EP0013942B1 - Centrifugal pump for liquids containing solids - Google Patents

Centrifugal pump for liquids containing solids Download PDF

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Publication number
EP0013942B1
EP0013942B1 EP80100220A EP80100220A EP0013942B1 EP 0013942 B1 EP0013942 B1 EP 0013942B1 EP 80100220 A EP80100220 A EP 80100220A EP 80100220 A EP80100220 A EP 80100220A EP 0013942 B1 EP0013942 B1 EP 0013942B1
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EP
European Patent Office
Prior art keywords
pump
impeller
housing
turnpin
face
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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
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EP80100220A
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German (de)
French (fr)
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EP0013942A3 (en
EP0013942A2 (en
Inventor
Hans Beham
Hans-Dieter Beham
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Beham Hans
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Individual
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Priority to AT80100220T priority Critical patent/ATE8924T1/en
Publication of EP0013942A2 publication Critical patent/EP0013942A2/en
Publication of EP0013942A3 publication Critical patent/EP0013942A3/en
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Publication of EP0013942B1 publication Critical patent/EP0013942B1/en
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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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/049—Roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous

Definitions

  • the invention relates to a centrifugal pump according to the preamble of claim 1.
  • Centrifugal pumps of a type deviating from the preamble of patent claim 1 are also known, in which the annular closure member forming the liquid inlet is arranged on the same housing end face on which the drive shaft also enters the pump housing.
  • the liquid enters the pump housing from above and is discharged via a tangential outlet line.
  • the bearings of the drive shaft are not under the liquid pressure of the flow, but only under the hydrostatic pressure of the liquid on the pump, which, however, is relatively low compared to the liquid pressure of the flow, so that these pumps seal the bearings against the Liquid with relatively long terms is possible.
  • such pumps cannot be used for a number of applications.
  • a centrifugal pump in particular a heating circulation pump, has also become known from DE-PS 1 276450, which comprises a pump impeller which is mounted in a surrounding pump housing, a drive shaft which is in positive engagement with the pump impeller and is guided in the pump housing and which. penetrates an end face of the pump housing, and sealing elements are provided for sealing the housing interior against the bearing of the impeller. Furthermore, to remove the impeller on the housing end face facing away from the drive shaft, a terminating member is detachably fastened, at the outer end of which a fixed receptacle is provided for a central bearing journal running to the pump housing for mounting the pump impeller.
  • the low-pressure side of this known centrifugal pump lies on the side of the pump housing facing the drive shaft, while the high-pressure side is formed in the region of the closing element.
  • this has several disadvantages.
  • this pump when replacing an impeller, the high-pressure nozzle that leads to the high-pressure line must always be unscrewed or uncoupled. Above all, however, this pump is not suitable for pumping aggressive liquids, in particular also media containing solids, such as liquid manure.
  • a seal with a stopper is arranged on the low-pressure side, but since only a slide bearing is provided on the high-pressure side in this known pump, this is attacked and impaired by the aggressive medium.
  • this slide bearing is increasingly damaged and deflected by the pressure surges that occur.
  • a further impairment arises from the long-fiber components in the medium to be pumped, which lead to windings in the known pump on the high-pressure side and further impair the function of the sealing effect.
  • the seal provided on the low-pressure side is also affected and attacked by possible cavitation impacts due to the inertia of fiber solids in the medium to be conveyed.
  • a pump with an internal high pressure side has also become known from US Pat. No. 3,155,043.
  • bores are provided in the rotor through which the medium to be conveyed is connected to a slide bearing of the rotor in the housing.
  • This pump too, is therefore due to the disadvantages described above for conveying aggressive media interspersed with solid parts, such as, for. B. Manure unsuitable, since this plain bearing is severely attacked and impaired in this case by the aggressive medium.
  • Another disadvantage of this known pump is that enormous impacts occur when pumping medium permeated with solids, by means of which such a bearing is knocked out after a short time without the possibility of collecting these pressure loads.
  • the main advantage of the subject matter of the invention is that the annular space formed by the inner surface of the impeller and the bearing journal at its inner end, i. H. That end, which faces the driver of the drive shaft, can be sealed absolutely hermetically against the liquid pressure of the delivery flow, since a seal provided for this purpose is not axially penetrated by a component, for example the drive shaft.
  • the development according to claim 5 ensures that the gap between the envelope jacket of the impeller and the envelope jacket defined by the inner surface of the cage web or the inner surface of the cage webs can be adjusted depending on the respective state of wear.
  • the development according to claim 6 ensures that the bearing of the impeller at the outer end of the journal is relatively insensitive to the ingress of liquid due to the hydrostatic pressure, in contrast to a ball bearing.
  • the eccentricity play of the drive shaft is reliably limited at its end facing the bearing journal, which can be important in particular in the event of intermittent radial loads on the impeller by suction of solids and in the limitation of resonance vibration amplitudes of the drive shaft.
  • the embodiment according to claim 10 ensures that the contact surface of the eccentricity limitation bearing can be relatively large, so that its wear can be neglected over the entire service life of the pump.
  • the centrifugal pump illustrated there comprises a four-bladed pump impeller 1, which is mounted in a surrounding pump housing 2 of circular cross section.
  • an annular end member 3 is detachably fastened by means of a plurality of screws 4 distributed over the circumference.
  • the end member 3 comprises at its outer end facing away from the pump housing 2 a receptacle 5 for a central bearing journal 6.
  • the receptacle 5 is via two diametrical eccentric cage webs 7, which diverge conically towards the pump housing 2, with the circumference of a component of the end member 3 forming base ring flange 8 connected.
  • the edges 9 of the webs 7 opposite the jacket envelope of the impeller 1 can be provided with hard metal build-up welding beads to form tear edges. This also applies to the outer edges of the impeller 1 that define a jacket envelope.
  • the bearing pin 6 is clamped in the receptacle 5 by means of centering screws 10 and can be adjusted axially for adjustment purposes in order to adjust the annular gap between the edges 9 of the webs 7 and the imaginary envelope of the impeller 1 to a predetermined favorable value, without prejudice to possible wear the edges of the blades of the impeller 1 or the edges 9 of the webs 7 cooperating therewith.
  • the bearing journal 6 receives a radial / axial ball bearing 11 which is held axially immovably by means of a snap ring 12 .
  • the outer ring of the ball bearing 11 is pressed into an axial bore at the inner end of the impeller 1 and there secured by a snap ring 13 against axial displacement.
  • the impeller 1 is mounted by means of a plain bearing 14. Downstream of the slide bearing in the direction of the outer end of the journal 6 is an axial seal or stuffing box seal 15, on which only the hydrostatic pressure of the liquid on the pump acts.
  • the inner cross section of the axial bore of the impeller 1 adjacent to the end face of the inner end of the bearing journal 6 or adjacent to the ball bearing 11 is hermetically sealed against the liquid pressure of the delivery flow of the pump by means of a cap-like plastic plug 16.
  • the annular space 17 formed by the bearing journal 6 and the inner surface of the impeller 1 surrounding it is filled with bearing grease from the plain bearing 14 to the stopper 16.
  • a jacket tube 20 is fastened by means of a diametrically divided clamping flange 18, the segments of which are connected to the pump housing 2 by means of screws 19, which serves to encapsulate a drive shaft 21 running essentially centrally therein.
  • a flange-like driver 23 is fastened on the drive shaft 21 by means of a heavy-duty spring pin 22, which engages with corresponding end cuts of the impeller 1 via a plurality of axial driver claws 24 distributed over the circumference.
  • the driver 23 is received at an end portion with radial play in the central bore of the impeller 1, in which the ball bearing 11 is also seated.
  • the driver 23 and indirectly also the drive shaft 21 is assigned an eccentricity limiting bearing 25 which is held with centering projections 26 in the associated end face of the pump housing 2 and is held in position by means of the screws 19 by the segments of the clamping flange 18.
  • the central bore of the eccentricity limiting bearing 25 has a larger diameter than the outer diameter of the surrounding assigned section of the driver 23, so that the drive shaft 21 has a total of a certain radial play both with respect to the eccentricity limiting bearing 25 and with respect to the impeller 1.
  • the centrifugal pump is arranged below a liquid level S.
  • the liquid to be conveyed reaches the region of the impeller on the two webs 7 according to the curved arrows Pf and is conveyed upward into the impeller housing 2, where it exits through a tangential outlet pipe 27.
  • the liquid pressure specific to the pump is only reached in the pump housing 2, so that, as has already been mentioned in the introduction, the plain bearing 14 is only under the hydrostatic pressure of the liquid.
  • the plug 16 is under the full liquid pressure of the flow, but a hermetic seal is achieved because the plug 16 is neither penetrated by the journal 6 nor by the drive shaft 21.

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

Abstract

1. A centrifugal pump for liquids mixed with solids and more specially for liquids mixed with fibrous substances, comprising, a pump impeller (1) bearinged in a pump housing (2) placed round it, a driving shaft (21), that is positively joined to the pump impeller (1) and is guided in said pump housing (2), said driving shaft (21) running through an end face of the pump housing (2), and sealing elements for sealing off the space inside said housing from the bearing means of the impeller, and to make it possible for the pump impeller to be dismounted a termination member (3) is fixed to, and may be taken off, the end face of the housing furthest from the drive shaft, and on the outer end of the member (3) is fixed to, and may be taken off, the end face of the housing furthest from the drive shaft, and on the outer end of the member (3) there is fixed take-up means (5) for a middle turnpin (6), pointing towards the pump housing, for bearing the pump impeller (1), characterized in that the high pressure side of the pump is at the end, nearest the driving shaft (21), of the turnpin (6), and the low pressure side is at the termination member (3), and the termination member (3) has the function of the liquid inlet and in that on the high pressure side the ring-like space (17) walled off by the inner face of the pump impeller (1) and by the turnpin (6) is fluid-tightly shut off from the pump housing (2) by way of a stopper (16) and the drive motor is placed higher up than the level (S) of the liquid.

Description

Die Erfindung betrifft eine Kreiselpumpe nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a centrifugal pump according to the preamble of claim 1.

Bei bekannten Kreiselpumpen durchsetzt die Antriebswelle das Pumpengehäuse auf seiner gesamten axialen Länge und ist an beiden Stirnflächen des Pumpengehäuses gelagert. Auf der Antriebswelle sitzt das Laufrad. Bei derartigen Pumpen ist es nur unter Inkaufnahme eines unvertretbar hohen Aufwandes möglich, die Lager der Antriebswelle bzw. des Laufrades gegenüber dem Flüssigkeitsdruck des Förderstromes abzudichten. Eine Abdichtung mit üblichen Stopfbüchsen, die naturgemäß dem Verschleiß unterliegen, ist nicht dauerhaft. Wenn die zu fördernden Flüssigkeiten aggessiv sind, beispielsweise im Falle von Gülle, werden beim Eindringen der Flüssigkeit die Lager in kurzer Zeit durch Korrosion zerstört. Dies erfordert eine Grund- überholung der Pumpe beim Herstellen oder in einer spezialisierten Werkstatt.In known centrifugal pumps, the drive shaft passes through the pump housing over its entire axial length and is mounted on both end faces of the pump housing. The impeller sits on the drive shaft. With pumps of this type, it is only possible with an unacceptably high outlay to seal the bearings of the drive shaft or the impeller against the liquid pressure of the delivery flow. Sealing with conventional stuffing boxes, which are naturally subject to wear, is not permanent. If the liquids to be pumped are aggressive, for example in the case of liquid manure, the bearings are destroyed by corrosion in a short time when the liquid penetrates. This requires a thorough overhaul of the pump during manufacture or in a specialized workshop.

Es sind auch Kreiselpumpen einer vom Oberbegriff des Patentanspruchs 1 abweichenden Art bekannt, bei denen das den Flüssigkeitseinlaß bildende ringförmige Abschlußglied an der gleichen Gehäusestirnfläche angeordnet ist, an welcher auch die Antriebswelle in das Pumpengehäuse eintritt. Bei vertikaler Anordnung der Antriebswelle tritt also die Flüssigkeit von oben her in das Pumpengehäuse ein und wird über eine tangentiale Auslaßleitung abgegeben. Bei derartigen Kreiselpumpen stehen die Lager der Antriebswelle nicht unter dem Flüssigkeitsdruck des Förderstromes, sondern lediglich unter dem hydrostatischen Druck der auf der Pumpe lastenden Flüssigkeit, der indessen gegenüber dem Flüssigkeitsdruck des Förderstromes verhältnismäßig gering ist, so daß bei diesen Pumpen eine Abdichtung der Lager gegenüber der Flüssigkeit mit verhältnismäßig langen Laufzeiten möglich ist. Jedoch sind derartige Pumpen für eine Reihe von Anwendungsfällen nicht verwendbar.Centrifugal pumps of a type deviating from the preamble of patent claim 1 are also known, in which the annular closure member forming the liquid inlet is arranged on the same housing end face on which the drive shaft also enters the pump housing. When the drive shaft is arranged vertically, the liquid enters the pump housing from above and is discharged via a tangential outlet line. In such centrifugal pumps, the bearings of the drive shaft are not under the liquid pressure of the flow, but only under the hydrostatic pressure of the liquid on the pump, which, however, is relatively low compared to the liquid pressure of the flow, so that these pumps seal the bearings against the Liquid with relatively long terms is possible. However, such pumps cannot be used for a number of applications.

Eine Kreiselpumpe, insbesondere Heizungsumwälzpumpe ist auch aus der DE-PS 1 276450 bekanntgeworden, die ein Pumpenlaufrad umfaßt, das in einem umgebenen Pumpengehäuse gelagert ist, wobei eine mit dem Pumpenlaufrad in Formschlußeingriff stehende sowie in dem Pumpengehäuse geführte Antriebswelle, die . eine Stirnfläche des Pumpengehäuses durchsetzt, und Abdichtelemente zur Abdichtung des Gehäuseinnenraums gegenüber der Lagerung des Laufrades vorgesehen sind. Ferner ist zur Entfernung des Laufrades an der von der Antriebswelle abgewandten Gehäusestirnfläche ein Abschlußglied lösbar befestigt, an dessen äußerem Ende eine feste Aufnahme für einen zum Pumpengehäuse verlaufenden zentralen Lagerzapfen zur Lagerung des Pumpenlaufrades vorgesehen. Die Niederdruckseite dieser bekannten Kreiselpumpe liegt auf der der Antriebswelle zugewandten Seite des Pumpengehäuses, während die Hochdruckseite im Bereich des Abschlußgliedes gebildet ist. Dadurch sind aber mehrere Nachteile bedingt. Zum einen muß bei dieser bekannten Pumpe beim Auswechseln eines Laufrades auch immer der Hochdruckstutzen, der zu der Hochdruckleitung führt, zunächst abgeschraubt bzw. abgekoppelt werden. Vor allem aber ist diese Pumpe nicht zum Fördern von aggressiven Flüssigkeiten, insbesondere auch von mit Feststoffen versetzten Medien wie beispielsweise Gülle geeignet. Zwar ist an der Niederdruckseite eine Dichtung unter anderem mit einem Stopfen angeordnet, da aber bei dieser bekannten Pumpe auf der Hochdruckseite lediglich ein Gleitlager vorgesehen ist, wird dieses durch das aggressive Medium angegriffen und beeinträchtigt. Insbesondere beim Abschalten von nachgeordneten Umschaltern und Ventilen wird durch die auftretenden Druckschläge dieses Gleitlager zunehmend beschädigt und ausgeschlagen. Eine weitere Beeinträchtigung entsteht durch die langfasrigen Bestandteile in dem zu fördernden Medium, die bei der bekannten Pumpe auf der Hochdruckseite zu Aufwicklungen führe und die Dichtwirkung in ihrer Funktion weiter beeinträchtigen. Ferner wird die auf der Niederdruckseite vorgesehene Dichtung auch durch mögliche Kavitationsstöße durch die Massenträgheit von Faserfeststoffen in dem zu fördernden Medium beeinträchtigt und angegriffen.A centrifugal pump, in particular a heating circulation pump, has also become known from DE-PS 1 276450, which comprises a pump impeller which is mounted in a surrounding pump housing, a drive shaft which is in positive engagement with the pump impeller and is guided in the pump housing and which. penetrates an end face of the pump housing, and sealing elements are provided for sealing the housing interior against the bearing of the impeller. Furthermore, to remove the impeller on the housing end face facing away from the drive shaft, a terminating member is detachably fastened, at the outer end of which a fixed receptacle is provided for a central bearing journal running to the pump housing for mounting the pump impeller. The low-pressure side of this known centrifugal pump lies on the side of the pump housing facing the drive shaft, while the high-pressure side is formed in the region of the closing element. However, this has several disadvantages. On the one hand, with this known pump, when replacing an impeller, the high-pressure nozzle that leads to the high-pressure line must always be unscrewed or uncoupled. Above all, however, this pump is not suitable for pumping aggressive liquids, in particular also media containing solids, such as liquid manure. Although a seal with a stopper is arranged on the low-pressure side, but since only a slide bearing is provided on the high-pressure side in this known pump, this is attacked and impaired by the aggressive medium. Particularly when switching downstream switches and valves, this slide bearing is increasingly damaged and deflected by the pressure surges that occur. A further impairment arises from the long-fiber components in the medium to be pumped, which lead to windings in the known pump on the high-pressure side and further impair the function of the sealing effect. Furthermore, the seal provided on the low-pressure side is also affected and attacked by possible cavitation impacts due to the inertia of fiber solids in the medium to be conveyed.

Auch aus der US-PS 3 155 043 ist eine Pumpe mit innenliegender Hochdruckseite bekanntgeworden. In dem Rotor sind jedoch Bohrungen vorgesehen, über die das zu fördernde Medium mit einer Gleitlagerung des Rotors im Gehäuse in Verbindung steht. Auch diese Pumpe ist von daher aufgrund der oben geschilderten Nachteile zum Fördern von mit Feststoffteilen durchsetzten aggressiven Medien wie z. B. Gülle ungeeignet, da dieses Gleitlager in diesem Falle von dem aggressiven Medium stark angegriffen und beeinträchtigt wird. Ein weiterer Nachteil bei dieser bekannten Pumpe wie bei der vorstehenden ist dadurch gegeben, daß beim Pumpen von mit Feststoffen durchsetzten Medium zusätzlich enorme Schläge auftreten, durch die ein derartiges Lager ohne Auffangmöglichkeit dieser Druckbelastungen bereits nach kurzer Zeit ausgeschlagen wird.A pump with an internal high pressure side has also become known from US Pat. No. 3,155,043. However, bores are provided in the rotor through which the medium to be conveyed is connected to a slide bearing of the rotor in the housing. This pump, too, is therefore due to the disadvantages described above for conveying aggressive media interspersed with solid parts, such as, for. B. Manure unsuitable, since this plain bearing is severely attacked and impaired in this case by the aggressive medium. Another disadvantage of this known pump, as in the case of the previous one, is that enormous impacts occur when pumping medium permeated with solids, by means of which such a bearing is knocked out after a short time without the possibility of collecting these pressure loads.

Demgegenüber ist es Aufgabe der Erfindung eine Kreiselpumpe zu schaffen, bei weicher das Abschlußglied, das Laufrad und die Lagerung des Laufrades eine gegen den Fiüssigkeitsdruck des Förderstromes insbesondere bei aggressiven mit Feststoffen versetzten Flüssigkeiten hermetisch abgeschlossene Baueinheit bildet, so daß insbesondere die Standzeit der Laufradlagerung nicht durch Korrosion seitens der zu fördernden Flüssigkeit beeinträchtigt werden kann.In contrast, it is an object of the invention to provide a centrifugal pump in which the sealing member, the impeller and the bearing of the impeller form a structural unit which is hermetically sealed against the liquid pressure of the flow, in particular in the case of aggressive liquids containing solids, so that in particular the service life of the impeller bearing is not reduced Corrosion on the part of the liquid to be pumped can be impaired.

Die Aufgabe wird erfindungsgemäß entsprechend den im kennzeichnenden Teil des Anspruches 1 angegebenen Merkmalen gelöst. Vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprüchen angegeben.The object is achieved according to the features specified in the characterizing part of claim 1. Advantageous embodiments of the invention are specified in the subclaims.

Der wesentliche Vorteil des Erfindungsgegenstandes besteht darin, daß der durch die Innenfläche des Laufrades sowie den Lagerzapfen gebildete Ringraum an dessen innerem Ende, d. h. demjenigen Ende, welches dem Mitnehmer der Antriebswelle zugewendet ist, absolut hermetisch gegen den Flüssigkeitsdruck des Förderstromes abgedichtet werden kann, da eine hierzu vorgesehene Dichtung nicht von einem Bauelement, beispielsweise der Antriebswelle, axial durchsetzt ist. Das äußere Ende des Ringraumes, welches dem Mitnehmer zugewendet ist, kann zwar nicht hermetisch gegenüber der Flüssigkeit abgedichtet werden, sondern es kann hier lediglich eine übliche Stopfbüchsdichtung verwendet werden, da das äußere Ende des Lagerzapfens den Ringraum hier durchsetzt, jedoch steht der Ringraum an diesem äußeren Ende des Lagerzapfens nicht unter dem Flüssigkeitsdruck des Förderstromes, sondern lediglich unter dem hydrostatischen Druck der auf der Pumpe lastenden Flüssigkeitssäule, der gegenüber dem Flüssigkeitsdruck des Förderstromes in den praktischen Anwendungsfällen als vernachlässigbar gering zu betrachten ist. Darüber hinaus ergibt sich als herstellungstechnischer Vorteil, daß die Baueinheit bestehend aus Abschlußglied, Laufrad, Lagerzapfen und Lagerung einerseits in unterschiedlichen Größen und Auslegungen hergestellt, andererseits aber ein und demselben Pumpengehäuse nebst Antriebswelle und Mitnehmer zugeordnet werden kann. Es ist also möglich, an ein und demselben Pumpengehäuse Baueinheiten bestehend aus Abschlußglied, Laufrad, Lagerzapfen und Lagerung von unterschiedlicher Förderleistung und sogar unterschiedlichen Laufradarten anzubringen, ohne daß hierzu Spezialwerkzeuge, insbesondere Abzieher erforderlich sind. Auch der Reparaturaustausch wird auf diese Weise erleichtert, weil in den meisten Fällen das Pumpengehäuse nebst Antriebswelle und Mitnehmer an Ort und Stelle verbleiben kann und lediglich die Baueinheit umfassend das Abschlußglied, das Laufrad, den Lagerzapfen und die Lagerung abgebaut werden muß. Dieser Abbau kann durch den Benutzer selbst, beispielsweise einen Landwirt, erfolgen und erfordert kein spezialisiertes Personal. Außerdem kann der Benutzer selbst durch Einsatz unterschiedlicher Baueinheiten die Pumpe auch an unterschiedliche Aufgaben anpassen. Ein weiterer Vorteil liegt darin, daß die Antriebswelle nur an dem vom Pumpengehäuse abgewendeten Ende gelagert werden muß, während sie an ihrem in das Pumpengehäuse verlaufenden Ende durch den Lagerzapfen des Laufrades über den Mitnehmer zentriert wird.The main advantage of the subject matter of the invention is that the annular space formed by the inner surface of the impeller and the bearing journal at its inner end, i. H. That end, which faces the driver of the drive shaft, can be sealed absolutely hermetically against the liquid pressure of the delivery flow, since a seal provided for this purpose is not axially penetrated by a component, for example the drive shaft. The outer end of the annular space, which faces the driver, cannot be hermetically sealed from the liquid, but only a conventional stuffing box seal can be used here, since the outer end of the bearing pin penetrates the annular space here, but the annular space stands on it outer end of the journal not under the liquid pressure of the flow, but only under the hydrostatic pressure of the liquid column on the pump, which is to be regarded as negligible compared to the liquid pressure of the flow in practical applications. In addition, there is a manufacturing advantage that the assembly consisting of end member, impeller, bearing journal and bearing manufactured on the one hand in different sizes and designs, but on the other hand, one and the same pump housing can be assigned together with the drive shaft and driver. It is therefore possible to attach units consisting of a terminating member, impeller, bearing journal and bearing of different delivery rates and even different types of impellers to one and the same pump housing without the need for special tools, in particular pullers. The exchange of repairs is also facilitated in this way, because in most cases the pump housing together with the drive shaft and driver can remain in place and only the structural unit comprising the end member, the impeller, the bearing journal and the bearing must be removed. This dismantling can be done by the user himself, for example a farmer, and does not require specialized personnel. In addition, the user can adapt the pump to different tasks by using different components. Another advantage is that the drive shaft only has to be supported at the end facing away from the pump housing, while it is centered at its end running into the pump housing by the bearing journal of the impeller over the driver.

Durch die Weiterbildung nach dem Patentanspruch 2 wird einerseits ein unbehinderter Flüssigkeitszutritt zu dem Laufrad ermöglicht, während andererseits an dem Steg auch noch eine aus verschleißfestem Hartmetall bestehende Reißkante angebracht werden kann, die mit der oder den Umfangskanten des Laufrades zusammenwirkt, um Feststoffe und Faserstoffe in der Flüssigkeit zu zerreißen oder zerkleinern. Durch die Ausgestaltung nach dem Patentanspruch 3, wird über die Merkmale des Patentanspruchs 2 hinausgehend ein besonders stabiler Aufbau mit einer Mehrzahl von Reißkanten erreicht. Durch die weitere Ausgestaltung nach dem Patentanspruch 4 wird eine Anpassung der Form des Abschlußgliedes an die hier verwandte und zur Niederdruckseite verlängerte Enveloppenfläche der Laufräder erzielt.Through the development according to claim 2, on the one hand, an unhindered liquid access to the impeller is made possible, while on the other hand, a tear-off edge made of wear-resistant hard metal can also be attached to the web, which cooperates with the peripheral edge or edges of the impeller to remove solids and fibrous materials in the Tear or crush liquid. Due to the configuration according to claim 3, a particularly stable structure with a plurality of tear edges is achieved in addition to the features of claim 2. Due to the further embodiment according to claim 4, an adaptation of the shape of the end member to the envelope surface of the impellers used here and extended to the low-pressure side is achieved.

Durch die Weiterbildung nach dem Patentanspruch 5 wird erreicht, daß der Spalt zwischen dem Enveloppenmantel des Laufrades und dem durch die Innenfläche des Käfigsteges bzw. die Innenfläche der Käfigstege definierten Enveloppenmantel in Abhängigkeit vom jeweiligen Abnutzungszustand justiert werden kann.The development according to claim 5 ensures that the gap between the envelope jacket of the impeller and the envelope jacket defined by the inner surface of the cage web or the inner surface of the cage webs can be adjusted depending on the respective state of wear.

Durch die Weiterbildung nach dem Patentanspruch 6 wird erreicht, daß die Lagerung des Laufrades am äußeren Ende des Lagerzapfens gegenüber dem Eindringen von Flüssigkeit aufgrund des hydrostatischen Druckes verhältnismäßig unempfindlich wird, im Gegensatz zu einem Kugellager.The development according to claim 6 ensures that the bearing of the impeller at the outer end of the journal is relatively insensitive to the ingress of liquid due to the hydrostatic pressure, in contrast to a ball bearing.

Durch die Weiterbildung nach dem Patentanspruch 7 wird erreicht, daß selbst beim Undichtwerden einer Dichtung am äußeren Ende des Lagerzapfens Flüssigkeit aufgrund des hydrostatischen Druckes nicht eindringen kann, da sich die praktisch inkompressible Fettfüllung in dem Ringraum gegen den Stopfen am inneren Ende des Lagerzapfens abstützen kann.The development according to claim 7 ensures that even if a seal leaks at the outer end of the journal, liquid cannot penetrate due to the hydrostatic pressure, since the practically incompressible grease filling in the annular space can be supported against the stopper at the inner end of the journal.

Durch die Weiterbildung nach dem Patentanspruch 8 wird eine günstige Zentrierung der Antriebswelle an ihrem in das Pumpengehäuse verlaufenden Ende erreicht, so daß es einer besonderen Lagerung der Antriebswelle an der zugeordneten Gehäusestirnfläche nicht bedarf. Dies ist deshalb wiederum günstig, weil sonst dieses Lager ebenfalls gegen das Eindringen von Flüssigkeit gekapselt werden müßte und einem beschleunigten Verschleiß aufgrund des Eindringens von Flüssigkeit unterliegen könnte.Through the development according to claim 8, a favorable centering of the drive shaft is achieved at its end extending into the pump housing, so that a special mounting of the drive shaft on the associated housing end face is not required. This is again favorable because otherwise this bearing would also have to be encapsulated against the penetration of liquid and could be subject to accelerated wear due to the penetration of liquid.

Durch die Weiterbildung nach dem Patentanspruch 9 wird das Exzentrizitätsspiel der Antriebswelle an ihrem dem Lagerzapfen zugewendeten Ende zuverlässig begrenzt, was insbesondere bei stoßweisen radialen Belastungen des Laufrades durch Einsaugen von Feststoffen und bei der Begrenzung von Resonanzschwingungsamplituden der Antriebswelle von Wichtigkeit sein kann. Durch die Ausgestaltung nach dem Patentanspruch 10 wird erreicht, daß die Berührungsfläche des Exzentrizitätsbegrenzungslagers verhältnismäßig groß sein kann, so daß dessen Abnützung über die gesamte Standzeit der Pumpe vernachlässigt werden kann.Through the development according to claim 9, the eccentricity play of the drive shaft is reliably limited at its end facing the bearing journal, which can be important in particular in the event of intermittent radial loads on the impeller by suction of solids and in the limitation of resonance vibration amplitudes of the drive shaft. The embodiment according to claim 10 ensures that the contact surface of the eccentricity limitation bearing can be relatively large, so that its wear can be neglected over the entire service life of the pump.

Wegen der zuverlässigen Begrenzung der Exzentrizitätsamplitude der Antriebswelle an ihrem in das Pumpengehäuse verlaufenden Ende wird die Weiterbildung gemäß dem Patentanspruch 11 möglich, deren wesentlicher Vorteil wiederum darin liegt, daß das Mantelrohr für die Antriebswelle in Anpassung an verschiedene Anwendungszwecke nicht in verschiedenen Längen bereitgehalten werden muß, da es beliebig ablängbar ist, während gemäß dem Stand der Technik, bei welchem beide Enden der Antriebswelle in dem Mantelrohr gelagert sind, dieses mit der Antriebswelle eine Baueinheit bildet, so daß für die verschiedenen Anwendungszwecke eine Anzahl unterschiedlich langer Baueinheiten bereitgehalten werden muß.Because of the reliable limitation of the eccentricity amplitude of the drive shaft at its end extending into the pump housing, the further development according to claim 11 is possible, the main advantage of which, in turn, lies in the fact that the casing tube for the drive shaft does not adapt to different applications in different lengths gene must be kept ready, since it can be cut to length, while according to the prior art, in which both ends of the drive shaft are mounted in the jacket tube, this forms a structural unit with the drive shaft, so that a number of differently long structural units are available for the various purposes must become.

Die Erfindung ist nachstehend anhand der Zeichnung näher erläutert. Es zeigt

  • Fig. 1 ein Ausführungsbeispiel einer erfindungsgemäßen Kreiselpumpe mit einem mehrere Flügel aufweisenden Pumpenlaufrad im Axialschnitt,
  • Fig. 2 ein gegenüber Fig. 1 abgewandeltes Ausführungsbeispiel einer erfindungsgemäßen Pumpe mit einem als konische Schnecke gestalteten Pumpenlaufrad in perspektivischer Darstellung.
The invention is explained below with reference to the drawing. It shows
  • 1 shows an embodiment of a centrifugal pump according to the invention with a pump impeller having several blades in axial section,
  • Fig. 2 shows a modified embodiment of a pump according to the invention with a pump impeller designed as a conical screw in a perspective view.

Gemäß Fig. 1 umfaßt die dort veranschaulichte Kreiselpumpe ein vierflügeliges Pumpenlaufrad 1, welches in einem umgebenden Pumpengehäuse 2 von Kreiselquerschnitt gelagert ist. An der unteren Gehäusestirnfläche ist ein ringförmiges Abschlußglied 3 mittels mehrerer über den Umfang verteilter Schrauben 4 lösbar befestigt. Das Abschlußglied 3 umfaßt an seinem von dem Pumpengehäuse 2 abgewandten äußeren Ende eine Aufnahme 5 für einen zentralen Lagerzapfen 6. Die Aufnahme 5 ist über zwei diametrale exzentrische Käfigstege 7, die zu dem Pumpengehäuse 2 hin konisch divergieren, mit dem Umfang eines einen Bestandteil des Abschlußgliedes 3 bildenden Basisringflansches 8 verbunden. Die der Mantelenveloppe des Laufrades 1 gegenüberstehenden Kanten 9 der Stege 7 können zur Bildung von Reißkanten mit Hartmetall-Auftragsschweißraupen versehen sein. Dies gilt auch für die eine Mantelenveloppe definierenden Außenkanten des Laufrades 1.1, the centrifugal pump illustrated there comprises a four-bladed pump impeller 1, which is mounted in a surrounding pump housing 2 of circular cross section. On the lower end face of the housing, an annular end member 3 is detachably fastened by means of a plurality of screws 4 distributed over the circumference. The end member 3 comprises at its outer end facing away from the pump housing 2 a receptacle 5 for a central bearing journal 6. The receptacle 5 is via two diametrical eccentric cage webs 7, which diverge conically towards the pump housing 2, with the circumference of a component of the end member 3 forming base ring flange 8 connected. The edges 9 of the webs 7 opposite the jacket envelope of the impeller 1 can be provided with hard metal build-up welding beads to form tear edges. This also applies to the outer edges of the impeller 1 that define a jacket envelope.

Der Lagerzapfen 6 ist in der Aufnahme 5 mittels Zentrierschrauben 10 festgeklemmt und kann zu Justierungszwecken axial verstellt werden, um den Ringspalt zwischen den Kanten 9 der Stege 7 und der gedachten Mantelenveloppe des Laufrades 1 auf einen vorgegebenen günstigen Wert einzustellen, unbeschadet von einem eventuellen Verschleiß an den Kanten der Flügel des Laufrades 1 bzw. den hiermit zusammenwirkenden Kanten 9 der Stege 7. An dem in das Pumpengehäuse 2 hinein verlaufenden inneren Ende nimmt der Lagerzapfen 6 ein Radial/ Axial-Kugellager 11 auf, das mittels eines Sprengringes 12 axial unverschieblich gehalten ist. Der äußere Ring des Kugellagers 11 ist in eine axiale Bohrung am inneren Ende des Laufrades 1 eingepreßt und dort durch einen Sprengring 13 gegen axiale Verschiebung gesichert. An dem äußeren Ende des Lagerzapfens 6 ist das Laufrad 1 mittels eines Gleitlagers 14 gelagert. Dem Gleitlager in Richtung zum äußeren Ende des Lagerzapfens 6 nachgeordnet ist eine Axialdichtung oder Stopfbüchsendichtung 15, auf welche lediglich der hydrostatische Druck der auf der Pumpe lastenden Flüssigkeit wirkt. Der Innenquerschnitt der axialen Bohrung des Laufrades 1 benachbart der Stirnfläche des inneren Endes des Lagerzapfens 6 bzw. benachbart dem Kugellager 11 ist mittels eines kappenartigen Kunststoffstopfens 16 hermetisch gegenüber dem Flüssigkeitsdruck des Förderstromes der Pumpe abgedichtet. Der durch den Lagerzapfen 6 und die diesen umgebende Innenfläche des Laufrades 1 gebildete Ringraum 17 ist von dem Gleitlager 14 bis zu dem Stopfen 16 mit Lagerfett gefüllt.The bearing pin 6 is clamped in the receptacle 5 by means of centering screws 10 and can be adjusted axially for adjustment purposes in order to adjust the annular gap between the edges 9 of the webs 7 and the imaginary envelope of the impeller 1 to a predetermined favorable value, without prejudice to possible wear the edges of the blades of the impeller 1 or the edges 9 of the webs 7 cooperating therewith. At the inner end running into the pump housing 2, the bearing journal 6 receives a radial / axial ball bearing 11 which is held axially immovably by means of a snap ring 12 . The outer ring of the ball bearing 11 is pressed into an axial bore at the inner end of the impeller 1 and there secured by a snap ring 13 against axial displacement. At the outer end of the journal 6, the impeller 1 is mounted by means of a plain bearing 14. Downstream of the slide bearing in the direction of the outer end of the journal 6 is an axial seal or stuffing box seal 15, on which only the hydrostatic pressure of the liquid on the pump acts. The inner cross section of the axial bore of the impeller 1 adjacent to the end face of the inner end of the bearing journal 6 or adjacent to the ball bearing 11 is hermetically sealed against the liquid pressure of the delivery flow of the pump by means of a cap-like plastic plug 16. The annular space 17 formed by the bearing journal 6 and the inner surface of the impeller 1 surrounding it is filled with bearing grease from the plain bearing 14 to the stopper 16.

An der von dem Abschlußglied 3 abgewendeten Stirnfläche des Pumpengehäuses 2 ist mittels eines diametral geteilten Klemmflansches 18, dessen Segmente mittels Schrauben 19 mit dem Pumpengehäuse 2 verbunden sind, ein Mantelrohr 20 befestigt, welches zur Kapselung einer im wesentlichen zentrisch darin verlaufenden Antriebswelle 21 dient. An ihrem in das Pumpengehäuse 2 verlaufenden, dem Lagerzapfen 6 zugewendeten Ende ist auf der Antriebswelle 21 mittels eines Schwerspannstiftes 22 ein flanschartiger Mitnehmer 23 befestigt, welcher über mehrere über den Umfang verteilte axiale Mitnehmerklauen 24 mit korrespondierenden stirnseitigen Einschnitten des Laufrades 1 in Eingriff steht. Der Mitnehmer 23 ist hierbei an einem Endabschnitt mit radialem Spiel in der zentralen Bohrung des Laufrades 1 aufgenommen, in welcher auch das Kugellager 11 sitzt. Dem Mitnehmer 23 und mittelbar auch der Antriebswelle 21 ist ein Exzentrizitätsbegrenzungslager 25 zugeordnet, welches mit Zentriervorsprüngen 26 in der zugeordneten Stirnfläche des Pumpengehäuses 2 gehalten und mittels der Schrauben 19 durch die Segmente des Klemmflansches 18 in seiner Lage festgehalten ist. Die zentrale Bohrung des Exzentrizitätsbegrenzungslagers 25 weist einen größeren Durchmesser als der Außendurchmesser des umgebenden zugeordneten Abschnittes des Mitnehmers 23 auf, so daß die Antriebswelle 21 insgesamt ein gewisses Radialspiel sowohl gegenüber dem Exzentrizitätsbegrenzungslager 25 als auch gegenüber dem Laufrad 1 hat.On the end face of the pump housing 2 facing away from the end member 3, a jacket tube 20 is fastened by means of a diametrically divided clamping flange 18, the segments of which are connected to the pump housing 2 by means of screws 19, which serves to encapsulate a drive shaft 21 running essentially centrally therein. At its end, which runs into the pump housing 2 and faces the bearing journal 6, a flange-like driver 23 is fastened on the drive shaft 21 by means of a heavy-duty spring pin 22, which engages with corresponding end cuts of the impeller 1 via a plurality of axial driver claws 24 distributed over the circumference. The driver 23 is received at an end portion with radial play in the central bore of the impeller 1, in which the ball bearing 11 is also seated. The driver 23 and indirectly also the drive shaft 21 is assigned an eccentricity limiting bearing 25 which is held with centering projections 26 in the associated end face of the pump housing 2 and is held in position by means of the screws 19 by the segments of the clamping flange 18. The central bore of the eccentricity limiting bearing 25 has a larger diameter than the outer diameter of the surrounding assigned section of the driver 23, so that the drive shaft 21 has a total of a certain radial play both with respect to the eccentricity limiting bearing 25 and with respect to the impeller 1.

Im Betrieb ist die Kreiselpumpe unterhalb eines Flüssigkeitsspiegels S angeordnet. Die zu fördernde Flüssigkeit gelangt an den beiden Stegen 7 gemäß den gekrümmten Pfeilen Pf in den Bereich des Laufrades und wird von diesem nach oben in das Pumpengehäuse 2 gefördert, wo sie durch ein tangentiales Auslaßrohr 27 austritt. Der für die Pumpe spezifische Flüssigkeitsdruck wird erst in dem Pumpengehäuse 2 erreicht, so daß wie dies bereits in der Einleitung erwähnt wurde, das Gleitlager 14 lediglich unter dem hydrostatischen Druck der Flüssigkeit steht. Hingegen steht der Stopfen 16 unter dem vollen Flüssigkeitsdruck des Förderstromes, jedoch wird ein hermetischer Abschluß erzielt, weil der Stopfen 16 weder von dem Lagerzapfen 6 noch von der Antriebswelle 21 durchsetzt ist. Außerdem kann unter dem Flüssigkeitsdruck des Förderstromes stehende Flüssigkeit aus dem zwischen dem Exzentrizitätsbegrenzungslagers 25 und dem Mitnehmer 23 gebildeten Ringraum nach oben in das Mantelrohr 20 eintreten, jedoch wird hierdurch eine Beschädigung von Lagern nicht bewirkt, da die Antriebswelle 21 lediglich an ihrem (nicht veranschaulichten) oberen Ende weit oberhalb des Flüssigkeitsspiegels S gelagert ist. Bei aufgetretenem Verschleiß an dem Laufrad 1 und/oder den Kanten 9 der Stege 7 kann die gesamte Baueinheit bestehend aus dem Laufrad 1, dem Abschlußglied 3, dem Lagerzapfen 6 nebst Lagern 11,14 durch Lösen der Schrauben 4 von dem Pumpengehäuse 2 abgebaut und durch eine andere Baueinheit ersetzt werden. Dieser Ersatz kann entweder zu Reparaturzwecken oder auch zum Zwecke eines Umbaues der Pumpe auf andere Pumpenparameter erfolgen. In dem letzteren Fall wird eine Baueinheit mit anderen Parametern des Laufrades 1 angebaut.In operation, the centrifugal pump is arranged below a liquid level S. The liquid to be conveyed reaches the region of the impeller on the two webs 7 according to the curved arrows Pf and is conveyed upward into the impeller housing 2, where it exits through a tangential outlet pipe 27. The liquid pressure specific to the pump is only reached in the pump housing 2, so that, as has already been mentioned in the introduction, the plain bearing 14 is only under the hydrostatic pressure of the liquid. In contrast, the plug 16 is under the full liquid pressure of the flow, but a hermetic seal is achieved because the plug 16 is neither penetrated by the journal 6 nor by the drive shaft 21. In addition, standing liquid under the liquid pressure of the flow from the between the eccentricity limiting bearing 25 and the Mit Participant 23 formed annular space enter upward in the casing tube 20, but this does not cause damage to bearings, since the drive shaft 21 is only mounted at its (not illustrated) upper end far above the liquid level S. In the event of wear on the impeller 1 and / or the edges 9 of the webs 7, the entire structural unit consisting of the impeller 1, the end member 3, the bearing journal 6 and bearings 11, 14 can be removed from the pump housing 2 by loosening the screws 4 and by another unit to be replaced. This replacement can be done either for repair purposes or for the purpose of converting the pump to other pump parameters. In the latter case, a structural unit with other parameters of the impeller 1 is attached.

Bei dem Ausführungsbeispiel von Fig. 2 sind ähnliche Bauelemente wie in Fig. 1 mit gleichen Bezugsziffern versehen und nicht gesondert beschrieben. Der wesentliche Unterschied besteht lediglich darin, daß ein Laufrad 1a in Form einer konischen Schnecke anstelle eines Laufrades 1 mit achsparallelen Flügeln verwendet wird.In the exemplary embodiment in FIG. 2, similar components to those in FIG. 1 are provided with the same reference numbers and are not described separately. The main difference is that an impeller 1a in the form of a conical screw is used instead of an impeller 1 with axially parallel blades.

Claims (11)

1. A centrifugal pump for liquids mixed with solids and more specially for liquids mixed with fibrous substances, comprising, a pump impeller (1) bearinged in a pump housing (2) placed round it, a driving shaft (21), that is positively joined to the pump impeller (1) and is guided in said pump housing (2), said driving shaft (21) running through an end face of the pump housing (2), and sealing elements for sealing off the space inside said housing from the bearing means of the impeller, and to make it possible for the pump impeller to be dismounted a termination member (3) is fixed to, and may be taken off, the end face of the housing furthest from the drive shaft, and on the outer end of the member (3) is fixed to, and may be taken off, the end face of the housing furthest from the drive shaft, and on the outer end of the member (3) there is fixed take-up means (5) for a middle turnpin (6), pointing towards the pump housing, for bearing the pump impeller (1), characterized in that the high pressure side of the pump is at the end, nearest the driving shaft (21), of the turnpin (6), and the low pressure side is at the termination member (3), and the termination member (3) has the function of the liquid inlet and in that on the high pressure side the ring-like space (17) walled off by the inner face of the pump impeller (1) and by the turnpin (6) is fluid-tightly shut off from the pump housing (2) by way of a stopper (16) and the drive motor is placed higher up than the level (S) of the liquid.
2. The pump as claimed in claim 1 characterized in that the take-up means (5), placed at the outer end of the termination member (3), for the turnpin (6) is joined up by way of at least one eccentric web (7) with the outer face of a base ring flange (8), said flange (8) forming a part of the termination member and being fixed to the pump housing (2).
3. The pump as claimed in claim 2 characterized in that the take-up means (5) for the turnpin (6) is joined up with the outer face of the base ring flange (8) by way of two or more webs (7), spaced out round the outer face, like a cage.
4. The pump as claimed in claim 3, characterized in that the cage webs (7) are placed running out at an angle conically from the take-up means (5) for the turnpin (6) towards the outer face of the base ring flange (8).
5. The pump as claimed in any one of claims 1 to 4 characterized in that the turnpin (5) may be adjusted axially in the take-up means (5) of the said termination member (3).
6. The pump as claimed in claim 1 characterized in that the impeller (1) is supported by a plain bearing (14) on the end, furthest from the driving shaft (21), of the turnpin (6).
7. The pump as claimed in claim 6 characterized in that the ring-like space (17) walled in by the turnpin (6) and the inner face, placed round same, of the impeller (1) is filled up with grease from the plain bearing (14) as far as the stopper (16).
8. The pump as claimed in claim 1 characterized by a driving dog (23) fixed to the end, running into the pump housing (2), of the drive shaft (21), said dog being formed like a flange with at least two axial catches (24) spaced out round the outer edge, said catches fitting into cutouts therefor in the end of the impeller (1).
9. The pump as claimed in claim 1 characterized in the drive shaft (21) has an eccentricity limiting bearing (25) on its end nearest to the turnpin (6).
10. The pump as claimed in claim 8 and claim 9 characterized in that the eccentricity limiting bearing (25) is placed round the outer face of the driving dog (23) so as to be in contact with a large area thereof.
11. The pump as claimed in any one of claims 8 to 10 characterized in that in a known way the drive shaft (21) is placed within a casing pipe (20), said pipe being fluid-tightly joined with an end face of the pump housing (2), and in that for fixing a casing pipe on the pump housing there is diametrally split claimping flange (18).
EP80100220A 1979-01-17 1980-01-17 Centrifugal pump for liquids containing solids Expired EP0013942B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80100220T ATE8924T1 (en) 1979-01-17 1980-01-17 CENTRIFUGAL PUMP FOR LIQUIDS CONTAINED WITH SOLIDS.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2901638A DE2901638B1 (en) 1979-01-17 1979-01-17 Centrifugal pump for liquids mixed with solids
DE2901638 1979-01-17

Publications (3)

Publication Number Publication Date
EP0013942A2 EP0013942A2 (en) 1980-08-06
EP0013942A3 EP0013942A3 (en) 1980-08-20
EP0013942B1 true EP0013942B1 (en) 1984-08-08

Family

ID=6060742

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80100220A Expired EP0013942B1 (en) 1979-01-17 1980-01-17 Centrifugal pump for liquids containing solids

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EP (1) EP0013942B1 (en)
AT (1) ATE8924T1 (en)
DE (1) DE2901638B1 (en)

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DE4327425A1 (en) * 1992-09-14 1994-03-17 Klein Schanzlin & Becker Ag storage
DE19638080A1 (en) * 1996-09-19 1998-03-26 Uts Umwelt Technik Sued Gmbh Pump with torus-shaped housing
RU2113274C1 (en) * 1996-06-17 1998-06-20 Владимир Павлович Грудинин Device for transfer and treatment of wet pulp
SE520740C2 (en) 1998-06-30 2003-08-19 Abs Pump Prod Ab centrifugal
DE19961196A1 (en) * 1999-12-18 2001-06-28 Erich Stallkamp Pump, in particular centrifugal pump for thick matter
NO311105B1 (en) * 2000-02-24 2001-10-08 Hamworthy Kse As centrifugal
ATE427427T1 (en) * 2004-12-03 2009-04-15 Brinkmann Pumpen K H Brinkmann PUMP WITH CUTTER IMPELLER
CN103727055B (en) * 2013-12-13 2016-06-22 山西临龙泵业有限公司 Single-pole single-suction double-blade high-pressure pump
CN115059619B (en) * 2022-08-16 2022-12-23 服务型制造研究院(杭州)有限公司 Industrial pump

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DE526779C (en) * 1931-06-10 Armaturen & Maschinenfabrik Ak Centrifugal pump
DE334496C (en) * 1920-06-04 1921-03-14 Luftverwertungs Ges M B H Centrifugal pump for acids
GB539172A (en) * 1939-05-25 1941-08-29 Nash Engineering Co Pump
GB922319A (en) * 1960-03-28 1963-03-27 Klaus Franz Centrifugal pump
DE1276450B (en) * 1961-01-09 1968-08-29 Loewe Pumpenfabrik G M B H Centrifugal pump, especially heating circulation pump
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Title
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Also Published As

Publication number Publication date
DE2901638C2 (en) 1980-08-14
ATE8924T1 (en) 1984-08-15
DE2901638B1 (en) 1979-08-30
EP0013942A3 (en) 1980-08-20
EP0013942A2 (en) 1980-08-06

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