EP0866918B1 - Twin feed screw - Google Patents

Twin feed screw Download PDF

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EP0866918B1
EP0866918B1 EP96920677A EP96920677A EP0866918B1 EP 0866918 B1 EP0866918 B1 EP 0866918B1 EP 96920677 A EP96920677 A EP 96920677A EP 96920677 A EP96920677 A EP 96920677A EP 0866918 B1 EP0866918 B1 EP 0866918B1
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Prior art keywords
flank
core
pct
cover
cycloid
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German (de)
French (fr)
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EP0866918A1 (en
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Ulrich Becher
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Ateliers Busch SA
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Ateliers Busch SA
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    • 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
    • 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
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—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
    • 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

Definitions

  • the invention relates to the profile geometries of twin screws for axially parallel, external axis operation in Pumps with pilot gear for counter-rotating guidance Screws.
  • Profile geometry, wrap angle, slope, Gap width, medium control and speed determine here the pump parameters such as delivery volume, efficiency, ind pressure, Leakage rate, temperature, noise and the manufacturing effort.
  • pumps are of higher interest End pressures at medium speeds, for which catchy Twin screws with axial sequence of the work cells and Wrap angles> 720 ° are more suitable: through the Training each one flank of the catchy profiles as elongated cycloids become alternately symmetrical Lines of engagement formed by the inner edges of the housing the core circles run along the outer screw contours. These lines of action divide the interior of the pump into axially moving work cells with twice the length of the Gradient in an overlapping arrangement.
  • the screws are available with Wrap angles of 1080 °, 1440 °, 1800 ° etc. manufactured and have the same end profiles.
  • the outlet will controlled by one of the screws on the front with opening along the second, there involute profile flank.
  • This task is shared with twin screws Profile contours from a circular arc, more cycloid-shaped Hollow flank, outer arc and second flank according to the invention solved by deviating from the known also the second Flank 6, called jacket flank, at the base point without kinks to the Core arc 4 connects and that the lateral flank 6th at least a middle, non-rising area, the Saddle 7, which contains the partial side flanks thus formed, the inner flank 8 and the outer flank 9 connects without kinks.
  • the feed screws 1, 2 (Fig. 1 and 3). Wrap angle of approx. 1600 ° and the same Forehead profiles with a jacket flank made up of several Flank partial curves is composed:
  • the saddle 7 (Fig.1 and 2) is arcuate with a radius the size of the half the center distance and corresponds in the installation with the saddle of the counter screw.
  • the inner flank 8 (Fig.2) consists of a kink-free connection to the saddle 7, eccentric circular arc, here flank circle 10 (Fig. 2) called, and a kink-free extended Cycloid, the root cycloid 11 (Fig.2), for connection to the Core arc 4 (Fig. 2 and 3).
  • the center of the Flank circle of the counter screw moves with respect to the viewed profile on a shortened epicycloid 12 (Fig.2), whose inner parallel curve at a distance from the Flank circle radius f the outer flank 9 (Fig.2) of the considered profile.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Macromolecular Compounds Obtained By Forming Nitrogen-Containing Linkages In General (AREA)
  • Polyesters Or Polycarbonates (AREA)
  • Gear Transmission (AREA)
  • Mixers Of The Rotary Stirring Type (AREA)
  • Formation And Processing Of Food Products (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Addition Polymer Or Copolymer, Post-Treatments, Or Chemical Modifications (AREA)

Abstract

PCT No. PCT/CH96/00251 Sec. 371 Date Aug. 24, 1998 Sec. 102(e) Date Aug. 24, 1998 PCT Filed Jul. 8, 1996 PCT Pub. No. WO97/21926 PCT Pub. Date Jun. 19, 1997In known embodiments, media are fed in a contact-free manner in propeller pumps by single-thread twin feed screws which are guided via pilot gears, the twin feed screws having the same transverse profile with a core circle, tip circle, an involute flank and a hollow flank, enabling the pump chamber to be divided into axially staggered cells and this obtain high pressure differences in one stage. In addition to dynamics, efficiency and production, the control of the medium is also determined by the contour of the end profile, the variation of which improves all the dependent variables. According to the invention, the involute is replaced by a curve which does not rise constantly and has a central saddle region and a smooth connection to the core circle. The variations in the end face achieved thereby improve the dynamics and volumetric efficiency and extend the possibilities for controlling medium at the end face. The detailed adaption to the new curve together with the smooth connection at the base point enable the core and flanks to be produced jointly by a single tool. Feed screws with profiles of this type are suitable for flow rates of between 100 and 1000 m3/h and ultimate pressure of <0.05 mbar at speeds of rotation of approximately 3000 min-1 and approximately 50% efficiency.

Description

Die Erfindung betrifft die Profilgeometrien von Zwillings-Förderschrauben zum achsparallelen, außenachsigen Betrieb in Pumpen mit Pilotgetriebe zum gegenläufigen Führen der Schrauben. Profilgeometrie, Umschlingungswinkel, Steigung, Spaltbreite, Medium-Steuerung und Drehzahl bestimmen hierbei die Pumpenkennwerte wie Fördermenge, Wirkungsgrad, Inddruck, Leckrate, Temperatur, Geräusche sowie den Fertigungsaufwand.The invention relates to the profile geometries of twin screws for axially parallel, external axis operation in Pumps with pilot gear for counter-rotating guidance Screws. Profile geometry, wrap angle, slope, Gap width, medium control and speed determine here the pump parameters such as delivery volume, efficiency, ind pressure, Leakage rate, temperature, noise and the manufacturing effort.

Die als SRM-Profil bekannten Geometrieen der Fa. SRM, Schweden, eignen sich zum Bau von schnelldrehenden ZwillingsFörderschrauben mit ungleichen Profilen in mehrgängiger Ausführung und kleinen Umschlingungswinkeln für Pumpen mit mittlerem Enddruck. Konstruktionsbedingte Lücken zwischen Eingriffslinie und Gehäuseinnenkante, allgemein als "Blasloch" bekannt, verhindern höheren Enddruck oder guten volumetrischen Wirkungsgrad bei kleinen und mittleren Drehzahlen.The geometries from SRM known as SRM profile, Sweden, are suitable for the construction of high-speed twin screws with unequal profiles in multiple courses Version and small wrap angles for pumps with medium final pressure. Design gaps between Line of engagement and inner edge of housing, generally as "blow hole" known to prevent higher ultimate pressure or good volumetric Efficiency at low and medium speeds.

Im Dokument GB-A-746 628 wird eine Verdrängermaschine mit eingängigen Rotoren, im gegenläufigen Drehsinn arbeitend, beschrieben. Jeder Rotor besitzt eine epizykloidenförmige Konkav-Seite und eine Konvex-Seite. Die Umschlingungswinkel sind ≥360°. Bei dieser Ausbildung der Rotoren existiert kein Blasloch; sie operieren deshalb bereits bei mittleren Drehzahlen für manche Anwendungen zufrieden-stellend.In document GB-A-746 628 a positive displacement machine is described catchy rotors, working in opposite directions, described. Each rotor has an epicycloid Concave side and a convex side. The wrap angle are ≥360 °. With this design of the rotors there is none Blowhole; therefore they are already operating on medium-sized ones Speeds satisfactory for some applications.

Im vorliegenden Fall gilt das Interesse jedoch Pumpen höherer Enddrücke bei mittleren Drehzahlen, wofür eingängige Zwillingsschrauben mit axialer Sequenz der Arbeitszellen und Umschlingungswinkeln >720° besser geeignet sind : Durch die Ausbildung jeweils einer Flanke der eingängigen Profile als verlängerte Zykloide werden wechselweise symmetrische Eingriffslinien gebildet, die von den Gehäuseinnenkanten zu den Kernkreisen entlang der Schraubenaußenkonturen verlaufen. Diese Eingriffslinien unterteilen den Innenraum der Pumpe in axial wandernde Arbeitszellen mit zweifacher Länge der Steigung in überlappender Anordnung. In the present case, however, pumps are of higher interest End pressures at medium speeds, for which catchy Twin screws with axial sequence of the work cells and Wrap angles> 720 ° are more suitable: through the Training each one flank of the catchy profiles as elongated cycloids become alternately symmetrical Lines of engagement formed by the inner edges of the housing the core circles run along the outer screw contours. These lines of action divide the interior of the pump into axially moving work cells with twice the length of the Gradient in an overlapping arrangement.

In bekannten Ausführungsformen, wie beispielsweise durch die Fa. Taiko, Japan, lieferbar, sind die Schrauben mit Umschlingungswinkeln von 1080°, 1440°, 1800° etc. gefertigt und weisen gleiche Stirnprofile auf. Der Auslaß wird stirnseitig durch eine der Schrauben gesteuert mit Öffnung entlang der zweiten, dort evolventenförmigen Profilflanke. In known embodiments, such as by the Taiko, Japan, the screws are available with Wrap angles of 1080 °, 1440 °, 1800 ° etc. manufactured and have the same end profiles. The outlet will controlled by one of the screws on the front with opening along the second, there involute profile flank.

Unter Beibehaltung des Arbeitsprinzips der axial wandernden Arbeitszellen mit zweifacher Länge der Steigung soll die Profilgeometrie neu gestaltet und definiert werden im Sinne einer modernen Serienfertigung und es soll eine Verbesserung des volumetrischen Wirkungsgrades, der Dynamik und der Steuerung des Mediums erreicht werden.While maintaining the working principle of axially wandering Work cells with twice the length of the slope should Profile geometry are redesigned and defined in the sense a modern series production and it is supposed to be an improvement of volumetric efficiency, dynamics and Control of the medium can be achieved.

Diese Aufgabe wird bei Zwillings-Förderschrauben mit Profilkonturen aus Kernkreisbogen, zykloidenförmiger Hohlflanke, Außenkreisbogen und zweiter Flanke erfindungsgemäß dadurch gelöst, daß abweichend von Bekanntem auch die zweite Flanke 6, Mantelflanke genannt, im Fußpunkt knickfrei an den Kernkreisbogen 4 anschließt und daß die Mantelflanke 6 zumindest einen mittleren, nicht ansteigenden Bereich, den Sattel 7 enthält, der die solchermaßen gebildeten Teil-Manfelflanken, die Innenflanke 8 und die Außenflanke 9 knickfrei verbindet.This task is shared with twin screws Profile contours from a circular arc, more cycloid-shaped Hollow flank, outer arc and second flank according to the invention solved by deviating from the known also the second Flank 6, called jacket flank, at the base point without kinks to the Core arc 4 connects and that the lateral flank 6th at least a middle, non-rising area, the Saddle 7, which contains the partial side flanks thus formed, the inner flank 8 and the outer flank 9 connects without kinks.

Anhand des in den Abbildungen dargestellten und in den Unteransprüchen 2, 3 gekennzeichneten Ausführungsbeispiels wird die Erfindung anschließend näher erläutert.Using the shown in the pictures and in the Subclaims 2, 3 marked embodiment the invention is explained in more detail below.

Es zeigen :

Fig.1 :
Einen Satz Zwillings-Förderschrauben in eingängiger Ausführung mit Pilotgetriebe und mit Umschlingungswinkeln von ca. 1600° nach der Erfindung mit einem mittleren Sattelbereich in der Mantelflanke, in verkleinertem Maßstab.
Fig.2 :
Eine Ausführung der Profilgeometrie und Eingriffsverhältnisse mit dem Gegenprofil eines Zwillings-Förderschraubensatzes von Fig.1.
Fig.3 :
Eine Ausführung der Zwillings-Förderschrauben in einem Schnitt entsprechend der Linie A-A von Fig.1, eingebaut in einem Gehäuse, im gleichen Maßstab dargestellt wie Fig.1.
Fig.4 :
Eine Ausführung der Förderschrauben in einem axialen Schnitt, ausschnittweise.
Show it :
Fig.1:
A set of twin feed screws in a single-thread version with pilot gear and with wrap angles of approx. 1600 ° according to the invention with a middle saddle area in the lateral flank, on a reduced scale.
Fig. 2:
An execution of the profile geometry and engagement conditions with the counter profile of a twin screw set from Fig. 1.
Fig. 3:
A version of the twin feed screws in a section along the line AA of Fig.1, installed in a housing, shown on the same scale as Fig.1.
Fig. 4:
A version of the feed screws in an axial section, in sections.

In der gewählten Ausführung haben die Förderschrauben 1, 2 (Fig.1 und 3). Umschlingungswinkel von ca. 1600° und gleiche Stirnprofile mit einer Mantelflanke, die aus mehreren Flankenteilkurven zusammengesetzt ist : Der Sattel 7 (Fig.1 und 2) ist kreisbogenförmig mit einem Radius der Größe des halben Achsabstands ausgeführt und korrespondiert im Einbau mit dem Sattel der Gegenschraube. Die Innenflanke 8 (Fig.2) besteht aus einem an den Sattel 7 knickfrei anschließenden, exzentrischen Kreisbogen, hier Flankenkreis 10 (Fig.2) genannt, und einer knickfrei anschließenden verlängerten Zykloide, der Wurzelzykloide 11 (Fig.2), zur Anbindung an den Kernkreisbogen 4 (Fig.2 und 3). Der Mittelpunkt des Flankenkreises der Gegenschraube bewegt sich bezüglich des betrachteten Profils auf einer verkürzten Epizykloide 12 (Fig.2), deren innere Parallelkurve im Abstand des Flankenkreisradius f die Außenflanke 9 (Fig.2) des betrachteten Profils ist.In the selected version, the feed screws 1, 2 (Fig. 1 and 3). Wrap angle of approx. 1600 ° and the same Forehead profiles with a jacket flank made up of several Flank partial curves is composed: The saddle 7 (Fig.1 and 2) is arcuate with a radius the size of the half the center distance and corresponds in the installation with the saddle of the counter screw. The inner flank 8 (Fig.2) consists of a kink-free connection to the saddle 7, eccentric circular arc, here flank circle 10 (Fig. 2) called, and a kink-free extended Cycloid, the root cycloid 11 (Fig.2), for connection to the Core arc 4 (Fig. 2 and 3). The center of the Flank circle of the counter screw moves with respect to the viewed profile on a shortened epicycloid 12 (Fig.2), whose inner parallel curve at a distance from the Flank circle radius f the outer flank 9 (Fig.2) of the considered profile.

Zur quantitativen Festlegung wird wie folgt vorgegangen :

  • 1. Festsetzung des Achsabstandes:
    a= 100 L.E. (Längeneinheiten).
  • 2. Hieraus folgt direkt der Sattelkreisradius:
    d = a/2 = 50 L.E.
  • 3. Festsetzung des Kernkreisradius: c = 23 L.E.
  • 4. Hieraus folgt direkt der Außenkreisradius:
    b = a-c = 77 L.E.
  • 5. Mit a und b wird die Hohlflanken-Zykloide 5 (Fig.2 und 3) berechnet.
    Einige Zahlenwerte sind in Tabelle I aufgeführt, wobei u, v die Koordinaten eines recht winkligen Koordinatensystems mit Ursprung in der Achsmitte sind.
  • 6. Aus a und b erhält man den Eintauchwinkel α, der den Bereich der gegenseitigen Durchdringung der kämmenden Förderschrauben 1, 2 (Fig.3) angibt: α/2 = 49,51°
  • 7. Festlegung des Außenkreissektorwinkels β: Zur Aufrechterhaltung der Funktion muß β > α/2 werden. Festlegung β = 76°.
    Wegen Gegeneingriff des gleichen Profils ist der Kernkreissektorwinkel ebenfalls = β = 76°.
  • 8. Festlegung der Schraubensteigung : 1 = 100 L.E.
  • 9. Die Werte 1, a, b, und die Forderung gemeinsamer Bearbeitung der Flanken 5, 6 und Kern 4 mit einem Werkzeug führt über Berechnungen am Axialschnitt (Fig.4) zu einer Bedingung für den Flankenkreisradius von f ≥ 22 L.E. Festlegung : f = 22 L.E., woraus sich die Exzentrizität e der Flankenkreismitte ergibt: e = d-f = 28 L.E.
  • 10. Die Wurzelzykloide 11 wird durch die Kopfecke am Stoßpunkt Außenkreis/Außenflanke des Gegenprofils erzeugt und ist wegen gleicher Hebel a, b deckungsgleich zu einem Teil der Hohlflanke 5. Bei knickfreier Verbindung von Flankenkreis 10 und Kernkreis 4 durch die Wurzelzykloide 11 ergibt sich der Innenflankensektorwinkel : γ = 65,94°.
    Wegen Gegeneingriff des gleichen Profils ist der AuBenflankensektorwinkel ebenfalls γ = 65,94°.
  • 11. Der Sattelsektorwinkel wird somit δ = 360°- 2β-2γ = 76,12°.
  • 12. Die Werte a, e, f führen zu der Kontur der Außenflanke 9, ein Abschnitt einer Innenparallelkurve zu einer verkürzten Epizykloide. Einige Zahlenwerte sind in Tabelle II aufgeführt, wobei u, v der Definition von Tabelle I entsprechen.
    • The quantitative procedure is as follows:
  • 1. Determining the center distance:
    a = 100 LE (length units).
  • 2. The saddle circle radius follows directly from this:
    d = a / 2 = 50 LE
  • 3. Determination of the core circle radius: c = 23 LE
  • 4. The outer circle radius follows directly from this:
    b = ac = 77 LE
  • 5. The hollow-side cycloid 5 (FIGS. 2 and 3) is calculated with a and b.
    Some numerical values are listed in Table I, where u, v are the coordinates of a right angled coordinate system originating in the center of the axis.
  • 6. From a and b one obtains the immersion angle α, which indicates the area of mutual penetration of the intermeshing conveyor screws 1, 2 (FIG. 3): α / 2 = 49.51 °
  • 7. Determination of the outer circle sector angle β: To maintain the function, β> α / 2. Definition β = 76 °.
    Due to counter-engagement of the same profile, the core sector angle is also = β = 76 °.
  • 8. Determination of the screw pitch: 1 = 100 LE
  • 9. The values 1, a, b, and the requirement for joint machining of the flanks 5, 6 and core 4 with a tool leads to a condition for the flank circle radius of f ≥ 22 LE, based on calculations on the axial section (FIG. 4): f = 22 LE, from which the eccentricity e of the flank circle center results: e = df = 28 LE
  • 10. The root cycloid 11 is generated by the top corner at the outer circle / outer flank of the counter profile and is congruent to part of the hollow flank 5 due to the same levers a, b. When the flank circle 10 and core circle 4 are connected by the root cycloid 11 without kinks, the inner flank sector angle results : γ = 65.94 °.
    Because of the counter-engagement of the same profile, the outer flank sector angle is also γ = 65.94 °.
  • 11. The saddle sector angle thus becomes δ = 360 ° - 2β-2γ = 76.12 °.
  • 12. The values a, e, f lead to the contour of the outer flank 9, a section of an inner parallel curve to a shortened epicycloid. Some numerical values are listed in Table II, where u, v correspond to the definition in Table I.

    • Nach Festlegung der Profilkontur folgt nunmehr:

  • 13. Schwerpunktmittenabstand g = 21,58 L.E.
  • 14. Rotorfläche = Z = 8295,4 (L.E.)2 und somit g·z = 1,79·105 (L.E.)3.
  • 15 Wirkungsgrad η = 49,51 %.
  • 16. Aus Betriebsdrehzahl und Geometriedaten erhält man die relative Förderleistung in (L.E.)3/Zeiteinheit, woraus sich durch Gleichsetzen mit der korrigierten Soll-Förderleistung der Wert für 1 L.E. ergibt. Bei einer Soll-Förderleistung von 250 m3/h (unkorrigiert) und einer Drehzahl von 3000 UpM ergibt sich: 1 L.E. = 1 mm.
    • After defining the profile contour, the following now follows:
  • 13. Center of gravity center distance g = 21.58 LE
  • 14.Rotor area = Z = 8295.4 (LE) 2 and thus gz = 1.79x10 5 (LE) 3 .
  • 15 efficiency η = 49.51%.
  • 16. From the operating speed and geometry data, the relative delivery rate in (LE) 3 / time unit is obtained, from which the value for 1 LE results from equating with the corrected target delivery rate. With a nominal delivery rate of 250 m 3 / h (uncorrected) and a speed of 3000 rpm, the result is: 1 LE = 1 mm.

    • Die danach jetzt am Profil für berührungsfreien Betrieb noch durchgeführten Maßkorrekturen sind zwar für einwandfreie Funktion und Fertigung unerläßlich und mit erheblichem Aufwand verbunden, spielen jedoch bei der Profilauswahl nur eine untergeordnete Rolle.The following now on the profile for non-contact operation made dimensional corrections are for flawless Function and production indispensable and with considerable effort connected, but only play one when selecting a profile subordinate role.

    Der Vergleich mit bekannten Profilen zeigt eine Verbesserung des volumetrischen Wirkungsgrades um ca. 6,5%-Punkte, eine Verbesserung der Dynamik (g.z veringert um 27,2 %) und eine gemeinsame Fertigungsmöglichkeit der gesamten Ganginnenfläche, gebildet durch Kern 4, Hohlflanke 5, Innenflanke 8, Sattel 7 und Außenflanke 9. Der Flächenanteil im Bereich des Flankenkreises erlaubt eine bessere Anpassung der Steuerung des Mediums, geführt über Kanäle 13 (Fig.3) in der Gehäusestirnwand.

    Figure 00070001
    The comparison with known profiles shows an improvement in the volumetric efficiency by approx. 6.5 percentage points, an improvement in the dynamics (currently reduced by 27.2%) and a common possibility of manufacturing the entire inner surface of the aisle, formed by core 4, hollow flank 5, Inner flank 8, saddle 7 and outer flank 9. The proportion of the area in the area of the flank circle permits better adjustment of the control of the medium, guided via channels 13 (FIG. 3) in the housing end wall.
    Figure 00070001

    Claims (3)

    1. Double conveyor worms for axis-parallel, counter-running outside engagement, with angles of contact of at least 720° and designed as single-flight with end profile contours, formed from core circles (4), a first cycloid-shaped hollow flank (5), outer arcs (3) and second flank (6), characterised in that the second flank, referred to as the cover flank, also connects free of folds to the core circles (4) at the foot point, in the same way as the hollow flank (5), with the result that the hollow flank (5) and the cover flank (6) together with the core (4) form a fold-free surface with common machining potential; and that the cover flank (6) features at least one central non-rising area, the saddle (7), which connects the part cover flanks thus formed, the inner flank (8) and the outer flank (9), as a result of which a surface distribution is achieved which is more favourable in relation to known profiles, with positive effects on degree of efficiency, dynamics, and medium control.
    2. Double conveying screw according to Claim 1, characterised in that the cover flank (6) is composed of several flank part curves, in such a way that the saddle support (7) is designed in the shape of an arc.
    3. Double conveying worms according to Claim 2, characterised in that the inner flank (8) is composed of an eccentric arc, referred to here as the flank arc (10), and an extended cycloid, designated as the root cycloid, in such a way that the root cycloid (11) connects to the core circle (4) and the flank arc (10) is connected to the saddle support (7), with the result that the outer flank (9), conditioned by the engagement of the counter-worm in each case, adopts the shape of the inner parallel arcs of a truncated epicycloid.
    EP96920677A 1995-12-11 1996-07-08 Twin feed screw Expired - Lifetime EP0866918B1 (en)

    Applications Claiming Priority (7)

    Application Number Priority Date Filing Date Title
    CH348895 1995-12-11
    CH3488/95 1995-12-11
    CH348895 1995-12-11
    CH362895 1995-12-21
    CH362895 1995-12-21
    CH3628/95 1995-12-21
    PCT/CH1996/000251 WO1997021926A1 (en) 1995-12-11 1996-07-08 Twin feed screw

    Publications (2)

    Publication Number Publication Date
    EP0866918A1 EP0866918A1 (en) 1998-09-30
    EP0866918B1 true EP0866918B1 (en) 1999-12-29

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    EP (1) EP0866918B1 (en)
    JP (1) JP4057059B2 (en)
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    AU (1) AU720108B2 (en)
    CA (1) CA2240169C (en)
    CZ (1) CZ289348B6 (en)
    DE (1) DE59604068D1 (en)
    ES (1) ES2140867T3 (en)
    NO (1) NO982675L (en)
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    SK (1) SK281393B6 (en)
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    DE19725462A1 (en) * 1997-06-16 1998-12-24 Storz Endoskop Gmbh Medical gear pump for suction and rinsing
    ES2221141T3 (en) * 1998-10-23 2004-12-16 Ateliers Busch S.A. ROTORS OF TWIN CONVEYOR SCREWS.
    EP1026399A1 (en) 1999-02-08 2000-08-09 Ateliers Busch S.A. Twin feed screw
    AU5205500A (en) * 1999-06-14 2001-01-02 Wei Xiong A gear and a fluid machine with a pair of gears
    JP4282867B2 (en) * 2000-03-15 2009-06-24 ナブテスコ株式会社 Screw rotor and screw machine
    CH694339A9 (en) 2000-07-25 2005-03-15 Busch Sa Atel Twin screw rotors and those containing Ve rdraengermaschinen.
    CN100460681C (en) * 2005-01-31 2009-02-11 浙江大学 Involute line screw tooth shape of large flow double screw pump
    CN100400875C (en) * 2005-01-31 2008-07-09 浙江大学 Cycloidal screw tooth form of large flow double screw pump
    CN100392249C (en) * 2005-01-31 2008-06-04 浙江大学 Arc screw tooth shape of large flow double screw pump
    JP4669011B2 (en) * 2005-02-16 2011-04-13 アテリエ ビスク ソシエテ アノニム Improvement of rotational displacement machine with asymmetric profile rotor
    CN103195716B (en) * 2013-05-07 2015-09-02 巫修海 A kind of tooth screw stem molded line
    KR102175543B1 (en) * 2013-05-10 2020-11-06 주식회사 케이티 Method for alleviating problem of hidden node in wireless local area network system
    DE102014105882A1 (en) 2014-04-25 2015-11-12 Kaeser Kompressoren Se Rotor pair for a compressor block of a screw machine
    KR102294105B1 (en) 2019-12-09 2021-08-25 김봉군 Delivering of materials for High-Rise Building construction and apparatus thereof
    KR102282062B1 (en) 2019-12-09 2021-07-26 김봉군 Delivering of construction materials and apparatus thereof

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    GB2165890B (en) * 1984-10-24 1988-08-17 Stothert & Pitt Plc Improvements in pumps
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    JP2904719B2 (en) * 1995-04-05 1999-06-14 株式会社荏原製作所 Screw rotor, method for determining cross-sectional shape of tooth profile perpendicular to axis, and screw machine

    Also Published As

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    NO982675L (en) 1998-08-07
    ATE188277T1 (en) 2000-01-15
    ES2140867T3 (en) 2000-03-01
    JP4057059B2 (en) 2008-03-05
    CN1089409C (en) 2002-08-21
    AU720108B2 (en) 2000-05-25
    JP2000501810A (en) 2000-02-15
    PT866918E (en) 2000-04-28
    CA2240169C (en) 2007-12-04
    AU6186296A (en) 1997-07-03
    EP0866918A1 (en) 1998-09-30
    CA2240169A1 (en) 1997-06-19
    SK281393B6 (en) 2001-03-12
    US6129535A (en) 2000-10-10
    WO1997021926A1 (en) 1997-06-19
    CN1207795A (en) 1999-02-10
    SK78198A3 (en) 1999-02-11
    CZ289348B6 (en) 2002-01-16
    CZ177198A3 (en) 2000-03-15
    NO982675D0 (en) 1998-06-10
    KR19990072057A (en) 1999-09-27
    KR100384926B1 (en) 2003-08-21
    DE59604068D1 (en) 2000-02-03

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