EP0866918A1 - Twin feed screw - Google Patents

Twin feed screw

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Publication number
EP0866918A1
EP0866918A1 EP96920677A EP96920677A EP0866918A1 EP 0866918 A1 EP0866918 A1 EP 0866918A1 EP 96920677 A EP96920677 A EP 96920677A EP 96920677 A EP96920677 A EP 96920677A EP 0866918 A1 EP0866918 A1 EP 0866918A1
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EP
European Patent Office
Prior art keywords
flank
core
arc
pct
twin
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Granted
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EP96920677A
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German (de)
French (fr)
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EP0866918B1 (en
Inventor
Ulrich Becher
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Ateliers Busch SA
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Ateliers Busch SA
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Publication of EP0866918A1 publication Critical patent/EP0866918A1/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
    • 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 feed screws for axially parallel, off-axis operation in pumps with a pilot gear for guiding the screws in opposite directions.
  • Profile geometry, wrap angle, pitch, gap width, medium control and speed determine the pump parameters such as flow rate, efficiency, final pressure, leak rate, temperature, noise and the manufacturing effort.
  • SRM profile The geometries from SRM, Sweden, known as the SRM profile, are suitable for the construction of fast-rotating twin-feed screws with unequal profiles in multiple threads and small wrap angles for pumps with medium final pressure.
  • the screws are manufactured with wrap angles of 1080 °, 1440 °, 1800 °, etc. and have the same end profiles.
  • the outlet is controlled at the end by one of the screws with an opening along the second, involute-shaped profile flank. While maintaining the working principle of the axially moving work cells with twice the length of the slope, the profile geometry should be redesigned and defined in terms of modern series production and an improvement in the volumetric efficiency, the dynamics and the control of the medium should be achieved.
  • This object is achieved according to the invention in the case of twin-conveying screws with profile contours made of an arc of a core, a cycloid-shaped hollow flank, an outer circular arc and a second flank in that, in deviation from the known, the second flank 6, called the flank flank, connects to the core circular arc 4 at the base without kinks and that the flank 6 is at least a central, non-rising area, the saddle 7, which connects the partial side flanks thus formed, the inner flank 8 and the outer flank 9 without kinks.
  • Fig.l A set of twin feed screws in a single version with pilot gear
  • Fig.2 An execution of the profile geometry
  • Fig. 3 An embodiment 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.l.
  • Fig. 4 An embodiment of the feed screws in an axial section, in sections.
  • the feed screws 1, 2 (Fig.l and 3). Wrap angle of approx. 1600 ° and the same end profiles with a jacket flank that is composed of several flank partial curves:
  • the saddle 7 (Fig. 1 and 2) is designed in a circular arc with a radius the size of half the center distance and corresponds in installation to the saddle of the counter screw .
  • the inner flank 8 (FIG. 2) consists of an eccentric circular arc, which here is called flank circle 10 (FIG. 2), which adjoins the saddle 7 without a kink, and an extended cycloid, the root cycloid 11 (FIG. 2), which connects without kinking the core arc 4 (Fig.2 and 3).
  • the center of the flank circle of the counter screw moves with respect to the profile under consideration on a shortened epicycloid 12 (FIG. 2), the inner parallel curve of which, at a distance from the flank circle radius f, is the outer flank 9 (FIG. 2) of the profile under consideration.
  • the hollow-side cycloid 5 (FIGS. 2 and 3) is calculated with a and b.
  • the root cycloid 11 is generated by the top corner at the joint 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.

Landscapes

  • 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)
  • Addition Polymer Or Copolymer, Post-Treatments, Or Chemical Modifications (AREA)
  • Mixers Of The Rotary Stirring Type (AREA)
  • Formation And Processing Of Food Products (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Gear Transmission (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

Zwillinσs-Förderschrauben Twin screws
Die Erfindung betrifft die Profilgeometrien von Zwillings- Förderschrauben zum achsparallelen, auβenachsigen 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, Enddruck, Leckrate, Temperatur, Geräusche sowie den Fertigungsaufwand.The invention relates to the profile geometries of twin feed screws for axially parallel, off-axis operation in pumps with a pilot gear for guiding the screws in opposite directions. Profile geometry, wrap angle, pitch, gap width, medium control and speed determine the pump parameters such as flow rate, efficiency, final pressure, leak rate, temperature, noise and the manufacturing effort.
Die als SRM-Profil bekannten Geometrieen der Fa. SRM, Schweden, eignen sich zum Bau von schnelldrehenden Zwillings- Förderschrauben 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, Sweden, known as the SRM profile, are suitable for the construction of fast-rotating twin-feed screws with unequal profiles in multiple threads and small wrap angles for pumps with medium final pressure. Design-related gaps between the line of engagement and the inner edge of the housing, commonly known as "blow hole", prevent higher ultimate pressure or good volumetric efficiency at low and medium speeds.
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, there is interest in pumping higher final pressures at medium speeds, for which single-thread twin screws with an axial sequence of the work cells and wrap angles> 720 ° are better suited: By forming one flank of the single-thread profile as an elongated cycloid, symmetrical engagement lines are alternately formed, which run from the inside edges of the housing to the core circles along the outer contours of the screws. These lines of action divide the interior of the pump into axially moving work cells with twice the length of the slope 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. 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.In known embodiments, such as those available from Taiko, Japan, the screws are manufactured with wrap angles of 1080 °, 1440 °, 1800 °, etc. and have the same end profiles. The outlet is controlled at the end by one of the screws with an opening along the second, involute-shaped profile flank. While maintaining the working principle of the axially moving work cells with twice the length of the slope, the profile geometry should be redesigned and defined in terms of modern series production and an improvement in the volumetric efficiency, the dynamics and the control of the medium should 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 object is achieved according to the invention in the case of twin-conveying screws with profile contours made of an arc of a core, a cycloid-shaped hollow flank, an outer circular arc and a second flank in that, in deviation from the known, the second flank 6, called the flank flank, connects to the core circular arc 4 at the base without kinks and that the flank 6 is at least a central, non-rising area, the saddle 7, which connects the partial side flanks thus formed, the inner flank 8 and the outer flank 9 without kinks.
Anhand des in den Abbildungen dargestellten und in den Unteransprüchen 2, 3 gekennzeichneten Ausführungsbeispiels wird die Erfindung anschließend näher erläutert.The invention is subsequently explained in more detail on the basis of the exemplary embodiment illustrated in the figures and characterized in subclaims 2, 3.
Es zeigen :Show it :
Fig.l : Einen Satz Zwillings-Förderschrauben in eingängiger Ausführung mit Pilotgetriebe und mitFig.l: A set of twin feed screws in a single version with pilot gear and
Umschlingungswinkeln von ca. 1600° nach der Erfindung mit einem mittleren Sattelbereich in der Mantelflanke, in verkleinertem Maßstab.Wrap angles of approximately 1600 ° according to the invention with a central saddle area in the side of the jacket, on a reduced scale.
Fig.2 : Eine Ausführung der Profilgeometrie undFig.2: An execution of the profile geometry and
Eingriffsverhältnisse mit dem Gegenprofil eines Zwillings-Förderschraubensatzes von Fig.l.Interaction with the counter profile of a twin screw set from Fig.l.
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.l. Fig.4 : Eine Ausführung der Förderschrauben in einem axialen Schnitt, ausschnittweise.Fig. 3: An embodiment 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.l. Fig. 4: An embodiment of the feed screws in an axial section, in sections.
In der gewählten Ausführung haben die Förderschrauben 1, 2 (Fig.l und 3). Umschlingungswinkel von ca. 1600° und gleiche Stirnprofile mit einer Mantelflanke, die aus mehreren Flankenteilkurven zusammengesetzt ist : Der Sattel 7 (Fig.l 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.l and 3). Wrap angle of approx. 1600 ° and the same end profiles with a jacket flank that is composed of several flank partial curves: The saddle 7 (Fig. 1 and 2) is designed in a circular arc with a radius the size of half the center distance and corresponds in installation to the saddle of the counter screw . The inner flank 8 (FIG. 2) consists of an eccentric circular arc, which here is called flank circle 10 (FIG. 2), which adjoins the saddle 7 without a kink, and an extended cycloid, the root cycloid 11 (FIG. 2), which connects without kinking the core arc 4 (Fig.2 and 3). The center of the flank circle of the counter screw moves with respect to the profile under consideration on a shortened epicycloid 12 (FIG. 2), the inner parallel curve of which, at a distance from the flank circle radius f, is the outer flank 9 (FIG. 2) of the profile under consideration.
Zur quantitativen Festlegung wird wie folgt vorgegangen :The quantitative procedure is as follows:
1. Festsetzung des Achsabstandes: a= 100 L.E. (Längeneinheiten) .1. Determination of the center distance: a = 100 L.E. (Units of length).
2. Hieraus folgt direkt der Sattelkreisradius: d = a/2 = 50 L.E.2. The saddle circle radius follows directly from this: d = a / 2 = 50 L.E.
3. Festsetzung des Kernkreisradius: c - 23 L.E.3.Determination of the core circle radius: c - 23 L.E.
4. Hieraus folgt direkt der Außenkreisradius: b = a-c = 77 L.E.4. The outer circle radius follows directly from this: b = a-c = 77 L.E.
5. Mit a und b wird die Hohlflanken-Zykloide 5 (Fig.2 und 3) berechnet.5. The hollow-side cycloid 5 (FIGS. 2 and 3) is calculated with a and b.
Einige Zahlenwerte sind in Tabelle I aufgeführt, wobei u, v die Koordinaten eines recht winkligen Koordinatensystems mit Ursprung in der Achsmitte sind.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. 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°6. From a and b one obtains the immersion angle α, which is the area of mutual penetration of the meshing Conveying screws 1, 2 (Fig. 3) indicate: α / 2 = 49.51 °
7. Festlegung des Außenkreissektorwinkels ß: Zur Aufrechterhaltung der Funktion muß ß > α/2 werden. Festlegung ß -» 76°.7. Definition of the outer circle sector angle ß: ß> α / 2 must be maintained in order to maintain the function. Definition of ß - »76 °.
Wegen Gegeneingriff des gleichen Profils ist der Kernkreissektorwinkel ebenfalls = ß ■ 76°.Due to counter-engagement of the same profile, the core sector angle is also = ß ■ 76 °.
8. Festlegung der Schraubensteigung : 1 = 100 L.E.8. Determination of the screw pitch: 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.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 L.E. via calculations on the axial section (Fig. 4). Determination: f - 22 L.E., from which the eccentricity e of the flank circle center results: 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 ll ergibt sich der Innenflankensektorwinkel : γ = 65,94°.10. The root cycloid 11 is generated by the top corner at the joint 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 ll without kinks, the inner flank sector angle results : γ = 65.94 °.
Wegen Gegeneingriff des gleichen Profils ist der Außenflankensektorwinkel ebenfalls γ = 65,94°.Because of the counter-engagement of the same profile, the outer flank sector angle is also γ = 65.94 °.
11. Der Sattelsektorwinkel wird somit δ = 360°- 2ß-2γ = 76,12°.11. The saddle sector angle is thus δ = 360 ° - 2ß-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.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:After defining the profile contour, the following now follows:
13. Schwerpunktmittenabstand g = 21,58 L.E.13.Center center distance g = 21.58 L.E.
14. Rotorfläche - Z = 8295,4 (L.E.)2 und somit g-z = l,79*105 (L.E.)3.14.Rotor area - Z = 8295.4 (LE) 2 and thus gz = 1.79 * 10 5 (LE) 3 .
15 Wirkungsgrad η = 49,51 %.15 efficiency 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 m /h (unkorrigiert) und einer Drehzahl von 3000 UpM ergibt sich: 1 L.E. = 1 mm.16. From the operating speed and geometry data, the relative delivery rate in (LE) 3 / unit of time is obtained, which results in the equation with the corrected target delivery rate resulting in the value for 1 LE. With a target Flow rate of 250 m / h (uncorrected) and a speed of 3000 rpm results: 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 dimensional corrections that are now carried out on the profile for non-contact operation are indispensable for proper function and production and involve considerable effort, but they only play a subordinate role in the selection of the profile.
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. 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.
Tabelle I Tabelle IITable I, Table II
(L.E.) v (L.E.) u (L.E) v (L.E.)(L.E.) v (L.E.) u (L.E) v (L.E.)
0 -39,37 -30,82 ,63 - 4,18 -33,98 -38,03 ,97 - 7,24 -31,69 -41,22 ,40 - 9,32 -29,85 -43,79 ,92 -10,97 -28,20 -46,05 ,71 -11,68 -26,64 -48,12 ,53 -12,34 -25,12 -50,05 ,21 -13,48 -23,62 -51,88 ,98 -14,44 -22,10 -53,63 ,81 -15,23 -20,55 -55,30 ,72 -15,86 -18,97 -56,92 ,69 -16,34 -17,33 -58,49 ,72 -16,67 -15,64 -59,99 ,80 -16,86 -14,78 -60,73 ,93 -16,90 -12,08 -62,85 ,10 -16,78 -10,20 -64,20 ,30 -16,52 - 8,24 -65,48 ,54 -16,11 - 6,20 -66,71 ,80 -15,55 - 4,09 -67,88 ,07 -14,83 - 1,90 -68,97 ,35 -13,96 + 0,37 -70,00 ,64 -12,92 + 1,54 -70,48 ,92 -11,73 + 2,73 -70,95 ,18 -10,38 + 5,17 -71,81 ,42 - 8,86 + 7,69 -72,59 ,63 - 7,18 + 10,30 -73,28 ,80 - 5,34 + 12,99 -73,87 ,92 - 3,33 + 15,77 -74,35 ,99 - 1,15 + 17,19 -74,540 -39.37 -30.82, 63 - 4.18 -33.98 -38.03, 97 - 7.24 -31.69 -41.22, 40 - 9.32 -29.85 -43, 79, 92 -10.97 -28.20 -46.05, 71 -11.68 -26.64 -48.12, 53 -12.34 -25.12 -50.05, 21 -13.48 - 23.62 -51.88, 98 -14.44 -22.10 -53.63, 81 -15.23 -20.55 -55.30, 72 -15.86 -18.97 -56.92, 69 -16.34 -17.33 -58.49, 72 -16.67 -15.64 -59.99, 80 -16.86 -14.78 -60.73, 93 -16.90 -12, 08 -62.85, 10 -16.78 -10.20 -64.20, 30 -16.52 - 8.24 -65.48, 54 -16.11 - 6.20 -66.71, 80 - 15.55 - 4.09 -67.88, 07 -14.83 - 1.90 -68.97, 35 -13.96 + 0.37 -70.00, 64 -12.92 + 1.54 - 70.48, 92 -11.73 + 2.73 -70.95, 18 -10.38 + 5.17 -71.81, 42 - 8.86 + 7.69 -72.59, 63 - 7, 18 + 10.30 -73.28, 80 - 5.34 + 12.99 -73.87, 92 - 3.33 + 15.77 -74.35, 99 - 1.15 + 17.19 -74, 54
0 + 18,63 -74,71 0 + 18.63 -74.71

Claims

Patentansprüche claims
1. Zwillings-Förderschrauben für achsparallelen, gegenläufigen Außeneingriff mit Umschlingungswinkeln von mindestens 720° und eingängig ausgeführt mit Stirnprofilkonturen, gebildet aus Kernkreisbogen, erster, zykloidenförmiger Hohlflanke, Außenkreisbogen und zweiter Flanke, dadurch gekennzeichnet, daß auch die zweite Flanke, Mantelflanke genannt, im Fußpunkt knickfrei an den Kernkreisbogen (4) anschließt, sodaß die Hohlflanke (5) und die Mantelflanke (6) mit dem Kern (4) zusammen eine knickfreie Fläche mit gemeinsamer Bearbeitungsmöglichkeit bilden; und/ oder daß die Mantelflanke (6) zumindest einen mittleren, nicht ansteigenden Bereich, den Sattel (7) enthält, der die solchermaßen gebildeten Teil-Mantelflanken, die Innenflanke (8) und die Außenflanke (9) verbindet, wodurch gegenüber bekannten Profilen günstigere Flächenverteilung erzielt wird, derart daß Erhöhung des Volumetrischen Wirkungsgrades, Verbesserung der Dynamik sowie bessere Steuerung des Mediumaustritts und Ballastgaseintritts erreicht werden.1.Twin conveyor screws for axially parallel, counter-rotating external engagement with wrap angles of at least 720 ° and single-ended design with end profile contours, formed from an arc of a core, first, cycloid-shaped hollow flank, outer circular arc and second flank, characterized in that the second flank, called the flank flank, at the base adjoins the core arc (4) without kinks, so that the hollow flank (5) and the lateral flank (6) together with the core (4) form a kink-free surface with common processing options; and / or that the jacket flank (6) contains at least a central, non-rising area, the saddle (7), which connects the partial jacket flanks formed in this way, the inner flank (8) and the outer flank (9), which makes them cheaper than known profiles Area distribution is achieved in such a way that an increase in the volumetric efficiency, improvement in the dynamics and better control of the medium outlet and ballast gas inlet are achieved.
2. Zwillings-Förderschrauben nach Anspruch 1, dadurch gekennzeichnet, daß die Mantelflanke (6) aus mehreren Flankenteilkurven zusammengesetzt ist, derart daß der Sattel (7) kreisbogenförmig ausgeführt ist.2. Twin screws according to claim 1, characterized in that the lateral flank (6) is composed of several partial flank curves, such that the saddle (7) is designed in the shape of a circular arc.
3. Zwillings-Förderschrauben nach Anspruch 2, dadurch gekennzeichnet, daß die Innenflanke (8) aus einem exzentrischen Kreisbogen, dem hier sog. Flankenkreis (10) und einer verlängerten Zykloide, als Wurzelzykloide bezeichnet, zusammengesetzt ist, derart daß die Wurzelzykloide (11) an den Kernkreisbogen (4) anschließt und knickfrei durch den Flankenkreiε (10) mit dem Sattel (7) verbunden ist, sodaß die Außenflanke (9) , bedingt durch den jeweiligen Eingriff der Gegenschraube, die Form der Innenparallelkurve einer verkürzten Epizykloide erhält. 3. Twin screw according to claim 2, characterized in that the inner flank (8) from an eccentric arc, the so-called flank circle (10) and an extended cycloid, referred to as root cycloid, is composed such that the root cycloid (11) adjoins the core arc (4) and is connected to the saddle (7) without kinks by the flank circles (10), so that the outer flank (9), due to the respective engagement of the counter screw, receives the shape of the inner parallel curve of a shortened 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
CH3488/95 1995-12-11
CH348895 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 true EP0866918A1 (en) 1998-09-30
EP0866918B1 EP0866918B1 (en) 1999-12-29

Family

ID=25693146

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96920677A Expired - Lifetime EP0866918B1 (en) 1995-12-11 1996-07-08 Twin feed screw

Country Status (15)

Country Link
US (1) US6129535A (en)
EP (1) EP0866918B1 (en)
JP (1) JP4057059B2 (en)
KR (1) KR100384926B1 (en)
CN (1) CN1089409C (en)
AT (1) ATE188277T1 (en)
AU (1) AU720108B2 (en)
CA (1) CA2240169C (en)
CZ (1) CZ289348B6 (en)
DE (1) DE59604068D1 (en)
ES (1) ES2140867T3 (en)
NO (1) NO982675L (en)
PT (1) PT866918E (en)
SK (1) SK281393B6 (en)
WO (1) WO1997021926A1 (en)

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US6702558B2 (en) 2000-07-25 2004-03-09 Ateliers Busch Sa Twin screw rotors and displacement machines containing the same

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EP1026399A1 (en) 1999-02-08 2000-08-09 Ateliers Busch S.A. Twin feed screw
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US6702558B2 (en) 2000-07-25 2004-03-09 Ateliers Busch Sa Twin screw rotors and displacement machines containing the same

Also Published As

Publication number Publication date
SK281393B6 (en) 2001-03-12
NO982675L (en) 1998-08-07
PT866918E (en) 2000-04-28
JP2000501810A (en) 2000-02-15
ATE188277T1 (en) 2000-01-15
DE59604068D1 (en) 2000-02-03
CA2240169A1 (en) 1997-06-19
JP4057059B2 (en) 2008-03-05
EP0866918B1 (en) 1999-12-29
SK78198A3 (en) 1999-02-11
US6129535A (en) 2000-10-10
CA2240169C (en) 2007-12-04
KR19990072057A (en) 1999-09-27
CZ289348B6 (en) 2002-01-16
CZ177198A3 (en) 2000-03-15
CN1207795A (en) 1999-02-10
WO1997021926A1 (en) 1997-06-19
AU720108B2 (en) 2000-05-25
NO982675D0 (en) 1998-06-10
ES2140867T3 (en) 2000-03-01
CN1089409C (en) 2002-08-21
KR100384926B1 (en) 2003-08-21
AU6186296A (en) 1997-07-03

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