EP1884660A1 - Screw feeder for a progressive cavity pump - Google Patents

Screw feeder for a progressive cavity pump Download PDF

Info

Publication number
EP1884660A1
EP1884660A1 EP07012876A EP07012876A EP1884660A1 EP 1884660 A1 EP1884660 A1 EP 1884660A1 EP 07012876 A EP07012876 A EP 07012876A EP 07012876 A EP07012876 A EP 07012876A EP 1884660 A1 EP1884660 A1 EP 1884660A1
Authority
EP
European Patent Office
Prior art keywords
screw
pump according
screw pump
webs
eccentric screw
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.)
Withdrawn
Application number
EP07012876A
Other languages
German (de)
French (fr)
Inventor
Markus Rosam
Karl-Heinz Grebisz
Melanie Wetzel
Helmuth Goschy
Ulrich Braun
Klaus Gerbl
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.)
Netzsch Pumpen and Systeme GmbH
Original Assignee
Netzsch Pumpen and Systeme 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 Netzsch Pumpen and Systeme GmbH filed Critical Netzsch Pumpen and Systeme GmbH
Publication of EP1884660A1 publication Critical patent/EP1884660A1/en
Withdrawn legal-status Critical Current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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/08—Scoop devices
    • F04B19/12—Scoop devices of helical or screw-type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/005—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/001—Pumps for particular liquids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts

Definitions

  • the invention relates to an eccentric screw pump with a screw conveyor which supplies the suction region of the screw rotor predominantly medium to highly viscous media.
  • Driers are mixed with liquid and then pumped by a pump.
  • a mixing screw which is connected on one side to a motor and on the other side to a screw pump, is seated in the region of a storage container. Between the reservoir and the pump liquid enters the screw area.
  • the screw conveyor consists of a helical band, which is fastened on one side only by means of four struts on the mixer shaft.
  • the DE 43 18 177 is to be taken from a mixing and conveying device.
  • the dry substances pass through a hopper into the area of a mixing screw, in the area also leads a liquid supply.
  • the mixture is then conveyed on to the mixing process by a screw pump.
  • the mixing screw itself consists of a section with a solid screw and a section with paddle and bar-shaped mixing elements.
  • Each pump is designed for a specific flow rate.
  • the suction-side pump area always sufficient medium must be available.
  • the Screw conveyors which are connected upstream of the actual screw or eccentric screw pump, can therefore promote a multiple volume of the pump power. Due to this, in the so-called stuffing space in the intake area, a stowage effect is created with which the risk of bridge formation in the hopper is connected via the auger. Due to this stuffing effect a much higher drive power must be provided as necessary.
  • the object of the invention is to adapt the stability of the screw conveyor to the required power while keeping the drive power constant even with different media.
  • the design according to the invention is of course dependent on which products are to be pumped with which viscosities and any solids present.
  • a screw conveyor having at least two openings, wherein the webs formed between these openings are connected with their Schneckenfuß with the coupling shaft.
  • the height of the apertures may be chosen in the range of 20% to 60% of the height of a screw pitch.
  • the width of the openings will correspond to the width of the webs because of the homogeneous return and uniform loading of the screw.
  • the width of the apertures is greater than the width of the webs.
  • the risk of bridge formation is relatively low, so that here the width of the webs can be greater than that of the breakthroughs.
  • the flow along the coupling shaft can be improved by the webs have a screw course opposite slope and thus provide flow direction.
  • the webs per worm gear can be offset by 30 to 120 ° to each other. So that the screw conveyor is stabilized by the coupling shaft over its entire length, the length of the pipe segments is adapted to the course of the screw conveyor.
  • a design possibility of a screw conveyor 10 with a screw tube 12 is shown.
  • a screw 14 is welded.
  • pipe segments 20 are provided for fixing the screw 14.
  • the pipe segments 20 each terminate at the point where the screw 14 ends in the axial direction.
  • couplings 22 for the two are not provided at both ends provided joints provided.
  • the screw 14 is made of flat band-shaped material.
  • the design of the worm 14 in FIG. 2 can be seen more clearly. From the perspective view, it can be seen that the worm 14 is provided with apertures 24 and webs 26. Each screw root 34 of the webs 26 is connected to the pipe segment 20 or the coupling shaft 32, for example, by a welding operation. While the medium in the axial direction flows through the apertures of the screw conveyor close to the screw tube from the rotor region back to the pump inlet, the screw 14 promotes with their end faces 28, the medium in the direction of the pump rotor. The pump rotor is by a not fully shown joint, which is attached to the clutch 22, with the screw conveyor in positive contact.
  • Fig. 3 shows the design and arrangement of the apertures 24 and webs 26 for a screw conveyor for highly viscous media.
  • the large open spaces of the openings 24 allow the medium very good backflow possibilities to adjust the back pressure in the stuffing chamber to the pump power. In this case, a dehydration of the medium and an increased tendency to bridge formation is prevented and avoided an undesirably high drive power.
  • the openings 24 are wider according to this embodiment than the webs 26.
  • the center of the openings is located respectively on the mid-perpendicular and is therefore offset by 90 ° to each other, resulting in per screw pitch 4 openings 24 and 4 webs 26 result.
  • the height of the openings corresponds to about 50% of the screw height.
  • a screw conveyor 10 can be seen.
  • a coupling shaft 32 is provided as the drive part.
  • a screw 14 is welded, which consists of individual screw segments as in all other embodiments. This embodiment of the screw 14 is used, for example, in low-viscosity media.
  • large end faces 28th more medium enters the rotor area and still prevent the smaller sized breakthroughs increased demand for drive power.
  • FIG. 6 Per each screw pitch, 3 apertures offset by 120 ° are introduced into the worm 14.
  • Fig. 7 shows a uniform distribution of 6 openings 24 and webs 26 again.
  • the height HD of the apertures is 50% compared to the height HS of the screw 14.
  • the width BD of the apertures corresponds to the width BS of the webs.
  • the worm 14 has four apertures 24 and four webs 26, wherein the width BD of the apertures is greater than the width BS of the webs.
  • the height HD of the apertures 24 is 50% of the height HS of the screw 14.

Abstract

The pump has a rotor that runs into a stator which is provided with an additional screw thread. The rotor stands in connection with a drive via a coupling shaft. The coupling shaft is surrounded by a conveying screw that comprises a slug (14). The slug has two openings (24), where bars (26) are formed between the openings. The coupling shaft has a screw tube, and a strip-shaped tube segment is arranged at the screw tube at an end parallel to a longitudinal axis of the conveying screw.

Description

Die Erfindung betrifft eine Exzenterschneckenpumpe mit einer Förderschnecke die dem Saugbereich des Schneckenrotors vorwiegend mittel- bis hochviskose Medien zuführt.The invention relates to an eccentric screw pump with a screw conveyor which supplies the suction region of the screw rotor predominantly medium to highly viscous media.

Aus der DE 101 60 335 A1 geht hierzu eine Exzenterschneckenpumpe hervor bei der im Pumpengehäuse vor dem Pumpenrotor eine Förderschnecke angeordnet ist. Die Schnecke ist über ihre gesamte Innenkontur mit dem Schneckenkern verbunden.From the DE 101 60 335 A1 For this purpose, an eccentric screw shown in the pump housing in front of the pump rotor, a screw conveyor is arranged. The screw is connected over its entire inner contour with the Schneckenkern.

Aus der DE 101 18 071 A1 geht eine Exzenterschneckenpumpe hervor um deren Kupplungsstange eine Hohlschnecke angeordnet ist. Diese Hohlschnecke steht antriebsseitig mit einer Scheibe in Verbindung. Das andere Ende im saugseitigen Bereich des Schneckenrotors weist keine Verbindung zu einen Gelenk oder der Kupplungsstange auf.From the DE 101 18 071 A1 an eccentric screw pump protrudes around the coupling rod a hollow screw is arranged. This hollow screw is on the drive side with a disc in connection. The other end in the suction-side region of the screw rotor has no connection to a joint or the coupling rod.

Bei einer Mischeinrichtung gemäß DE 1 277 819 werden Trockenstoffe mit Flüssigkeit gemischt und anschließend von einer Pumpe gefördert. Dazu sitzt im Bereich eines Vorratsbehälters eine Mischschnecke, die an der einen Seite mit einem Motor und auf der anderen Seite mit einer Schneckenpumpe verbunden ist. Zwischen dem Vorratsbehälter und der Pumpe gelangt Flüssigkeit in den Schneckenbereich. Die Förderschnecke besteht aus einem schraubenlinienförmigen Band, das nur einseitig mittels vier Verstrebungen an der Mischerwelle befestigt ist.In a mixing device according to DE 1 277 819 Driers are mixed with liquid and then pumped by a pump. For this purpose, a mixing screw, which is connected on one side to a motor and on the other side to a screw pump, is seated in the region of a storage container. Between the reservoir and the pump liquid enters the screw area. The screw conveyor consists of a helical band, which is fastened on one side only by means of four struts on the mixer shaft.

Auch der DE 43 18 177 ist eine Misch- und Fördereinrichtung zu entnehmen. Die Trockenstoffe gelangen über einen Fülltrichter in den Bereich einer Mischschnecke, in deren Bereich auch eine Flüssigkeitszuleitung führt. Das Gemisch wird anschließend an den Mischvorgang von einer Schneckenpumpe weitergefördert. Die Mischschnecke selbst besteht aus einem Bereich mit einer Vollschnecke und einem Bereich mit paddel- und stegförmigen Mischelementen.Also the DE 43 18 177 is to be taken from a mixing and conveying device. The dry substances pass through a hopper into the area of a mixing screw, in the area also leads a liquid supply. The mixture is then conveyed on to the mixing process by a screw pump. The mixing screw itself consists of a section with a solid screw and a section with paddle and bar-shaped mixing elements.

Jede Pumpe wird für eine bestimmte Fördermenge ausgelegt. Dazu muß dem saugseitigen Pumpenbereich immer ausreichend Medium zur Verfügung stehen. Die Förderschnecken, welche der eigentlichen Schnecken- bzw. Exzenterschneckenpumpe vorgeschaltet sind, können deshalb ein vielfaches Volumen der Pumpenleistung fördern. Aufgrund dessen entsteht im sogenannten Stopfraum im Ansaugbereich eine Stauwirkung mit der die Gefahr der Brückenbildung im Fülltrichter über der Schnecke verbunden ist. Aufgrund dieser Stopfwirkung muß eine wesentlich höhere Antriebsleistung zur Verfügung gestellt werden als notwendig.Each pump is designed for a specific flow rate. For this purpose, the suction-side pump area always sufficient medium must be available. The Screw conveyors, which are connected upstream of the actual screw or eccentric screw pump, can therefore promote a multiple volume of the pump power. Due to this, in the so-called stuffing space in the intake area, a stowage effect is created with which the risk of bridge formation in the hopper is connected via the auger. Due to this stuffing effect a much higher drive power must be provided as necessary.

Die Aufgabe der Erfindung besteht darin, die Stabilität der Förderschnecke an die erforderliche Leistung anzupassen und dabei die Antriebsleistung auch bei unterschiedlichen Medien konstant niedrig zu halten.The object of the invention is to adapt the stability of the screw conveyor to the required power while keeping the drive power constant even with different media.

Gelöst wird diese Aufgabe durch die Merkmale des Anspruchs 1. Weitere erfindungsgemäße Gestaltungen der Zuführschnecke gehen aus den Merkmalen der Unteransprüche hervor.This object is achieved by the features of claim 1. Further inventive designs of the feed screw will be apparent from the features of the dependent claims.

Die Entwicklung einer entsprechenden Förderschnecke zwischen dem Pumpenrotor und dem Antrieb hat gezeigt, daß die aus dem Stand der Technik bekannten Vorrichtungen nur Teilprobleme der erfindungsgemäßen Aufgabe lösen.The development of a corresponding auger between the pump rotor and the drive has shown that the devices known from the prior art solve only part of the problem of the invention.

Die erfindungsgemäße Gestaltung ist selbstverständlich abhängig davon, welche Produkte mit welchen Viskositäten und gegebenenfalls vorhandenen Feststoffen zu pumpen sind.The design according to the invention is of course dependent on which products are to be pumped with which viscosities and any solids present.

Erfindungsgemäß handelt es sich in der Normalausführung um eine Förderschnecke die mindestens zwei Durchbrüche aufweist, wobei die zwischen diesen Durchbrüchen gebildeten Stege mit ihrem Schneckenfuß mit der Kuppelwelle verbunden sind. Je nachdem welche Viskosität das Produkt aufweist, kann es sinnvoll sein, die Anzahl der Durchbrüche auf mindestens vier zu steigern, um den Rückfluß des Mediums zu erleichtern und für eine homogenere Durchmischung zu sorgen, wobei bereits am saugseitigen Ende der Pumpe einer Brückenbildung des Mediums entgegenwirkt wird.According to the invention in the normal version is a screw conveyor having at least two openings, wherein the webs formed between these openings are connected with their Schneckenfuß with the coupling shaft. Depending on the viscosity of the product, it may be useful to increase the number of openings to at least four in order to facilitate the reflux of the medium and to ensure a more homogeneous mixing, which already counteracts bridging of the medium at the suction end of the pump becomes.

Durch die erfindungsgemäßen Durchbrüche läßt sich gegenüber Fördereinrichtungen aus dem Stand der Technik eine auf die Beschaffenheit des Mediums ausgelegte verlustarme Antriebsleistung installieren.By means of the breakthroughs according to the invention, it is possible to install a low-loss drive power which is designed for the nature of the medium, compared with conveyors of the prior art.

Damit sich der erfindungsgemäße Vorteil auch in den Bereichen der Kupplungen (Gelenke) einstellt, erstreckt sich die Schnecke auch über diesen Bereich, wozu das als Kuppelstange eingesetzte Rohr streifenförmige Rohrsegmente aufweist, die mit der Schnecke verbunden sind. Entspricht die Anzahl der Rohrsegmente der Anzahl der Durchbrüche so steht eine dementsprechende Anzahl von Stegen für deren Befestigung zur Verfügung.In order for the advantage according to the invention also to be established in the areas of the couplings (joints), the worm also extends over this area, for which purpose the tube used as a coupling rod has strip-shaped pipe segments which are connected to the worm. Corresponds to the number of pipe segments the number of openings so there is a corresponding number of bars for their attachment available.

Da für die Rückströmung des Mediums nicht nur die Anzahl der Durchbrüche sondern auch deren Fläche eine wesentliche Rolle spielt, kann entsprechend einer erfindungsgemäßen Variante vorgesehen sein, die Durchbrüche zwischen 30% und 70% der Höhe des Schneckenganges zu bemessen. Bei niedrigviskosen Stoffen kann die Höhe der Durchbrüche im Bereich von 20 % bis 60 % der Höhe einer Schneckensteigung gewählt werden.Since not only the number of openings but also their surface plays an essential role for the backflow of the medium, according to a variant of the invention may be provided to measure the breakthroughs between 30% and 70% of the height of the screw. For low viscosity materials, the height of the apertures may be chosen in the range of 20% to 60% of the height of a screw pitch.

Wie in einem Ausführungsbeispiel dargestellt, wird wegen der homogenen Rückführung und gleichmäßigen Belastung der Schnecke die Breite der Durchbrüche der Breite der Stege entsprechen. Bei hochviskosen Medien muß sicherlich die Rückströmmöglichkeit verbessert werden, wobei die Breite der Durchbrüche größer ist als die Breite der Stege. Bei niedrigviskosen Stoffen ist die Gefahr der Brückenbildung relativ gering, so daß hier die Breite der Stege größer als die der Durchbrüche sein kann.As shown in one embodiment, the width of the openings will correspond to the width of the webs because of the homogeneous return and uniform loading of the screw. For highly viscous media certainly the Rückströmmöglichkeit must be improved, the width of the apertures is greater than the width of the webs. For low-viscosity materials, the risk of bridge formation is relatively low, so that here the width of the webs can be greater than that of the breakthroughs.

Zur Verbesserung des Rückflusses und damit Verringerung der Stauwirkung kann die Strömung entlang der Kuppelwelle verbessert werden, indem die Stege eine dem Schneckenverlauf entgegengesetzte Neigung aufweisen und damit Strömungsrichtung ergeben.To improve the reflux and thus reduce the accumulation effect, the flow along the coupling shaft can be improved by the webs have a screw course opposite slope and thus provide flow direction.

Je nachdem welche Gestaltung der Schnecke benötigt wird, können die Stege pro Schneckengang um 30 bis 120 ° zueinander versetzt sein. Damit die Förderschnecke um ihre gesamte Länge durch die Kuppelwelle stabilisiert wird, ist die Länge der Rohrsegmente an den Verlauf der Förderschnecke angepaßt.Depending on which design of the worm is required, the webs per worm gear can be offset by 30 to 120 ° to each other. So that the screw conveyor is stabilized by the coupling shaft over its entire length, the length of the pipe segments is adapted to the course of the screw conveyor.

Ein leichteres Anbringen der Förderschnecke auf der Kuppelwelle erreicht man dadurch, daß die Förderschnecke aus mehreren Teilen besteht, die eine bessere Handhabung während des zumeist angewendeten Schweißvorgangs ermöglichen.Easier attachment of the auger on the coupling shaft is achieved in that the auger consists of several parts that allow better handling during the most commonly used welding process.

Die Erfindung wird nachstehend anhand von Ausführungsbeispielen exemplarisch beschrieben.The invention will now be described by way of example with reference to exemplary embodiments.

Es zeigt:

Fig. 1
Seitenansicht der Förderschnecke
Fig. 2
eine dreidimensionale Darstellung der Förderschnecke
Fig. 3
einen Querschnitt der Förderschnecke
Fig. 4
Förderschnecke mit beidseitigem Gelenkteil
Fig. 5
Seitenansicht der Förderschnecke nach Fig. 4
Fig. 6
Querschnitt einer Förderschnecke
Fig. 7
Schneckenquerschnitt mit 6 Durchbrüchen
Fig. 8
Schneckenquerschnitt mit 4 Durchbrüchen
Fig. 9
Schneckenquerschnitt mit verschiedenen Durchbruchabständen von der Kuppelstange
It shows:
Fig. 1
Side view of the screw conveyor
Fig. 2
a three-dimensional representation of the screw conveyor
Fig. 3
a cross section of the screw conveyor
Fig. 4
Feed screw with bilateral joint part
Fig. 5
Side view of the screw conveyor according to FIG. 4
Fig. 6
Cross section of a screw conveyor
Fig. 7
Screw cross section with 6 openings
Fig. 8
Screw cross section with 4 openings
Fig. 9
Screw cross-section with different breakthrough distances from the coupling rod

In Fig. 1 ist eine Gestaltungsmöglichkeit einer Förderschnecke 10 mit einem Schneckenrohr 12 dargestellt. Auf die Umfangsfläche des Schneckenrohres 12 ist eine Schnecke 14 aufgeschweißt. An den beiden Enden 16, 18 des Schneckenrohres 12 sind Rohrsegmente 20 zur Befestigung der Schnecke 14 vorgesehen. Die Rohrsegmente 20 enden jeweils an der Stelle an der die Schnecke 14 in axialer Richtung endet. Im Bereich der Rohrelemente 20 sind an beiden Enden Kupplungen 22 für die nicht dargestellten Gelenke vorgesehen. Die Schnecke 14 wird aus flachem bandförmigen Material gefertigt.In Fig. 1, a design possibility of a screw conveyor 10 with a screw tube 12 is shown. On the peripheral surface of the screw tube 12, a screw 14 is welded. At the two ends 16, 18 of the screw tube 12 pipe segments 20 are provided for fixing the screw 14. The pipe segments 20 each terminate at the point where the screw 14 ends in the axial direction. In the area of the tubular elements 20, couplings 22 for the two are not provided at both ends provided joints provided. The screw 14 is made of flat band-shaped material.

Deutlicher erkennen läßt sich die Gestaltung der Schnecke 14 in Fig. 2. Aus der perspektivischen Darstellung wird ersichtlich, daß die Schnecke 14 mit Durchbrüchen 24 und Stegen 26 versehen ist. Jeder Schneckenfuß 34 der Stege 26 ist mit dem Rohrsegment 20 oder der Kuppelwelle 32 zum Beispiel durch einen Schweißvorgang verbunden. Während das Medium in axialer Richtung durch die Durchbrüche der Förderschnecke nahe am Schneckenrohr entlang aus dem Rotorbereich zurück zum Pumpeneinlaß strömt, fördert die Schnecke 14 mit ihren Stirnflächen 28 das Medium in Richtung zum Pumpenrotor. Der Pumpenrotor steht durch ein nicht vollständig dargestelltes Gelenk, das an der Kupplung 22 befestigt wird, mit der Förderschnecke in formschlüssigem Kontakt.The design of the worm 14 in FIG. 2 can be seen more clearly. From the perspective view, it can be seen that the worm 14 is provided with apertures 24 and webs 26. Each screw root 34 of the webs 26 is connected to the pipe segment 20 or the coupling shaft 32, for example, by a welding operation. While the medium in the axial direction flows through the apertures of the screw conveyor close to the screw tube from the rotor region back to the pump inlet, the screw 14 promotes with their end faces 28, the medium in the direction of the pump rotor. The pump rotor is by a not fully shown joint, which is attached to the clutch 22, with the screw conveyor in positive contact.

Fig. 3 zeigt die Ausführung und Anordnung der Durchbrüche 24 und Stege 26 für eine Förderschnecke für hochviskose Medien. Hier ermöglichen die großen Freiflächen der Durchbrüche 24 dem Medium sehr gute Rückströmungsmöglichkeiten um den Staudruck im Stopfraum an die Pumpleistung anzupassen. Dabei wird eine Dehydrierung des Mediums und eine verstärkte Neigung zur Brückenbildung verhindert und eine unerwünscht hohe Antriebsleistung vermieden.Fig. 3 shows the design and arrangement of the apertures 24 and webs 26 for a screw conveyor for highly viscous media. Here, the large open spaces of the openings 24 allow the medium very good backflow possibilities to adjust the back pressure in the stuffing chamber to the pump power. In this case, a dehydration of the medium and an increased tendency to bridge formation is prevented and avoided an undesirably high drive power.

Die Durchbrüche 24 sind gemäß diesem Ausführungsbeispiel breiter als die Stege 26. Die Mitte der Durchbrüche befindet sich jeweils auf der Mittelsenkrechten und ist demnach um 90 ° zueinander versetzt, woraus sich pro Schneckensteigung 4 Durchbrüche 24 und 4 Stege 26 ergeben. Die Höhe der Durchbrüche entspricht etwa 50% der Schneckenhöhe.The openings 24 are wider according to this embodiment than the webs 26. The center of the openings is located respectively on the mid-perpendicular and is therefore offset by 90 ° to each other, resulting in per screw pitch 4 openings 24 and 4 webs 26 result. The height of the openings corresponds to about 50% of the screw height.

Auch aus Fig. 4 und Fig. 5 läßt sich eine Förderschnecke 10 entnehmen. Hier ist als Antriebsteil eine Kuppelwelle 32 vorgesehen. Auf die Kuppelwelle 32 im Bereich zwischen den Gelenkteilen 30 ist eine Schnecke 14 aufgeschweißt, die wie bei allen anderen Ausführungsbeispielen aus einzelnen Schneckensegmenten besteht. Diese Ausführung der Schnecke 14 kommt z.B. bei niedrigviskosen Medien zum Einsatz. Über die im Vergleich zu den Flächen der Durchbrüche 24 großen Stirnflächen 28 gelangt mehr Medium in den Rotorbereich und trotzdem verhindern die kleiner dimensionierten Durchbrüche einen erhöhten Bedarf an Antriebsleistung.Also from Fig. 4 and Fig. 5, a screw conveyor 10 can be seen. Here, a coupling shaft 32 is provided as the drive part. On the coupling shaft 32 in the region between the joint parts 30, a screw 14 is welded, which consists of individual screw segments as in all other embodiments. This embodiment of the screw 14 is used, for example, in low-viscosity media. About the compared to the surfaces of the apertures 24 large end faces 28th more medium enters the rotor area and still prevent the smaller sized breakthroughs increased demand for drive power.

Die Anordnung der Durchbrüche 24 und deren Größe der in Fig. 4 und 5 dargestellten Förderschnecke 10 zeigt Fig. 6. Pro Schneckensteigung sind jeweils 3 um 120 ° versetzte Durchbrüche in die Schnecke 14 eingebracht.The arrangement of the apertures 24 and their size of the screw conveyor 10 shown in FIGS. 4 and 5 is shown in FIG. 6. Per each screw pitch, 3 apertures offset by 120 ° are introduced into the worm 14.

Aus den Fig. 7, 8, 9 entnimmt man weitere Ausführungsbeispiele für die Schneckengestaltung für jeweils eine Windung.From FIGS. 7, 8, 9, further embodiments for the screw configuration are taken for one turn each.

Fig. 7 gibt eine gleichmäßige Verteilung von 6 Durchbrüchen 24 und Stegen 26 wieder. Die Höhe HD der Durchbrüche beträgt 50 % im Vergleich zur Höhe HS der Schnecke 14. Die Breite BD der Durchbrüche entspricht der Breite BS der Stege.Fig. 7 shows a uniform distribution of 6 openings 24 and webs 26 again. The height HD of the apertures is 50% compared to the height HS of the screw 14. The width BD of the apertures corresponds to the width BS of the webs.

In Fig. 8 weist die Schnecke 14 vier Durchbrüche 24 und vier Stege 26 auf, wobei die Breite BD der Durchbrüche größer ist als die Breite BS der Stege. Die Höhe HD der Durchbrüche 24 beträgt 50 % der Höhe HS der Schnecke 14.In FIG. 8, the worm 14 has four apertures 24 and four webs 26, wherein the width BD of the apertures is greater than the width BS of the webs. The height HD of the apertures 24 is 50% of the height HS of the screw 14.

Aus den unterbrochenen Linien der Fig. 9 sind unterschiedliche Größenverhältnisse bezüglich der Höhe HD der Durchbrüche zur Höhe HS der Schnecke 14 zu entnehmen, wobei bei einer Teilung von 120° drei Durchbrüche 24 dargestellt sind.From the broken lines of FIG. 9, different size ratios with respect to the height HD of the openings to the height HS of the screw 14 can be seen, wherein at a pitch of 120 ° three openings 24 are shown.

BezugsziffernlisteReferences list

1010
Förderschneckenscrew conveyors
1212
Schneckenrohrscrew tube
1414
Schneckeslug
16, 1816, 18
KuppelwellenendenCoupling shaft ends
2020
Rohrsegmentepipe segments
2222
Kupplungenclutches
2424
Durchbrüchebreakthroughs
2626
StegeStege
2828
Stirnflächeface
3030
Gelenkteilejoint parts
3232
Kuppelwellecoupling shaft
3434
SchneckenfußSchneckenfuß

Claims (14)

Exzenterschneckenpumpe mit einem exzentrisch umlaufenden Rotor der in einem mit einem zusätzlichen Schraubengang versehenen Stator umläuft, wobei der Rotor über eine Kuppelwelle mit einem Antrieb in Verbindung steht und die Kuppelwelle von einer Förderschnecke umgeben ist,
dadurch gekennzeichnet,
daß die Förderschnecke (10) eine Schnecke (14) aufweist, die pro Steigung mindestens zwei Durchbrüche (24) aufweist, und daß die zwischen diesen Durchbrüchen (24) gebildeten Stege 26 mit der Kuppelwelle verbunden sind.Eccentric screw pump with an eccentrically rotating rotor which rotates in a provided with an additional screw stator, wherein the rotor is connected via a coupling shaft with a drive and the coupling shaft is surrounded by a screw conveyor,
characterized,
in that the screw conveyor (10) has a screw (14) which has at least two apertures (24) per lead, and in that the webs 26 formed between these apertures (24) are connected to the coupling shaft. Exzenterschneckenpumpe nach Anspruch 1,
dadurch gekennzeichnet,
daß pro Schneckensteigung mindestens vier Durchbrüche vorhanden sind.Eccentric screw pump according to claim 1,
characterized,
that at least four breakthroughs are available per screw pitch. Exzenterschneckenpumpe nach Anspruch 1 oder 2,
dadurch gekennzeichnet,
daß die Kuppelwelle ein Schneckenrohr aufweist, an dem sich mindestens an einem Ende parallel zur Längsachse der Förderschnecke (10) streifenförmige Rohrsegmente (20) befinden, die mit der Schnecke (14) verbunden sind.Eccentric screw pump according to claim 1 or 2,
characterized,
in that the coupling shaft has a screw tube on which strip-shaped tube segments (20), which are connected to the screw (14), are located at least at one end parallel to the longitudinal axis of the conveyor screw (10). Exzenterschneckenpumpe nach Anspruch 3,
dadurch gekennzeichnet,
daß die Anzahl der Rohrsegmente (20) der Anzahl der Durchbrüche (24) entspricht.Eccentric screw pump according to claim 3,
characterized,
that the number of tube segments (20) corresponds to the number of the openings (24). Exzenterschneckenpumpe nach einem der Ansprüche 1, 2 oder 4,
dadurch gekennzeichnet,
daß die Höhe (HD) der Durchbrüche (24) zwischen 30 % und 70 % der Höhe (HS) der Schnecke (14) entspricht.Eccentric screw pump according to one of claims 1, 2 or 4,
characterized,
that the height (HD) of the openings (24) between 30% and 70% of the height (HS) of the screw (14). Exzenterschneckenpumpe nach Anspruch 5,
dadurch gekennzeichnet,
daß die Höhe (HD) der Durchbrüche (24) zwischen 20 % bis 60 % der Höhe (HS) der Schnecke (14) entspricht.Eccentric screw pump according to claim 5,
characterized,
that the height (HD) of the openings (24) between 20% to 60% of the height (HS) of the screw (14). Exzenterschneckenpumpe nach Anspruch 3 oder 4,
dadurch gekennzeichnet,
daß die Rohrsegmente (20) im Betriebszustand das oder die Gelenkelement/e (30) überdecken.Eccentric screw pump according to claim 3 or 4,
characterized,
that the pipe segments (20) in the operating state cover the one or more joint element / s (30). Exzenterschneckenpumpe nach einem der Ansprüche 1 bis 7,
dadurch gekennzeichnet,
daß die Breite (BD) der Durchbrüche (24) der Breite (BS) der Stege (26), die mit der Kuppelstange verbunden sind, entspricht.Eccentric screw pump according to one of claims 1 to 7,
characterized,
in that the width (BD) of the apertures (24) corresponds to the width (BS) of the webs (26) which are connected to the coupling rod. Exzenterschneckenpumpe nach einem der Ansprüche 1 bis 7,
dadurch gekennzeichnet,
daß die Breite (BD) der Durchbrüche (24) größer ist als die Breite (BS) der Stege (26).Eccentric screw pump according to one of claims 1 to 7,
characterized,
that the width (BD) of the openings (24) is greater than the width (BS) of the webs (26). Exzenterschneckenpumpe nach einem der Ansprüche 1 bis 8,
dadurch gekennzeichnet,
daß die Breite (BS) der Stege (24) größer ist als die Breite (BD) der Durchbrüche (26).Eccentric screw pump according to one of claims 1 to 8,
characterized,
that the width (BS) of the webs (24) is greater than the width (BD) of the apertures (26). Exzenterschneckenpumpe nach einem der Ansprüche 1 bis 10,
dadurch gekennzeichnet,
daß die Stege (26) eine dem Schneckenverlauf entgegengesetzte Neigung aufweisen.Eccentric screw pump according to one of claims 1 to 10,
characterized,
that the webs (26) have an opposite inclination of the worm course. Exzenterschneckenpumpe nach einem der Ansprüche 1 bis 11,
dadurch gekennzeichnet,
daß die Stege (26) um 30 ° bis 120 ° zueinander versetzt sind.Eccentric screw pump according to one of claims 1 to 11,
characterized,
that the webs (26) are offset by 30 ° to 120 ° to each other. Exzenterschneckenpumpe nach Anspruch 7,
dadurch gekennzeichnet,
daß die Länge der Rohrsegmente (20) an den Verlauf der Schnecke (14) angepaßt ist.Eccentric screw pump according to claim 7,
characterized,
that the length of the tube segments (20) is adapted to the course of the screw (14). Exzenterschneckenpumpe nach einem der Ansprüche 1 bis 13,
dadurch gekennzeichnet,
daß die Schnecke (14) aus mehreren Teilen besteht.Eccentric screw pump according to one of claims 1 to 13,
characterized,
that the worm (14) consists of several parts.
EP07012876A 2006-08-03 2007-06-30 Screw feeder for a progressive cavity pump Withdrawn EP1884660A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006036243A DE102006036243A1 (en) 2006-08-03 2006-08-03 Feed screw for eccentric screw pump

Publications (1)

Publication Number Publication Date
EP1884660A1 true EP1884660A1 (en) 2008-02-06

Family

ID=38535631

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07012876A Withdrawn EP1884660A1 (en) 2006-08-03 2007-06-30 Screw feeder for a progressive cavity pump

Country Status (9)

Country Link
US (1) US20080031758A1 (en)
EP (1) EP1884660A1 (en)
JP (1) JP2008038907A (en)
KR (1) KR20080012769A (en)
CN (1) CN101122287A (en)
AU (1) AU2007203551A1 (en)
BR (1) BRPI0703164A (en)
CA (1) CA2595015A1 (en)
DE (1) DE102006036243A1 (en)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009024088A1 (en) 2009-06-06 2010-12-09 Zeus Gmbh Tire filler, method for producing a tire filling and apparatus for carrying out the method
KR101035078B1 (en) * 2011-01-14 2011-05-19 주식회사 유성엔지니어링 Screw pump
US10087758B2 (en) 2013-06-05 2018-10-02 Rotoliptic Technologies Incorporated Rotary machine
US10436068B2 (en) * 2016-02-12 2019-10-08 General Electric Company Flowpath contouring
CN108373929A (en) * 2018-05-07 2018-08-07 青岛科技大学 The continuous output device of cracked residue and method of a kind of scrap rubber or waste plastics
CA3112348A1 (en) 2018-09-11 2020-03-19 Rotoliptic Technologies Incorporated Helical trochoidal and offset-trochoidal rotary machines
USD927968S1 (en) * 2019-03-28 2021-08-17 Ojjo, Inc. Screw anchor
US11815094B2 (en) 2020-03-10 2023-11-14 Rotoliptic Technologies Incorporated Fixed-eccentricity helical trochoidal rotary machines
US11802558B2 (en) 2020-12-30 2023-10-31 Rotoliptic Technologies Incorporated Axial load in helical trochoidal rotary machines

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4531892A (en) * 1983-03-14 1985-07-30 Sunds Defibrator Aktiebolag Apparatus for pumping of pulp
DE4121717A1 (en) * 1991-06-07 1992-12-10 Allweiler Ag Eccentric scroll pump - has rotor connected to drive unit and feeding hopper with storage space at base for handling highly viscous material
DE4442060C1 (en) * 1994-11-25 1996-03-14 Netzsch Mohnopumpen Gmbh Eccentric screw pump for highly viscous media
DE10160335A1 (en) * 2001-12-07 2003-06-18 Ksb Ag Input device for eccentric spiral pump has rise of spiral equal to at least half the filing funnel width measured in axial direction of spiral

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3271081A (en) * 1964-09-28 1966-09-06 Phillips Petroleum Co Apparatus and process for pumping slurry
DE1277819B (en) * 1965-05-12 1968-09-19 Karl Schlecht Dipl Ing Device for continuous mixing of powdery to fine-grained bulk material
DE1244723B (en) * 1965-05-12 1967-07-20 Karl Schlecht Dipl Ing Device for the continuous mixing of dry material with a liquid
US4134736A (en) * 1978-02-22 1979-01-16 E. I. Du Pont De Nemours And Company Steam-polymer separation apparatus
JPS58192814U (en) * 1982-06-15 1983-12-22 株式会社神戸製鋼所 Screw blade structure
JPH0748587Y2 (en) * 1988-07-12 1995-11-08 兵神装備株式会社 Powder transfer device
DE9211567U1 (en) * 1992-08-27 1992-10-29 Bug Betriebsanlagen- Und Grundbesitz Gmbh, 8046 Garching, De
DE10118071C2 (en) * 2001-04-11 2003-05-28 Seepex Seeberger Gmbh & Co Eccentric screw pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4531892A (en) * 1983-03-14 1985-07-30 Sunds Defibrator Aktiebolag Apparatus for pumping of pulp
DE4121717A1 (en) * 1991-06-07 1992-12-10 Allweiler Ag Eccentric scroll pump - has rotor connected to drive unit and feeding hopper with storage space at base for handling highly viscous material
DE4442060C1 (en) * 1994-11-25 1996-03-14 Netzsch Mohnopumpen Gmbh Eccentric screw pump for highly viscous media
DE10160335A1 (en) * 2001-12-07 2003-06-18 Ksb Ag Input device for eccentric spiral pump has rise of spiral equal to at least half the filing funnel width measured in axial direction of spiral

Also Published As

Publication number Publication date
BRPI0703164A (en) 2008-03-25
CN101122287A (en) 2008-02-13
AU2007203551A1 (en) 2008-02-21
US20080031758A1 (en) 2008-02-07
CA2595015A1 (en) 2008-02-03
DE102006036243A1 (en) 2008-02-14
JP2008038907A (en) 2008-02-21
KR20080012769A (en) 2008-02-12

Similar Documents

Publication Publication Date Title
EP1884660A1 (en) Screw feeder for a progressive cavity pump
EP1768771B1 (en) Mixing device
EP1797327B1 (en) Rotary piston pump comprising a pump housing and two double-bladed rotary pistons
DE60104086T2 (en) Screw conveyor for liquids and / or chunks of material
EP2910783B1 (en) Dual spindle helical spindle pump with a single-entry design
EP0509218B1 (en) Gear pump
DE10112028A1 (en) Screw pump and twin screw extruder with such a screw pump
DE102005061667A1 (en) Planetary gear pump
DE1553031A1 (en) Rotary lobe pump for viscous media
DE102012112618B3 (en) Multiple pump
DE69906110T2 (en) GEAR PUMP FOR HIGH VISCOSE LIQUIDS
EP3239525B1 (en) Dual spindle helical spindle pump with a single-entry design
DE102008045440B4 (en) Rotary piston of a rotary lobe pump and rotary lobe pump
EP2616640B1 (en) Rotary piston pump and rotary piston
DE4442060C1 (en) Eccentric screw pump for highly viscous media
DE3045192C2 (en) Gear pump
EP3613497A1 (en) Mixer and metering device
EP2199059A2 (en) Extruder assembly comprising a gear pump and method of operating such an arrangement
DE2428932C3 (en) Liquid pump
DE3502839A1 (en) Pump
DE3426029A1 (en) CONVEYOR DEVICE FOR INHOMOGENEOUS LIQUIDS, ESPECIALLY GUELL
EP3253554B1 (en) Stuffing screw
EP0930093A2 (en) Apparatus for stirring a mixture as well as use of apparatus
AT520198A4 (en) plasticizing
DE102010049439A1 (en) External gear pump for lubrication of internal combustion engines of motor vehicles, has housing and two gear wheels which are rotatable within housing around parallel rotational axes

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

Kind code of ref document: A1

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

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

17P Request for examination filed

Effective date: 20080806

17Q First examination report despatched

Effective date: 20080918

AKX Designation fees paid

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

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

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20090129