EP1327781B1 - Pompe centrifuge auto-amorçante - Google Patents

Pompe centrifuge auto-amorçante Download PDF

Info

Publication number
EP1327781B1
EP1327781B1 EP03000155A EP03000155A EP1327781B1 EP 1327781 B1 EP1327781 B1 EP 1327781B1 EP 03000155 A EP03000155 A EP 03000155A EP 03000155 A EP03000155 A EP 03000155A EP 1327781 B1 EP1327781 B1 EP 1327781B1
Authority
EP
European Patent Office
Prior art keywords
self
impeller
centrifugal pump
priming centrifugal
pump according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03000155A
Other languages
German (de)
English (en)
Other versions
EP1327781A2 (fr
EP1327781A3 (fr
Inventor
Gerhard Ursinus
Heinz Rust
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.)
Hilge GmbH and Co KG
Original Assignee
Philipp Hilge & Co KG GmbH
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 Philipp Hilge & Co KG GmbH filed Critical Philipp Hilge & Co KG GmbH
Publication of EP1327781A2 publication Critical patent/EP1327781A2/fr
Publication of EP1327781A3 publication Critical patent/EP1327781A3/fr
Application granted granted Critical
Publication of EP1327781B1 publication Critical patent/EP1327781B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/026—Selection of particular materials 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
    • F04D9/00—Priming; Preventing vapour lock
    • F04D9/04—Priming; Preventing vapour lock using priming pumps; using booster pumps to prevent vapour-lock
    • F04D9/041—Priming; Preventing vapour lock using priming pumps; using booster pumps to prevent vapour-lock the priming pump having evacuating action
    • 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
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/10—Metals, alloys or intermetallic compounds
    • F05D2300/17—Alloys
    • F05D2300/171—Steel alloys
    • 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
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/40—Organic materials
    • F05D2300/43—Synthetic polymers, e.g. plastics; Rubber

Definitions

  • the present invention relates to a self-priming centrifugal pump having a suction cover with suction port, an impeller, a flow channel housing receiving the impeller, a pressure-side opening in the flow channel housing and a breaker area in the peripheral region between the pressure-side opening and the suction port.
  • US 3551067 shows a suction cast-iron volute casing pump with a PTFE lining of the pump parts which contact the medium to be conveyed.
  • Centrifugal pumps have long been known in the art, such as from the German Offenlegungsschrift No. 44 00 289 , Centrifugal pumps usually have a suction cover, an impeller and a flow channel housing receiving the impeller. Furthermore, a suction opening and a pressure-side outlet opening are provided.
  • a self-priming centrifugal pump has the special feature that the actual intake is not centrally provided on the suction cover and that circumferentially offset thereto and usually on the opposite side of the suction cover, an outlet opening is provided, wherein suction and pressure-side outlet effectively separated by a so-called breaker area become.
  • the breaker area in the circumferential direction must have a length of at least two bucket wheel chambers, the bucket wheel chamber being the volume between two adjacent bucket wheels. If, then, when moving over the interruption area, a bucket wheel chamber opens to the suction-side section of the flow channel, the next following bucket wheel chamber, coming from the pressure side, is already completely in the interrupter area and thus terminated.
  • the present invention seeks to provide a self-priming centrifugal pump with the features mentioned, which is also suitable for sterile applications with a simple construction possible.
  • suction cover, impeller and flow channel housing made of a sterility requirements sufficient material and / or coated with such a material, and that suction cover and flow channel housing and all other acted upon by the pumping medium static components of the pump are sealed to the functional spaces exposed and well acted upon by the pumping medium seals against each other.
  • the seals in the case of the present invention are deliberately exposed to the pumping medium.
  • the seals are preferably arranged so that the pumping medium acting on the seals must not pass through bottlenecks, the cross-section of which would be significantly smaller (by a factor of 2 or more) than the surfaces of the seal itself to be acted upon.
  • the seals may be arranged, for example, in whole or in part be that the extension of the wall contour of the mutually sealed surfaces in the pump falls in the cross section of the seal.
  • the seals bulge at least slightly in the smooth (ie substantially straight and concave without avoidable curvatures) complemented area of the inner surface of the housing parts before.
  • the pump components in the area of the seals can be designed so that the inner component surfaces, which adjoin the surfaces in contact with the seals, are of a relatively small radius of curvature, typically of the order of 5 mm or smaller, of the Curve away the surface of the seal or at an angle greater than 30 °, from the surface or a tangent to the surface of the seal away.
  • the invention provides that then the width or smallest dimension of the opening between the seal and the other space acted upon with pumping medium is at least 0.5 mm.
  • the aspect ratio of a corresponding opening defined as the depth to width ratio of the access opening or access channel to the seal, should be at most 2, and preferably less than 1. It is essential in any case that neither before the seals or at the transition between seals and the adjacent surfaces narrow and deep gaps or even clear undercuts arise that can only be rinsed poorly by the pumping medium and / or a detergent.
  • the sealing wall sections of the pump components should therefore not hit with less than 30 ° to the sealing surface with the largest possible angle.
  • the wall portion should curve away from the surface of the gasket, at least with a relatively small radius of curvature of less than 5 mm, so that any remaining wedge-shaped gap between gasket and adjoining wall portion has only a very small depth and thus can be easily rinsed out.
  • the seals have expediently a cross section of at least 4 to 8 mm 2 .
  • the gap width should be between the edges of the individual blades of the impeller and the adjacent walls, namely the suction cover and the opposite wall of the flow channel housing and also the corresponding housing portion along the circumference of the impeller is less than 0.5 mm, preferably less than 0.3 mm.
  • a constant 0.2 mm gap width or less can be maintained, and in the interrupter region, this small gap distance can also be maintained with respect to the wall of the flow channel housing opposite the suction cover.
  • a seal is preferably located in the corner region between the suction cover and the edge of the flow channel housing which adjoins it and is arranged offset backwards away from the corresponding corner of the impeller blades by approximately 0.5 mm. That is, the sealing surface jumps back from an imaginary (straight or concave) transition in the corner between the suction cover and the flow channel housing by about 0.2 to 0.3 mm.
  • the flow channel is preferably widened in the radial direction, that is, it has, with the exception of the directly adjacent to the suction cover and the seal in this area bearing portion, a significantly larger diameter than the impeller.
  • the flow channel also runs parallel to the space acted upon by the impeller blades, during which a toroidal vortex is formed in the flow channel and the directly adjoining pump chamber acted on by the impeller. This torus begins in the region of the suction opening and ends at the pressure-side outlet opening, is therefore not complete, but interrupted by the breaker area.
  • the flow channel tapers in the direction of the pressure-side outlet opening, wherein this tapered section is also referred to by experts as "worm extension".
  • worm extension Radially within this appendix a vent hole is provided in the wall of the flow channel housing for the gas, which was possibly sucked at the beginning of a suction by the pump or which is possibly released by degassing from the pumping medium.
  • a pressure chamber is additionally provided, which extends in the preferred embodiment of the invention substantially parallel to the flow channel and thereby also partially encloses the flow channel or the flow channel housing.
  • the pressure chamber finally opens into a radial or tangential outlet nozzle.
  • the pressure chamber is formed by the interior of a pot-shaped housing, which has an additional central bore for the passage of a drive shaft for the impeller.
  • the outer diameter of the pressure chamber housing is preferably the same as the outer diameter of the flow channel housing, but the latter has on its outer side a stepped taper, the outer diameter substantially equal to the inner diameter of the pressure chamber housing, so that it can be placed from the outside onto the flow channel housing and thereby the mentioned stepped Rejuvenation absorbs. On the outside then close the flow channel housing with its extended section and the Pressure chamber housing flush with each other.
  • the drive shaft expediently extends through a central bore of the pressure chamber housing and also the flow channel housing and is sealed in this area by a sliding seal.
  • the shaft is also still stored in the region of the suction cover in a sliding bearing.
  • the plain bearing can also be formed integrally with the impeller, wherein the impeller is connected non-positively not only in the circumferential direction with the shaft, but is also fixed in the axial direction on the shaft.
  • the self-priming centrifugal pump is preceded by an additional non-self-priming centrifugal pump stage.
  • This centrifugal pump stage has expediently the same outer diameter and also a step-like taper, as previously described for the flow channel housing, wherein the suction cover of the self-priming pump is pot-shaped and, as previously described between pressure chamber housing and flow channel housing, the tapered portion of the housing the upstream non-self-priming centrifugal pump comprises.
  • the upstream, not self-priming centrifugal pump increases the pumping power of the entire system and also contributes to the fact that cavitation effects could be better avoided because the pressure differences occurring in the self-priming pump are thereby reduced.
  • the material for the pump according to the invention in particular for suction cover, flow channel housing and optionally also for the impeller, a stainless steel, e.g. Chrome-molybdenum-nickel steel can be used, which forges well and process.
  • a stainless steel e.g. Chrome-molybdenum-nickel steel
  • plastic materials or a plastic coating can also be used for the impeller itself.
  • the impeller or its coating may also be integrally formed with the arranged in a central bore of the suction cover slide bearing.
  • the generally designated 20 in Figure 1 self-priming pump consists essentially of the suction cover 2, the impeller 5, the flow channel housing 6 and the drive shaft 10 for the impeller 5.
  • the pump is completed by a housing cover 12 having a central intake manifold 1 , and a pressure chamber housing 8, which has a tangential discharge nozzle or outlet 16.
  • the pressure housing 8, the flow channel housing 6 and the suction cover 2 have a cylindrical circumference with substantially the same outer diameter, wherein the suction cover 2 and the flow channel housing 6 have a stepped taper whose outer diameter corresponds to the inner diameter of the next following part, so that the flow channel housing 6 suitable can be inserted into the pressure housing 8, while the suction cover can be accommodated with its tapered portion in the axially projecting edge portion of the flow channel housing 6.
  • the suction cover 2 has a cylindrical circumferential rim, which in turn receives the tapered cylindrical portion of a housing cover 12.
  • the housing cover 12 finally has a laterally projecting flange with mounting holes through which mounting bolts 18 extend, which are the four essential and assembled into an approximately cylindrical unit parts, namely the housing cover 12, the suction cover 2, the flow channel housing 6 and the pressure housing 8 to press the bracket 17 of a corresponding engine block, which is not shown here and through which the shaft 10 is driven to rotate.
  • the individual blades 25 of the impeller 5 are in the axial view shown in Figure 1 substantially rectangular, plate-shaped parts, however, beveled to their edges or “sharpened", which by the prismatic edge surfaces of the blades in the upper region of the impeller in Figure 1 is indicated.
  • the suction cover 2 has in its lower part in Figure 1 on a suction port 3 and is otherwise completely closed, that is, it covers the impeller 5 except the region of the suction port 3.
  • the suction cover 2 rests on a flat peripheral surface of the flow channel housing 6 and is sealed by a seal 14 against the flow channel housing 6.
  • the flow channel housing has approximately the shape of a torus, parts of which are cut away, so that the impeller 5 can rotate freely inside the torus about the axis and The impeller blades 25 thereby cover about half of the free Torusqueritess.
  • the cross-sectional area of the flow channel housing 6 which is not acted upon by the impeller blades 25 is referred to as the flow channel 7.
  • This flow channel 7 extends axially offset parallel to the acted upon by the impeller blades 25 and swept, cylindrical volume, but is slightly widened compared to the area acted upon by the impeller blades in the radial direction. Due to the fluid dynamic conditions during operation of the pump, a more or less spiral vortex is formed during operation in the flow channel 7, which detects both the region of the chambers between the blades and the region of the flow channel 7 outside the impeller chambers. The radial extension of the flow channel 7 serves above all the unimpeded formation of this vortex. However, the flow channel 7 does not extend over the entire circumference of the flow channel housing 6, as best seen in FIG 4.
  • Figure 4 corresponds substantially to a plan view of Figure 1 from the left, however, the housing cover 12 with the intake manifold 1 and the suction cover 2 are omitted. Also, the shaft 10 with the impeller nut 11 is not shown in Figure 4. In the position shown in Figure 4, the suction port 3 of the suction cover would be located in a bottom right in the region of the intake port 7 indicated by a dashed circle position. As can be seen, there begins the flow channel 7 with the so-called intake 7 ', wherein the diameter of the suction port of the width of the flow channel 7 is adjusted (slightly larger than the dashed circle at 7'). The impeller 5 with the impeller blades 25 rotates in Figure 4 counterclockwise.
  • the fluid entering the suction region 7 'of the flow channel 7 through the suction port 3 is entrained by the impeller blades 25 and accelerated in the circumferential direction.
  • a permanent exchange of the medium takes place between the blades (in the blade chambers) and the flow channel 7 running parallel thereto, overall, however, the fluid or pumping medium is entrained in the circumferential direction counterclockwise and increasingly compressed.
  • the pressure-side outlet opening 26 is in the region of the maximum pressure in the flow channel 7. Behind it begins an increasingly tapering region of the flow channel, which is also referred to as the "worm appendage” 7 "by experts 7 "in the form of a gradual taper of the flow channel 7 behind the outlet opening 26 terminates immediately radially outside of a vent 19 in the housing 6 of the flow channel 7.
  • This vent hole 19 serves to escape from entrained during suction or otherwise during pumping in the pumping medium gases, which also may result from degassing of the pumping medium, if this contains corresponding dissolved gases.
  • the pressure region 7 "and the degassing opening 19 are arranged in the circumferential direction at a distance from the suction port 3 and the beginning of the flow channel 7, which corresponds approximately to the circumferentially measured width of two pumping chambers, wherein a pumping chamber as the enclosed between two impeller blades 25 volume 1, this means that a corresponding section laid through the interrupter region 22 would no longer show a flow channel 7 running parallel to the blade region.
  • the suction cover 2 runs close to these edges.Also, the radial extension of the flow duct 7 is reduced in the interrupter region 22 to a narrow gap S2 which is so small e is held possible without it may come to a contact of the blade edges with the flow channel housing 6 due to vibrations or tolerance deviations.
  • FIG. 1 An axial section through the breaker area at the transition of the flow channel housing 6 to the suction cover 2 is shown enlarged in FIG. This corresponds approximately to the area circled in Figure 1 above in the region of the seal 14 and denoted by II area.
  • the edges of the impeller blades 25 to the inner wall of the impeller cover have a very small distance S1, which is typically not more than 0.2 mm.
  • the outer edge of the impeller blade 25 has only a very small distance corresponding to the specified gap S2, which is slightly larger than the gap S1, but should not exceed 0.5 mm as far as possible. It should be noted that in the interrupter region 22, the gap between the blade edges and the radial wall shown above over the entire axial length of the impeller blades 25 would be reduced to the gap width S2, while in the section of Figure 1 shown in Figure 2 nor the radial extension of Flow channel is recognizable.
  • the seal 14 is received in corresponding recesses of the suction cover 2 and the adjacent wall of the flow channel housing 6, wherein these recesses are dimensioned in relation to the diameter of the cylindrical sealing ring cross-section so that the sealing ring 14th is squeezed by the dimension S3 when touching the facing wall portions of the suction cover 2 and the flow channel housing 6.
  • the inner wall of the suction cover 2 and a corresponding projecting corner of the flow channel housing 6 have a very small radius of curvature r which is significantly smaller than the radius of the sealing cross-section. In this way it is achieved that a narrow and deep gap is avoided between the sealing surface and the adjacent walls, but the walls of the respective components quickly bend away from the surface of the seal immediately outside the sealing contact.
  • seals 13, 15 or 23, which can be seen in Figure 1.
  • FIG. 1 An enlargement of the seal 15 according to the area indicated by a circle III in FIG. 1 is shown again in FIG.
  • the seal 15 seals off the transition from the flow channel housing 6 to the pressure chamber housing 8, which are otherwise identical in the embodiment according to FIG. 5 as in the embodiment according to FIG. It can be seen in Figure 3, the upper curved course of the outer wall of the flow channel housing 6 at the transition to the tapered region, which is enclosed by the cylindrical wall of the pressure chamber housing 8.
  • the wall of the pressure chamber housing 8 has in this area a recess for receiving the sealing ring 15, which, however, is dimensioned so that the sealing ring 15 clearly protrudes from this recess and so can enter into sealing contact with the curved corner region on the outside of the flow channel housing 6.
  • the seal 15, the recess in the wall of the pressure chamber housing 8 and the curvature of the wall of the flow channel housing 6 are formed so that the dashed lines projections or extensions of the corresponding wall sections fall into the sealing cross-section.
  • the impeller 5 is formed integrally with a cylindrical projection 24 and also the slide bearing 4 can be wholly or partially formed integrally with this cylindrical projection 24.
  • This plain bearing 4 allows a very precise bearing of the impeller 5 and the shaft 10, which is additionally sealed by a sliding seal 21 against the pressure chamber housing 8 and the flow channel housing 6.
  • FIG 5 shows another, preferred for some applications embodiment of the present invention, in which the self-priming pump 20 is also preceded by a non-self-priming centrifugal pump stage 30 of conventional design.
  • the transition from the pump of Figure 1 to the pump of Figure 5 is carried out simply by the fact that the cover 12 is released from the self-priming pump 20 and replaced by the centrifugal pump module 30. Then the cover 12 is placed unchanged on the centrifugal pump module 30 and connected with correspondingly longer clamping screws 18 to the engine block 17.
  • the drive of the impeller 35 of the superior centrifugal pump is carried out either by a corresponding connection with the cylindrical projection of the impeller 5 or by a correspondingly extended, replaced shaft 10 ', which extends through the impeller 5 and into the impeller 35 inside. All other components of the pump shown in Figure 1 can be used identically.
  • the seals 13 have the same arrangements and cross sections as the newly added seals 13 '.
  • the upstream normal and non-self-priming centrifugal pump 30 has the effect that the pump power is increased overall and the pressure drop in the self-priming pump 20 is less pronounced, so that in such a construction cavitations, as they may occur in some pumping media easier avoid it.
  • the suction initially takes place essentially only by the self-priming pump 20, which sucks the medium to be pumped through the upstream centrifugal pump 30.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • External Artificial Organs (AREA)

Claims (22)

  1. Pompe centrifuge à amorçage automatique, ladite pompe comprenant un couvercle du côté aspiration (2) dans lequel est ménagée une ouverture du côté aspiration (3), une roue à aubes (5), un boîtier à canal d'écoulement (6) recevant une roue à aubes (5), une ouverture du côté sous pression ménagée dans le boîtier à canal d'écoulement (6) et une région d'interruption (22) prévue dans la région périphérique entre l'ouverture du côté sous pression et l'ouverture du côté aspiration (3), caractérisée en ce que toutes les pièces de la pompe qui sont soumises à une matière à pomper sont fabriquées à partir d'un matériau satisfaisant à des exigences de stérilité ou sont revêtues d'un tel matériau, et en ce que le capot du côté aspiration (2) et le boîtier à canal d'écoulement (6) ainsi que tous les autres composants statiques au contact de la matière à pomper sont rendus étanches l'un par rapport à l'autre par des garnitures d'étanchéité dégagées du côté des espaces fonctionnels.
  2. Pompe centrifuge à amorçage automatique selon la revendication 1, caractérisée en ce que le contour en coupe transversale des garnitures d'étanchéité (13, 14, 15) est prolongé par le contour imaginaire, se prolongeant dans la région des garnitures d'étanchéité, des surfaces intérieures des composants de la pompe.
  3. Pompe centrifuge à amorçage automatique selon la revendication 1, dans laquelle le contour d'au moins une des garnitures (13, 14, 15) n'est pas prolongé par le contour, se prolongeant dans la région de la garniture, des parois intérieures des composants de la pompe de sorte que la garniture d'étanchéité est totalement reçue dans un évidement ménagé en retrait en arrière du contour des surfaces intérieures de la pompe, caractérisée en ce que l'ouverture de liaison restante entre la surface de la garniture d'étanchéité et l'espace intérieur au contact de la matière à pomper a en coupe transversale un rapport d'allongement inférieur à 2, avantageusement inférieur à 1.
  4. Pompe centrifuge à amorçage automatique selon la revendication 3, caractérisée en ce que l'ouverture d'accès à la forme d'une fente d'une largeur minimale de 0,5 mm.
  5. Pompe centrifuge à amorçage automatique selon l'une des revendications 1 à 4, caractérisée en ce que la surface au contact de la matière à pomper d'une garniture d'étanchéité est égale au maximum à deux fois la section libre d'une ouverture d'accès menant de l'espace intérieur de la pompe à cette surface.
  6. Pompe centrifuge à amorçage automatique selon l'une des revendications 1 à 5, caractérisée en ce que les garnitures d'étanchéité sont essentiellement des bagues d'étanchéité de section circulaire ou elliptique.
  7. Pompe centrifuge à amorçage automatique selon l'une des revendications 1 à 6, caractérisée en ce que les portions de surface des composants de la pompe, lesquelles sont adjacentes aux surfaces de contact avec les garnitures d'étanchéité, sont incurvées de façon à s'écarter de la surface de la bague d'étanchéité avec un rayon de courbure correspondant au maximum à trois fois le rayon de courbure de la section de bague d'étanchéité ou s'étendent en faisant un angle d'au moins 30° par rapport à une tangente à la surface de la bague d'étanchéité.
  8. Pompe centrifuge à amorçage automatique selon l'une des revendications 1 à 6, caractérisée en ce que la roue à aubes (5) est montée de façon étanche sur l'arbre (10) de la pompe (20).
  9. Pompe centrifuge à amorçage automatique selon l'une des revendications 1 à 8, caractérisée en ce que le canal d'écoulement (7) est également élargi radialement dans la région entourant la roue à aubes, à l'exception de la région d'interruption (22).
  10. Pompe centrifuge à amorçage automatique selon l'une des revendications 1 à 9, caractérisée en ce que le canal d'écoulement comporte à son extrémité distante de l'ouverture du côté aspiration (3) dans la direction périphérique, juste avant la région d'interruption, une portion du côté sous pression (7") qui s'amincit et qui comporte une ouverture de sortie donnant dans un espace sous pression (9), un perçage de dégazage (19) reliant le volume occupé par la roue à aubes à l'espace sous pression (9), avantageusement en plus radialement à l'intérieur de la région de canal qui s'amincit.
  11. Pompe centrifuge à amorçage automatique selon l'une des revendications 1 à 10, caractérisée en ce que la largeur de la fente entre le bord des aubes de la roue à aubes (5) d'une part et le disque d'aspiration (2) ainsi que la paroi du boîtier à canal d'écoulement (6) dans la région d'interruption (22), aussi bien axialement que radialement, est inférieure à 0,5 mm et avantageusement inférieure à 0,3 mm.
  12. Pompe centrifuge à amorçage automatique selon la revendication 11, caractérisée en ce que la largeur axiale dans la région d'interruption est égale des deux côtés à 0,2 mm ou moins.
  13. Pompe centrifuge à amorçage automatique selon l'une des revendications 1 à 12, caractérisée en ce qu'il est prévu un espace sous pression (9) qui est essentiellement parallèle au canal d'écoulement (7), qui entoure partiellement le canal d'écoulement (7) et qui débouche dans une tubulure sous pression (17) radiale ou tangentielle.
  14. Pompe centrifuge à amorçage automatique selon la revendication 13, caractérisée en ce que l'espace sous pression (9) est formé par l'intérieur d'un boîtier en forme de cuvette (8) qui est doté d'un perçage central destiné à l'arbre d'entraînement (10) de la roue à aubes (5).
  15. Pompe centrifuge à amorçage automatique selon la revendication 14, caractérisée en ce que le diamètre extérieur du boîtier d'espace sous pression (8) est égal au diamètre du boîtier à canal d'écoulement (6) qui comporte sur son côté extérieur un amincissement en forme de gradin dont le diamètre extérieur correspond au diamètre intérieur du boîtier d'espace sous pression (8).
  16. Pompe centrifuge à amorçage automatique selon l'une des revendications 1 à 15, caractérisée en ce que l'arbre comporte une garniture d'étanchéité de glissement dans l'espace sous pression (9) et au niveau de la transition de l'espace sous pression (9) vers l'espace de pompage.
  17. Pompe centrifuge à amorçage automatique selon l'une des revendications 1 à 16, caractérisée en ce qu'il est prévu, dans la région du couvercle du côté aspiration (2), un palier se présentant sous la forme d'un palier à glissement axial et destiné à l'arbre (10) et/ou à la roue à aubes (5) reliée à l'arbre (10).
  18. Pompe centrifuge à amorçage automatique selon l'une des revendications 1 à 17, caractérisée en ce qu'un ou plusieurs étages de pompes centrifuges qui ne sont pas à amorçage automatique sont montés en amont de la pompe.
  19. Pompe centrifuge à amorçage automatique selon l'une des revendications 1 à 18, caractérisée en ce que le disque d'aspiration (2), le boîtier à canal d'écoulement (6), le boîtier d'espace sous pression (8) et éventuellement également une tubulure d'admission (1) sont fabriqués à partir d'un acier forgeable, avantageusement à partir d'un acier au chrome/molybdène/nickel à faible teneur en carbone.
  20. Dispositif selon la revendication 19, caractérisé en ce que la roue à aubes (5) est fabriquée essentiellement à partir du même matériau que le couvercle du côté aspiration (2) et/ou le boîtier à canal d'écoulement (6).
  21. Pompe centrifuge à amorçage automatique selon l'une des revendications 1 à 20, caractérisée en ce que la roue à aubes (5) est fabriquée à partir d'une matière plastique présentant une certaine résistance mécanique et chimique ou est revêtue d'une telle matière plastique.
  22. Pompe centrifuge à amorçage automatique selon la revendication 21, caractérisée en ce que le palier à glissement (4) destiné à l'arbre dans la région du couvercle du côté aspiration (2) est fabriqué d'une seule pièce avec le matériau de la roue à aubes (1) ou d'un revêtement de roue à aubes.
EP03000155A 2002-01-09 2003-01-04 Pompe centrifuge auto-amorçante Expired - Lifetime EP1327781B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10200579A DE10200579B4 (de) 2002-01-09 2002-01-09 Selbstansaugende Kreiselpumpe
DE10200579 2002-01-09

Publications (3)

Publication Number Publication Date
EP1327781A2 EP1327781A2 (fr) 2003-07-16
EP1327781A3 EP1327781A3 (fr) 2004-12-01
EP1327781B1 true EP1327781B1 (fr) 2007-06-20

Family

ID=7711762

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03000155A Expired - Lifetime EP1327781B1 (fr) 2002-01-09 2003-01-04 Pompe centrifuge auto-amorçante

Country Status (5)

Country Link
EP (1) EP1327781B1 (fr)
AT (1) ATE365275T1 (fr)
DE (2) DE10200579B4 (fr)
DK (1) DK1327781T3 (fr)
ES (1) ES2289186T3 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012223462B3 (de) * 2012-12-17 2013-08-08 Siemens Aktiengesellschaft Backup Dichtung in Kompaktbauweise bei einem Gehäuse einer Strömungsmaschine
EP3303844B1 (fr) * 2015-06-03 2019-09-18 GEA Tuchenhagen GmbH Roue pour une pompe centrifuge et pompe centrifuge
US20180058464A1 (en) * 2016-08-24 2018-03-01 Q.E.D. Environmental Systems, Inc. Pump Having Edge Mounted O-Ring Seal
CN110017299B (zh) * 2019-05-22 2024-04-09 台州市禺工泵业科技有限公司 一种离心泵的新型叶轮组合体
CN114251269B (zh) * 2020-09-24 2024-08-20 温兄控股集团股份有限公司 高扬程食品级卫生泵
DE102021122216A1 (de) 2021-08-27 2023-03-02 KSB SE & Co. KGaA Geschlossene Dickschicht für Pumpen

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3551067A (en) * 1969-01-22 1970-12-29 Duriron Co Lined corrosion resistant pump
US3973867A (en) * 1975-04-09 1976-08-10 Chien Fu Lee Radial flow type pump
DE3831068A1 (de) * 1988-09-13 1990-03-22 Sihi Gmbh & Co Kg Verfahren zur reinigung einer stoffbuchslosen, rotierend arbeitenden foerdereinrichtung fuer fluide
DE4020520A1 (de) * 1990-06-28 1992-01-02 Bosch Gmbh Robert Aggregat zum foerdern von kraftstoff vom vorratstank zur brennkraftmaschine eines kraftfahrzeuges
US5318403A (en) * 1990-12-25 1994-06-07 Ebara Corporation Interstage casing for a pump made of sheet metal and method of manufacturing the same
DE4400289C2 (de) * 1994-01-07 2001-07-05 Ksb Ag Kreiselpumpe
JP2665140B2 (ja) * 1994-02-03 1997-10-22 株式会社ワールドケミカル 自吸式ケミカルポンプ
DE29513904U1 (de) * 1995-08-30 1997-01-09 Sihi GmbH & Co KG, 25524 Itzehoe Seitenkanalkreiselpumpe mit Stufenpaketen in Blechkonstruktion
DE10033402A1 (de) * 2000-07-08 2002-01-24 Hilge Philipp Gmbh Kreiselpumpe

Also Published As

Publication number Publication date
DK1327781T3 (da) 2007-10-15
DE10200579B4 (de) 2013-06-06
ATE365275T1 (de) 2007-07-15
DE10200579A1 (de) 2003-07-10
EP1327781A2 (fr) 2003-07-16
DE50307499D1 (de) 2007-08-02
EP1327781A3 (fr) 2004-12-01
ES2289186T3 (es) 2008-02-01

Similar Documents

Publication Publication Date Title
DE69005510T2 (de) Pumpe um Gas von einer zu pumpenden Flüssigkeit abzutrennen.
DE102010046870B4 (de) Seitenkanalgebläse, insbesondere Sekundärluftgebläse für eine Verbrennungskraftmaschine
DE10327574B4 (de) Laufrad für eine Kraftstoffpumpe
EP1811184B1 (fr) Roue pour une unité de pompage et unité de pompage correspondante
EP1797327A1 (fr) Pompe à pistons rotatifs comportant un carter et deux pistons rotatifs à deux pales
EP3140548B1 (fr) Rotor pour turbomachine régénératrice
WO2010086210A1 (fr) Soufflante de canal latéral, en particulier soufflante d'air secondaire pour une machine à combustion interne
EP3179112B1 (fr) Couvercle de pompe avec trous formés comme filtres inertiels
EP1327781B1 (fr) Pompe centrifuge auto-amorçante
DE102009021620A1 (de) Vakuumpumpe
WO2011079892A1 (fr) Pompe immergée
EP3088743B1 (fr) Étage de pompe a vide à canal latéral avec un barrage de canal qui présente une rampe du côté de l'aspiration
DE102007020218A1 (de) Förderpumpe
DE102010005517B4 (de) Dispergierpumpe
DE4239071C2 (de) Tauchpumpenaggregat
WO2019120550A1 (fr) Ventilateur à canal latéral, notamment ventilateur à aire secondaire pour moteur à combustion interne
DE102008056106B4 (de) Seitenkanalgebläse, insbesondere Sekundärluftgebläse für eine Verbrennungskraftmaschine
DE20305113U1 (de) Leitvorrichtung für ein in Blechbauweise ausgeführtes Gehäuse einer Kreiselpumpe
DE102021110936A1 (de) Pumpenlaufrad, Gehäuseelement und Pumpe hiermit
DE102016110224B4 (de) Kreiselpumpe und Laufrad für eine Kreiselpumpe
DE102012023731B4 (de) Kreiselpumpe insbesondere für Abwasser oder Schmutzwasser
DE19748448C2 (de) Peripheralpumpe
WO2019120633A1 (fr) Compresseurs à canal latéral, en particulier compresseurs d'air secondaires pour un moteur à combustion interne
DE10008811C2 (de) Flüssigkeitsringpumpe
DE2523213B2 (de) Kompakte mehrstufige Kreiselpumpe mit Zwischenentnahme und Wiedereinspeisung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: PHILIPP HILGE GMBH & CO. KG

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO

RIC1 Information provided on ipc code assigned before grant

Ipc: 7F 04D 7/02 B

Ipc: 7F 04D 9/04 B

Ipc: 7F 04D 9/02 A

17P Request for examination filed

Effective date: 20050401

17Q First examination report despatched

Effective date: 20050524

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT SE SI SK TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 50307499

Country of ref document: DE

Date of ref document: 20070802

Kind code of ref document: P

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: HILGE GMBH & CO. KG

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070920

NLT2 Nl: modifications (of names), taken from the european patent patent bulletin

Owner name: HILGE GMBH & CO. KG

Effective date: 20070815

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

Ref country code: CH

Ref legal event code: NV

Representative=s name: ISLER & PEDRAZZINI AG

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20071001

ET Fr: translation filed
NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
BECA Be: change of holder's address

Owner name: *HILGE G.M.B.H. & CO. K.G.HILGESTRASSE, D-55294 BO

Effective date: 20070620

BECH Be: change of holder

Owner name: *HILGE G.M.B.H. & CO. K.G.

Effective date: 20070620

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070620

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070620

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070620

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071120

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070620

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070920

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2289186

Country of ref document: ES

Kind code of ref document: T3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070620

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070921

26N No opposition filed

Effective date: 20080325

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070620

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070620

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080104

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070620

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080104

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071221

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070620

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20140121

Year of fee payment: 12

Ref country code: DE

Payment date: 20140321

Year of fee payment: 12

Ref country code: CH

Payment date: 20140121

Year of fee payment: 12

Ref country code: DK

Payment date: 20140121

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20140127

Year of fee payment: 12

Ref country code: ES

Payment date: 20140129

Year of fee payment: 12

Ref country code: FR

Payment date: 20140123

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20140121

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150131

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50307499

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

Effective date: 20150131

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20150104

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150104

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150131

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150801

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150131

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20150930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150202

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150104

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150131

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20160506

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150105