EP1327781A2 - Selbstansaugende Kreiselpumpe - Google Patents
Selbstansaugende Kreiselpumpe Download PDFInfo
- Publication number
- EP1327781A2 EP1327781A2 EP03000155A EP03000155A EP1327781A2 EP 1327781 A2 EP1327781 A2 EP 1327781A2 EP 03000155 A EP03000155 A EP 03000155A EP 03000155 A EP03000155 A EP 03000155A EP 1327781 A2 EP1327781 A2 EP 1327781A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- self
- flow channel
- impeller
- centrifugal pump
- priming centrifugal
- 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.)
- Granted
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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
- 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
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- 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
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- 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
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- 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 with a suction cover with suction opening, an impeller, a flow channel housing accommodating the impeller, a pressure-side opening in the flow channel housing and an interrupter area in the Circumferential area between the pressure-side opening and the suction opening.
- Centrifugal pumps have long been known in the art, e.g. from the German published application No. 44 00 289. Centrifugal pumps generally have a suction cover, an impeller and a flow channel housing receiving the impeller. There are also a suction opening and a pressure-side outlet opening is provided. In contrast, a self-priming centrifugal pump has the peculiarity that the actual suction opening is not provided centrally on the suction cover is and that offset in the circumferential direction to this and usually on the suction cover opposite side, an outlet opening is provided, the suction opening and the pressure side Effective opening separated from each other by a so-called interrupter area become.
- the interrupter area In order to Intake opening and pressure outlet opening always remain separate from each other, without having to worry about larger ones Pressure equalization can take place across cross sections, the interrupter area must be circumferential have a length of at least two impeller chambers, being the impeller chamber the volume between two adjacent paddle wheels is designated. If then moving a paddle wheel chamber to that when moving across the break area section of the flow channel on the suction side is located, coming from the pressure side, the next following paddle wheel chamber is completely in the breaker area and is finished with it.
- suction cover, impeller and flow channel housing from a the requirements of sterility enough material is made and / or coated with such a material, and that suction cover and flow channel housing as well as all other static ones acted upon by the pump medium Components of the pump with the function rooms exposed and from the pump medium well loaded seals are sealed against each other.
- the manufacture of the components acted upon by the pump medium is one of the sterility requirements sufficient material or at least the coating of the components with such Material a necessary conditions, without the fulfillment of which the invention is based Task would not be solved.
- meeting this requirement creates new difficulties with it, because at least some of these materials are suitable for sterile applications Have properties that make them less suitable for use with a self-priming pump make it seem appropriate. While e.g.
- the seals become the pumping medium deliberately exposed.
- the seals are preferably arranged so that the Pump medium acting on seals does not have to pass through narrow sections whose cross-section would be significantly (by a factor of 2 or more) smaller than the areas to be covered Seal itself.
- the seals can e.g. be arranged in whole or in part so that the extension of the wall contour of the surfaces sealed against each other in the pump in the Cross section of the seal falls.
- the seals are at least slightly bulging which complemented smooth (i.e. essentially straight and concave with no avoidable curvatures) Area of the inner surface of the housing parts.
- the pump components be designed in the area of the seals so that the inner component surfaces, the adjacent to the surfaces that come into contact with the seals, below a relatively small Radius of curvature, typically on the order of 5 mm or less, from the surface bend the seal away or at an angle greater than 30 ° from the surface or extend a tangent to the surface of the seal.
- the width or smallest dimension of the opening between the seal and the remaining space with pump medium is at least 0.5 mm.
- Aspect ratio of a corresponding aperture defined as the depth to width ratio of the Access opening or an access channel to the seal, at most 2 and preferably less be as 1. It is essential in any case that neither in front of the seals nor at the transition narrow and deep gaps or even clear gaps between the seals and the adjacent surfaces Undercuts arise that are poor from the pumping medium and / or a cleaning agent can be flushed.
- the sealing wall sections of the pump components should therefore do not hit the sealing surface with the largest possible angle at less than 30 °.
- the wall section in question should be at least with a relatively small radius of curvature less than 5 mm from the surface of the seal bend away so that any remaining wedge-shaped gap between the seal and adjacent wall section has only a very small depth and can therefore be easily rinsed out can.
- the seals advantageously have a cross section of at least 4 to 8 mm 2 .
- the gap width 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 section that runs along the circumference of the impeller is less than 0.5 mm, preferably less than 0.3 mm.
- a gap width of 0.2 mm or less can be maintained at all times and in the interrupter area this small gap distance can also be compared to that Suction cover opposite wall of the flow channel housing are observed.
- a Seal is preferably located in the corner area between the suction cover and the one attached there Edge of the flow channel housing and is to the rear away from the corresponding corner of the Impeller blades offset by approximately 0.5 mm. That means the sealing surface jumps opposite an imaginary (straight or concave) transition in the corner between the suction cover and flow channel housing by about 0.2 to 0.3 mm.
- the flow channel is preferably in the radial direction expanded, that is, it has, with the exception of the immediately adjacent to the suction cover and the Seal in this area bearing section, a significantly larger diameter than that Wheel.
- the flow channel also runs parallel to the space acted upon by the impeller blades, whereby during a pumping process a toroidal vortex in the flow channel and the immediately adjacent one, the pump chamber acted upon by the impeller.
- This torus begins in the area of the intake opening and ends at the pressure-side outlet opening, so it is not complete, but through the Interrupt area interrupted.
- the flow channel tapers in the direction of the discharge opening on the pressure side, this tapered section also being referred to by experts as a "worm process" referred to as.
- Radial within this appendix is in the wall of the flow channel housing a vent hole is provided for the gas, which may be at the beginning a suction process has been sucked in by the pump or which may have been Degassing is released from the pump medium.
- a pressure chamber is also provided, which is the preferred one Embodiment of the invention runs essentially parallel to the flow channel and partially also encloses the flow channel or the flow channel housing.
- the pressure room finally opens into a radial or tangential outlet nozzle.
- the pressure space is expediently formed by the interior of a pot-shaped housing, which has an additional central hole for the passage of a drive shaft for the impeller.
- the outside diameter of the pressure chamber housing is preferably the same as the outside diameter of the flow channel housing, the latter, however, a step-shaped on its outside Has taper whose outer diameter is essentially the inner diameter corresponds to the pressure chamber housing, so that this from the outside onto the flow channel housing can be put on and takes up the aforementioned step-shaped taper. On the outside then close the flow channel housing with its expanded portion and that Pressure chamber housing flush with each other.
- the drive shaft expediently runs through a central bore of the pressure chamber housing and also the flow channel housing and is in sealed in this area with a sliding seal.
- the shaft is also still in the Area of the suction cover stored in a plain bearing.
- the plain bearing can also if necessary be integrally formed with the impeller, the impeller not only in the circumferential direction with the Shaft is non-positively connected, but is also fixed in the axial direction on the shaft.
- the impeller as precisely within the pump housing, i.e. between the suction cover and suction channel housing and in particular in the interrupter area that the small gap seal distances between the edges of the impeller and the suction cover or the flow channel housing of less than 0.2 mm must be observed.
- the self-priming centrifugal pump an additional non-self-priming centrifugal pump stage.
- This centrifugal pump stage expediently has the same outside diameter and also a stepped shape Taper, as previously described for the flow channel housing, wherein the suction cover of the self-priming pump is pot-shaped and similar to this was previously described between the pressure chamber housing and flow channel housing, the tapered Section of the housing of the upstream non-self-priming centrifugal pump comprises.
- the upstream, non-self-priming centrifugal pump increases the pumping capacity of the overall system and also helps to avoid cavitation effects could be because of the pressure differences occurring in the self-priming pump be reduced.
- Flow channel housings can be used as material for the pump according to the invention, in particular for suction covers and possibly also a stainless steel for the impeller, e.g. Chromium-molybdenum-nickel steel can be used, which can be easily forged and processed.
- a stainless steel for the impeller e.g. Chromium-molybdenum-nickel steel can be used, which can be easily forged and processed.
- plastic materials or a plastic coating can also be used come.
- the impeller or its coating can also be made in one piece with that in a central bore of the suction cover arranged slide bearing can be integrally formed.
- the self-priming pump designated overall by 20 in FIG. 1, essentially consists 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, which is a central Has intake manifold 1, and a pressure chamber housing 8, which has a tangential pressure nozzle or outlet nozzle 16.
- the pressure housing 8, the flow channel housing 6 and the suction cover 2 has a cylindrical circumference with essentially the same outside diameter, wherein the suction cover 2 and the flow channel housing 6 have a stepped taper have, whose outer diameter each the inner diameter of the next part corresponds so that the flow channel housing 6 can be inserted into the pressure housing 8 can, while the suction cover with its tapered section in the axially projecting Edge part of the flow channel housing 6 can be added.
- the suction cover 2 also has a cylindrical circumferential rim, which in turn the tapered cylindrical portion of a Housing cover 12 picks up.
- the housing cover 12 has a laterally protruding one Flange edge with fastening holes through which fastening bolts 18 extend, which the four essential and put together into an approximately cylindrical unit Parts, namely the housing cover 12, the suction cover 2, the flow channel housing 6 and press the pressure housing 8 onto the bracket 17 of a corresponding engine block, which here is not shown and by which the shaft 10 is driven in rotation.
- the individual blades 25 of the impeller 5 are in the axial view shown in Figure 1 in essentially rectangular, plate-shaped parts, which, however, beveled towards their edges or “sharpened", which is due to the prismatic edge surfaces of the blades in the upper area of the impeller is indicated in Figure 1.
- the suction cover 2 has a suction opening 3 in its lower area in FIG. 1 and is otherwise completely closed, ie it covers the impeller 5 with the exception of the area the suction opening 3.
- the suction cover 2 lies on a flat peripheral surface of the flow channel housing 6 and is sealed against the flow channel housing 6 via a seal 14.
- the flow channel housing has approximately the shape of a torus, from which parts are cut away are so that the impeller 5 can rotate freely inside the torus about its axis and the impeller blades 25 cover about half of the free toroidal cross section.
- flow channel 7 Especially the cross-sectional area of the flow channel housing not acted upon by the impeller blades 25 6 is referred to as flow channel 7.
- This flow channel 7 is axially offset parallel to the cylindrical volume acted upon and swept by the impeller blades 25, but is also radial compared to the area impinged by the impeller blades Slightly expanded towards. Due to the dynamic flow conditions during operation of the pump forms a more or less spiral vortex during operation in the flow channel 7, the both the area of the chambers between the blades and the area of the flow channel 7 detected outside the impeller chambers. The radial expansion of the flow channel 7 serves especially the unhindered formation of this vortex.
- the flow channel 7 extends however, not over the entire circumference of the flow channel housing 6, as is best recognizes with the help of FIG.
- Figure 4 corresponds essentially to a plan view of Figure 1 from the left, but with 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 would be the suction opening 3 of the suction cover in a lower right in the area of the intake duct 7 are indicated by a dashed circle position. As you can see The flow channel 7 begins there with the so-called suction area 7 ', the diameter the suction opening is adapted to the width of the flow channel 7 (slightly larger than the dashed line Circle at 7 '). The impeller 5 with the impeller blades 25 rotates counter to that in FIG Clockwise.
- the outlet opening 26 on the pressure side is offset by approximately 270 ° with respect to the suction region 7 ' in the area of the maximum pressure in the flow channel 7. Behind it begins an increasing tapering area of the flow channel, which experts call the "worm process” 7 referred to as.
- This worm process 7 in the form of a gradual tapering of the flow channel 7 behind the outlet opening 26 ends immediately radially outside a degassing opening 19 in the housing 6 of the flow channel 7.
- This degassing bore 19 serves for the exit of the Suction process or other gases entrained in the pumping medium during pumping can also arise from degassing processes of the pump medium, if this corresponds contains dissolved gases.
- the liquid concentrates more in the radially outer area, while gases accumulate in the radially inner area of the impeller, so that consequently also the degassing opening 19 can be found at the radially inner attachment area of the individual blades 25.
- the appendix forms with the Degassing opening 19 a bypass to the pressure-side outlet opening 26, through which also Part of the pump medium is transferred from the flow channel 7 of the pump 20 into the pressure chamber 9 becomes.
- the pressure region 7 ′′ and the degassing opening 19 are at a distance from one another in the circumferential direction the suction opening 3 or the beginning of the flow channel 7, which is approximately that in the circumferential direction corresponds to the measured width of two pumping chambers, one pumping chamber as the volume enclosed between two impeller blades 25 is defined.
- the radial expansion of the flow channel 7 is also in the interrupter area 22 reduced to a narrow gap S2, which is kept as small as possible without it due to vibrations or tolerance deviations from touching the blade edges the flow channel housing 6 can come.
- the edges of the impeller blades 25 have the inner wall of the impeller cover a very small distance S1, which is typically not more than 0.2 mm. Also to the circumferential wall section of the flow channel housing 6 has the outer Edge of the impeller blade 25 only a very small distance according to the specified Gap S2, which is slightly larger than gap S1, but not 0.5 mm if possible should exceed. Note that in the breaker area 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 shown in FIG. 2 the radial expansion of the flow channel can also be seen from FIG.
- the seal 14 is in corresponding recesses of the suction cover 2 and the adjacent one Wall of the flow channel housing 6 added, these recesses in proportion are dimensioned to the diameter of the cylindrical sealing ring cross section such that the sealing ring 14 when touching the mutually facing wall sections of the suction cover 2 and the flow channel housing 6 is squeezed by dimension S3.
- 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 with the curved corner area on the Outside of the flow channel housing 6 can come into sealing contact.
- Figure 3 recognizes the seal 15, the recess in the wall of the pressure chamber housing 8 and Curvature of the wall of the flow channel housing 6 is formed so that the dashed lines Projections or extensions of the corresponding wall sections in the sealing cross section fall.
- the arrangement of the seal 13, and also the seal 23 in the area of the Impeller nut 11 and the shaft or a corresponding cylindrical extension of the impeller 5 is designed so that no narrow and deep gaps form between the seal and sealing surfaces can.
- the impeller 5 is integral with a cylindrical approach 24 formed and the slide bearing 4 can be made in one piece or in whole be formed with this cylindrical approach 24.
- This slide bearing 4 enables one very precise mounting of the impeller 5 or the shaft 10, which also has a sliding seal 21 is sealed off from the pressure chamber housing 8 and the flow channel housing 6.
- FIG. 5 shows a further embodiment of the present, which is preferred for some applications Invention, in which the self-priming pump 20 additionally a non-self-priming Centrifugal pump stage 30 is connected upstream of a conventional type.
- the term "more conventional Type" refer only to the principle of operation of the centrifugal pump 30, which in the rest has a special modular design, so that it can be easily used with the one shown in FIG Self-priming pump 20 can be assembled in the embodiment 5 is contained identically. The transition from the pump according to Figure 1 to the pump 5 is done simply by the cover 12 from the self-priming pump 20th solved and replaced by the centrifugal pump module 30.
- the impeller 35 of the centrifugal pump is driven either by an appropriate connection with the cylindrical approach of the impeller 5 or but by a correspondingly lengthened, exchanged shaft 10 ', which extends through the impeller 5 extends through and into the impeller 35. All other components of the shown in Figure 1 Pumps can continue to be used identically.
- the seals 13 have the same arrangements and cross sections like the new seals 13 'to be added.
- the upstream normal and not self-priming centrifugal pump 30 has the effect that the overall pump capacity is increased and the pressure drop in the self-priming pump 20 is less pronounced, so that there is cavitation in such a construction, as in some pump media can occur, can be avoided more easily.
- the upstream centrifugal pump 30 does not achieve any self-priming conditions worth mentioning Suction effect, but the suction takes place initially only through the self-priming Pump 20, which sucks the medium to be pumped through the upstream centrifugal pump 30. As soon as this suction process is complete and the corresponding liquid Pump medium flows into the upstream centrifugal pump 30, this also develops a noticeable Additional pumping action, so that the entire pump then has a correspondingly higher pumping capacity shows.
- centrifugal pump module 30 instead of only one centrifugal pump module 30, several such modules are also used can be connected upstream, as is also the case in the parallel and not yet published German patent application No. 100 33 402.4 of the same applicant is disclosed.
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- Engineering & Computer Science (AREA)
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- Exhaust-Gas Circulating Devices (AREA)
- External Artificial Organs (AREA)
Abstract
Description
- Figur 1
- eine erste Ausführungsform der erfindungsgemäßen Pumpe in einem axialen Schnitt,
- Figur 2
- ein Detail aus Figur 1 im Bereich der Dichtung 14,
- Figur 3
- einen vergrößerten Ausschnitt aus Figur 1 im Bereich der Dichtung 15,
- Figur 4
- die Draufsicht auf ein offenes Strömungskanalgehäuse mit einem darin angeordneten Laufrad, entsprechend einer Ansicht auf Figur 1 von links ohne Saugdeckel und Pumpengehäusedeckel und
- Figur 5
- einen axialen Schnitt durch eine zweite Ausführungsform.
Claims (22)
- Selbstansaugende Kreiselpumpe mit einem Saugdeckel (2) mit Ansaugöffnung (3), einem Laufrad (5), einem das Laufrad (5) aufnehmenden Strömungskanalgehäuse (6), einer druckseitigen Öffnung im Strömungskanalgehäuse (6) und einem im Umfangsbereich zwischen der druckseitigen Öffnung und der Ansaugöffnung (3) vorgesehenen Unterbrechungsbereich (22), dadurch gekennzeichnet, daß alle mit dem Pumpmedium beaufschlagten Teile der Pumpe aus einem Sterilitätsanforderungen genügenden Material hergestellt oder mit einem solchen beschichtet sind und daß der Saugdeckel (2) und das Strömungskanalgehäuse (6) sowie alle weiteren vom Pumpmedium beaufschlagten, statischen Bauelemente der Pumpe mit zu den Funktionsräumen hin freiliegenden Dichtungen gegeneinander abgedichtet sind.
- Selbstansaugende Kreiselpumpe nach Anspruch, dadurch gekennzeichnet, daß die Querschnittskontur der Dichtungen (13, 14, 15) in die in den Bereich der Dichtungen fortgesetzt gedachte Kontur der Innenflächen der Bauelemente der Pumpe hineinragt.
- Selbstansaugende Kreiselpumpe nach Anspruch 1, bei welcher die Kontur mindestens einer der Dichtungen (13, 14, 15) nicht in den Bereich der Dichtung fortgesetzt gedachte Kontur der Innenwände der Pumpenbauteile hineinragt, so daß die Dichtung vollständig in einer hinter die Kontur der Innenflächen der Pumpe zurückspringenden Ausnehmung aufgenommen sind, dadurch gekennzeichnet, daß die verbleibende Verbindungsöffnung zwischen der Oberfläche der Dichtung und dem vom Pumpmedium beaufschlagten Innenraum im Querschnitt ein Aspektverhältnis von < 2, vorzugsweise von < 1 hat.
- Selbstansaugende Kreiselpumpe nach Anspruch 3, dadurch gekennzeichnet, daß die Zugangsöffnung die Form eines Spaltes mit einer minimalen Spaltbreite von 0,5 mm hat.
- Selbstansaugende Kreiselpumpe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die vom Pumpmedium beaufschlagbare Fläche einer Dichtung höchstens das Zweifache des freien Querschnitts einer vom Innenraum der Pumpe zu dieser Fläche führenden Zugangsöffnung beträgt.
- Selbstansaugende Kreiselpumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Dichtungen im wesentlichen Dichtringe mit kreisförmigem oder elliptischem Querschnitt sind.
- Selbstansaugende Kreiselpumpe nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die an die Kontaktflächen mit den Dichtungen angrenzende Flächenabschnitte der Pumpenbauteile unter einem Krümmungsradius, der höchstens dem Dreifachen des Krümmungsradius des Dichtringquerschnittes entspricht, von der Oberfläche des Dichtringes weg gekrümmt ist oder unter einem Winkel von mindestens 30° zu einer Tangente an die Oberfläche des Dichtringes verlaufen.
- Selbstansaugende Kreiselpumpe nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß das Laufrad (5) abgedichtet auf der Welle (10) der Pumpe (20) montiert ist.
- Selbstansaugende Kreiselpumpe nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, daß der Strömungskanal (7) mit Ausnahme des Unterbrecherbereiches (22) auch in dem das Laufrad umgreifenden Bereich in radialer Richtung erweitert ist.
- Selbstansaugende Kreiselpumpe nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß der Strömungskanal an seinem der Ansaugöffnung (3) in Umfangsrichtung entfernten Ende kurz vor dem Unterbrechungsbereich einen sich verjüngenden Druckabschnitt (7") mit einer Austrittsöffnung in einen Druckraum (9) aufweist, wobei vorzugsweise zusätzlich radial innerhalb des sich verjüngenden Kanalbereiches eine Entgasungsbohrung (19) das vom Laufrad beaufschlagte Volumen mit dem Druckraum (9) verbindet.
- Selbstansaugende Kreiselpumpe nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß die Spaltbreite zwischen den Schaufelkanten des Laufrades (5) einerseits und der Saugscheibe (2) sowie der Wand des Strömungskanalgehäuses (6) im Unterbrecherbereich (22) sowohl axial als auch radial kleiner als 0,5 mm und vorzugsweise kleiner als 0,3 mm ist.
- Selbstansaugende Kreiselpumpe nach Anspruch 11, dadurch gekennzeichnet, daß die axiale Spaltbreite im Unterbrecherbereich beidseitig 0,2 mm oder weniger beträgt.
- Selbstansaugende Kreiselpumpe nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, daß ein zum Strömungskanal (7) weitgehend paralleler und den Strömungskanal (7) teilweise umschließender Druckraum (9) vorgesehen ist, der in einen radialen oder tangentialen Druckstutzen (17) mündet.
- Selbstansaugende Kreiselpumpe nach Anspruch 13, dadurch gekennzeichnet, daß der Druckraum (9) durch das Innere eines topfförmigen Gehäuses (8) gebildet wird, welches mit einer zentralen Bohrung für die Antriebswelle (10) des Laufrades (5) versehen ist.
- Selbstansaugende Kreiselpumpe nach Anspruch 14, dadurch gekennzeichnet, daß der Außendurchmesser des Druckraumgehäuses (8) gleich dem Durchmesser des Strömungskanalgehäuses (6) ist, welcher auf seiner Außenseite eine stufenförmige Verjüngung aufweist, deren Außendurchmesser dem Innendurchmesser des Druckraumgehäuses (8) entspricht.
- Selbstansaugende Kreiselpumpe nach einem der Ansprüche 1 bis 15, dadurch gekennzeichnet, daß die Welle im Druckraum (9) und am Übergang vom Druckraum (9) zum Pumpraum eine Gleitdichtung aufweist.
- Selbstansaugende Kreiselpumpe nach einem der Ansprüche 1 bis 16, dadurch gekennzeichnet, daß im Bereich des Saugdeckels (2) eine Lagerung der Welle (10) und/oder des mit der Welle (10) verbundenen Laufrades (5) in Form eines axialen Gleitlagers vorgesehen ist.
- Selbstansaugende Kreiselpumpe nach einem der Ansprüche 1 bis 17, dadurch gekennzeichnet, daß der Pumpe eine oder mehrere Stufen nicht selbstansaugender Kreiselpumpen vorgeschaltet sind.
- Selbstansaugende Kreiselpumpe nach einem der Ansprüche 1 bis 18, dadurch gekennzeichnet, daß Saugscheibe (2), Strömungskanalgehäuse (6), Druckraumgehäuse (8) und gegebenenfalls auch ein Eingangsstutzen (1) aus einem schmiedbaren Stahl, vorzugsweise aus einem Chrom-Molybdän-Nickel-Stahl mit geringem Kohlenstoffgehalt hergestellt sind.
- Vorrichtung nach Anspruch 19, dadurch gekennzeichnet, daß das Laufrad (5) im wesentlichen aus demselben Material hergestellt ist wie der Saugdeckel (2) und/oder das Strömungskanalgehäuse (6).
- Selbstansaugende Kreiselpumpe nach einem der Ansprüche 1 bis 20, dadurch gekennzeichnet, daß das Laufrad (5) aus einem mechanisch beständigen und chemisch widerstandsfähigen Kunststoff hergestellt oder mit einem solchen beschichtet ist.
- Selbstansaugende Kreiselpumpe nach Anspruch 21, dadurch gekennzeichnet, daß das Gleitlager (4) für die Welle im Bereich des Saugdeckels (2) mit dem Material des Laufrades (1) oder einer Laufradbeschichtung einstückig hergestellt ist.
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 true EP1327781A2 (de) | 2003-07-16 |
EP1327781A3 EP1327781A3 (de) | 2004-12-01 |
EP1327781B1 EP1327781B1 (de) | 2007-06-20 |
Family
ID=7711762
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03000155A Expired - Lifetime EP1327781B1 (de) | 2002-01-09 | 2003-01-04 | Selbstansaugende Kreiselpumpe |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP1327781B1 (de) |
AT (1) | ATE365275T1 (de) |
DE (2) | DE10200579B4 (de) |
DK (1) | DK1327781T3 (de) |
ES (1) | ES2289186T3 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014095843A1 (de) * | 2012-12-17 | 2014-06-26 | Siemens Aktiengesellschaft | Backup dichtung in kompaktbauweise bei einem gehäuse einer strömungsmaschine |
EP3287643A1 (de) * | 2016-08-24 | 2018-02-28 | Q.E.D. Environmental Systems, Inc. | Pumpe mit kantenmontierter o-ring-dichtung |
CN110017299A (zh) * | 2019-05-22 | 2019-07-16 | 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 |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2016193387A1 (de) * | 2015-06-03 | 2016-12-08 | Gea Tuchenhagen Gmbh | Laufrad für eine kreiselpumpe und kreiselpumpe |
DE102021122216A1 (de) | 2021-08-27 | 2023-03-02 | KSB SE & Co. KGaA | Geschlossene Dickschicht für Pumpen |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3551067A (en) * | 1969-01-22 | 1970-12-29 | Duriron Co | Lined corrosion resistant pump |
US5338151A (en) * | 1990-06-28 | 1994-08-16 | Robert Bosch Gmbh | Unit for delivering fuel from the fuel tank to the internal combustion engine of a motor vehicle |
DE4400289A1 (de) * | 1994-01-07 | 1995-07-13 | Klein Schanzlin & Becker Ag | Kreiselpumpe |
US5509779A (en) * | 1994-02-03 | 1996-04-23 | World Chemical Co., Ltd. | Self-priming chemical pump |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
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 |
DE29513904U1 (de) * | 1995-08-30 | 1997-01-09 | Sihi Gmbh & Co Kg | Seitenkanalkreiselpumpe mit Stufenpaketen in Blechkonstruktion |
DE10033402A1 (de) * | 2000-07-08 | 2002-01-24 | Hilge Philipp Gmbh | Kreiselpumpe |
-
2002
- 2002-01-09 DE DE10200579A patent/DE10200579B4/de not_active Expired - Fee Related
-
2003
- 2003-01-04 ES ES03000155T patent/ES2289186T3/es not_active Expired - Lifetime
- 2003-01-04 DE DE50307499T patent/DE50307499D1/de not_active Expired - Lifetime
- 2003-01-04 EP EP03000155A patent/EP1327781B1/de not_active Expired - Lifetime
- 2003-01-04 AT AT03000155T patent/ATE365275T1/de not_active IP Right Cessation
- 2003-01-04 DK DK03000155T patent/DK1327781T3/da active
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3551067A (en) * | 1969-01-22 | 1970-12-29 | Duriron Co | Lined corrosion resistant pump |
US5338151A (en) * | 1990-06-28 | 1994-08-16 | Robert Bosch Gmbh | Unit for delivering fuel from the fuel tank to the internal combustion engine of a motor vehicle |
DE4400289A1 (de) * | 1994-01-07 | 1995-07-13 | Klein Schanzlin & Becker Ag | Kreiselpumpe |
US5509779A (en) * | 1994-02-03 | 1996-04-23 | World Chemical Co., Ltd. | Self-priming chemical pump |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014095843A1 (de) * | 2012-12-17 | 2014-06-26 | Siemens Aktiengesellschaft | Backup dichtung in kompaktbauweise bei einem gehäuse einer strömungsmaschine |
CN104884742A (zh) * | 2012-12-17 | 2015-09-02 | 西门子公司 | 流体机械的壳体中紧凑构型的后备密封件 |
EP3287643A1 (de) * | 2016-08-24 | 2018-02-28 | Q.E.D. Environmental Systems, Inc. | Pumpe mit kantenmontierter o-ring-dichtung |
CN110017299A (zh) * | 2019-05-22 | 2019-07-16 | 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 |
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 |
Also Published As
Publication number | Publication date |
---|---|
EP1327781B1 (de) | 2007-06-20 |
DE10200579B4 (de) | 2013-06-06 |
DE50307499D1 (de) | 2007-08-02 |
EP1327781A3 (de) | 2004-12-01 |
DE10200579A1 (de) | 2003-07-10 |
ES2289186T3 (es) | 2008-02-01 |
DK1327781T3 (da) | 2007-10-15 |
ATE365275T1 (de) | 2007-07-15 |
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