EP0995879B1 - Twin feed screw rotors - Google Patents
Twin feed screw rotors Download PDFInfo
- Publication number
- EP0995879B1 EP0995879B1 EP98811063A EP98811063A EP0995879B1 EP 0995879 B1 EP0995879 B1 EP 0995879B1 EP 98811063 A EP98811063 A EP 98811063A EP 98811063 A EP98811063 A EP 98811063A EP 0995879 B1 EP0995879 B1 EP 0995879B1
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- European Patent Office
- Prior art keywords
- circle
- pitch
- screw
- section
- rotors
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
- F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
- F01C1/14—Rotary-piston machines or engines 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
- F01C1/16—Rotary-piston machines or engines 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
- F01C1/082—Details specially related to intermeshing engagement type machines or engines
- F01C1/084—Toothed wheels
Definitions
- the invention relates to twin screw rotors for installation in positive displacement machines for compressible media, especially pumps, which Rotors catchy executed with varying pitch and intended are, in paraxial, opposite external engagement with wrap angles of at least 720 ° and in an enclosure an axial chamber sequence to form without blast hole connections, wherein the end profile of a Kern Vietnamesebogen, a cycloid-shaped hollow flank, an outer circle arc and another flank (see WO 97/21926).
- the patent DE 87685 shows a fferenganganlwerk designated machine in which the screw rotors with variable pitch are formed.
- the machine is both a motor and a pump usable.
- the patent application EP 0697523 relates to a screw displacement machine, in which the intermeshing rotors unequal, as "male” and “female” designated screw profiles, so-called S.R.M. profiles with continuous slope change.
- the forehead profile is varied so that the tooth head angle or the length of the outer circle arc a monotonically growing function in dependence from the wrap angle.
- Such profiles have the disadvantage that a good foreclosure of the axial sequence of working cells because of the remaining Blasloches is not possible.
- the vacuum losses caused by the blow hole have efficiency losses result, so with such a Machine at least at low and medium speeds no good inner Compaction is possible.
- the published patent application DE 19530662 discloses a screw suction pump with externally meshing screw elements, at the slope the screw members continuously from their inlet end to their outlet end decreases to cause the compression of the gas to be dispensed.
- the shape of the teeth of the screw rotor exhibits an epitrochoidal and / or Archimedean curve.
- This machine has the disadvantage that the achievable internal compression rate in the geometric relationships shown moderate.
- the missing forehead profile variation fixes that anyway not good compression ratio and leads because of the reduction in depth the gap between the screw outer diameter and the housing for Screw end towards an increased leak rate.
- the laid-open specification DE 4445958 describes a screw compressor with counter-rotating, external-meshing screw elements.
- the thread helices of the screw elements are from an axial End to the second axial end away from it continuously smaller.
- Profile is proposed a rectangular or trapezoidal profile.
- a disadvantage of such Profile geometries is that they only work lossless enough, when the flight depth in relation to the diameter is small, as stated in the above Publication is executed. Such a machine thus has a big one Construction volume and a big weight. It is another disadvantage of such Profile geometries that require extremely high pitch changes are when a satisfactory internal compression rate is to be achieved. How in the mentioned DE 19530662 also fixed here the missing Stirnprofilvariation this shortcoming and this leads to an increased leakage rate due to reduction the depth of the gap between screw outside diameter and housing towards the end of the screw.
- the invention is the Task to propose twin screw rotors, which the above have not mentioned disadvantages.
- the slope is not monotonous and as a dependent variable of the wrap angle is defined that the slope in a first portion of the suction end of the screw increases and after about one wrap reaches a maximum value that the slope in one to the first subarea subsequent second portion decreases and about one wrap reaches a minimum value before the pressure end of the screw and that the Gradient in a subsequent to the second portion third portion is substantially constant.
- FIG. 1 shows an exemplary embodiment of a pair of screw rotors 1 and 2 which stand together in an axially parallel external engagement.
- FIGS. 2 and 3 show each of the rotors 1 and 2 according to FIG. 1 separately. It can be clearly seen in these figures that the outer shell and the core are cylindrical and thus the flight depth is constant over the screw length.
- the mass ⁇ w 1 and ⁇ w 3 show that the pitch of the screw varies along the axis, but that the height h of the helical outer cylindrical rotor surface remains constant, whereby leakage losses between rotor and housing inner wall against the pressure side, as at Some of the above-mentioned machines according to the prior art occur in an undesirable manner, be avoided.
- the reference numeral 7 designates the reference spiral in this figure, which will be discussed in more detail later, and 8 is the second limiting spiral of the outer cylindrical rotor surface.
- FIG. 4 shows a rotor in a section at right angles to the rotor axis.
- the resulting end profile has a Kem Vietnamesebogen 3 with a constant over the entire screw length radius Rb, which - in a clockwise direction - after a sector angle ⁇ in a cycloid-shaped hollow flank 4 passes.
- the geometry of the hollow flank 4 is unchanged over the entire screw length.
- At the hollow flank 4 closes at point B at an acute angle an outer circle arc 5 with a constant over the entire screw length radius Ra, which passes to a sector angle ⁇ at point C in a further edge 6.
- the variation of the front profile contour along the screw axis is based on a change in the sector angle ⁇ and on a change in the geometry of the further flank 6.
- the variation of the sector angle ⁇ along the screw axis is preferably at least spatially approximately equidistant course of a reference spiral formed by the outermost points of the hollow flank B ⁇ (7 in FIG. 3) and the second limiting spiral (points C) (8 in FIG. 3) of the outer cylindrical rotor surface.
- FIG. 5 shows in a diagram the development w of the reference spiral mentioned in connection with FIG. 4 as a function of the wrap angle ⁇ .
- a straight line g and corresponding sections P 0 , 2P 0, etc. of the development of a spiral with a constant pitch are shown.
- the course of the slope is more clearly recognizable when the first derivative shown in Figure 6 the settlement w considered.
- w 'increases and, at ⁇ 2 ⁇ , reaches the maximum value (1 + A) * L 0 / 2 ⁇ , where A is the amplitude moderator.
- FIG. 7 shows the chamber cross-section F as a function of the wrap angle ⁇ , wherein the curve F o shown by a solid line shows the chamber cross-section without profile variation and the dashed curve F m shows the chamber cross-section with profile variation.
- Figure 8a the cross section is shown of the invention for receiving twin screw rotors certain housing
- Figure 8b shows one of the representation of Figure 4 corresponding section through the rotors
- in figure 8c the chamber cross-section F o is shown hatched.
- FIGS. 9a to 9p the development of the working chamber cross section is shown in end sections represented as a function of the wrap angle. The latter is indicated in the figures in degrees.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Rotary Pumps (AREA)
- Cleaning In General (AREA)
- Compressor (AREA)
- Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
- Extrusion Moulding Of Plastics Or The Like (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Treatment Of Fiber Materials (AREA)
Description
Die Erfindung betrifft Zwillingsschraubenrotoren zum Einbau in Verdrängermaschinen für kompressible Medien, insbesondere Pumpen, welche Rotoren eingängig mit variierender Steigung ausgeführt und dazu bestimmt sind, in achsparallelem, gegenläufigem Ausseneingriff mit Umschlingungswinkeln von mindestens 720° zu stehen und in einem Gehäuse eine axiale Kammersequenz ohne Blaslochverbindungen zu bilden, wobei das Stirnprofil aus einem Kernkreisbogen, einer zykloidenförmigen Hohlflanke, einem Aussenkreisbogen und einer weiteren Flanke besteht (siehe WO 97/21926).The invention relates to twin screw rotors for installation in positive displacement machines for compressible media, especially pumps, which Rotors catchy executed with varying pitch and intended are, in paraxial, opposite external engagement with wrap angles of at least 720 ° and in an enclosure an axial chamber sequence to form without blast hole connections, wherein the end profile of a Kernkreisbogen, a cycloid-shaped hollow flank, an outer circle arc and another flank (see WO 97/21926).
Die Patentschrift DE 87685 zeigt eine als Schraubenräderkapselwerk bezeichnete Maschine, bei der die Schraubenrotoren mit veränderlicher Steigung ausgebildet sind. Die Maschine ist sowohl als Motor als auch als Pumpe verwendbar. Um - beim Betrieb als Motor - die Zunahme des Volumens der Arbeitskammem in Richtung des sich entspannenden Mediums zusätzlich zu steigern, sind die Rotoren wahlweise konisch ausgebildet.The patent DE 87685 shows a Schraubenräderkapselwerk designated machine in which the screw rotors with variable pitch are formed. The machine is both a motor and a pump usable. To - when operating as an engine - the increase in the volume of Arbeitskammem in addition to boosting the relaxing medium the rotors are optionally conical.
In der Patentschrift DE 609405 ist eine Luftkältemaschine mit Verdichter und Entspanner beschrieben, die beide Schraubenpaare mit veränderlicher Steigung und Gangtiefe aufweisen. Die Hüllflächen der Rotoren sind konisch ausgebildet.In the patent DE 609405 is an air chiller with compressor and expander described, the two screw pairs with variable Have slope and flight depth. The envelope surfaces of the rotors are conical educated.
Beide der vorher genannten Maschinen haben den Nachteil, dass sie konische Zylinder erfordern, wodurch die Rotoren nur auf einer Seite ein- und ausgebaut werden können. Dies erhöht den Aufwand bei der Montage- und Demontage der Maschinen, was insbesondere bei Unterhalts- und Reinigungsarbeiten sehr nachteilig ist.Both of the aforementioned machines have the disadvantage that they conical cylinders require, whereby the rotors on one side only and can be expanded. This increases the effort in the assembly and Dismantling of the machines, especially during maintenance and cleaning work is very disadvantageous.
Die Patentanmeldung EP 0697523 betrifft eine Schrauben-Verdrängermaschine, bei der die miteinander im Eingriff stehenden Rotoren ungleiche, als "männlich" und "weiblich" bezeichnete Schraubenprofile, sogenannte S.R.M.-Profile mit kontinuierlicher Änderung der Steigung haben. Das Stirnprofil ist dabei derart variiert, dass der Zahnkopfwinkel beziehungsweise die Länge des Aussenkreisbogens eine monoton wachsende Funktion in Abhängigkeit vom Umschlingungswinkel ist. Solche Profile haben den Nachteil, dass eine gute Abschottung der axialen Sequenz von Arbeitszellen wegen des verbleibenden Blasloches nicht möglich ist. Die durch das Blasloch verursachten Vakuumverluste haben Wirkungsgradverluste zur Folge, so dass mit einer solchen Maschine zumindest bei kleinen und mittleren Drehzahlen keine gute innere Verdichtung möglich ist.The patent application EP 0697523 relates to a screw displacement machine, in which the intermeshing rotors unequal, as "male" and "female" designated screw profiles, so-called S.R.M. profiles with continuous slope change. The forehead profile is varied so that the tooth head angle or the length of the outer circle arc a monotonically growing function in dependence from the wrap angle. Such profiles have the disadvantage that a good foreclosure of the axial sequence of working cells because of the remaining Blasloches is not possible. The vacuum losses caused by the blow hole have efficiency losses result, so with such a Machine at least at low and medium speeds no good inner Compaction is possible.
Die Offenlegungsschrift DE 19530662 offenbart eine Schraubensaugpumpe mit aussen kämmenden Schraubenelementen, bei der die Steigung der Schraubenelemente kontinuierlich von ihrem Einlassende zu ihrem Auslassende abnimmt, um die Kompression des abzugebenden Gases zu veranlassen. Die Form der Zähne des Schraubenrotors weist eine epitrochoidale und/oder archimedische Kurve auf. Diese Maschine hat den Nachteil, dass die erreichbare innere Verdichtungsrate bei den gezeigten geometrischen Verhältnissen mässig ist. Zudem fixiert die fehlende Stirnprofil-Variation das ohnehin nicht gute Verdichtungsverhältnis und führt wegen der Verringerung der Tiefe des Spaltes zwischen Schraubenaussendurchmesser und Gehäuse zum Schraubenende hin zu einer erhöhten Leckrate.The published patent application DE 19530662 discloses a screw suction pump with externally meshing screw elements, at the slope the screw members continuously from their inlet end to their outlet end decreases to cause the compression of the gas to be dispensed. The shape of the teeth of the screw rotor exhibits an epitrochoidal and / or Archimedean curve. This machine has the disadvantage that the achievable internal compression rate in the geometric relationships shown moderate. In addition, the missing forehead profile variation fixes that anyway not good compression ratio and leads because of the reduction in depth the gap between the screw outer diameter and the housing for Screw end towards an increased leak rate.
Die Offenlegungsschrift DE 4445958 beschreibt einen Schraubenverdichter mit gegenläufig rotierenden, aussenkämmenden Schraubenelementen. Die Gewindewendeln der Schraubenelemente werden vom einen axialen Ende zum davon entfernten zweiten axialen Ende hin kontinuierlich kleiner. Als Profil wird ein Rechteck- oder Trapezprofil vorgeschlagen. Ein Nachteil solcher Profilgeometrien besteht darin, dass sie nur genügend verlustfrei arbeiten, wenn die Gangtiefe in Relation zum Durchmesser gering ist, wie dies in der genannten Publikation ausgeführt ist. Eine solche Maschine weist somit ein grosses Bauvolumen und ein grosses Gewicht auf. Es ist ein weiterer Nachteil solcher Profilgeometrien, dass extrem hohe Steigungsänderungen erforderlich sind, wenn eine befriedigende innere Verdichtungsrate erreicht werden soll. Wie bei der erwähnten DE 19530662 fixiert auch hier die fehlende Stirnprofilvariation dieses Manko und dieses führt zu einer erhöhten Leckrate wegen Verringerung der Tiefe des Spaltes zwischen Schraubenaussendurchmesser und Gehäuse zum Schraubenende hin. The laid-open specification DE 4445958 describes a screw compressor with counter-rotating, external-meshing screw elements. The thread helices of the screw elements are from an axial End to the second axial end away from it continuously smaller. As Profile is proposed a rectangular or trapezoidal profile. A disadvantage of such Profile geometries is that they only work lossless enough, when the flight depth in relation to the diameter is small, as stated in the above Publication is executed. Such a machine thus has a big one Construction volume and a big weight. It is another disadvantage of such Profile geometries that require extremely high pitch changes are when a satisfactory internal compression rate is to be achieved. How in the mentioned DE 19530662 also fixed here the missing Stirnprofilvariation this shortcoming and this leads to an increased leakage rate due to reduction the depth of the gap between screw outside diameter and housing towards the end of the screw.
Weitere Publikationen, wie beispielsweise SE 85331, DE 2434782 und DE 2434784 betreffen innenachsige Schraubenmaschinen mit nicht konstanter Steigung der Schrauben oder variierenden Stirnprofilen. Diese Maschinen weisen alle den Nachteil auf, dass der Bauaufwand hoch ist und dass in jedem Fall auch saugseitig dynamische Dichtungen benötigt werden.Other publications, such as SE 85331, DE 2434782 and DE 2434784 relate to internal-axis screw machines with non-constant Slope of the screws or varying forehead profiles. These machines all have the disadvantage that the construction cost is high and that in In any case, also on the intake side dynamic seals are needed.
Ferner gibt es einige Publikationen, beispielsweise DE 2934065, DE2944714, DE 3332707 und AU 261792, welche zweiwellige Verdichter mit schraubenähnlichen Rotoren beschreiben. Dort sind die Rotoren und in einigen Fällen auch das Gehäuse aus axial hintereinander angeordneten Profilscheiben unterschiedlicher Dicke und/oder Kontur zusammengesetzt und bewirken solchermassen innere Verdichtung. Alle Maschinen mit schraubenähnlichen Rotoren haben den Nachteil, dass ihr Wirkungsgrad gegenüber demjenigen von Maschinen mit schraubenförmigen Rotoren vermindert ist, weil durch den gestuften Aufbau Schadräume und Wirbelzonen entstehen. Ferner sind bei schraubenähnlichen Rotoren Probleme bezüglich Formkonstanz zu erwarten, da sie sich im Betrieb erwärmen.There are also some publications, for example DE 2934065, DE 2944714, DE 3332707 and AU 261792, which two-shaft compressor with describe screw-like rotors. There are the rotors and in some Cases also the housing of axially successively arranged profile discs composed of different thickness and / or contour and cause such internal compression. All machines with screw-type rotors have the disadvantage that their efficiency over that of machines is reduced with helical rotors, because by the stepped Construction of dead spaces and vortex zones arise. Furthermore, in screw-like Rotors to expect problems in terms of shape consistency, as they to warm up during operation.
Ausgehend von diesem Stand der Technik liegt der Erfindung die Aufgabe zugrunde, Zwillingsschraubenrotoren vorzuschlagen, welche die oben erwähnten Nachteile nicht aufweisen.Based on this prior art, the invention is the Task to propose twin screw rotors, which the above have not mentioned disadvantages.
Diese Aufgaben werden gemäss der Erfindung dadurch gelöst, dass die Steigung nicht monoton verläuft und als abhängige Variable vom Umschlingungswinkel definiert ist, dass die Steigung in einem ersten Teilbereich vom saugseitigen Schraubenende her zunimmt und nach ca. einer Umschlingung einen Maximalwert erreicht, dass die Steigung in einem an den ersten Teilbereich anschliessenden zweiten Teilbereich abnimmt und ca. eine Umschlingung vor dem druckseitigen Schraubenende einen Minimalwert erreicht und dass die Steigung in einem an den zweiten Teilbereich anschliessenden dritten Teilbereich im wesentlichen konstant ist.These objects are achieved according to the invention in that the slope is not monotonous and as a dependent variable of the wrap angle is defined that the slope in a first portion of the suction end of the screw increases and after about one wrap reaches a maximum value that the slope in one to the first subarea subsequent second portion decreases and about one wrap reaches a minimum value before the pressure end of the screw and that the Gradient in a subsequent to the second portion third portion is substantially constant.
Besondere Ausführungsarten der Erfindung sind in den abhängigen Ansprüchen umschrieben. Particular embodiments of the invention are in the dependent Claims circumscribed.
Die Erfindung wird nachstehend unter Bezugnahme auf in den Zeichnungen dargestellte Ausführungsarten näher beschrieben. Es zeigt
Figur 1- ein Paar miteinander in Eingriff stehende Schraubenrotoren,
- Figur 2
- den rechtsgängigen Rotor,
- Figur 3
- den linksgängigen Rotor,
- Figur 4
- einen Stirnschnitt eines Schraubenrotors mit variierendem Profil,
Figur 5- die Abwicklung der Referenzspirale eines erfindungsgemässen Rotors,
- Figur 6
- den Steigungsverlauf der Abwicklung gemäss Figur 4,
Figur 7- den Verlauf des Arbeitskammerquerschnitts bei einer Maschine ohne und mit Profilvariation,
- Figur 8a bis 8c
- Gehäuse-, Rotor-, und Arbeitskammerquerschnitt eines mit erfindungsgemässen Rotoren ausgestatteten Verdichters und
- Figur 9a bis 9p
- Stirnschnitte durch ein Rotorenpaar, welche die Entwicklung
des Arbeitskammerquerschnitts gemäss
Figur 7 veranschaulichen.
- FIG. 1
- a pair of intermeshing screw rotors,
- FIG. 2
- the right-hand rotor,
- FIG. 3
- the left-handed rotor,
- FIG. 4
- a front section of a screw rotor with varying profile,
- FIG. 5
- the development of the reference spiral of a rotor according to the invention,
- FIG. 6
- the gradient course of the development according to FIG. 4,
- FIG. 7
- the course of the working chamber cross-section in a machine without and with profile variation,
- FIGS. 8a to 8c
- Housing, rotor, and working chamber cross-section of a compressor equipped with rotors according to the invention and
- FIGS. 9a to 9p
- End sections through a pair of rotors, which illustrate the development of the working chamber cross-section according to Figure 7.
Figur 1 zeigt ein Ausführungsbeispiel eines Paars miteinander in
achsparallelem Ausseneingriff stehender Schraubenrotoren 1 und 2. Die Figuren
2 und 3 zeigen jeden der Rotoren 1 und 2 gemäss Figur 1 separat. Es ist in
diesen Figuren deutlich zu erkennen, dass der Aussenmantel und der Kern zylindrisch
sind und somit die Gangtiefe über die Schraubenlänge konstant ist. In
Figur 3 zeigen die Masse Δw1 und Δw3, dass die Steigung der Schraube entlang
der Achse variiert, dass dabei aber die Höhe h der schraubenförmigen äusseren
zylindrischen Rotorfläche konstant bleibt, wodurch Leckageverluste zwischen
Rotor und Gehäuseinnenwand gegen die Druckseite hin, wie sie bei einigen
der eingangs erwähnten Maschinen nach dem Stand der Technik in unerwünschter
Weise auftreten, vermieden werden. Mit der Bezugszahl 7 ist in dieser
Figur die Referenzspirale bezeichnet, auf die später noch näher eingegangen
wird und 8 ist die zweite Begrenzungsspirale der äusseren, zylindrischen
Rotorfläche.FIG. 1 shows an exemplary embodiment of a pair of
In Figur 4 ist ein Rotor in einem Schnitt rechtwinklig zur Rotorachse
dargestellt. Das so entstehende Stirnprofil weist einen Kemkreisbogen 3 mit
einem über die ganze Schraubenlänge konstanten Radius Rb auf, der - im
Uhrzeigersinn - nach einem Sektorwinkel γ in eine zykloidenförmige Hohlflanke
4 übergeht. Die Geometrie der Hohlflanke 4 ist über die ganze Schraubenlänge
unverändert. An die Hohlflanke 4 schliesst im Punkt B mit einem spitzen Winkel
ein Aussenkreisbogen 5 mit einem über die ganze Schraubenlänge konstanten
Radius Ra an, welcher nach einem Sektorwinkel γ im Punkt C in eine weitere
Flanke 6 übergeht. Diese mündet schliesslich mit tangentialem Übergang in den
Kernkreisbogen 3. Die Variation der Stirnprofilkontur entlang der Schraubenachse
basiert auf einer Änderung der Sektorwinkel γ sowie auf einer Änderung
der Geometrie der weiteren Flanke 6. Die Variation der Sektorwinkel γ
entlang der Schraubenachse ist vorzugsweise durch einen räumlich mindestens
annähernd äquidistanten Verlauf einer durch die äussersten Punkte der Hohlflanke
Bα gebildeten Referenzspirale (7 in Figur 3) und der zweiten Begrenzungsspirale
(Punkte C) (8 in Figur 3) der äusseren, zylindrischen Rotorfläche
bestimmt.FIG. 4 shows a rotor in a section at right angles to the rotor axis. The resulting end profile has a Kemkreisbogen 3 with a constant over the entire screw length radius Rb, which - in a clockwise direction - after a sector angle γ in a cycloid-shaped hollow flank 4 passes. The geometry of the hollow flank 4 is unchanged over the entire screw length. At the hollow flank 4 closes at point B at an acute angle an
Figur 5 zeigt in einem Diagramm die Abwicklung w der im Zusammenhang mit Figur 4 erwähnten Referenzspirale in Abhängigkeit vom Umschlingungswinkel α. Zum Vergleich sind noch eine Gerade g und entsprechende Abschnitte P0, 2P0 etc. der Abwicklung einer Spirale mit konstanter Steigung eingezeichnet. Der Verlauf der Steigung ist deutlicher erkennbar, wenn man die in Figur 6 dargestellte erste Ableitung der Abwicklung w betrachtet. Dieser Wert w' ist die dynamische Steigung der oben erwähnten Referenzspirale. Man sieht in dieser Figur, dass die Steigung bei α=0 mit dem Wert L0 / 2π beginnt, wobei L0 eine der mittleren Steigungshöhe entsprechende Konstante ist. In einem ersten Teilbereich T1 nimmt w' zu und erreicht bei α=2π den Maximalwert (1+A)·L0 / 2π, wobei A der Amplitudenmoderator ist. Im zweiten Teilbereich T2, der sich von 2π bis 6π erstreckt, nimmt die Steigung ab und erreicht bei α=6π den Minimalwert (1+A)·L0 / 2π, den sie im dritten Teilbereich T3 bis zum Ende der Schraube beibehält.FIG. 5 shows in a diagram the development w of the reference spiral mentioned in connection with FIG. 4 as a function of the wrap angle α. For comparison, a straight line g and corresponding sections P 0 , 2P 0, etc. of the development of a spiral with a constant pitch are shown. The course of the slope is more clearly recognizable when the first derivative shown in Figure 6 the settlement w considered. This value w 'is the dynamic slope of the above-mentioned reference spiral. It can be seen in this figure that the slope at α = 0 starts with the value L 0 / 2π, where L 0 is a constant corresponding to the mean slope height. In a first subregion T 1 , w 'increases and, at α = 2π, reaches the maximum value (1 + A) * L 0 / 2π, where A is the amplitude moderator. In the second subregion T 2 , which extends from 2π to 6π, the slope decreases and reaches at α = 6π the minimum value (1 + A) · L 0 / 2π, which it retains in the third subregion T 3 to the end of the screw ,
Figur 7 zeigt den Kammerquerschnitt F in Funktion des Umschlingungswinkels α, wobei die mit einer durchgezogenen Linie dargestellte Kurve Fo den Kammerquerschnitt ohne Profilvariation und die gestrichelt gezeichnete Kurve Fm den Kammerquerschnitt mit Profilvariation zeigt.FIG. 7 shows the chamber cross-section F as a function of the wrap angle α, wherein the curve F o shown by a solid line shows the chamber cross-section without profile variation and the dashed curve F m shows the chamber cross-section with profile variation.
In Figur 8a ist der Querschnitt eines zur Aufnahme erfindungsgemässer Zwillingsschraubenrotoren bestimmten Gehäuses dargestellt, Figur 8b zeigt einen der Darstellung von Figur 4 entsprechenden Schnitt durch die Rotoren und in Figur 8c ist der Kammerquerschnitt Fo schraffiert dargestellt.In Figure 8a the cross section is shown of the invention for receiving twin screw rotors certain housing, Figure 8b shows one of the representation of Figure 4 corresponding section through the rotors and in figure 8c the chamber cross-section F o is shown hatched.
In den Figuren 9a bis 9p ist in Stirnschnitten die Entwicklung des Arbeitskammerquerschnitts in Abhängigkeit vom Umschlingungswinkel dargestellt. Letzterer ist in den Figuren in Winkelgraden angegeben.In FIGS. 9a to 9p, the development of the working chamber cross section is shown in end sections represented as a function of the wrap angle. The latter is indicated in the figures in degrees.
Claims (3)
- Twin screw rotors for installation in displacement machines for compressible media, which rotors are designed single-threaded with varying pitch and are intended to be in axis-parallel, opposed, outside engagement with angles of contact of at least 720°, and to form in a housing an axial sequence of chambers without blow-hole connections, the end profile comprising a core arc of a circle (3), a cycloidal hollow flank (4), an outer arc of a circle (5) and a further flank (6), characterised in that the pitch does not run monotone and is defined as a variable dependent upon the angle of contact, in that the pitch in a first section (T1) increases from the suction-side screw end, and reaches a maximal value after approximately one turn, in that the pitch in a second section (T2), adjacent to the first section, decreases and reaches a minimal value at approximately one turn before the delivery side screw end, and in that the pitch in a third section (T3), adjacent to the second section, is substantially constant.
- Twin screw rotors according to claim 1, characterised in that the end profile contours along the screw axis vary in that the sector angle (γ) of the core arc of a circle (3) and outer arc of a circle (5) change and in that the geometry of the further flank (6) changes, the core circle radius (Rb), the outer circle radius (Ra) and the geometry of the hollow flank being constant, and the outermost points of the hollow flank forming the reference spiral (7) for definition of the pitch course.
- Twin screw rotors according to claim 2, characterised in that the variation of the sector angle (γ) of the core arc of a circle (3) and outer arc of a circle (5) along the screw axis is determined by a spatially at least almost equidistant course of the reference spiral (7) and of the second demarcation spiral (8) of the outer, cylindrical rotor surface.
Priority Applications (21)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE59811390T DE59811390D1 (en) | 1998-10-23 | 1998-10-23 | Twins conveyor screw rotors |
AT98811063T ATE266800T1 (en) | 1998-10-23 | 1998-10-23 | TWIN CONVEYOR SCREW ROTORS |
EP98811063A EP0995879B1 (en) | 1998-10-23 | 1998-10-23 | Twin feed screw rotors |
ES98811063T ES2221141T3 (en) | 1998-10-23 | 1998-10-23 | ROTORS OF TWIN CONVEYOR SCREWS. |
PCT/CH1999/000466 WO2000025004A1 (en) | 1998-10-23 | 1999-10-01 | Twin helical rotors for installation in displacement machines for compressible media |
BR9914716-5A BR9914716A (en) | 1998-10-23 | 1999-10-01 | Twin screw rotors for placement on displacement machines for compressible media |
AU58464/99A AU5846499A (en) | 1998-10-23 | 1999-10-01 | Twin helical rotors for installation in displacement machines for compressible media |
PL347374A PL202371B1 (en) | 1998-10-23 | 1999-10-01 | Twin helical rotors for installation in displacement machines for compressible media |
EEP200100230A EE200100230A (en) | 1998-10-23 | 1999-10-01 | Double screw rotors for use in compressor machines |
US09/807,737 US6447276B1 (en) | 1998-10-23 | 1999-10-01 | Twin screw rotors for installation in displacement machines for compressible media |
JP2000578545A JP3955731B2 (en) | 1998-10-23 | 1999-10-01 | Twin screw rotor on positive displacement machine for compressible media |
CA002347781A CA2347781C (en) | 1998-10-23 | 1999-10-01 | Twin helical rotors for installation in displacement machines for compressible media |
CN99812527A CN1113151C (en) | 1998-10-23 | 1999-10-01 | Twin helical rotors installated in displacement machines for compressible media |
KR1020017005036A KR100607156B1 (en) | 1998-10-23 | 1999-10-01 | Twin helical rotors for installation in displacement machines for compressible media |
SK218-2001A SK2182001A3 (en) | 1998-10-23 | 1999-10-01 | Twin helical rotors for installation in displacement machines for compressible media |
CZ20010514A CZ296509B6 (en) | 1998-10-23 | 1999-10-01 | Twin helical rotors for installation in displacement machines for compressible media |
TR2001/01123T TR200101123T2 (en) | 1998-10-23 | 1999-10-01 | Twin-bladed rotors for compressible materials. |
PE1999001047A PE20001430A1 (en) | 1998-10-23 | 1999-10-18 | TWIN HELICAL ROTORS TO BE MOUNTED IN COMPRESSIBLE MEDIA COMPRESSOR MACHINES |
PA19998484601A PA8484601A1 (en) | 1998-10-23 | 1999-10-21 | TWIN HELICAL ROTORS TO BE MOUNTED IN COMPRESSIBLE MEDIA COMPRESSOR MACHINES |
ARP990105343A AR020939A1 (en) | 1998-10-23 | 1999-10-22 | HELICOIDAL ROTORS TWINS TO BE ASSEMBLED IN COMPRESSIBLE MEDIA COMPRESSOR MACHINES. |
BG105371A BG64490B1 (en) | 1998-10-23 | 2001-03-22 | Twin helical rotors for installation in displacement machines for compressibble media |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP98811063A EP0995879B1 (en) | 1998-10-23 | 1998-10-23 | Twin feed screw rotors |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0995879A1 EP0995879A1 (en) | 2000-04-26 |
EP0995879B1 true EP0995879B1 (en) | 2004-05-12 |
Family
ID=8236402
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98811063A Expired - Lifetime EP0995879B1 (en) | 1998-10-23 | 1998-10-23 | Twin feed screw rotors |
Country Status (21)
Country | Link |
---|---|
US (1) | US6447276B1 (en) |
EP (1) | EP0995879B1 (en) |
JP (1) | JP3955731B2 (en) |
KR (1) | KR100607156B1 (en) |
CN (1) | CN1113151C (en) |
AR (1) | AR020939A1 (en) |
AT (1) | ATE266800T1 (en) |
AU (1) | AU5846499A (en) |
BG (1) | BG64490B1 (en) |
BR (1) | BR9914716A (en) |
CA (1) | CA2347781C (en) |
CZ (1) | CZ296509B6 (en) |
DE (1) | DE59811390D1 (en) |
EE (1) | EE200100230A (en) |
ES (1) | ES2221141T3 (en) |
PA (1) | PA8484601A1 (en) |
PE (1) | PE20001430A1 (en) |
PL (1) | PL202371B1 (en) |
SK (1) | SK2182001A3 (en) |
TR (1) | TR200101123T2 (en) |
WO (1) | WO2000025004A1 (en) |
Cited By (1)
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CN102937094A (en) * | 2012-10-22 | 2013-02-20 | 台州职业技术学院 | Dry screw vacuum pump varying pitch screw |
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CH694339A9 (en) * | 2000-07-25 | 2005-03-15 | Busch Sa Atel | Twin screw rotors and those containing Ve rdraengermaschinen. |
DE10102341A1 (en) * | 2001-01-19 | 2002-08-08 | Ralf Steffens | Profile contour of a screw pump |
KR20050010753A (en) * | 2002-06-24 | 2005-01-28 | 호쿠에츠 고교 가부시키가이샤 | Screw rotor |
DE10300203A1 (en) | 2003-01-08 | 2004-07-22 | Pfeiffer Vacuum Gmbh | Twin-shaft vacuum pump and method for manufacturing a twin-shaft vacuum pump |
US7753040B2 (en) * | 2003-10-24 | 2010-07-13 | Michael Victor | Helical field accelerator |
US7625191B2 (en) * | 2005-02-16 | 2009-12-01 | Ateliers Busch Sa | Rotary displacement machines having rotors of asymmetrical profile |
KR101145127B1 (en) * | 2005-10-28 | 2012-05-14 | 한라공조주식회사 | Design method of air expander |
GB0525378D0 (en) * | 2005-12-13 | 2006-01-18 | Boc Group Plc | Screw Pump |
JP4853168B2 (en) * | 2006-08-10 | 2012-01-11 | 株式会社豊田自動織機 | Screw pump |
KR100976112B1 (en) * | 2006-09-05 | 2010-08-16 | 가부시키가이샤 도요다 지도숏키 | Screw pump and screw rotor |
US8328542B2 (en) * | 2008-12-31 | 2012-12-11 | General Electric Company | Positive displacement rotary components having main and gate rotors with axial flow inlets and outlets |
DE102012009103A1 (en) * | 2012-05-08 | 2013-11-14 | Ralf Steffens | spindle compressor |
EP3094849A4 (en) * | 2014-01-15 | 2017-11-15 | Eaton Corporation | Method of optimizing supercharger performance |
EP4421323A2 (en) * | 2015-10-30 | 2024-08-28 | Industrial Technologies and Services, LLC | Complex screw rotors |
CN105422448B (en) * | 2016-01-05 | 2017-05-31 | 中国石油大学(华东) | A kind of screw rotor of Varied pole piece varying pitch |
CN111773990A (en) * | 2020-05-22 | 2020-10-16 | 上海恒奕环境科技有限公司 | Unpowered self-adjusting mixing and dosing integrated device for industrial sewage treatment |
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-
1998
- 1998-10-23 AT AT98811063T patent/ATE266800T1/en not_active IP Right Cessation
- 1998-10-23 DE DE59811390T patent/DE59811390D1/en not_active Expired - Fee Related
- 1998-10-23 EP EP98811063A patent/EP0995879B1/en not_active Expired - Lifetime
- 1998-10-23 ES ES98811063T patent/ES2221141T3/en not_active Expired - Lifetime
-
1999
- 1999-10-01 WO PCT/CH1999/000466 patent/WO2000025004A1/en active IP Right Grant
- 1999-10-01 PL PL347374A patent/PL202371B1/en not_active IP Right Cessation
- 1999-10-01 CZ CZ20010514A patent/CZ296509B6/en not_active IP Right Cessation
- 1999-10-01 JP JP2000578545A patent/JP3955731B2/en not_active Expired - Fee Related
- 1999-10-01 EE EEP200100230A patent/EE200100230A/en unknown
- 1999-10-01 US US09/807,737 patent/US6447276B1/en not_active Expired - Fee Related
- 1999-10-01 TR TR2001/01123T patent/TR200101123T2/en unknown
- 1999-10-01 AU AU58464/99A patent/AU5846499A/en not_active Abandoned
- 1999-10-01 CN CN99812527A patent/CN1113151C/en not_active Expired - Fee Related
- 1999-10-01 CA CA002347781A patent/CA2347781C/en not_active Expired - Fee Related
- 1999-10-01 KR KR1020017005036A patent/KR100607156B1/en not_active IP Right Cessation
- 1999-10-01 SK SK218-2001A patent/SK2182001A3/en unknown
- 1999-10-01 BR BR9914716-5A patent/BR9914716A/en not_active IP Right Cessation
- 1999-10-18 PE PE1999001047A patent/PE20001430A1/en not_active Application Discontinuation
- 1999-10-21 PA PA19998484601A patent/PA8484601A1/en unknown
- 1999-10-22 AR ARP990105343A patent/AR020939A1/en active IP Right Grant
-
2001
- 2001-03-22 BG BG105371A patent/BG64490B1/en unknown
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102937094A (en) * | 2012-10-22 | 2013-02-20 | 台州职业技术学院 | Dry screw vacuum pump varying pitch screw |
CN102937094B (en) * | 2012-10-22 | 2016-05-04 | 台州职业技术学院 | A kind of dry screw vacuum pump varying pitch screw |
Also Published As
Publication number | Publication date |
---|---|
PA8484601A1 (en) | 2001-12-14 |
CN1324429A (en) | 2001-11-28 |
JP3955731B2 (en) | 2007-08-08 |
KR100607156B1 (en) | 2006-08-01 |
PE20001430A1 (en) | 2000-12-15 |
BG64490B1 (en) | 2005-04-30 |
CA2347781A1 (en) | 2000-05-04 |
CA2347781C (en) | 2008-10-14 |
CN1113151C (en) | 2003-07-02 |
PL202371B1 (en) | 2009-06-30 |
ES2221141T3 (en) | 2004-12-16 |
EE200100230A (en) | 2002-06-17 |
EP0995879A1 (en) | 2000-04-26 |
ATE266800T1 (en) | 2004-05-15 |
WO2000025004A1 (en) | 2000-05-04 |
CZ296509B6 (en) | 2006-03-15 |
SK2182001A3 (en) | 2001-11-06 |
BR9914716A (en) | 2001-08-07 |
DE59811390D1 (en) | 2004-06-17 |
KR20010080888A (en) | 2001-08-25 |
TR200101123T2 (en) | 2001-08-21 |
CZ2001514A3 (en) | 2001-12-12 |
PL347374A1 (en) | 2002-04-08 |
AR020939A1 (en) | 2002-06-05 |
BG105371A (en) | 2001-10-31 |
US6447276B1 (en) | 2002-09-10 |
AU5846499A (en) | 2000-05-15 |
JP2002528668A (en) | 2002-09-03 |
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