungsweise durch die Rückseite 25a des Schraubenzentrifugalrades 20 bedeckt, sodass die Durchbrechung 2a ständig offen ist. Dabei wir im Bereich der Durchbrechung 2a vorteilhafterweise eine Strömung in Drehrichtung R des Schraubenzentrifugalrades 20 erzeugt, um den Eintritt von festen Verunreinigungen in die Durchbrechung 2a zu erschweren oder zu verhindern. Über die Durchbrechung 2a wird eine Fluid leitende Verbindung zwischen der Vorderseite 2h und dem Innenraum 37 ausbildet, um einen Fluidstrom F1 zu erzeugen, der über die Durchbrechung 2a in den Innenraum 37 hinein strömt und über den Spalt 2b wieder aus dem Innenraum 37 hinaus strömt.In an advantageous embodiment, the Schraubenzentrifugalrad 20 could as in the FIGS. 12 and 13 be configured represented. FIG. 12 shows a pump housing 3 in which a cover plate 2 and a Schraubenzentrifugalrad 20 is arranged. The hub 21 is connected to a circular base part 30, wherein the blade 25 is connected via the end edge 28 with the base part 30. The Schraubenzentrifugalrad 20 includes an end edge 26, a pressure-side blade edge 27, and a suction-side edge 39 and a blade outlet tip 35th FIG. 13 shows the Schraubenzentrifugalrad 20 in a plan view, wherein the base member 30 is circular and with respect to the axis A has a maximum radius R1. FIG. 13 shows an example of a possible arrangement of an opening or an opening 2a with respect to the Schraubenzentrifugalrad 20. In this arrangement, the opening 2a is not covered by the Schraubenzentrifugalrad 20 and by the back 25a of the Schraubenzentrifugalrades 20 so that the opening 2a is constantly open. In this case, in the region of the opening 2a, a flow in the direction of rotation R of the helical centrifugal wheel 20 is advantageously generated in order to hinder or prevent the entry of solid contaminants into the opening 2a. A fluid-conducting connection between the front side 2h and the interior 37 is formed via the opening 2a in order to generate a fluid flow F1, which flows into the interior space 37 via the opening 2a and flows out of the interior space 37 via the gap 2b.

In einer weiteren vorteilhaften Ausgestaltung könnte das Schraubenzentrifugalrad 20 wie in den Figuren 1a und 1b dargestellt ausgestaltet sein. Die Nabe 21 des Schraubenzentrifugalrades 20 umfasst ein sichelförmige Basisteil 30, wobei die Schaufel 25 auf dem sichelförmigen Basisteil 30 angeordnet ist und das sichelförmige Basisteil 30 bezüglich der Drehachse A einen maximalen Radius R1 und einen minimalen Radius R2 aufweist. Das sichelförmige Basisteil 30 ist bezüglich der Durchbrechung 2a derart verlaufend ausgestaltet, dass die Rückseite 25a des Schraubenzentrifugalrades 20 die Durchbrechung 2a beim minimalen Radius R2 nicht bedeckt, wobei die Rückseite 25a des Schraubenzentrifugalrades 20 die Durchbrechung 2a bei einer Rotation des Schraubenzentrifugalrades 20 um 360° während eines Teilwinkels Δ bedeckt. Die Durchbrechung 2a wird somit während jeder Drehung des Schraubenzentrifugalrades 20 kurzfristig überdeckt. Diese Ausgestaltung weist den Vorteil auf, dass im Bereich der Durchbrechung 2a vorteilhafterweise eine Strömung in Drehrichtung R des Schraubenzentrifugalrades 20 erzeugt wird, um den Eintritt von festen Verunreinigungen in die Durchbrechung 2a zu erschweren oder zu verhindern. Ein weiterer Vorteil ist darin zu sehen, dass feste Verunreinigungen, die sich an der Eintrittsöffnung der Durchbrechung 2a anlagern, durch die sich über die Durchbrechung 2a bewegende Nabe 21,30 mechanisch entfernt werden, falls die Verunreinigungen über die Vorderseite 2h vorstehen.In a further advantageous embodiment, the Schraubenzentrifugalrad 20 could as in the FIGS. 1a and 1b be configured represented. The hub 21 of the Schraubenzentrifugalrades 20 includes a crescent-shaped base portion 30, wherein the blade 25 is disposed on the crescent-shaped base portion 30 and the crescent-shaped base portion 30 with respect to the rotation axis A has a maximum radius R1 and a minimum radius R2. The crescent-shaped base part 30 is extending with respect to the opening 2a in such a way designed such that the rear side 25a of the Schraubenzentrifugalrades 20, the aperture 2a at the minimum radius R2 is not covered, wherein the back 25a of the Schraubenzentrifugalrades 20, the aperture 2a covered during rotation of the Schraubenzentrifugalrades 20 by 360 ° during a partial angle Δ. The opening 2a is thus briefly covered during each rotation of the Schraubenzentrifugalrades 20. This embodiment has the advantage that in the region of the opening 2a advantageously a flow in the direction of rotation R of the Schraubenzentrifugalrades 20 is generated to complicate the entry of solid impurities in the opening 2a or prevent. A further advantage is the fact that solid impurities, which accumulate at the inlet opening of the opening 2a, are mechanically removed by the hub 2a moving through the opening 2a, if the impurities protrude beyond the front side 2h.

Die Antriebswelle 33 könnte auch weiter vorgezogen sein, sodass der Spalt 2b zumindest teilweise oder auch ausschliesslich zwischen der Deckplatte 2 und der Antriebswelle 33 ausgebildet wird.The drive shaft 33 could also be further advanced, so that the gap 2 b is formed at least partially or exclusively between the cover plate 2 and the drive shaft 33.

Die Deckplatte 2 weist zumindest eine Durchbrechung 2a auf und vorzugsweise zumindest zwei Durchbrechungen 2a. Vorteilhafterweise sind die Durchbrechungen 2a in der Teiloberfläche 2k symmetrisch bezüglich der Achse A angeordnet. Die Durchbrechungen 2a können in einer Vielzahl von Möglichkeiten ausgestaltet sein. Die in Figur 2 unten dargestellte Durchbrechung 2a ist in Figur 3 vergrössert dargestellt. An der Vorderseite 2h der Deckplatte 2 strömt eine Strömung F2. Die Öffnung 2 umfasst eine Eintrittsöffnung 21, deren Querschnitt eine Eintrittsfläche 2m ausbildet. Der Teilstrom F1 strömt durch die Durchbrechung 2a zur Rückseite 2i der Deckplatte 2. Der Teilstrom F1 wird beim Hineinströmen in die Durchbrechung 2a umgelenkt, was den Vorteil ergibt, dass in der Strömung F2 befindliche Feststoffe erschwert in die Durchbrechung 2a hineinströmen können. Der Teilstrom F1 wird dadurch zumindest teilweise von Feststoffen gereinigt, weil die Feststoffe zumindest teilweise in der Strömung F2 verbleiben und von dieser fort getragen werden.The cover plate 2 has at least one opening 2a and preferably at least two openings 2a. Advantageously, the openings 2a are arranged symmetrically with respect to the axis A in the partial surface 2k. The openings 2a can be configured in a variety of ways. In the FIG. 2 shown below opening 2a is in FIG. 3 shown enlarged. At the front 2h of the cover plate 2 flows a flow F2. The opening 2 comprises an inlet opening 21 whose cross section has an entrance surface 2m formed. The partial flow F1 flows through the opening 2a to the rear 2i of the cover plate 2. The partial flow F1 is deflected when flowing into the opening 2a, which has the advantage that in the flow F2 located solids difficult to flow into the opening 2a. The partial flow F1 is thereby at least partially cleaned of solids because the solids remain at least partially in the flow F2 and be carried away by this.

Die Deckplatte 2 könnte, ähnlich wie die in Figur 1a dargestellte Gehäuserückwand, einen Kegelwinkel γ im Bereich zwischen 5° und 70° aufweisen.The cover plate 2 could, similar to those in FIG. 1a shown housing rear wall, have a cone angle γ in the range between 5 ° and 70 °.

Figur 4 zeigt ein weiteres Ausführungsbeispiel einer Durchbrechung 2a. Im Unterschied zu der in Figur 3 dargestellten Ausführungsform ist die in Figur 4 dargestellte Durchbrechung 2a derart verlaufend angeordnet, dass der Teilstrom F1 bezüglich der an der Vorderseite 2h der Deckplatte 2 auftretenden Strömung F2 derart umgelenkt wird, dass dieser eine teilweise Strömungsumkehr erfährt. Die Durchbrechung 2a verläuft wie in Figur 4 dargestellt zumindest teilweise entgegengesetzt zur Drehrichtung R des Schraubenzentrifugalrades 20. Die derart verlaufende Durchbrechung 2a weist den Vorteil auf, dass Feststoffe weniger gut durch die Durchbrechung 2a zur Rückseite 2i der Deckplatte 2 gelangen können. FIG. 4 shows a further embodiment of an opening 2a. Unlike the in FIG. 3 The embodiment shown in FIG FIG. 4 represented opening 2a arranged such that the partial flow F1 is deflected with respect to the occurring at the front side 2h of the cover plate 2 flow F2 such that it undergoes a partial flow reversal. The opening 2a extends as in FIG. 4 represented at least partially opposite to the direction of rotation R of the Schraubenzentrifugalrades 20. The thus extending aperture 2a has the advantage that solids can get through the opening 2a to the back 2i of the cover plate 2 less well.

Die in Figur 2 oben dargestellte Durchbrechung 2a ist in Figur 5 vergrössert dargestellt. Auf der Vorderseite 2h der Deckplatte 2 ist eine Vertiefung 2c angeordnet, welche zur Durchbrechung 2a mündet, wobei die Durchbrechung 2a eine Eintrittsöffnung 21 mit Eintrittsfläche 2m ausbildet, sodass die Eintrittsöffnung 21 in der Vertiefung 2c angeordnet ist. Die Eintrittsöffnung 21 beziehungsweise die Eintrittsfläche 2m kann auf unterschiedlichste Weise angeordnet sein, vorteilhafterweise jedoch wie in Figur 5 dargestellt derart, dass der Teilstrom F1 umgelenkt wird und bezüglich der an der Vorderseite 2h der Deckplatte 2 auftretenden Strömung F2 eine zumindest teilweise Strömungsumkehr erfährt. Die derart angeordnete Eintrittsöffnung 21 weist den Vorteil auf, dass Feststoffe weniger gut durch die Durchbrechung 2a zur Rückseite 2i der Deckplatte 2 gelangen können. Wie in Figur 5 dargestellt ist die Eintrittsfläche 2m in einer vorteilhaften Ausführungsform derart angeordnet, dass diese parallel oder im Wesentlichen parallel zur Achse A verläuft. Wie in Figur 5 dargestellt ist die Eintrittsfläche 2m vorzugsweise bezüglich der Drehrichtung R abgewandt ausgerichtet angeordnet. In Figur 5 ist nicht die Achse A an sich, jedoch die Verlaufsrichtung der Achse A dargestellt. Wie in Figur 5 dargestellt ist die Eintrittsfläche 2m in einer weiteren vorteilhaften Ausführungsform derart angeordnet, dass diese senkrecht oder im Wesentlichen senkrecht zur Rotationsrichtung R der Antriebswelle 33 verläuft, wobei die Eintrittsfläche 2m abgewandt zur Rotationsrichtung R angeordnet ist.In the FIG. 2 The opening 2a shown above is in FIG. 5 shown enlarged. On the front side 2h of the cover plate 2, a recess 2c is arranged, which opens to the opening 2a, wherein the opening 2a forms an inlet opening 21 with inlet surface 2m, so that the inlet opening 21 in the Recess 2c is arranged. The inlet opening 21 or the inlet surface 2m can be arranged in various ways, but advantageously as in FIG. 5 represented such that the partial flow F1 is deflected and undergoes an at least partial flow reversal with respect to the occurring at the front 2h of the cover plate 2 flow F2. The inlet opening 21 arranged in this way has the advantage that solids can pass through the opening 2a to the back 2i of the cover plate 2 less effectively. As in FIG. 5 shown, the entrance surface 2m is arranged in an advantageous embodiment such that it is parallel or substantially parallel to the axis A. As in FIG. 5 illustrated is the entrance surface 2m preferably arranged facing away from the direction of rotation R arranged. In FIG. 5 is not the axis A per se, but the course of the axis A is shown. As in FIG. 5 illustrated, the entrance surface 2m is arranged in a further advantageous embodiment such that it is perpendicular or substantially perpendicular to the rotational direction R of the drive shaft 33, wherein the entrance surface 2m facing away from the rotation direction R is arranged.

Die Figuren 6, 7 und 8 zeigen ein Ausführungsbeispiel einer Deckplatte 2 in Draufsicht, in perspektivischer Ansicht und in einem Schnitt entlang der Schnittlinie B-B. In einer vorteilhaften Ausgestaltung kann die Vertiefung 2c, wie in den Figuren 6 und 7 dargestellt, zumindest teilweise durch eine im Wesentlichen senkrecht oder senkrecht zur Achse A verlaufenden Bohrung ausgebildet sind. Figur 6 zeigt den Verlauf der Achse A sowie die bevorzugte Rotationsrichtung R. Aus Figur 6 ist somit ersichtlich, dass die Eintrittsfläche 2m parallel zur Achse A und senkrecht zur Rotationsrichtung R verläuft. Figur 8 zeigt im Schnitt die Deckplatte 2 mit Vorderseite 2h, Rückseite 2i und Mittenöffnung 2g. In der kegelstumpfförmig oder im Wesentlichen kegelstumpfförmig verlaufenden Teiloberfläche 2k sind die Durchbrechungen 2a angeordnet, wobei die Durchbrechungen 2a immer beabstandet zur Mittenöffnung 2g angeordnet sind. Die Durchbrechungen 2a könnten auch, wie in Figur 3 dargestellt, senkrecht oder im Wesentlichen senkrecht bezüglich der Teiloberfläche 2k verlaufen, oder wie in Figur 4 dargestellt, quer bezüglich der Teiloberfläche 2k verlaufen.The FIGS. 6, 7 and 8th show an embodiment of a cover plate 2 in plan view, in perspective view and in a section along the section line BB. In an advantageous embodiment, the recess 2c, as in the FIGS. 6 and 7 are at least partially formed by a substantially perpendicular or perpendicular to the axis A extending bore. FIG. 6 shows the course of the axis A and the preferred direction of rotation R. Off FIG. 6 is thus seen that the entrance surface 2m parallel to the axis A and perpendicular to Rotation direction R runs. FIG. 8 shows in section the cover plate 2 with front 2h, back 2i and center opening 2g. In the frusto-conical or substantially frusto-conical extending part surface 2k, the openings 2a are arranged, wherein the openings 2a are always arranged at a distance from the central opening 2g. The openings 2a could also, as in FIG. 3 shown, perpendicular or substantially perpendicular with respect to the partial surface 2k run, or as in FIG. 4 shown, transverse to the part surface 2k run.

Abhängig vom jeweils verwendeten Schraubenzentrifugalrad 20 wird von der Rückseite 25a des Schraubenzentrifugalrades 20 eine unterschiedlich grosse Teiloberfläche 2k bedeckt. Unter Verwendung des in den Figuren 1a und 1b dargestellten Schraubenzentrifugalrades 20 könnte beispielsweise die in Figur 6 mit 2k bezeichnete Teilfläche der Vorderseite 2h bedeckt werden, auf die mit Figur 1a und 1b beschriebene Weise. Unter Verwendung des in den Figuren 12 und 13 dargestellten Schraubenzentrifugalrades 20 könnte beispielsweise die in Figur 6 mit 2k2 bezeichnete Teilfläche der Vorderseite 2h permanent bedeckt werden.Depending on the screw centrifugal wheel 20 used in each case, a differently sized partial surface 2k is covered by the rear side 25a of the screw centrifugal wheel 20. Using the in the FIGS. 1a and 1b Screw centrifugal wheel 20 shown could, for example, the in FIG. 6 Covered with 2k part surface of the front 2h are covered on the with FIG. 1a and 1b described way. Using the in the FIGS. 12 and 13 Screw centrifugal wheel 20 shown could, for example, the in FIG. 6 2k2 designated partial surface of the front 2h are permanently covered.

In einer vorteilhaften Ausführungsform weist die Deckplatte 2, wie in den Figuren 6 bis 8 dargestellt, eine in Umfangsrichtung verlaufende Vertiefung auf, insbesondere eine spiralförmig verlaufende Vertiefung 2d, welche vorteilhafterweise im Bereich der Mittenöffnung 2g beginnend entlang der Teiloberfläche 2h nach Aussen verläuft. Vorteilhafterweise verläuft die Vertiefung 2d wie in Figur 6 dargestellt in Drehrichtung R spiralförmig von Innen nach Aussen. Diese Ausgestaltung weist den Vorteil auf, dass eine Verschmutzung, welche mit Hilfe des Teilstromes F1 über die Mittenöffnung 2g beziehungsweise den Spalt 2b zur Vorderseite 2h der Deckplatte 2 gefördert wird, entlang der Vertiefung 2d gegen die Peripherie der Teiloberfläche 2k hin gefördert wird. Die über der Teiloberfläche 2k in Drehrichtung R drehende Nabe 21 beziehungsweise das in Drehrichtung R drehende Schraubenzentrifugalrad 20 hilft zudem die sich in der Vertiefung 2d oder an der Teiloberfläche 2k befindliche Verschmutzung in Drehrichtung R zu bewegen und bezüglich der Teiloberfläche 2k gegen Aussen zu fördern, bis die Verschmutzung zum Hautstrom F gelangt, und von diesem erfasst und fort getragen wird. Besonders vorteilhaft ist somit eine Anordnung der Durchbrechung 2a wie in den Figuren 6 bis 8 dargestellt. Insbesondere aus Figur 6 ist ersichtlich, dass die Verschmutzung im Wesentlichen in Drehrichtung R bewegt wird, wobei die Durchbrechung 2a in einer Vertiefung 2c angeordnet ist und die Eintrittsfläche 2m abgewandt zur Drehrichtung R ausgerichtet ist, sodass Verschmutzungen, selbst wenn sie über die Vertiefung 2c fliessen, auf Grund der Strömungsverhältnisse und der Bewegungsrichtung der Verschmutzungen kaum oder überhaupt nicht durch die Durchbrechung 2a strömen sondern dem Hauptstrom F zugeführt werden.In an advantageous embodiment, the cover plate 2, as in the FIGS. 6 to 8 illustrated, a recess extending in the circumferential direction, in particular a spiral-shaped recess 2d, which advantageously extends in the region of the central opening 2g along the partial surface 2h to the outside. Advantageously, the depression 2d extends as in FIG FIG. 6 shown in the direction of rotation R spiral from inside to outside. This embodiment has the advantage that contamination, which with the help of the partial flow F1 through the center opening 2g or the gap 2b is conveyed to the front side 2h of the cover plate 2, is conveyed along the recess 2d against the periphery of the partial surface 2k out. In addition, the hub 21 rotating in the direction of rotation R over the part surface 2k or the screw centrifugal wheel 20 rotating in the direction of rotation R helps to move the dirt in the direction of rotation R in the depression 2d or on the part surface 2k and to move it towards the outside with respect to the part surface 2k the pollution reaches the skin stream F, and is detected by this and carried away. Thus, an arrangement of the aperture 2a is particularly advantageous as in the FIGS. 6 to 8 shown. In particular from FIG. 6 It can be seen that the contamination is moved substantially in the direction of rotation R, wherein the aperture 2a is arranged in a recess 2c and the inlet surface 2m facing away from the direction of rotation R is aligned so that dirt, even if they flow over the recess 2c, due to Flow conditions and the direction of movement of the contaminants hardly or not at all flow through the opening 2a but the main stream F are supplied.

Die Deckplatte 2 kann, wie in den Figuren 7 und 8 dargestellt, zudem eine entlang des Randbereichs verlaufende Vertiefungen 2f aufweisen, welche insbesondere zur Aufnahme eines O-Ringes und somit zum Abdichten vorgesehen ist.The cover plate 2 can, as in the FIGS. 7 and 8th shown, in addition, a running along the edge region recesses 2f, which is provided in particular for receiving an O-ring and thus for sealing.

Figur 9 zeigt in einem Schnitt ein weiteres Ausführungsbeispiel einer Deckplatte 2, welche im Unterschied zu dem in Figur 8 dargestellten Schnitt jedoch eine flach verlaufende Teiloberfläche 2k bzw. 2k2 aufweist. Ansonsten ist die Deckplatte 2 ähnlich ausgestaltet wie die in Figur 8 dargestellte Ausführungsform, indem die Deckplatte 2 gemäss Figur 9 auch eine Vertiefung 2c aufweist, welche in eine Öffnung 2a mündet. Sofern die spiralförmig verlaufende Vertiefung 2d weggedacht wird, offenbart die Figur 6 eine Draufsicht auf die in Figur 9 dargestellte Deckplatte 2. Die in Figur 9 dargestellte Deckplatte 2 könnte jedoch auch eine spiralförmig verlaufende Vertiefung 2d aufweisen, sodass eine Draufsicht auf diese Ausführungsform wie in Figur 6 dargestellt aussehen würde. Die in Figur 9 dargestellte Deckplatte 2 weist zudem eine Mittenöffnung 2g sowie eine Vorderseite 2h und eine Rückseite 2i auf. Die Vorderseite 2h beziehungsweise die Teiloberfläche 2k kann in einer Vielzahl von Möglichkeiten verlaufen, so zum Beispiel gekrümmt, wie in Figur 10 schematisch in einem Schnitt dargestellt, oder kantig, wie in Figur 11 schematisch in einem Schnitt dargestellt. In der am meisten bevorzugten Ausführungsform verläuft die Teiloberfläche, wie in Figur 8 dargestellt, kegelstumpfförmig. FIG. 9 shows in a section a further embodiment of a cover plate 2, which in contrast to the in FIG. 8 However, shown section has a flat extending part surface 2k and 2k2. Otherwise, the cover plate 2 is configured similar to the in FIG. 8 illustrated embodiment by the cover plate 2 according to FIG. 9 also has a recess 2c, which opens into an opening 2a. If the spiraling depression 2d is thought away, discloses FIG. 6 a top view of the in FIG. 9 shown cover plate 2. The in FIG. 9 However, shown cover plate 2 could also have a spiral extending recess 2d, so that a plan view of this embodiment as in FIG. 6 would look like. In the FIG. 9 shown cover plate 2 also has a central opening 2g and a front side 2h and a back 2i. The front side 2h or the partial surface 2k can run in a variety of ways, such as curved, as in FIG. 10 shown schematically in a section, or edged, as in FIG. 11 shown schematically in a section. In the most preferred embodiment, the sub-surface is as shown in FIG FIG. 8 shown, frustoconical.

In einer vorteilhaften Ausgestaltung ist die Deckplatte 2 als Gussstück ausgestaltet, wobei die Vertiefung 2c und vorteilhafterweise auch die Durchbrechung 2a beziehungsweise die Eintrittsöffnung 21 bereits ein Teil des noch unbearbeiteten Gussstücks bilden. Zur Fertigstellung der Deckplatte 2 ist es dann im Wesentlichen noch erforderlich die Vorderseite 2h zu bearbeiten, insbesondere durch Span abhebende Bearbeitung. Eine Deckplatte 2 hergestellt aus einem derart ausgestalteten Gussstück weist den Vorteil, dass sich bei der Herstellung keine oder nur sehr geringe Mehrkosten ergeben, da die Span abhebende Bearbeitung der Deckplatte 2 sowieso erforderlich ist. Die in den Figuren 6 bis 8 dargestellte Deckplatte 2, umfassend zwei Vertiefungen 2c mit Durchbrechurigen 2a, kann somit, im Verglich zu Deckplatten 2 ohne Durchbrechungen 2a, mit vernachlässigbar kleinen Zusatzkosten hergestellt werden. Das Gussstück kann eine Dicke zwischen 2 und 10 mm aufweisen. Die Deckplatte 2 könnte jedoch auch aus einem Metallblech gefertigt sein.In an advantageous embodiment, the cover plate 2 is designed as a casting, wherein the recess 2c and advantageously also the opening 2a or the inlet opening 21 already form part of the still unprocessed casting. For the completion of the cover plate 2, it is then still essentially necessary to machine the front side 2h, in particular by removing machining machining. A cover plate 2 made of a casting designed in this way has the advantage that there are no or only very small additional costs during production, since the chip-removing machining of the cover plate 2 is required anyway. The in the FIGS. 6 to 8 shown cover plate 2, comprising two recesses 2c with Durchbrechurigen 2a, thus, in comparison to cover plates 2 without Openings 2a, are manufactured with negligible additional costs. The casting may have a thickness between 2 and 10 mm. However, the cover plate 2 could also be made of a metal sheet.

Das erfindungsgemässe Verfahren ermöglicht die Selbstreinigung einer Schraubenzentrifugalradpumpe 1. Dabei weist die Schraubenzentrifugalradpumpe 1 ein drehbar gelagertes Schraubenzentrifugalrad 20 sowie eine unmittelbar neben beziehungsweise hinter dem Schraubenzentrifugalrad 20 angeordnete Deckplatte 2 mit einer Mittenöffnung 2g auf, wobei eine Nabe 21 des Schraubenzentrifugalrades 20 oder eine das Schraubenzentrifugalrad 15 lagernde Achse 33 durch die Mittenöffnung 2g verläuft, sodass sich zwischen der Mittenöffnung 2g und der Nabe 21 oder der Achse 33 ein Fluid leitender Spalt 2b ausbildet. Wenn das Schraubenzentrifugalrad 20 in Drehrichtung R rotiert wird und dadurch ein Fluid entlang eines Hauptstromes F gefördert wird, so wird ein Teilstrom F1 des Fluides über eine bezüglich der Mittenöffnung 2g beabstandete Durchbrechung 2a zur Rückseite 2i der Deckplatte 2 strömen und dieser Teilstrom F1 danach über den Spalt 2b wieder zum Hauptstrom F strömen, auf Grund der zwischen der Durchbrechung 2a und dem Spalt 2b herrschenden Druckdifferenz. Dieser Teilstrom F1 fördert allfällig sich im Raum hinter der Deckplatte 2 befindlichen Verunreinigungen wieder zum Hauptstrom F. Vorteilhafterweise weist die Deckplatte 2 auf deren Vorderseite 2h an deren Teiloberfläche 2k eine spiralförmig verlaufende Vertiefung 2d auf, wobei die spiralförmig verlaufende Vertiefung 2d in Drehrichtung R von Innen nach Aussen verläuft, sodass der aus dem Spalt 2b austretende Teilstrom F1 und die sich gegebenenfalls darin befindlichen Verunreinigungen über die spiralförmig verlaufende Vertiefung 2d dem Hauptstrom F zugeführt wird.The inventive method allows self-cleaning a Schraubenzentrifugalradpumpe 1. Here, the Schraubenzentrifugalradpumpe 1 has a rotatably mounted Schraubenzentrifugalrad 20 and arranged immediately adjacent to or behind the Schraubenzentrifugalrad 20 cover plate 2 with a central opening 2g, wherein a hub 21 of the Schraubenzentrifugalrades 20 or the Schraubenzentrifugalrad 15th The bearing axis 33 passes through the central opening 2g, so that between the center opening 2g and the hub 21 or the axis 33, a fluid-conducting gap 2b is formed. If the Schraubenzentrifugalrad 20 is rotated in the direction of rotation R and thereby a fluid along a main flow F is promoted, then a partial flow F1 of the fluid over a center opening 2g spaced opening 2a to the back 2i of the cover plate 2 and flow this flow part F1 thereafter Slit 2b again flow to the main flow F, due to the prevailing between the aperture 2a and the gap 2b pressure difference. Advantageously, the cover plate 2 on the front side 2h on the part surface 2k has a spiral recess 2d, wherein the spirally extending recess 2d in the direction of rotation R from inside extends to the outside, so that the outgoing from the gap 2b partial flow F1 and possibly located therein impurities on the spiraling depression 2d is supplied to the main flow F.

In den dargestellten Ausführungsbeispielen sind die Deckplatte 2 sowie die Gehäuserückwand 23 immer als separate Teile dargestellt. Die Deckplatte 2 sowie die Gehäuserückwand 23 könnten auch einstückig ausgestaltet sein, beispielsweise indem diese aus einem einzigen Teil, zum Beispiel ein Gussteil gefertigt sind. Ein solches einzige Gussteil, umfassend sowohl die Deckplatte 2 als auch die Gehäuserückwand 23, weist den Vorteil auf, dass dieses kostengünstig herstellbar ist, und dass zwischen Deckplatte 2 und Gehäuserückwand 23 keine Dichtung mehr erforderlich ist. Dies ermöglicht eine besonders wartungsarme Ausführungsform.In the illustrated embodiments, the cover plate 2 and the housing rear wall 23 are always shown as separate parts. The cover plate 2 and the housing rear wall 23 could also be designed in one piece, for example by being made of a single part, for example a cast part. Such a single casting, comprising both the cover plate 2 and the housing rear wall 23, has the advantage that this is inexpensive to produce, and that between the cover plate 2 and the housing rear wall 23 no seal is required. This allows a particularly low-maintenance embodiment.

Figur 14 zeigt in einer Draufsicht ein weiteres Ausführungsbeispiel der bereits in Figur 6 dargestellten. Deckplatte 2. Die Öffnung 2a beziehungsweise die Eintrittsfläche 2m verläuft wiederum parallel zur Achse A, wobei die Öffnung 2a beziehungsweise die Eintrittsfläche 2m, im Unterschied zu Figur 6, bezüglich einer radial durch die Achse A verlaufenden Geraden L um einen Winkel α geneigt verläuft, wobei der Winkel α vorzugsweise einen Wert im Bereich von +/- 60 Grad aufweist. FIG. 14 shows in a plan view another embodiment of the already in FIG. 6 shown. Cover plate 2. The opening 2a and the entrance surface 2m again runs parallel to the axis A, wherein the opening 2a and the inlet surface 2m, in contrast to FIG. 6 , with respect to a radially extending through the axis A extending straight line L inclined at an angle α, wherein the angle α preferably has a value in the range of +/- 60 degrees.

Claims (20)

  1. Screw-type centrifugal wheel pump (1), comprising a pump housing (3) with a pump inlet opening (3a) and a housing rear wall (23) situated opposite the pump inlet opening, comprising a screw-type centrifugal wheel (20), which is rotatably arranged within the pump housing (3), with a hub (21) and with an impeller (25), and comprising a rotatable drive shaft (33) which is connected to the screw-type centrifugal wheel (20), further comprising a cover plate (2) which is arranged between the screw-type centrifugal wheel (20) and the housing rear wall (23), wherein the cover plate (2) features a central opening (2g) through which the hub (21) or the drive shaft (33) extends, and with an inner space (37) being implemented between the cover plate (2) and the housing rear wall (23), wherein the cover plate (2) features a front side (2h) oriented towards the pump inlet opening (3a), and wherein the front side (2h) comprises a partial surface (2k), the course of which is embodied to be adapted to the rear side (25a) of the screw-type centrifugal wheel (20) in such a way that a first gap (24) of maximally up to 3 mm is implemented between the front side (2h) of the cover plate (2) and the rear side (25a) of the screw-type centrifugal wheel (20), wherein a second gap (2b) is implemented between the central opening (2g) of the cover plate (2) and the hub (21) or the drive shaft (33), which second gap (2b) is fluid-conductively connected to the inner space (37) and to the first gap (24), wherein the cover plate (2) features at least one through hole (2a), which is arranged spaced apart from the central opening (2g), wherein the screw-type centrifugal wheel (20) and the arrangement of the through hole (2a) are embodied adapted to each other in such a way that, in a viewing direction in parallel to a rotary axis (A) of the screw-type centrifugal wheel (20), the rear side (25a) of the screw-type centrifugal wheel (20) does not cover the through hole (2a) or, in a rotation of the screw-type centrifugal wheel (20), covers the through hole (2a) only during a partial angle, and wherein the through hole (2a) forms a fluid-conducting connection between the front side (2h) and the inner space (37) for the purpose of generating a fluid flow (F1) flowing into the inner space (37) via the through hole (2a) and then flowing out of the inner space (37) via the gap (2b).
  2. Screw-type centrifugal wheel pump according to claim 1, characterised in that the gap (24) has a width in a range of 0.5 to 2 mm.
  3. Screw-type centrifugal wheel pump according to one of the preceding claims, characterised in that the partial surface (2k) extends substantially frusto-conically.
  4. Screw-type centrifugal wheel pump according to one of the preceding claims, characterised in that the cover plate (2) features at least two through holes (2a), wherein the at least two through holes (2a) are arranged in particular symmetrically with respect to the rotary axis (A).
  5. Screw-type centrifugal wheel pump according to one of the preceding claims, characterised in that the through hole (2a) features towards the front side (2h) an inlet opening (21), that the front side (2h) features a hollow (2c) and that the inlet opening (21) is arranged in said hollow (2c).
  6. Screw-type centrifugal wheel pump according to claim 5, characterised in that the inlet opening (21) forms an inlet surface (2m) extending substantially in parallel to the rotary axis (A).
  7. Screw-type centrifugal wheel pump according to one of claims 5 to 7, characterised in that the hollow (2c) is embodied at least partly by a bore extending substantially perpendicularly to the rotary axis (A).
  8. Screw-type centrifugal wheel pump according to claim 5 or 6, characterised in that the cover plate (2) consists of a casting and that the hollow (2c) and advantageously the inlet opening (21) as well already form part of the unprocessed casting.
  9. Screw-type centrifugal wheel pump according to one of claims 1 to 5, characterised in that the through hole (2a) extends perpendicularly or substantially perpendicularly with respect to the partial surface (2k).
  10. Screw-type centrifugal wheel pump according to one of claims 1 to 5, characterised in that the through hole (2a) extends transversely with respect to the partial surface (2k).
  11. Screw-type centrifugal wheel pump according to one of claims 1 to 7 or 9 to 10, characterised in that the cover plate (2) is embodied of a metal sheet.
  12. Screw-type centrifugal wheel pump according to one of the preceding claims, characterised in that the through hole (2a) extends counter to the rotary direction (R) of the screw-type centrifugal wheel (20).
  13. Screw-type centrifugal wheel pump according to one of the preceding claims, characterised in that the screw-type centrifugal wheel (20) features a rotary direction (R) and that the inlet surface (2m) formed by the inlet opening (21) of the through hole (2a) extends substantially in parallel to the rotary axis (A) and facing away from the rotary direction (R).
  14. Screw-type centrifugal wheel pump according to one of the preceding claims, characterised in that the hub (21) of the screw-type centrifugal wheel (20) comprises a circle-shaped basis element (30), that the impeller (25) is arranged on the circle-shaped basis element (30) and that the circle-shaped basis element (30) is arranged concentrically with respect to the rotary axis (A) and features a maximum radius (R1), wherein the maximum radius (R1) is adapted with respect to the through hole (2a) in such a way that the basis element (30) does not cover the through hole (2a).
  15. Screw-type centrifugal wheel pump according to one of claims 1 to 12, characterised in that the hub (21) of the screw-type centrifugal wheel (20) comprises a sickle-shaped basis element (30), that the impeller (25) is arranged on the sickle-shaped basis element (30) and that the sickle-shaped basis element (30) features, with respect to the rotary axis (A), a maximum radius (R1) and a minimum radius (R2), wherein the sickle-shaped basis element (30) is implemented extending in such a way with respect to the through hole (2a) that the basis element (30) does not cover the through hole (2a) in case of the minimum radius (R2) and that, in a rotation of the screw-type centrifugal wheel (20) by 360°, the basis element (30) covers the through hole (2a), in a rotation of the screw-type centrifugal wheel (20) by 360°, during a partial angle (Δ).
  16. Screw-type centrifugal wheel pump according to one of the preceding claims, characterised in that the partial surface (2h) features a spirally extending hollow (2d) which substantially extends, starting in a region of the central opening (2g), outwards along the partial surface (2h).
  17. Screw-type centrifugal wheel pump (1) according to claim 16, characterised in that the spirally extending hollow (2d) extends in the rotary direction (R) from inside outwards.
  18. Method for self-cleaning of a screw-type centrifugal wheel pump (1), comprising a rotarily supported screw-type centrifugal wheel (20) as well as a cover plate (2), which is arranged on the rear side 25a of the screw-type centrifugal wheel (20) forming a first gap (24) and features a central opening (2g), wherein the cover plate (2) features a through hole (2a), which is spaced apart from the central opening (2g), wherein a hub (21) or a drive shaft (33) of the screw-type centrifugal wheel (20) extends through the central opening (2g), as a result of which a fluid-conducting second gap (2b) forms between the central opening (2g) and the hub (21) or the drive shaft (33), wherein the screw-type centrifugal wheel (20) and the arrangement of the through hole (2a) are embodied respectively adapted in such a way that, in a viewing direction in parallel to a rotary axis (A) of the screw-type centrifugal wheel (20), the through hole (2a) is not covered by the rear side (25a) of the screw-type centrifugal wheel (20) during rotation of the screw-type centrifugal wheel (20) or is covered only during a partial angle (Δ), wherein the screw-type centrifugal wheel (20) is rotated in a rotary direction (R) and a fluid is thus conveyed along a main flow (F), wherein a partial flow (F1) of the fluid flows to the rear side (2i) of the cover plate (2) via the through hole (2a) and wherein said partial flow (F1) then flows to the main flow (F) via the gaps (2b, 24), due to the pressure difference prevailing between the through hole (2a) and the second gap (2b).
  19. Method according to claim 18, characterised in that the cover plate (2) features a spirally extending hollow (2d) on its front side (2h), wherein the spirally extending hollow (2d) extends from inside outwards in a rotary direction (R), resulting in the partial flow (F1) leaving the gap (2b) is conveyed to the main flow (F) via the spirally extending hollow (2d).
  20. Method according to claim 18 or 19, characterised in that the partial flow (F1) is deflected when flowing into the through hole (2a) for the purpose of thus separating off solid matter from the partial flow (F1).
EP11796936.0A 2010-11-24 2011-11-24 Self cleaning radial flow pump with recirculation behind the impeller Active EP2643595B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP11796936.0A EP2643595B1 (en) 2010-11-24 2011-11-24 Self cleaning radial flow pump with recirculation behind the impeller
EP17152843.3A EP3179112B1 (en) 2010-11-24 2011-11-24 Pump cover plate with through holes that are designed as inertial filters
DK17152843.3T DK3179112T3 (en) 2010-11-24 2011-11-24 PUMP COVER SHEET WITH THROUGHHOLES DESIGNED AS INERT FILTERS

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP10192467A EP2458225A1 (en) 2010-11-24 2010-11-24 Covering board for a screw centrifuge wheel pump and screw centrifuge wheel pump comprising such a covering board
PCT/EP2011/070995 WO2012069618A1 (en) 2010-11-24 2011-11-24 Self-cleaning screw-type centrifugal wheel pump with recirculation behind the impeller
EP11796936.0A EP2643595B1 (en) 2010-11-24 2011-11-24 Self cleaning radial flow pump with recirculation behind the impeller

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP17152843.3A Division EP3179112B1 (en) 2010-11-24 2011-11-24 Pump cover plate with through holes that are designed as inertial filters
EP17152843.3A Division-Into EP3179112B1 (en) 2010-11-24 2011-11-24 Pump cover plate with through holes that are designed as inertial filters

Publications (2)

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EP2643595A1 EP2643595A1 (en) 2013-10-02
EP2643595B1 true EP2643595B1 (en) 2017-05-24

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EP10192467A Withdrawn EP2458225A1 (en) 2010-11-24 2010-11-24 Covering board for a screw centrifuge wheel pump and screw centrifuge wheel pump comprising such a covering board
EP17152843.3A Active EP3179112B1 (en) 2010-11-24 2011-11-24 Pump cover plate with through holes that are designed as inertial filters
EP11796936.0A Active EP2643595B1 (en) 2010-11-24 2011-11-24 Self cleaning radial flow pump with recirculation behind the impeller
EP11799082.0A Active EP2643596B1 (en) 2010-11-24 2011-11-24 Self-cleaning centrifugal screw pump with auxiliary flushing flow behind the impeller

Family Applications Before (2)

Application Number Title Priority Date Filing Date
EP10192467A Withdrawn EP2458225A1 (en) 2010-11-24 2010-11-24 Covering board for a screw centrifuge wheel pump and screw centrifuge wheel pump comprising such a covering board
EP17152843.3A Active EP3179112B1 (en) 2010-11-24 2011-11-24 Pump cover plate with through holes that are designed as inertial filters

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Application Number Title Priority Date Filing Date
EP11799082.0A Active EP2643596B1 (en) 2010-11-24 2011-11-24 Self-cleaning centrifugal screw pump with auxiliary flushing flow behind the impeller

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US (2) US9879695B2 (en)
EP (4) EP2458225A1 (en)
JP (2) JP6028162B2 (en)
CN (2) CN103339386B (en)
DK (3) DK2643595T3 (en)
RU (2) RU2559958C2 (en)
WO (2) WO2012069618A1 (en)

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Publication number Priority date Publication date Assignee Title
US9719515B2 (en) * 2013-01-11 2017-08-01 Liberty Pumps, Inc. Liquid pump
IL233615A (en) * 2014-07-10 2016-02-29 Ettem Eng S A Ltd Method and devices for discharging contaminants out of a seal chamber
CN104131980B (en) * 2014-08-14 2017-01-25 杨付许 Drum-type slurry whitewashing machine and slurry pump thereof
DE102016110224B4 (en) * 2015-06-03 2020-03-12 Gea Tuchenhagen Gmbh Centrifugal pump and impeller for a centrifugal pump
RU170010U1 (en) * 2016-09-28 2017-04-11 Валентина Ильинична Жушман SINGLE AUGER PUMP PUMP
EP3864295A4 (en) 2017-10-12 2022-05-25 Weir Minerals Australia Ltd INLET ELEMENT FOR A SLUDGE PUMP
CN112941827B (en) * 2019-11-26 2022-12-09 青岛海尔洗衣机有限公司 Top-wheel washing machine with self-cleaning device

Family Cites Families (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2297001A (en) * 1939-03-17 1942-09-29 Bour Harry E La Self-priming centrifugal pump
US2769390A (en) * 1954-06-02 1956-11-06 Brummer Seal Co Water cooled annular seal
CH396639A (en) * 1959-10-08 1965-07-31 Voith Gmbh J M Centrifugal pump
US3115841A (en) * 1961-11-16 1963-12-31 Thompson Ramo Wooldridge Inc Pump assembly
DE1528651B2 (en) * 1965-01-23 1975-12-18 Albert 5204 Lohmar Blum Dirty water pump
US3632220A (en) * 1970-08-27 1972-01-04 Chrysler Corp Coolant pump
CH627236A5 (en) * 1978-02-14 1981-12-31 Martin Staehle
CH633617A5 (en) * 1978-08-31 1982-12-15 Martin Staehle CENTRIFUGAL PUMP WITH A VIBRATED IMPELLER FOR CONVEYING LONG-FIBER FLUSHED SOLIDS.
AU538118B2 (en) * 1979-10-29 1984-08-02 Rockwell International Inc. Seal assembly
US4575312B1 (en) * 1982-06-02 1989-05-16 Impeller
CH660511A5 (en) * 1982-12-22 1987-04-30 Martin Staehle Centrifugal pump having a single-blade impeller
CH662864A5 (en) 1983-04-20 1987-10-30 Martin Staehle Centrifugal pump having an open-type single-blade impeller
IT1174991B (en) * 1983-07-06 1987-07-01 Pompe F B M Spa CENTRIFUGAL PUMP FOR VERY DENSE AND / OR VISCOUS MATERIALS AND PRODUCTS
US4773823A (en) * 1984-11-13 1988-09-27 Tolo, Inc. Centrifugal pump having improvements in seal life
DE3517499A1 (en) * 1985-05-15 1986-11-20 Klein, Schanzlin & Becker Ag, 6710 Frankenthal WHEEL
JPS6352992U (en) * 1986-09-25 1988-04-09
SU1528035A1 (en) * 1987-02-18 1994-10-30 А.И. Золотарь Centrifugal pump
FI872967A7 (en) * 1987-07-06 1989-01-07 Ahlstroem Oy PUMP OCH FOERFARANDE FOER SEPARING AV GAS MED PUMPEN UR MEDIET SOM SKALL PUMPAS.
CA2015777C (en) * 1990-04-30 1993-10-12 Lynn P. Tessier Centrifugal pump
US5167418A (en) * 1991-04-04 1992-12-01 Dunford Joseph R Grit protector
US5195867A (en) * 1992-03-05 1993-03-23 Barrett, Haentjens & Co. Slurry pump shaft seal flushing
US5553868A (en) * 1994-11-03 1996-09-10 Dunford; Joseph R. Seal cavity throat bushing
US6190121B1 (en) * 1999-02-12 2001-02-20 Hayward Gordon Limited Centrifugal pump with solids cutting action
GB9907372D0 (en) * 1999-03-30 1999-05-26 Concentric Pumps Ltd Improvements in pumps
US6422358B2 (en) * 2000-01-24 2002-07-23 William T. Deibel Ventilated disc brake rotor
US7008177B2 (en) * 2002-11-14 2006-03-07 Cummins Inc. Centrifugal pump with self cooling and flushing features
JP2005061391A (en) * 2003-07-30 2005-03-10 Aisin Seiki Co Ltd Pump device
US7037069B2 (en) * 2003-10-31 2006-05-02 The Gorman-Rupp Co. Impeller and wear plate
CN101280922B (en) * 2006-11-07 2010-06-09 河北宏业机械股份有限公司 A cone-shaped burner for a fuel oil heater
CN101294580B (en) * 2007-04-26 2010-04-21 李世煌 A spiral flow constant pressure pump
US9350475B2 (en) 2010-07-26 2016-05-24 Qualcomm Incorporated Physical layer signaling to user equipment in a wireless communication system
US8892118B2 (en) 2010-07-23 2014-11-18 Qualcomm Incorporated Methods and apparatuses for use in providing position assistance data to mobile stations

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EP2643595A1 (en) 2013-10-02
JP2014502328A (en) 2014-01-30
DK3179112T3 (en) 2020-10-12
CN103339386A (en) 2013-10-02
RU2013128532A (en) 2014-12-27
WO2012069618A1 (en) 2012-05-31
EP2643596A1 (en) 2013-10-02
EP3179112B1 (en) 2020-08-05
DK2643595T3 (en) 2017-09-18
EP3179112A1 (en) 2017-06-14
JP5988106B2 (en) 2016-09-07
JP2014500930A (en) 2014-01-16
RU2559958C2 (en) 2015-08-20
EP2458225A1 (en) 2012-05-30
DK2643596T3 (en) 2017-10-30
CN103299085B (en) 2016-11-16
CN103299085A (en) 2013-09-11
RU2013128547A (en) 2014-12-27
US20130243634A1 (en) 2013-09-19
US20130243568A1 (en) 2013-09-19
CN103339386B (en) 2017-03-29
US9879695B2 (en) 2018-01-30
RU2566865C2 (en) 2015-10-27
US9709071B2 (en) 2017-07-18
WO2012069619A1 (en) 2012-05-31
EP2643596B1 (en) 2017-07-12

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