EP1366296B1 - Screw vacuum pump comprising additional flow bodies - Google Patents

Screw vacuum pump comprising additional flow bodies Download PDF

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Publication number
EP1366296B1
EP1366296B1 EP02710783A EP02710783A EP1366296B1 EP 1366296 B1 EP1366296 B1 EP 1366296B1 EP 02710783 A EP02710783 A EP 02710783A EP 02710783 A EP02710783 A EP 02710783A EP 1366296 B1 EP1366296 B1 EP 1366296B1
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EP
European Patent Office
Prior art keywords
rotors
rotor
pump according
flow
bodies
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02710783A
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German (de)
French (fr)
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EP1366296A1 (en
Inventor
Wolfgang Giebmanns
Thomas Dreifert
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Leybold GmbH
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Leybold Vakuum GmbH
Leybold Vacuum GmbH
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Publication of EP1366296A1 publication Critical patent/EP1366296A1/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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/122—Arrangements for supercharging the working space
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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 a screw vacuum pump having the features of the preamble of claim 1.
  • a pump of this kind is known from international patent application WO / 00/12900.
  • intermeshing threads form closed volumes which are conveyed from the inlet to the outlet during synchronized rotation of the rotors.
  • Inlet and outlet are usually designed in such a way that the thread rims of the rotors - generally single-thread threads - start or end in a plane perpendicular to the rotor axes.
  • the effective inlet cross section (or outlet cross section) of the pump-active elements therefore corresponds in each case to the sum of the surfaces forming the respective hub of the rotors, the housing or, depending on the position of the rotor, the adjacent rotor and the lateral boundaries of the respective threaded ridge , For single-start threads, the inlet cross-section extends over 180 °.
  • Figures 1 and 2 show a rotor inlet according to the prior art, in which the rotors with catchy Are equipped threads.
  • FIG. 2 shows a development of the rotor 5.
  • the two thread ridges 8, 9 begin in a plane extending perpendicular to the rotor axes 10, 11, which is denoted by 14 in both FIGS. This results in each rotor, an inlet cross-section 15 and 16, which is formed by the components involved and extends - with single-threaded threads 8,9 - over 180 °.
  • the rotors are assigned on its suction side further pumping effective means.
  • These other pump-effective means are each a mechanical kinetic pumping stage or high-vacuum pumping stage, which is designed in the manner of a Holweck pumping stage. They hinder the gas streams entering the inlet cross sections of the screw rotors.
  • the present invention has for its object, in a screw vacuum pump according to the preamble of claim 1, the Einströmmik to improve the inlet cross sections of the screw rotors and the Ausströmmik from the Ausströmquerroughen the screw rotors.
  • the invention realizes an "inlet booster".
  • the arrangement of flow bodies arranged upstream of the inlet cross-sections has the effect of improving the degree of filling of the volumes delivered by the rotors from the inlet to the outlet, so that a pump designed according to the invention has better conveying properties, in particular improved pumping speed, Has.
  • similar flow bodies assigned to the outlet cross sections can improve the outflow conditions such that flow losses in the exhaust gas system are reduced. Aerodynamically, the flow velocities and the residual spin can be reduced and the static pressure with a cross-sectional widening can be additionally increased by a downstream flow body, so that lower flow losses due to deflection and friction occur in the subsequent exhaust system. Since the backpressure in the exhaust gas area is always at 1 bar anyway, the aerodynamic improvements can also be effective over the entire operating range of the screw pump. Finally, because of the advantages described above, it is also possible to use shorter rotors.
  • the invention is independent of the screw geometry (single-start or multi-start screws, constant or variable pitch, variable pitch with gradient areas, cylindrical, stepped or conical rotors, single-flow or twin-flow rotors, rotors with flying or double-sided storage) used.
  • An advantageous development of the invention consists in providing the thread ridge of the respective neighboring rotor (second rotor) with a recess in the region which interacts with the flow body (s) of the first rotor.
  • Another advantage of the invention is that the flow body can be used simultaneously as balancing masses. Imbalances of the rotors, which are unavoidable due to the design of the end portions of the threads can be completely or at least largely eliminated by the flow body. Even with rotors produced by casting only a fine balancing is needed.
  • Rotor dynamic offer exit-side flow body the ability to additionally reduce the primary imbalance of a screw rotor in a second plane constructive-constructive and then use this as a second level compensation during fine balancing, which can minimize the internal moments in the overall rotor.
  • exit contours are also applicable to all screw geometries. Due to the reduced in the screw passage cross-sectional areas remains with threads with decreasing web width on the pressure-side rotor end only a small wall thickness, which offers little leeway to the design of blade contours. Of course, almost any emergence contour can be added via an additional part, but a reshaping an additional thread turn, as it is possible on the inlet side with a vacuum screw with variable pitch due to the great gait, can be used on the exit side only in rare cases.
  • the trailing bodies of the end faces of the threaded struts 8, 9, which follow the flow body 21, 22, are equipped with recesses 23 (rotor 4, not visible) 24. They delay the completion of the delivery volumes and at the same time ensure their complete filling.
  • the respective flow body 21 or 22 can be made together with its hub portion as a separate part and subsequently to the cut screw end face to be assembled. Particularly advantageous, however, is the integral production, in the hub portion and flow body z. B. by milling, from the residual material, which has remained in the production of the screw profile (by milling, whirling, rolling, forming, etc.) has stopped (shown in phantom in Figure 4).
  • FIG. 5a shows an embodiment corresponding to FIG. 4 with the difference that the width and the slope of the web 9 decrease in the direction of the pressure side.
  • the pressure side can be designed according to Figure 5b.
  • the hub 7 is extended beyond the outlet cross section 29 by about four times the pressure-side thread pitch and supports a blade-like extension 25 of the thread 9. This extends with strong toward pressure side increasing pitch and web width about 140 °.
  • Figure 6a shows as a development of the rotor inlet of a further embodiment of the rotor 5.
  • the rotor 4, not shown, is formed accordingly.
  • the inlet cross section 16 are three upstream of the threaded ridge 9 flow body 26, 27, 28 upstream. They are based on the hub 7 and have approximately the shape of rotor blades whose pitch increases in the direction of the suction side, starting with about the pitch of the threaded ridge.
  • 9 Figures 6b and 6c show two embodiments for the rotor outlet, depending on whether the thread 9 has a constant pitch and web width or a decreasing pitch and land width.
  • the hub 7 extends beyond the outlet cross-section 29 out and carries blades 31, 32, 33 and 34, 35.
  • the blades are independent of the thread 9 and have an increasing slope to the pressure side.
  • the blades are designed approximately mirror-symmetrically with respect to the blades 26, 27, 28.
  • the web width of the blades 34, 35 increases in the direction of the pressure side.
  • the inlet-side and outlet-side blades together with their hub portions expediently consist of separately produced blade rings, which are components of the rotors 4 and 5 after their frontal mounting. This solution makes it possible to adjust the arrival and - under certain conditions - and outflow conditions in a simple manner by changing the blade rings to customer requirements.
  • the pressure-side flow bodies 25 (FIGS. 5b) and 34 (FIG. 6c) have a relatively large volume. As a result, sufficient mass is available in the outlet area of the pump for balancing the rotors.
  • flow body 36, 37 are provided.
  • Flow body 36 is - substantially as in the embodiment of Figures 3, 4 - an extension of the threaded ridge 8 with reduced width (here about 1/5).
  • the foot of the paddle-shaped flow body 37 is located approximately in the middle of the inlet cross-section 16.
  • constant web width and pitch of the rotor outlet can be designed accordingly (approximately mirror-image).
  • FIG. 7b shows the rotor outlet in a version with a thread 9, whose pitch and web width decrease in the direction of the pressure side.
  • the thread pitch increases sharply with further decrease of the web width in the direction of the pressure side.
  • Figure 8 shows in perspective an embodiment which substantially corresponds to the embodiment of Figures 3, 4. It is different that the hubs 6, 7 are extended only in the area of the flow bodies 21, 22. They each extend only to the inner edges of the respective flow body 21 and 22, respectively.
  • the flow bodies in such a way, whether with regard to their design, arrangement and / or mass, that they simultaneously eliminate the unbalance of the screw rotors 4, 5.
  • balancing masses must be added. Large Urunwuchten are avoided, consuming balancing methods can be omitted.
  • the flow bodies may, therefore, also be considered as balancing weights designed to improve the supply (or exhaust) flow conditions of the gases to be conveyed, that is to say they have the shape of flow bodies.

Description

Die Erfindung bezieht sich auf eine Schraubenvakuumpumpe mit den Merkmalen des Oberbegriffs des Patentanspruchs 1. Eine Pumpe dieser Art ist aus der internationalen Patent-Anmeldung WO/00/12900 bekannt.The invention relates to a screw vacuum pump having the features of the preamble of claim 1. A pump of this kind is known from international patent application WO / 00/12900.

Bei einer Schraubenpumpe bilden ineinander greifende Gewinde abgeschlossene Volumina, die während der synchronisierten Drehung der Rotoren vom Einlauf zum Auslauf gefördert werden. Einlauf und Auslauf sind üblicherweise so gestaltet, dass die Gewindestege der Rotoren - in der Regel eingängige Gewinde - in einer Ebene senkrecht zu den Rotorachsen beginnen bzw. enden. Der effektive Eintrittsquerschnitt (bzw. Austrittsquerschnitt) der pump-aktiven Elemente entspricht deshalb jeweils der Summe der Flächen, die die jeweilige Nabe der Rotoren, das Gehäuse bzw. - je nach Stellung des Rotors - der benachbarte Rotor sowie die seitlichen Begrenzungen des jeweiligen Gewindesteges bilden. Bei eingängigen Gewinden erstreckt sich der Eintrittsquerschnitt jeweils über 180°.In a screw pump, intermeshing threads form closed volumes which are conveyed from the inlet to the outlet during synchronized rotation of the rotors. Inlet and outlet are usually designed in such a way that the thread rims of the rotors - generally single-thread threads - start or end in a plane perpendicular to the rotor axes. The effective inlet cross section (or outlet cross section) of the pump-active elements therefore corresponds in each case to the sum of the surfaces forming the respective hub of the rotors, the housing or, depending on the position of the rotor, the adjacent rotor and the lateral boundaries of the respective threaded ridge , For single-start threads, the inlet cross-section extends over 180 °.

Die Figuren 1 und 2 zeigen einen Rotoreinlauf nach dem Stand der Technik, bei dem die Rotoren mit eingängigen Gewinden ausgerüstet sind. In den Figuren 1 und 2 sind die nur teilweise dargestellte Schraubenvakuumpumpe mit 1, ihr Gehäuse mit 2, ihr Einlass mit 3, die Rotoren mit 4 bzw. 5, ihre Rotornaben mit 6 bzw. 7, ihre Gewindestege mit 8 bzw. 9 und die Rotorachsen mit 10 bzw. 11 bezeichnet. In Figur 2 ist eine Abwicklung des Rotors 5 dargestellt.Figures 1 and 2 show a rotor inlet according to the prior art, in which the rotors with catchy Are equipped threads. In Figures 1 and 2, the only partially shown screw vacuum pump with 1, their housing with 2, their inlet with 3, the rotors with 4 and 5, their rotor hubs with 6 and 7, their thread ranks with 8 and 9 and Rotor axes designated 10 and 11 respectively. FIG. 2 shows a development of the rotor 5.

Die beiden Gewindestege 8,9 beginnen in einer sich senkrecht zu den Rotorachsen 10,11 erstreckenden Ebene, die in beiden Figuren mit 14 bezeichnet ist. Dadurch ergibt sich bei jedem Rotor ein Eintrittsquerschnitt 15 bzw. 16, der von den beteiligten Bauteilen gebildet wird und der sich - bei eingängigen Gewindestegen 8,9 - über 180° erstreckt.The two thread ridges 8, 9 begin in a plane extending perpendicular to the rotor axes 10, 11, which is denoted by 14 in both FIGS. This results in each rotor, an inlet cross-section 15 and 16, which is formed by the components involved and extends - with single-threaded threads 8,9 - over 180 °.

Bei den Schraubenvakuumpumpen nach der japanischen Patent-Anmeldung 43 70 379 sowie der US-A-5,352,097 sind den Rotoren auf ihrer Saugseite weitere pumpwirksame Mittel zugeordnet. Bei diesen weiteren pumpwirksamen Mitteln handelt es sich um jeweils eine mechanisch kinetische Pumpstufe bzw. Hochvakuumpumpstufe, die nach Art einer Holweck-Pumpstufe ausgebildet ist. Sie behindern die in die Eintrittsquerschnitte der Schraubenrotoren eintretenden Gasströme.In the screw vacuum pump according to Japanese Patent Application 43 70 379 and US-A-5,352,097 the rotors are assigned on its suction side further pumping effective means. These other pump-effective means are each a mechanical kinetic pumping stage or high-vacuum pumping stage, which is designed in the manner of a Holweck pumping stage. They hinder the gas streams entering the inlet cross sections of the screw rotors.

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, bei einer Schraubenvakuumpumpe nach dem Oberbegriff des Patentanspruchs 1 die Einströmverhältnisse zu den Eintrittsquerschnitten der Schraubenrotoren und auch die Ausströmverhältnisse aus den Ausströmquerschnitten der Schraubenrotoren zu verbessern.The present invention has for its object, in a screw vacuum pump according to the preamble of claim 1, the Einströmverhältnisse to improve the inlet cross sections of the screw rotors and the Ausströmverhältnisse from the Ausströmquerschnitten the screw rotors.

Erfindungsgemäß wird diese Aufgabe durch die kennzeichnenden Merkmale der Patentansprüche gelöst.According to the invention this object is achieved by the characterizing features of the claims.

Durch die Erfindung wird ein "Einlauf-Booster" realisiert. Die Anordnung von den Eintrittsquerschnitten vorgelagerten Strömungskörpern hat die Wirkung einer Verbesserung des Füllungsgrades der von den Rotoren vom Einlauf zum Auslauf geförderten Volumina, so dass eine erfindungsgemäß ausgebildete Pumpe bessere Fördereigenschaften, insbesondere ein verbessertes Saugvermögen, hat. Auch im Bereich des Rotorauslaufs können ähnliche den Austrittsquerschnitten zugeordnete Strömungskörper die Abströmverhältnisse dahingehend verbessern, dass Strömungsverluste im Abgassystem verringert werden. Aerodynamisch können durch einen abströmseitig angeordneten Strömungskörper die Strömungsgeschwindigkeiten und der Restdrall reduziert sowie der statische Druck mit einer Querschnittserweiterung zusätzlich angehoben werden, so dass im nachfolgenden Abgassystem geringere Strömungsverluste infolge Umlenkung und Reibung auftreten. Da der Gegendruck im Abgasbereich ohnehin ständig bei 1 bar liegt, können hier die aerodynamischen Verbesserungen auch über den gesamten Betriebsbereich der Schraubenpumpe wirksam werden. Wegen der vorbeschriebenen Vorteile besteht schließlich auch die Möglichkeit, kürzere Rotoren einzusetzen.The invention realizes an "inlet booster". The arrangement of flow bodies arranged upstream of the inlet cross-sections has the effect of improving the degree of filling of the volumes delivered by the rotors from the inlet to the outlet, so that a pump designed according to the invention has better conveying properties, in particular improved pumping speed, Has. Also in the region of the rotor outlet, similar flow bodies assigned to the outlet cross sections can improve the outflow conditions such that flow losses in the exhaust gas system are reduced. Aerodynamically, the flow velocities and the residual spin can be reduced and the static pressure with a cross-sectional widening can be additionally increased by a downstream flow body, so that lower flow losses due to deflection and friction occur in the subsequent exhaust system. Since the backpressure in the exhaust gas area is always at 1 bar anyway, the aerodynamic improvements can also be effective over the entire operating range of the screw pump. Finally, because of the advantages described above, it is also possible to use shorter rotors.

Die Erfindung ist unabhängig von der Schraubengeometrie (eingängige oder mehrgängige Schrauben, konstante oder variable Steigung, variable Steigung mit steigungskonstanten Bereichen, zylindrische, gestufte oder kegelige Rotoren, einflutige oder zweiflutige Rotoren, Rotoren mit fliegender oder doppelseitiger Lagerung) einsetzbar.The invention is independent of the screw geometry (single-start or multi-start screws, constant or variable pitch, variable pitch with gradient areas, cylindrical, stepped or conical rotors, single-flow or twin-flow rotors, rotors with flying or double-sided storage) used.

Eine vorteilhafte Weiterbildung der Erfindung besteht darin, den Gewindesteg des jeweiligen Nachbarrotors (zweiter Rotor) in dem Bereich, der mit dem oder den Strömungskörpern des ersten Rotors zusammenwirkt, mit einer Aussparung zu versehen. Dadurch wird das Schließen des Eintrittsquerschnittes des ersten Rotors bei gleichzeitig sicherer Füllung des durch die Aussparung vergrößerten Eintrittsvolumens verzögert. Es findet eine Vorkompression statt, die den Wirkungsgrad der Pumpe verbessert und ihren Leitungsbedarf reduziert.An advantageous development of the invention consists in providing the thread ridge of the respective neighboring rotor (second rotor) with a recess in the region which interacts with the flow body (s) of the first rotor. As a result, the closing of the inlet cross-section of the first rotor at the same time secure filling of the through the recess delayed entry volume delayed. There is a pre-compression, which improves the efficiency of the pump and reduces their line requirements.

Ein weiterer Vorteil der Erfindung besteht darin, dass die Strömungskörper gleichzeitig als Wuchtmassen verwendet werden können. Unwuchten der Rotoren, die infolge der Gestaltung der Endbereiche der Gewinde unvermeidbar sind, können durch die Strömungskörper vollständig oder zumindest weitestgehend beseitigt werden. Selbst bei durch Gießen hergestellten Rotoren ist nur noch ein Feinwuchten nötig. Rotordynamisch bieten austrittsseitige Strömungskörper die Möglichkeit, die Urunwucht eines Schraubenrotors zusätzlich in einer zweiten Ebene rechnerisch-konstruktiv zu reduzieren sowie diese dann auch als zweite Ausgleichsebene beim Feinwuchten zu nutzen, wodurch sich die inneren Momente im Gesamtrotor minimieren lassen.Another advantage of the invention is that the flow body can be used simultaneously as balancing masses. Imbalances of the rotors, which are unavoidable due to the design of the end portions of the threads can be completely or at least largely eliminated by the flow body. Even with rotors produced by casting only a fine balancing is needed. Rotor dynamic offer exit-side flow body the ability to additionally reduce the primary imbalance of a screw rotor in a second plane constructive-constructive and then use this as a second level compensation during fine balancing, which can minimize the internal moments in the overall rotor.

Die Austrittskonturen sind ebenfalls für alle Schraubengeometrien anwendbar. Durch die im Schraubengang reduzierten Querschnittsflächen bleibt bei Gewinden mit abnehmender Stegbreite am druckseitigen Rotorende lediglich eine geringe Wandstärke übrig, die wenig Spielraum zur Gestaltung von Schaufelkonturen bietet. Natürlich kann über ein zusätzliches Teil nahezu jede Austrittskontur angefügt werden, doch ein spanendes Nachformen eines zusätzlichen Gewindeganges, wie es bei einer Vakuumschraube mit variabler Steigung aufgrund der großen Gangstärke eintrittsseitig möglich ist, kann austrittsseitig nur in seltenen Fällen angewendet werden. Es wäre denkbar, dass, nach entsprechendem Schlitzen entlang des Nabendurchmessers, die dünnwandige Restkontur durch gezieltes Biegen eine Schaufelform erhält, die über eine stoffschlüssige Verbindung (wie Schweißen, Löten oder Kleben) dann wieder mit der Nabe zu fixieren ist. Besser ist es, diese Geometrie direkt bei der Gewindefertigung herzustellen, um so eine kostengünstige und betriebssichere Kontur zu erhalten, die zudem den rotordynamischen Bedürfnissen optimal angepasst werden kann.The exit contours are also applicable to all screw geometries. Due to the reduced in the screw passage cross-sectional areas remains with threads with decreasing web width on the pressure-side rotor end only a small wall thickness, which offers little leeway to the design of blade contours. Of course, almost any emergence contour can be added via an additional part, but a reshaping an additional thread turn, as it is possible on the inlet side with a vacuum screw with variable pitch due to the great gait, can be used on the exit side only in rare cases. It would be conceivable that, after appropriate slitting along the hub diameter, the thin-walled residual contour is replaced by targeted bending a blade shape, which is then about a cohesive connection (such as welding, soldering or gluing) to fix with the hub again. It is better to produce this geometry directly during the threading process in order to obtain a cost-effective and reliable contour, which can also be optimally adapted to the rotor dynamic requirements.

Die integrale spanende Fertigung von Schraubengeometrie und Ein- und Austrittskonturen bietet einen weiteren Vorteil. Durch stirnseitiges Abplanen, senkrecht zur Rotorachse, entstehen bei einem herkömmlichen Schraubenrotor an beiden Enden scharfe Eintritts- und Austrittskanten, die häufig zurückgeschnitten werden müssen, um ein Verformen oder Abbrechen dieser dünnen Restmaterialien zu verhindern. Demgegenüber kann bei den integral hergestellten Konturen ein kontinuierlicher Übergang erzielt werden, der gleichzeitig eine Versteifung der Endkanten darstellt.The integral machining of screw geometry and inlet and outlet contours offers another advantage. By frontal planing, perpendicular to the rotor axis, arise in a conventional screw rotor at both ends of sharp entry and exit edges, which often have to be cut back to prevent deformation or breaking these thin residual materials. In contrast, in the integrally formed contours, a continuous transition can be achieved, which simultaneously represents a stiffening of the end edges.

Weitere Vorteile und Einzelheiten der Erfindung sollen anhand von in den Figuren 3 bis 8 dargestellten Ausführungsbeispielen erläutert werden. Es zeigen:

  • Figuren 3, 4 und 8 Lösungen mit jeweils einem Strömungskörper,
  • Figuren 5, 6 und 7 Lösungen mit jeweils mehreren Strömungskörpern. Beim Ausführungsbeispiel nach den Figuren 3 und 4 (Figur 4 stellt wieder eine Abwicklung des Rotors 5 dar) sind die Rotornaben 6, 7 über die Ebene 14 der Eintrittsquerschnitte 15, 16 um ein bis zwei Gewindestegbreiten verlängert. Sie dienen sowohl der Abstützung jeweils eines Strömungskörpers 21, 22, der sich jeweils oberhalb der Eintrittsquerschnitte 15 bzw. 16 erstreckt, als auch der nabenseitigen Förderraum-Abgrenzung. Es handelt sich in etwa um eine Verlängerung der Gewindestege 8, 9 mit verminderter Stegbreite (etwa 1/3). Bei - wie dargestellt - eingängigen Schrauben erstreckt sich jeder Strömungskörper über etwas weniger als den halben Rotorumfang und demzufolge steht dem offenen Teilbereich etwas mehr als ein halber Rotorumfang zur Verfügung. Um 180° zueinander verdreht, dringt jeder der Strömungskörper jeweils berührungsfrei in die entsprechende Lücke des Nachbarrotors ein. Die Steigung der jeweils vorlaufenden Kanten der Strömungskörper 21, 22 nimmt in Richtung Saugseite etwas zu. Der Endbereich ist abgerundet. Die in das noch offene Fördervolumen einströmenden Gase sind in Figur 4 durch Pfeile gekennzeichnet.
Further advantages and details of the invention will be explained with reference to embodiments shown in Figures 3 to 8. Show it:
  • FIGS. 3, 4 and 8 solutions each with a flow body,
  • Figures 5, 6 and 7 solutions, each with a plurality of flow bodies. In the embodiment according to FIGS. 3 and 4 (FIG. 4 again represents a development of the rotor 5), the rotor hubs 6, 7 are extended over the plane 14 of the inlet cross sections 15, 16 by one or two thread pitches. They serve both to support a respective flow body 21, 22, which extends in each case above the inlet cross sections 15 and 16, as well as the hub-side delivery chamber delimitation. It is about an extension of the thread ridges 8, 9 with reduced web width (about 1/3). In the case of single-start screws, as shown, each flow body extends over slightly less than half the circumference of the rotor, and consequently slightly more than half the circumference of the rotor is available to the open sub-region. Twisted by 180 ° to each other, each of the flow body penetrates each without contact in the corresponding gap of the neighboring rotor. The slope of the respective leading edges of the flow body 21, 22 increases in the direction of the suction side something. The end area is rounded. The gases flowing into the still open delivery volume are indicated in FIG. 4 by arrows.

Die dem Strömungskörper 21, 22 nachlaufenden Bereiche der Stirnseiten der Gewindestege 8, 9 sind mit Aussparungen 23 (Rotor 4, nicht sichtbar), 24 ausgerüstet. Sie verzögern den Abschluss der Fördervolumina und sichern gleichzeitig deren vollständige Füllung.The trailing bodies of the end faces of the threaded struts 8, 9, which follow the flow body 21, 22, are equipped with recesses 23 (rotor 4, not visible) 24. They delay the completion of the delivery volumes and at the same time ensure their complete filling.

Der jeweilige Strömungskörper 21 bzw. 22 kann zusammen mit seinem Nabenabschnitt als separates Teil gefertigt und nachträglich an die abgeschnittene Schraubenstirnfläche montiert werden. Besonders vorteilhaft ist jedoch die integrale Fertigung, bei der Nabenabschnitt und Strömungskörper z. B. durch Fräsen geformt werden, und zwar aus dem Restmaterial, das bei der Herstellung des Schraubenprofils (durch Fräsen, Wirbeln, Walzen, Formdrehen usw.) stehen geblieben ist (in Figur 4 gestrichelt dargestellt).The respective flow body 21 or 22 can be made together with its hub portion as a separate part and subsequently to the cut screw end face to be assembled. Particularly advantageous, however, is the integral production, in the hub portion and flow body z. B. by milling, from the residual material, which has remained in the production of the screw profile (by milling, whirling, rolling, forming, etc.) has stopped (shown in phantom in Figure 4).

Figur 5a zeigt eine der Figur 4 entsprechende Ausführung mit dem Unterschied, dass Breite und Steigung des Steges 9 in Richtung Druckseite abnehmen. Bei einer Ausführung dieser Art kann die Druckseite gemäß Figur 5b gestaltet sein. Die Nabe 7 ist über den Austrittsquerschnitt 29 hinaus um etwa das Vierfache der druckseitigen Gewindestegbreite verlängert und stützt eine schaufelartige Verlängerung 25 des Gewindes 9. Diese erstreckt sich mit stark in Richtung Druckseite zunehmender Steigung und Stegbreite etwa über 140°.FIG. 5a shows an embodiment corresponding to FIG. 4 with the difference that the width and the slope of the web 9 decrease in the direction of the pressure side. In one embodiment of this type, the pressure side can be designed according to Figure 5b. The hub 7 is extended beyond the outlet cross section 29 by about four times the pressure-side thread pitch and supports a blade-like extension 25 of the thread 9. This extends with strong toward pressure side increasing pitch and web width about 140 °.

Figur 6a zeigt als Abwicklung den Rotoreinlauf eines weiteren Ausführungsbeispieles für den Rotor 5. Der nicht dargestellte Rotor 4 ist entsprechend ausgebildet. Dem Eintrittsquerschnitt 16 sind drei vom Gewindesteg 9 unabhängige Strömungskörper 26, 27, 28 vorgelagert. Sie stützen sich an der Nabe 7 ab und haben etwa die Form von Rotorschaufeln, deren Steigung in Richtung Saugseite zunimmt, und zwar beginnend mit etwa der Steigung des Gewindesteges 9.
Die Figuren 6b und 6c zeigen zwei Ausführungen für den Rotorauslauf, je nach dem, ob das Gewinde 9 eine konstante Steigung und Stegbreite oder eine abnehmende Steigung und Stegbreite hat. Druckseitig ist die Nabe 7 jeweils über den Austrittsquerschnitt 29 hinaus verlängert und trägt Schaufeln 31, 32, 33 bzw. 34, 35. Sie sind unabhängig vom Gewinde 9 und haben eine zur Druckseite zunehmende Steigung. Bei der Ausführung nach Fig. 6b sind die Schaufeln etwa spiegelsymmetrisch zu den Schaufeln 26, 27, 28 gestaltet. Bei der Ausführung nach Figur 6c nimmt die Stegbreite der Schaufeln 34, 35 in Richtung Druckseite zu. Bei diesen Ausführungen bestehen die einlaufseitigen und auslaufseitigen Schaufeln zusammen mit ihren Nabenabschnitten zweckmäßig aus separat hergestellten Schaufelringen, die nach ihrer stirnseitigen Montage Bestandteile der Rotoren 4 und 5 sind. Diese Lösung erlaubt es, die An- und - unter bestimmten Voraussetzungen - auch Abströmbedingungen in einfacher Weise durch Wechsel der Schaufelringe den Kundenwünschen anzupassen.Figure 6a shows as a development of the rotor inlet of a further embodiment of the rotor 5. The rotor 4, not shown, is formed accordingly. The inlet cross section 16 are three upstream of the threaded ridge 9 flow body 26, 27, 28 upstream. They are based on the hub 7 and have approximately the shape of rotor blades whose pitch increases in the direction of the suction side, starting with about the pitch of the threaded ridge. 9
Figures 6b and 6c show two embodiments for the rotor outlet, depending on whether the thread 9 has a constant pitch and web width or a decreasing pitch and land width. On the pressure side, the hub 7 extends beyond the outlet cross-section 29 out and carries blades 31, 32, 33 and 34, 35. They are independent of the thread 9 and have an increasing slope to the pressure side. In the embodiment according to FIG. 6b, the blades are designed approximately mirror-symmetrically with respect to the blades 26, 27, 28. In the embodiment according to FIG. 6 c, the web width of the blades 34, 35 increases in the direction of the pressure side. In these embodiments, the inlet-side and outlet-side blades together with their hub portions expediently consist of separately produced blade rings, which are components of the rotors 4 and 5 after their frontal mounting. This solution makes it possible to adjust the arrival and - under certain conditions - and outflow conditions in a simple manner by changing the blade rings to customer requirements.

Die druckseitigen Strömungskörper 25 (Fig. 5b) und 34 (Fig. 6c) haben ein relativ großes Volumen. Dadurch steht im Austrittsbereich der Pumpe genügend Masse für das Wuchten der Rotoren zur Verfügung.The pressure-side flow bodies 25 (FIGS. 5b) and 34 (FIG. 6c) have a relatively large volume. As a result, sufficient mass is available in the outlet area of the pump for balancing the rotors.

Bei der Ausführung nach Figur 7a sind zwei Strömungskörper 36, 37 vorgesehen. Strömungskörper 36 ist - im wesentlichen wie bei der Ausführung nach den Figuren 3, 4 - eine Verlängerung des Gewindesteges 8 mit verminderter Breite (hier etwa 1/5). Der Fuß des schaufelförmigen Strömungskörpers 37 befindet sich etwa in der Mitte des Eintrittsquerschnittes 16. Bei einer Ausführung mit einem Gewinde 9 konstanter Stegbreite und Steigung kann der Rotorauslauf entsprechend (etwa spiegelbildlich) gestaltet sein.In the embodiment of Figure 7a, two flow body 36, 37 are provided. Flow body 36 is - substantially as in the embodiment of Figures 3, 4 - an extension of the threaded ridge 8 with reduced width (here about 1/5). The foot of the paddle-shaped flow body 37 is located approximately in the middle of the inlet cross-section 16. In a version with a thread 9 constant web width and pitch of the rotor outlet can be designed accordingly (approximately mirror-image).

Figur 7b zeigt den Rotorauslauf bei einer Ausführung mit einem Gewinde 9, dessen Steigung und Stegbreite in Richtung Druckseite abnehmen. Im Bereich der Verlängerung der Nabe 7 über den Austrittsquerschnitt 29 hinaus nimmt die Gewindesteigung bei weiterer Abnahme der Stegbreite in Richtung Druckseite stark zu.FIG. 7b shows the rotor outlet in a version with a thread 9, whose pitch and web width decrease in the direction of the pressure side. In the area of the extension of the hub 7 beyond the outlet cross section 29, the thread pitch increases sharply with further decrease of the web width in the direction of the pressure side.

Schließlich zeigt Figur 8 perspektivisch eine Ausführungsform, die im wesentlichen der Ausführung nach den Figuren 3, 4 entspricht. Unterschiedlich ist, dass die Naben 6, 7 nur im Bereich der Strömungskörper 21, 22 verlängert sind. Sie erstrecken sich jeweils nur bis zu den Innenkanten der jeweiligen Strömungskörper 21 bzw. 22.Finally, Figure 8 shows in perspective an embodiment which substantially corresponds to the embodiment of Figures 3, 4. It is different that the hubs 6, 7 are extended only in the area of the flow bodies 21, 22. They each extend only to the inner edges of the respective flow body 21 and 22, respectively.

Zweckmäßig ist es, die Strömungskörper so zu gestalten, sei es in Bezug auf ihre Ausbildung, Anordnung und/oder Masse, dass sie gleichzeitig die Unwucht der Schraubenrotoren 4, 5 beseitigen. Vorteilhafterweise ergibt sich, dass gerade dort, wo die Anordnung von aerodynamisch wirksamen Strömungskörpern zweckmäßig ist, auch Wuchtmassen hinzugefügt werden müssen. Große Urunwuchten sind dadurch vermieden, aufwendige Wuchtverfahren können entfallen. Die Strömungskörper können deshalb auch als Wuchtgewichte angesehen werden, die so gestaltet sind, dass sie die Zu-(bzw. Ab-)strömverhältnisse der zu fördernden Gase verbessern, d.h., dass sie die Form von Strömungskörpern haben.It is expedient to design the flow bodies in such a way, whether with regard to their design, arrangement and / or mass, that they simultaneously eliminate the unbalance of the screw rotors 4, 5. Advantageously, it results that just where the arrangement of aerodynamically effective flow bodies is appropriate, also balancing masses must be added. Large Urunwuchten are avoided, consuming balancing methods can be omitted. The flow bodies may, therefore, also be considered as balancing weights designed to improve the supply (or exhaust) flow conditions of the gases to be conveyed, that is to say they have the shape of flow bodies.

Claims (8)

  1. Screw vacuum pump with two rotors (4, 5) which in each case have a hub (6, 7) and a thread (8, 9), and with a housing (2) in which the rotors with meshing threads are accommodated such that, together with the housing, they form inlet cross sections (15, 16) disposed on the intake side and outlet cross sections (29) disposed on the delivery side and cause gases to be delivered from the intake side to the delivery side during the rotational movement of the rotors (4, 5), characterised in that the rotors (4, 5) are provided on the intake side with flow bodies (21, 22, 36) which are mounted upstream of the inlet cross sections (15, 16), that the flow bodies (21, 22, 36) extend over 90° to 180°, and that they are substantially formed as a prolongation of a ridge (8, 9) with a reduced ridge width, so that they improve the inflow conditions of the gases to be delivered to the inlet cross sections (15, 16) of the rotors (4, 5).
  2. Screw vacuum pump according to Claim 1, characterised in that the slope of the respective leading edges of the flow bodies (21, 22, 36) increases in the direction of the intake side.
  3. Screw vacuum pump according to Claim 1 or 2, characterised in that the end region of the flow bodies which is on the intake side is rounded.
  4. Pump according to any one of Claims 1 to 3, characterised in that at least one further flow body which is independent of the thread ridge (8, 9) is provided in the region of the respective inlet cross sections, which body has the shape of a blade which is curved such that it extends on the delivery side approximately in the direction of the thread ridges (8, 9) and is steeper on the intake side.
  5. Pump according to any one of the preceding Claims, characterised in that a recess (23, 24) is provided in the trailing region of the face of the thread ridge (8, 9).
  6. Pump according to any one of the preceding Claims, characterised in that the rotor outlet is provided with corresponding flow bodies.
  7. Pump according to any one of the preceding Claims, characterised in that the flow body/bodies (21, 22; 26, 27, 28; 31, 32, 33; 34, 35; 36, 37) and the associated hub portion (6, 7) are mounted as a separate component on the face or rear of the rotor (4, 5).
  8. Pump according to any one of the preceding Claims, characterised in that the flow bodies are designed with respect to their formation, arrangement and/or mass such that the imbalance of the associated rotor (4, 5) is at least largely removed.
EP02710783A 2001-03-09 2002-01-09 Screw vacuum pump comprising additional flow bodies Expired - Lifetime EP1366296B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10111525A DE10111525A1 (en) 2001-03-09 2001-03-09 Screw vacuum pump with rotor inlet and rotor outlet
DE10111525 2001-03-09
PCT/EP2002/000122 WO2002073037A1 (en) 2001-03-09 2002-01-09 Screw vacuum pump comprising additional flow bodies

Publications (2)

Publication Number Publication Date
EP1366296A1 EP1366296A1 (en) 2003-12-03
EP1366296B1 true EP1366296B1 (en) 2006-11-22

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EP02710783A Expired - Lifetime EP1366296B1 (en) 2001-03-09 2002-01-09 Screw vacuum pump comprising additional flow bodies

Country Status (5)

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US (1) US20040067149A1 (en)
EP (1) EP1366296B1 (en)
JP (1) JP4200007B2 (en)
DE (2) DE10111525A1 (en)
WO (1) WO2002073037A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008018261A1 (en) 2006-08-07 2008-02-14 Seiko Instruments Inc. Method for manufacturing electroformed mold, electroformed mold, and method for manufacturing electroformed parts
DE102010019402A1 (en) * 2010-05-04 2011-11-10 Oerlikon Leybold Vacuum Gmbh Screw vacuum pump
US9057373B2 (en) * 2011-11-22 2015-06-16 Vilter Manufacturing Llc Single screw compressor with high output

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Publication number Priority date Publication date Assignee Title
US2994562A (en) * 1959-02-05 1961-08-01 Warren Pumps Inc Rotary screw pumping of thick fibrous liquid suspensions
DE7611162U1 (en) * 1976-04-09 1978-04-20 Kaeser Kompressoren Gmbh, 8630 Coburg DOUBLE SCREW SCREW COMPRESSOR
JPH02502743A (en) * 1987-12-25 1990-08-30 ショロホフ　ヴァレリイ　ボリソヴィチ molecular vacuum pump
CA2058325A1 (en) * 1990-12-24 1992-06-25 Mark E. Baran Positive displacement pumps
JPH04370379A (en) * 1991-06-17 1992-12-22 Seiko Seiki Co Ltd Dry vacuum pump
JPH05195957A (en) * 1992-01-23 1993-08-06 Matsushita Electric Ind Co Ltd Vacuum pump
JPH05272478A (en) * 1992-01-31 1993-10-19 Matsushita Electric Ind Co Ltd Vacuum pump
DE4242406C2 (en) * 1992-12-08 2002-10-31 Grasso Gmbh Refrigeration Tech Arrangement in a screw compressor
US5797735A (en) * 1995-04-03 1998-08-25 Tochigi Fuji Sangyo Kabushiki Kaisha Fluid machine having balance correction
CZ289289B6 (en) * 1995-12-11 2001-12-12 Ateliers Busch S. A. Double worm system
DE19632874A1 (en) * 1996-08-16 1998-02-19 Leybold Vakuum Gmbh Friction vacuum pump
DE19745616A1 (en) * 1997-10-10 1999-04-15 Leybold Vakuum Gmbh Cooling system for helical vacuum pump
DE19839501A1 (en) * 1998-08-29 2000-03-02 Leybold Vakuum Gmbh Dry compacting screw pump

Also Published As

Publication number Publication date
JP4200007B2 (en) 2008-12-24
DE10111525A1 (en) 2002-09-12
EP1366296A1 (en) 2003-12-03
WO2002073037A1 (en) 2002-09-19
US20040067149A1 (en) 2004-04-08
DE50208778D1 (en) 2007-01-04
JP2004522038A (en) 2004-07-22

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