EP1496257B1 - Screw rotor pump - Google Patents

Screw rotor pump Download PDF

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Publication number
EP1496257B1
EP1496257B1 EP04012939A EP04012939A EP1496257B1 EP 1496257 B1 EP1496257 B1 EP 1496257B1 EP 04012939 A EP04012939 A EP 04012939A EP 04012939 A EP04012939 A EP 04012939A EP 1496257 B1 EP1496257 B1 EP 1496257B1
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EP
European Patent Office
Prior art keywords
spindle
spindles
screw pump
elastic layer
faces
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP04012939A
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German (de)
French (fr)
Other versions
EP1496257A2 (en
EP1496257A3 (en
Inventor
Helmut Engelmann
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Allweiler GmbH
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Allweiler AG
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Publication date
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Publication of EP1496257A2 publication Critical patent/EP1496257A2/en
Publication of EP1496257A3 publication Critical patent/EP1496257A3/en
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Publication of EP1496257B1 publication Critical patent/EP1496257B1/en
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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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F04C2/165—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type having more than two rotary pistons with parallel axes
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/90—Improving properties of machine parts
    • F04C2230/91—Coating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/02—Rubber

Definitions

  • the invention relates to a screw pump - for conveying a flow medium - provided in a pump housing, flanked by spindles drive spindles, wherein the head surfaces having spindle threads of the spindles touch and the latter are at least partially provided with an elastic layer.
  • a drive spindle is for example the script to DE 92 11 523 the Applicant can be seen with a spindle shaft coaxially adjoining spindle portion whose circumference is determined by tooth flanks.
  • a screw pump of the type described above - especially for impure liquids - discusses the CH 232 200 A ;
  • two different materials are used for the screw spindles, some of them with convex, some with concave thread flanks, in order to avoid wear and tear.
  • These spindles have at the threads inserts of a non-metallic material of such elasticity and strength that it avoids the wear of the housing and Spindelgleit vom by solid particles in the liquid; this material is present in the region of sliding friction between the spindles and between the spindles and their housing only on one side, while serving for mutual drive of the spindles, rolling on each other points of the threaded surfaces consist on both sides of the metallic base material of the spindles.
  • the metallic outer edges of the spindles with concave thread flanks with respect to the outer diameter formed by the non-metallic insert should be greater than the size exceeding the size of the hard parts contained in the conveyed liquid. It should also be noted that the particular choice of metallic and non-metallic material depends on the operating conditions; It can easily be taken as soon as the requirements regarding strength, oil resistance, etc., are known.
  • the US-A-5,314,321 deals with a rotary piston machine - in particular with a screw compressor or screw vacuum pump - which contains at least one male rotor and at least one female rotor. These rotate lubricated or dry in a housing with or without contact with each other, wherein the surface of at least one rotor is coated with a non-electrolytic nickel plating layer consisting of Ni-P or Ni-B, is connected to the rotor by heat treatment and a Having fine crystal grain structure.
  • the non-electrolytic Nickel plating layer is provided by heating the rotor to 300 ° C to 500 ° C followed by cooling with cracks and impregnated with a solid lubricant.
  • the inventor has set the goal to enable a broader scope for screw pumps of the type mentioned and in particular to achieve a damping during operation.
  • elastic layers are like a shell attached to the top surfaces of the spindle threads, wherein an elastic layer is formed as a cup-shaped part and pushed onto a spindle end.
  • the other spindle areas can remain layer-free here.
  • the elastic layer is preferably made of an elastomer and is vulcanized, for example; It should have a damping effect and have a suitable thickness. The latter must ensure that a pressure between the spindles can be maintained at these coated areas so that a continuous flexing work can be carried out on these layers.
  • the occurring torsional vibration and Axialschwingungsenergy is consumed in this embodiment to a certain extent and thus damped, so that the vibration energy is not destroyed in its entirety in the meshing contact and the wear attack is reduced.
  • the elastic infiltration layer is provided outside the pump housing at the suction end of the spindles.
  • a further embodiment of the screw pump optionally has cross-sectional part-circular curved head surfaces of the spindle gears and between the top surfaces extending side surfaces of the spindle;
  • both the top surfaces of the spindle gear and the side surfaces of the spindle are covered with the elastic layer; the latter gives a closed sleeve-like envelope. All meshed surfaces are coated to a limited length; The highest level of flexing work must be done here and will therefore offer the highest damping effect.
  • screw pump has in the interior of a pump housing a drive spindle 10 which is flanked by two sealing or running spindles 30.
  • the longitudinal axes A and B of the drive spindle 10 and the two spindles 30 are parallel to each other.
  • the drive spindle 10 has on a metallic spindle body 12 of a length a to the right in Fig. 1 to 3 pressure side a coaxial - cross-sectionally multi-stepped - spindle shaft 14 of diameter b with a - Drollenuten offering - compensating piston 15. This is in the installed position on the inside - not recognizable - a flange or an end wall of that pump housing. From the compensating piston 15 goes to the spindle body 12 toward a coaxial shaft portion 14 a of the diameter b 1 .
  • the diameter d of the spindle body 12 is otherwise determined by a spirally arranged spindle gear 33 of the drive spindle 10, which meshes with corresponding metallic spindle gears 33 of the spindles 30.
  • suction side - At the other end - ie suction side - are the two metallic sealing or running spindles 30, which also each contain a spindle body 32, stored in a neglected in the drawing pump cover.
  • a suction-side cylindrical design - shaft end 16 with cylindrical end pin 18 of the drive spindle 10 is located between adjacent end portions of the sealing or running spindle 30, and these in turn each end with a cylindrical end pin 34.
  • These end pins 18, 34 are shown in FIG. 5 in a common Level E.
  • the end pins 34 of the sealing and running spindles 30 and the end pins 18 of the drive spindle 10 are covered by the same diameter c and each of a pipe cup 40 made of flexible material of length q, which is closed endwise by a molded cup bottom 41; the aligned cup bases 42 each span the free end 19 and 35 of the associated spigot 18 and 34.
  • the cup bases 42 on the spindles 30 are shown in FIG. 2, 3 provided with diametrically molded inner ribs 42 and abut with their comb to the subsequent Forehead 35.
  • tube cups 40 roll off one another and, as shown in FIG. 5, are temporarily deformed on both sides of the central spigot 18 and on both sides of that plane E (panel S); the cross-sectional mid-axes M of the two end pins 34 of the spindles 30 are displaced from their rest positions M r to the central end pin 18 in this deformation process.
  • a milling operation is changed which changes the spindle position.
  • Fig. 8 illustrates the transverse axis Q symmetrical cross section of the spindle set of Fig. 7 shows an embodiment of the spindle body 12, which consists of a central portion 20 circular outer contour of the diameter d 1 and two - lying in that transverse axis Q - projections 22 approximately oval design composed as a spindle profile; FIG. 8 also illustrates that the height h of these projections 22 is shorter than the central spindle diameter d 1 .
  • two axially parallel shaft stubs 31 of the spindles 30 run.
  • the three spindles 10, 30 are surrounded by a certain length of an elastic - ie damping - layer, which is vulcanized, for example.
  • the elastic layer must now be designed in a corresponding thickness z, that a pressure between the spindles 10, 30 can be maintained at these coated locations so that in turn leads to a continuous flexing work on these layers.
  • this flexing work the occurring torsional vibration and axial vibration energy is consumed to a certain extent and thus damped, so that the vibration energy is no longer destroyed in its entirety in the meshing contact. As a result, the wear attack is significantly reduced.
  • the latter is - as possibly also the above-described pipe cup 40 - formed from an elastomer; This material must be chemically resistant, especially with regard to emulsions, oil or water.
  • the likewise part-circular outer surface 52 of the layer 50 extends in a circular contour K 1 ; whose distance from the adjacent circle contour K determines the layer thickness z.
  • Each running spindle 30 is determined cross-sectionally by a circular contour N of the diameter e, which here depends on the circumference of the tooth flanks or of the spindle passage 33.
  • the barrel spindle 30 has a - in the sketched in Fig. 8 to 10 position a common center axis T determining - I-shaped cross-section on with a web portion 36, which merges into integrally formed head extensions 38 at both ends; the cross-sectional shape of the tooth flanks or top surfaces 39 are determined by that circular contour N and are therefore each designed cross-sectionally part-circular.
  • the top surfaces 39 are respectively spanned by a layer 54, which is likewise formed of elastomeric material, whose outer surface 56 lies in a circular contour N 1 .
  • the radial contour spacing determines the thickness y of the layer 54.
  • FIG. 10 shows drive and running spindles 10 and 30, which are completely surrounded by a closed layer or sheath 28 or 60 made of elastomeric material. All meshed surfaces are coated to a limited length. As a result, the highest level of flexing work must be done, and will therefore come up with the highest damping effect.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Screw Conveyors (AREA)

Abstract

The screw spindle pump has a drive spindle flanked by working spindles (30), whereby the turns (13,33) of the spindles are in contact. The spindles are provided at least partially with an elastic coating (40) which may consist of an elastomer or may be vulcanized on. The elastic coating is provided outside the pump casing on the suction side end of the spindles. The elastic coating may be constructed in cup form and fitted onto the end of the spindle.

Description

Die Erfindung betrifft eine Schraubenspindelpumpe -- zum Fördern eines Strömungsmediums -- mit in einem Pumpengehäuse vorgesehener, von Laufspindeln flankierte Antriebsspindeln, wobei sich die Kopfflächen aufweisenden Spindelgänge der Spindeln berühren sowie letztere zumindest teilweise mit einer elastischen Schicht versehen sind.The invention relates to a screw pump - for conveying a flow medium - provided in a pump housing, flanked by spindles drive spindles, wherein the head surfaces having spindle threads of the spindles touch and the latter are at least partially provided with an elastic layer.

Die Gestalt einer Antriebsspindel ist beispielsweise der Schrift zu DE 92 11 523 der Anmelderin zu entnehmen mit an einen Spindelschaft koaxial anschließenden Spindelabschnitt, dessen Umfang von Zahnflanken bestimmt wird.The shape of a drive spindle is for example the script to DE 92 11 523 the Applicant can be seen with a spindle shaft coaxially adjoining spindle portion whose circumference is determined by tooth flanks.

Bei dreispindeligen, innengelagerten Schraubenspindelpumpen ist die Aufrechterhaltung eines tragenden Schmierfilms zwischen belastungsorientierter Anlage der Nebenspindel und der Laufgehäusebohrung notwendig, um Mischreibungszustände zwischen der durch den Laufspindel-Außendurchmesser bestimmten Oberfläche einerseits und der vom Laufspindel-Bohrungsdurchmesser anderseits bestimmten Oberfläche zu vermeiden.In the case of three-spindle internally-mounted screw pumps, it is necessary to maintain a bearing lubricating film between the load-oriented abutment of the slave spindle and the housing bore in order to avoid mixed friction conditions between the surface defined by the spindle outer diameter and the surface determined by the spindle bore diameter.

In Einzelfällen, in denen wegen zu hoher Belastung, zu niedriger Viskosität des Fördermediums oder wegen ungenügend feiner Rauhtiefe der möglichen Berührungsflächen Mischreibung auftritt, ist die Bauteil-Lebensdauer vom Verschleißwiderstand beider Berührungspartner abhängig.In individual cases where mixed friction occurs due to excessive load, too low viscosity of the pumped medium or insufficient surface roughness of the possible contact surfaces, the component life depends on the wear resistance of both contact partners.

Die bei Förderung von Medien im niederviskosen Bereich auftretenden Torsions- und Axialschwingungen zwischen den rotierenden Verdrängerelementen führen zu dynamischen Belastungen in den Zahneingriffskontakten und einen davon abhängigen Verschleiß an den Spindeln und verlangt deshalb nach einer geeigneten Dämpfungsmethode.The torsional and axial vibrations between the rotating displacement elements occurring in the promotion of media in the low-viscosity range lead to dynamic loads in the meshing contacts and a dependent wear on the spindles and therefore requires a suitable damping method.

Eine Schraubenspindelpumpe der eingangs beschriebenen Art - - insbesondere für unreine Flüssigkeiten -- erörtert die CH 232 200 A ; dort werden zwei verschiedene Werkstoffe für die teils mit konvexen, teils mit konkaven Gewindeflanken versehenen Schraubenspindeln eingesetzt, um Abnutzungserscheinungen zu vermeiden. Diese Spindeln haben an den Gewindegängen Einsätze aus einem nichtmetallischen Werkstoff von solcher Elastizität und Festigkeit, dass durch ihn die Abnutzung der Gehäuse- und Spindelgleitflächen durch feste Teilchen in der Flüssigkeit vermieden wird; dieser Werkstoff ist im Bereich gleitender Reibung zwischen den Spindeln und zwischen den Spindeln und ihrem Gehäuse nur auf einer Seite vorhanden, während die zum gegenseitigen Antrieb der Spindeln dienenden, sich aufeinander abwälzenden Stellen der Gewindeflächen auf beiden Seiten aus dem metallischen Grundstoff der Spindeln bestehen.A screw pump of the type described above - especially for impure liquids - discusses the CH 232 200 A ; There, two different materials are used for the screw spindles, some of them with convex, some with concave thread flanks, in order to avoid wear and tear. These spindles have at the threads inserts of a non-metallic material of such elasticity and strength that it avoids the wear of the housing and Spindelgleitflächen by solid particles in the liquid; this material is present in the region of sliding friction between the spindles and between the spindles and their housing only on one side, while serving for mutual drive of the spindles, rolling on each other points of the threaded surfaces consist on both sides of the metallic base material of the spindles.

Zudem sollen die metallischen Außenkanten der Spindeln mit konkaven Gewindeflanken gegenüber dem durch den nichtmetallischen Einsatz gebildeten Außendurchmesser um ein die Größe der in der Förderflüssigkeit enthaltenen harten Teile übersteigendes Maß zurückstehen. Auch wird darauf hingewiesen, dass die besondere Auswahl des metallischen und des nichtmetallischen Werkstoffes von den jeweiligen Betriebsbedingungen abhängt; sie kann ohne weiteres getroffen werden, sobald die hinsichtlich Festigkeit, Ölbeständigkeit usw. zu stellenden Anforderungen bekannt sind.In addition, the metallic outer edges of the spindles with concave thread flanks with respect to the outer diameter formed by the non-metallic insert should be greater than the size exceeding the size of the hard parts contained in the conveyed liquid. It should also be noted that the particular choice of metallic and non-metallic material depends on the operating conditions; It can easily be taken as soon as the requirements regarding strength, oil resistance, etc., are known.

Die US-A-5 314 321 befasst sich mit einer Rotationskolbenmaschine -- insbesondere mit einer Schraubenkompressor- oder Schraubenvakuumpumpe --, die wenigstens einen männlichen Rotor und zumindest einen weiblichen Rotor enthält. Diese drehen sich geschmiert oder trocken in einem Gehäuse mit oder ohne Kontakt miteinander, wobei die Oberfläche wenigstens eines Rotors mit einer nicht-elektrolytischen Nickelplattierungsschicht überzogen ist, die aus Ni-P oder Ni-B besteht, mit dem Rotor durch Wärmebehandlung verbunden ist und eine Feinkristall-Kornstruktur aufweist. Die nichtelektrolytische Nickelplattierungsschicht ist durch Erhitzen des Rotors auf 300°C bis 500°C und anschließendes Abkühlen mit Rissen versehen und mit einem Festschmierstoff imprägniert.The US-A-5,314,321 deals with a rotary piston machine - in particular with a screw compressor or screw vacuum pump - which contains at least one male rotor and at least one female rotor. These rotate lubricated or dry in a housing with or without contact with each other, wherein the surface of at least one rotor is coated with a non-electrolytic nickel plating layer consisting of Ni-P or Ni-B, is connected to the rotor by heat treatment and a Having fine crystal grain structure. The non-electrolytic Nickel plating layer is provided by heating the rotor to 300 ° C to 500 ° C followed by cooling with cracks and impregnated with a solid lubricant.

In Kenntnis dieser Gegebenheiten hat sich der Erfinder das Ziel gesetzt, einen breiteren Anwendungsbereich für Schraubenspindelpumpen der eingangs genannten Art zu ermöglichen und insbesondere eine Dämpfung während des Betriebs zu erreichen.In view of these circumstances, the inventor has set the goal to enable a broader scope for screw pumps of the type mentioned and in particular to achieve a damping during operation.

Zur Lösung dieser Aufgabe führt die Lehre des unabhängigen Patentanspruchs, die Unteransprüche geben vorteilhafte Weiterbildungen an. Zudem fallen in den Rahmen der Erfindung alle Kombinationen aus zumindest zwei der in der Beschreibung der Zeichnung und/oder den Ansprüchen offenbarten Merkmale.To achieve this object, the teaching of the independent claim, the dependent claims indicate advantageous developments. In addition, all combinations of at least two of the features disclosed in the description of the drawing and / or the claims fall within the scope of the invention.

Erfindungsgemäß sind elastische Schichten schalenartig an den Kopfflächen der Spindelgänge angebracht, wobei eine elastische Schicht als napfartiger Teil ausgeformt und auf ein Spindelende aufgeschoben ist. Die anderen Spindelbereiche können hier schichtfrei bleiben. Zudem besteht die elastische Schicht bevorzugt aus einem Elastomer und ist beispielsweise aufvulkanisiert; sie soll dämpfend wirken und eine dafür geeignete Dicke aufweisen. Letztere muss gewährleisten, dass eine Pressung zwischen den Spindeln an diesen beschichteten Stellen so aufrechterhalten werden kann, dass eine dauernde Walkarbeit an diesen Schichten zu erfolgen vermag. Für die Verrichtung dieser Walkarbeit wird bei dieser Ausführung zu einem bestimmten Maß die auftretende Drehschwingungs- und Axialschwingungsenergie verbraucht und damit gedämpft, so dass die Schwingungsenergie nicht mehr in gesamter Größe im Zahneingriffskontakt vernichtet sowie der Verschleißangriff reduziert wird.According to the invention elastic layers are like a shell attached to the top surfaces of the spindle threads, wherein an elastic layer is formed as a cup-shaped part and pushed onto a spindle end. The other spindle areas can remain layer-free here. In addition, the elastic layer is preferably made of an elastomer and is vulcanized, for example; It should have a damping effect and have a suitable thickness. The latter must ensure that a pressure between the spindles can be maintained at these coated areas so that a continuous flexing work can be carried out on these layers. For the performance of this flexing work, the occurring torsional vibration and Axialschwingungsenergie is consumed in this embodiment to a certain extent and thus damped, so that the vibration energy is not destroyed in its entirety in the meshing contact and the wear attack is reduced.

Nach einem weiteren Merkmal der Erfindung ist die elastische Walkschicht außerhalb des Pumpengehäuses am saugseitigen Ende der Spindeln vorgesehen.According to a further feature of the invention, the elastic infiltration layer is provided outside the pump housing at the suction end of the spindles.

In einem anderen Falle hat es sich bei einer Schraubenspindelpumpe mit zwischen Kopfflächen der Spindelgänge verlaufenden Seitenflächen der Spindel als günstig erwiesen, dass die elastische Schicht die Seitenflächen der Spindel überdeckt, d. h. die Walkschicht ist auf die Zahnflanken der Spindel und auf den Kerndurchmesser der Antriebsspindel aufgebracht. Die Außendurchmesser sind hier nicht beschichtet. Dadurch wird in dreidimensionaler Richtung Walkarbeit in höherem Maß geleistet und die Dämpfungswirkung ist in größerem Maße zu erwarten als bei zuvor umrissener Ausführung.In another case, it has been found in a screw pump with running between top surfaces of the spindle threads side surfaces of the spindle to be favorable that the elastic layer covers the side surfaces of the spindle, d. H. the flexing layer is applied to the tooth flanks of the spindle and to the core diameter of the drive spindle. The outer diameters are not coated here. As a result, flexing work is performed to a greater extent in the three-dimensional direction and the damping effect is to be expected to a greater extent than in the previously outlined embodiment.

Eine weitere Ausbildung der Schraubenspindelpumpe weist gegebenenfalls querschnittlich teilkreisförmig gekrümmte Kopfflächen der Spindelgänge und sich zwischen den Kopfflächen erstreckende Seitenflächen der Spindel auf; erfindungsgemäß sind sowohl die Kopfflächen des Spindelganges als auch die Seitenflächen der Spindel mit der elastischen Schicht abgedeckt; letztere ergibt eine geschlossene hülsenartige Umhüllung. Alle im Zahneingriff stehenden Oberflächen sind auf eine begrenzte Länge beschichtet; das höchste Maß an Walkarbeit muss hier verrichtet werden und wird deshalb die höchste Dämpfungswirkung anbieten.A further embodiment of the screw pump optionally has cross-sectional part-circular curved head surfaces of the spindle gears and between the top surfaces extending side surfaces of the spindle; According to the invention, both the top surfaces of the spindle gear and the side surfaces of the spindle are covered with the elastic layer; the latter gives a closed sleeve-like envelope. All meshed surfaces are coated to a limited length; The highest level of flexing work must be done here and will therefore offer the highest damping effect.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnung; diese zeigt in

Fig. 1:
die Seitenansicht der Spindeln einer erfindungsgemäßen Schraubenspindelpumpe;
Fig. 2:
die Draufsicht auf den Spindelsatz nach Fig. 1;
Fig. 3:
die vergrößerte Darstellung eines Abschnittes der Fig. 2;
Fig. 4:
einen vergrößerten Abschnitt der Fig. 3;
Fig. 5:
einen vergrößerten Querschnitt durch einen Teil der Fig. 4 nach deren Linie V-V;
Fig. 6:
eine Schrägsicht auf die Spindeln der Schraubenspindelpumpe;
Fig. 7:
eine Draufsicht auf einen anderen Spindelsatz einer Schraubenspindelpumpe;
Fig. 8 bis Fig. 10:
jeweils den vergrößerten Querschnitt durch Fig. 6 nach deren Linie VIII-X zu drei unterschiedlichen Ausgestaltungen.
Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawing; this shows in
Fig. 1:
the side view of the spindles of a screw pump according to the invention;
Fig. 2:
the top view of the spindle set of Fig. 1;
3:
the enlarged view of a portion of Fig. 2;
4:
an enlarged portion of Fig. 3;
Fig. 5:
an enlarged cross-section through a part of Figure 4 along its line VV.
Fig. 6:
an oblique view of the spindles of the screw pump;
Fig. 7:
a plan view of another spindle set of a screw pump;
8 to 10:
in each case the enlarged cross section through Fig. 6 along the line VIII-X to three different embodiments.

Eine aus Gründen der Übersichtlichkeit in ihrer Gesamtheit nicht dargestellten Schraubenspindelpumpe weist im Innenraum eines Pumpenlaufgehäuses eine Antriebsspindel 10 auf, die von zwei Dicht- oder Laufspindeln 30 flankiert ist. Die Längsachsen A bzw. B der Antriebsspindel 10 sowie der beiden Laufspindeln 30 verlaufen parallel zueinander.A for reasons of clarity in its entirety not shown screw pump has in the interior of a pump housing a drive spindle 10 which is flanked by two sealing or running spindles 30. The longitudinal axes A and B of the drive spindle 10 and the two spindles 30 are parallel to each other.

Die Antriebsspindel 10 weist an einem metallischen Spindelkörper 12 einer Länge a an der in Fig. 1 bis 3 rechts liegenden Druckseite eine koaxiale -- querschnittlich mehrfach gestufte -- Spindelwelle 14 des Durchmessers b auf mit einem -- Drollenuten anbietenden -- Ausgleichskolben 15. Diesem liegt in Einbaustellung innenseitig -- nicht erkennbar -- ein Flansch bzw. eine Stirnwand jenes Pumpenlaufgehäuses an. Vom Ausgleichskolben 15 geht zum Spindelkörper 12 hin ein koaxialer Wellenabschnitt 14a des Durchmesser b1 aus.The drive spindle 10 has on a metallic spindle body 12 of a length a to the right in Fig. 1 to 3 pressure side a coaxial - cross-sectionally multi-stepped - spindle shaft 14 of diameter b with a - Drollenuten offering - compensating piston 15. This is in the installed position on the inside - not recognizable - a flange or an end wall of that pump housing. From the compensating piston 15 goes to the spindle body 12 toward a coaxial shaft portion 14 a of the diameter b 1 .

Der Durchmesser d des Spindelkörpers 12 wird im übrigen von einem spiralartig angeordneten Spindelgang 33 der Antriebsspindel 10 bestimmt, der mit entsprechenden metallischen Spindelgängen 33 der Laufspindeln 30 kämmt.The diameter d of the spindle body 12 is otherwise determined by a spirally arranged spindle gear 33 of the drive spindle 10, which meshes with corresponding metallic spindle gears 33 of the spindles 30.

Andernends -- also saugseitig -- sind die beiden metallischen Dicht- oder Laufspindeln 30, die ebenfalls jeweils einen Spindelkörper 32 enthalten, in einem in der Zeichnung vernachlässigten Pumpendeckel gelagert. Ein saugseitigeszylindrisch ausgebildetes -- Wellenende 16 mit zylindrischem Stirnzapfen 18 der Antriebsspindel 10 liegt zwischen beidseits benachbarten Endabschnitten der Dicht- oder Laufspindel 30, und diese enden ihrerseits jeweils mit einem zylindrischen Stirnzapfen 34. Diese Stirnzapfen 18, 34 liegen gemäß Fig. 5 in einer gemeinsamen Ebene E.At the other end - ie suction side - are the two metallic sealing or running spindles 30, which also each contain a spindle body 32, stored in a neglected in the drawing pump cover. A suction-side cylindrical design - shaft end 16 with cylindrical end pin 18 of the drive spindle 10 is located between adjacent end portions of the sealing or running spindle 30, and these in turn each end with a cylindrical end pin 34. These end pins 18, 34 are shown in FIG. 5 in a common Level E.

Die Stirnzapfen 34 der Dicht- und Laufspindeln 30 sowie der Stirnzapfen 18 der Antriebsspindel 10 sind von gleichem Durchmesser c und jeweils von einem Rohrnapf 40 aus flexiblem Werkstoff der Länge q überdeckt, der endwärts durch einen angeformten Napfboden 41 geschlossen ist; die miteinander fluchtenden Napfböden 42 überspannen jeweils die freie Stirn 19 bzw. 35 des zugeordneten Stirnzapfens 18 bzw. 34. Die Napfböden 42 an den Laufspindeln 30 sind gemäß Fig. 2, 3 mit diametral angeformten Innenrippen 42 versehen und stoßen mit ihrem Kamm an die anschließende Stirn 35.The end pins 34 of the sealing and running spindles 30 and the end pins 18 of the drive spindle 10 are covered by the same diameter c and each of a pipe cup 40 made of flexible material of length q, which is closed endwise by a molded cup bottom 41; the aligned cup bases 42 each span the free end 19 and 35 of the associated spigot 18 and 34. The cup bases 42 on the spindles 30 are shown in FIG. 2, 3 provided with diametrically molded inner ribs 42 and abut with their comb to the subsequent Forehead 35.

Durch die Rotation der Spindeln 10, 30 rollen dir Rohrnäpfe 40 aneinander ab und werden gemäß Fig. 5 beidseits des mittleren Stirnzapfens 18 sowie beidseits jener Ebene E zeitweilig verformt (Feld S); die Querschnittsmittelachsen M der beiden Stirnzapfen 34 der Laufspindeln 30 werden bei diesem Verformungsvorgang aus ihren Ruhepositionen Mr zum mittleren Stirnzapfen 18 hin verschoben. Durch diese die Dicke z der Rohrnapfwandungen 44 verändernde Verformung wird ein die Spindellage verändernder Walkvorgang erzeugt.As a result of the rotation of the spindles 10, 30, tube cups 40 roll off one another and, as shown in FIG. 5, are temporarily deformed on both sides of the central spigot 18 and on both sides of that plane E (panel S); the cross-sectional mid-axes M of the two end pins 34 of the spindles 30 are displaced from their rest positions M r to the central end pin 18 in this deformation process. As a result of this deformation changing the thickness z of the tube wall walls 44, a milling operation is changed which changes the spindle position.

Fig. 8 verdeutlicht zur Querachse Q symmetrischen Querschnitts des Spindelsatzes der Fig. 7 eine Ausgestaltung des Spindelkörpers 12, der sich aus einem zentrischen Abschnitt 20 kreisförmiger Außenkontur des Durchmessers d1 sowie zwei -- in jener Querachse Q liegenden -- Anformungen 22 etwa ovaler Gestaltung als Spindelprofil zusammensetzt; Fig. 8 verdeutlicht auch, dass die Höhe h dieser Anformungen 22 kürzer ist als der zentrische Spindeldurchmesser d1. In dieser Ausgestaltung verlaufen neben dem Wellenabschnitt 14a der Spindelwelle 14 zwei achsparallele Wellenstümpfe 31 der Laufspindeln 30.Fig. 8 illustrates the transverse axis Q symmetrical cross section of the spindle set of Fig. 7 shows an embodiment of the spindle body 12, which consists of a central portion 20 circular outer contour of the diameter d 1 and two - lying in that transverse axis Q - projections 22 approximately oval design composed as a spindle profile; FIG. 8 also illustrates that the height h of these projections 22 is shorter than the central spindle diameter d 1 . In this embodiment, in addition to the shaft portion 14 a of the spindle shaft 14 , two axially parallel shaft stubs 31 of the spindles 30 run.

Am saugseitigen Ende -- also außerhalb des die Spindeln 10, 30 umschließenden Pumpenlaufgehäuses -- sind die drei Spindeln 10, 30 auf eine bestimmte Länge von einer elastischen -- also dämpfenden -- Schicht umgeben, die beispielsweise aufvulkanisiert ist. Die elastische Schicht muss nun in einer entsprechenden Dicke z ausgeführt sein, dass eine Pressung zwischen den Spindeln 10, 30 an diesen beschichteten Stellen so aufrechterhalten werden kann, dass sie ihrerseits zu einer dauernden Walkarbeit an diesen Schichten führt. Für die Verrichtung dieser Walkarbeit wird zu einem bestimmten Maß die auftretende Drehschwingungs- und Axialschwingungsenergie verbraucht und damit gedämpft, so dass die Schwingungsenergie nicht mehr in gesamter Größe im Zahneingriffskontakt vernichtet wird. Hierdurch wird der Verschleißangriff erheblich reduziert.At the suction end - ie outside of the spindles 10, 30 enclosing the pump housing - the three spindles 10, 30 are surrounded by a certain length of an elastic - ie damping - layer, which is vulcanized, for example. The elastic layer must now be designed in a corresponding thickness z, that a pressure between the spindles 10, 30 can be maintained at these coated locations so that in turn leads to a continuous flexing work on these layers. For the performance of this flexing work, the occurring torsional vibration and axial vibration energy is consumed to a certain extent and thus damped, so that the vibration energy is no longer destroyed in its entirety in the meshing contact. As a result, the wear attack is significantly reduced.

So sind in Fig. 8 die querschnittlich in einer -- von den Zahnflächen des Spindelganges 13 bestimmten -- Kreiskontur K verlaufenden sog. Kopfflächen 23 der Anformungen 22 von der ihrer querschnittlichen Krümmung angepassten (Walk-) Schicht 50 überlagert. Letztere ist -- wie gegebenenfalls auch der oben beschriebene Rohrnapf 40 -- aus einem Elastomer geformt; dieser Werkstoff muss chemisch beständig sein, dies vor allem im Hinblick auf Emulsionen, Öl oder Wasser. Die ebenfalls teilkreisförmige Außenfläche 52 der Schicht 50 verläuft in einer Kreiskontur K1; deren Abstand von der benachbarten Kreiskontur K bestimmt die Schichtdicke z.Thus, in Fig. 8, the cross-section in a - determined by the tooth surfaces of the spindle gear 13 - circular contour K extending so-called head surfaces 23 of the projections 22 of the cross-sectional curvature adapted (Walk) layer 50 superimposed. The latter is - as possibly also the above-described pipe cup 40 - formed from an elastomer; This material must be chemically resistant, especially with regard to emulsions, oil or water. The likewise part-circular outer surface 52 of the layer 50 extends in a circular contour K 1 ; whose distance from the adjacent circle contour K determines the layer thickness z.

Jede Laufspindel 30 wird querschnittlich von einer Kreiskontur N des Durchmessers e bestimmt, welche hier vom Umfang der Zahnflanken bzw. des Spindelgangs 33 abhängt. Die Lauf spindel 30 weist einen -- in der in Fig. 8 bis 10 skizzierten Stellung eine gemeinsame Mittelachse T bestimmenden -- I-förmigen Querschnitt auf mit einem Stegbereich 36, der beidends in angeformte Kopferweiterungen 38 übergeht; die querschnittliche Gestalt von deren Zahnflanken oder Kopfflächen 39 werden von jener Kreiskontur N bestimmt und sind somit jeweils querschnittlich teilkreisförmig gestaltet. Die Kopfflächen 39 werden im Ausführungsbeispiel der Fig. 8 jeweils von einer -- ebenfalls aus elastomerem Werkstoff geformten -- Schicht 54 überspannt, deren Außenfläche 56 in einer Kreiskontur N1 liegt. Der radiale Konturenabstand bestimmt die Dicke y der Schicht 54.Each running spindle 30 is determined cross-sectionally by a circular contour N of the diameter e, which here depends on the circumference of the tooth flanks or of the spindle passage 33. The barrel spindle 30 has a - in the sketched in Fig. 8 to 10 position a common center axis T determining - I-shaped cross-section on with a web portion 36, which merges into integrally formed head extensions 38 at both ends; the cross-sectional shape of the tooth flanks or top surfaces 39 are determined by that circular contour N and are therefore each designed cross-sectionally part-circular. In the exemplary embodiment of FIG. 8, the top surfaces 39 are respectively spanned by a layer 54, which is likewise formed of elastomeric material, whose outer surface 56 lies in a circular contour N 1 . The radial contour spacing determines the thickness y of the layer 54.

Beim Ausführungsbeispiel der Fig. 9 sind jene Kopfflächen 23 der Anformungen 22 der Antriebsspindel 10 frei, hingegen die zwischen diesen querschnittlich verlaufenden Seitenflächen 24 der Anformungen 22 und des zentrischen Abschnitts 20 jeweils von einer Schicht oder Walkschicht 26 abgedeckt; letztere enthält -- dem Spindelquerschnitt entsprechend -- querschnittlich drei rinnenförmig gekrümmte Abschnitte. Die Laufspindeln 30 tragen hier Flankenschichten oder -schalen 58 auf den Seitenflächen 37 der Stegbereiche 36. Bei dieser Ausgestaltung ist also auf dem -- der Fig. 9 entsprechenden -- gleichen Längenabschnitt die Walkschicht aber in den Zahnflanken 13, 33 aller drei Spindeln 10, 30 und am Kerndurchmesser der Antriebsspindel 10 aufgebracht. Die Außendurchmesser sind nicht beschichtet. Dadurch wird in dreidimensionaler Richtung Walkarbeit in höherem Maß geleistet und die Dämpfungswirkung ist in größerem Maße zu erwarten als bei der Ausführung nach Fig. 9.In the embodiment of Figure 9 those top surfaces 23 of the projections 22 of the drive spindle 10 are free, however, the between these cross-sectional side surfaces 24 of the projections 22 and the central portion 20 each covered by a layer or flexing layer 26; The latter contains - cross-sectionally three channel-shaped curved sections - corresponding to the spindle cross-section. The spindles 30 here carry flank layers or shells 58 on the side surfaces 37 of the web portions 36. In this embodiment, therefore, on the - Fig. 9 corresponding - same length section of the flex layer but applied in the tooth flanks 13, 33 of all three spindles 10, 30 and the core diameter of the drive spindle 10. The outside diameters are not coated. As a result, flexing work is performed to a greater extent in the three-dimensional direction and the damping effect is to be expected to a greater extent than in the embodiment according to FIG. 9.

Schließlich zeigt Fig. 10 jeweils gänzlich von einer geschlossenen Schicht oder Hülle 28 bzw. 60 aus elastomerem Werkstoff umfangene Antriebs- und Laufspindeln 10 bzw. 30; es sind alle im Zahneingriff stehenden Oberflächen auf eine begrenzte Länge beschichtet. Dadurch muss das höchste Maß an Walkarbeit verrichtet werden, und wird deshalb mit der höchsten Dämpfungswirkung aufwarten.Finally, FIG. 10 shows drive and running spindles 10 and 30, which are completely surrounded by a closed layer or sheath 28 or 60 made of elastomeric material. all meshed surfaces are coated to a limited length. As a result, the highest level of flexing work must be done, and will therefore come up with the highest damping effect.

Claims (8)

  1. Screw pump with a drive spindle (10), provided in an impeller housing and flanked by impeller spindles (30), wherein the spindle threads (13 or 33) of the spindles (10, 30) comprising head faces (23 or 39) touch one another and the spindles (10, 30) are provided at least partially with an elastic layer (26, 28, 40, 50, 54, 58, 60),
    characterised in that
    elastic layers (50, 54) are attached like shells to the head faces (23, 39) of the spindle threads (13, 33), one elastic layer (40) being constructed like a bowl and pushed on to one end (18, 34) of the spindle (10, 30).
  2. Screw pump according to claim 1, characterised in that the elastic layer (26, 28, 40, 50, 54, 58, 60) consists of an elastomer.
  3. Screw pump according to claim 1 or 2, characterised in that the elastic layer (26, 28, 50, 54, 58, 60) is vulcanised on.
  4. Screw pump according to one of claims 1 to 3, characterised in that the elastic layer (26, 28, 40, 50, 54, 58, 60) is provided outside the impeller housing on the suction-side end of the spindles (10, 30).
  5. Screw pump with side faces (24 or 37) of the spindle (10 or 30) running between head faces (23 or 39) of the spindle threads (13 or 33) according to one of claims 1 to 4, characterised in that the elastic layer (26 or 58) overlaps the side faces (24 or 37) of the spindle (10 or 30) (Fig. 9).
  6. Screw pump according to claim 5, characterised in that the elastic layer (26 or 58) ends at the head faces (23 or 39) of the spindle threads (13 or 34).
  7. Screw pump with head faces (23 or 39) of the spindle threads (13 or 34) and side faces (24 or 37) of the spindle (10 or 30) extending between the head faces according to one of claims 1 to 4, characterised in that both the head faces (23 or 39) of the spindle thread (13 or 34) and the side faces (24 or 37) of the spindle (10 or 30) are covered by the elastic layer (28 or 60) (Fig. 10).
  8. Screw pump according to claim 7, characterised in that the elastic layers (28 or 60) of the head faces (23 or 39) of the spindle thread (13 or 34) and the elastic layers of the side faces (24 or 37) of the spindle (10 or 30) form a closed covering.
EP04012939A 2003-07-10 2004-05-29 Screw rotor pump Expired - Lifetime EP1496257B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE20310651 2003-07-10
DE20310651U 2003-07-10
DE20313288 2003-08-26
DE20313288U 2003-08-26

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EP1496257A2 EP1496257A2 (en) 2005-01-12
EP1496257A3 EP1496257A3 (en) 2005-08-17
EP1496257B1 true EP1496257B1 (en) 2007-07-18

Family

ID=32109020

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Application Number Title Priority Date Filing Date
EP04012939A Expired - Lifetime EP1496257B1 (en) 2003-07-10 2004-05-29 Screw rotor pump

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EP (1) EP1496257B1 (en)
AT (1) ATE367528T1 (en)
DE (2) DE20318594U1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106640628A (en) * 2016-10-09 2017-05-10 广东技术师范学院 Micro meshing clearance high-pressure screw pump
DE102018103446A1 (en) * 2018-02-15 2019-08-22 Michael Schröter Apparatus and method for compacting and / or displacing a fluid
DE102018222516A1 (en) 2018-12-20 2020-06-25 Audi Ag Drive device for a motor vehicle
DE102022207330A1 (en) 2022-07-19 2024-01-25 Vitesco Technologies GmbH Spindle pump stage, fluid delivery device and motor vehicle

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH232200A (en) * 1942-03-09 1944-05-15 Fried Krupp Germaniawerft Akti Screw pump.
JPS58148292A (en) * 1982-02-26 1983-09-03 Hitachi Ltd Surface processing of rotor of a screw compressor
SU1437575A1 (en) * 1987-03-17 1988-11-15 И.М.Чесноков и А.И.Чеснаков Double-screw mortar pump
JPH03290086A (en) * 1990-04-06 1991-12-19 Hitachi Ltd Screw type rotary machine, its rotor surface treatment, and dry system screw type rotary machine and its rotor surface treatment

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP1496257A2 (en) 2005-01-12
DE502004004339D1 (en) 2007-08-30
DE20318594U1 (en) 2004-04-08
EP1496257A3 (en) 2005-08-17
ATE367528T1 (en) 2007-08-15

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