EP1307657B1 - Two-shaft vacuum pump - Google Patents

Two-shaft vacuum pump Download PDF

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Publication number
EP1307657B1
EP1307657B1 EP01960473A EP01960473A EP1307657B1 EP 1307657 B1 EP1307657 B1 EP 1307657B1 EP 01960473 A EP01960473 A EP 01960473A EP 01960473 A EP01960473 A EP 01960473A EP 1307657 B1 EP1307657 B1 EP 1307657B1
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EP
European Patent Office
Prior art keywords
shaft
rotor
rotors
shafts
pump according
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
EP01960473A
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German (de)
French (fr)
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EP1307657A1 (en
Inventor
Hartmut Kriehn
Lothar Brenner
Manfred Behling
Thomas Dreifert
Klaus Rofall
Heinrich Engländer
Michael Froitzheim
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Leybold GmbH
Original Assignee
Leybold Vakuum GmbH
Leybold Vacuum GmbH
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Publication date
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Publication of EP1307657A1 publication Critical patent/EP1307657A1/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
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • 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 a two-shaft vacuum pump, in particular screw vacuum pump, having the features of the preamble of the new patent claim 1.
  • the flying bearing is the cause of problems with the play-free mounting of the rotors on their shafts. It is known that it is expedient for a flying bearing when the center of gravity of the rotating system is as close as possible to the rotor-side bearing. This can be achieved by choosing the lightest possible material for the rotor, for. As aluminum. However, aluminum has a significantly higher coefficient of thermal expansion (about 23 x 10 -6 / K) than steel (12 x 10 -6 / K), which is particularly suitable as a shaft material for flying bearings. Steel has a high modulus of elasticity, which makes it possible to produce stiff waves.
  • the JP-08 261183 discloses a rotary unit screw machine having a steel shaft and a two-piece hollow rotor made of aluminum. Part of each rotor is a central sleeve, which is fixed on the associated shaft. The sleeve carries an outer component with the screw contour. The shaft projects out of the rotor on both sides.
  • the present invention has for its object to provide a vacuum pump with the generic features that optimally meet the objectives of the manufacturer and developer of these vacuum pumps, d. their rotors are equipped with a flying bearing favorable for screw vacuum pumps, that allow the material selection for their rotors and shafts high speeds and that due to the selection of both the shaft material and the rotor / shaft connections operation of the pump with small Gap leakage is possible.
  • the shafts are made of a material with the highest possible modulus of elasticity (eg steel) and that means for securing a play-free fastening of the rotors on the shafts are provided at all operating temperatures of the pump, is a precise guidance of the shafts and thus the rotors ensured.
  • the gaps between the rotors themselves and their housing walls can be kept small.
  • the rotor material which is lightweight compared to the shaft material, allows the pumps to be operated at high speeds.
  • the rotors are denoted by 1 (or 1 and 2 in Figure 2) and their shafts with 3 (or 3, 4).
  • the rotors are cantilevered and equipped with axial hollow holes into which the free ends of the shafts 3, 4 extend. On these shaft ends, the rotors 1, 2 are fixed without play.
  • the rotor 1 has two end-side hollow holes 5 and 6, which are connected approximately in the middle of the rotor 1 via a narrower bore 7.
  • the suction-side opening of the hollow bore 6 is sealed with a disc 8, the z. B. - as shown - is screwed into the opening of the hollow bore by means of a thread 9.
  • the shaft 1 which is frontally equipped with an axially directed collar 11.
  • the hollow bores 5 and 6 interconnecting bore 7 of the annular, inwardly extending projection 12 is equipped with an axially directed collar 13, whose direction and diameter are chosen so that it the collar 11 of the shaft 1 from the inside is applied. If the shaft 3 made of steel and the rotor 1 made of aluminum with a larger expansion coefficient compared to steel and are the collar 11, 13th At ambient temperature each other without clearance, resulting in an internal centering, which remains free of play even at higher temperatures.
  • axial bolts 14 are provided, which are accessible from the hollow bore 6 ago. They enforce the projection 12 of the rotor 1 and are screwed into the collar 11 of the shaft. Appropriately, the bolt heads associated with a ring 15, which consists of the shaft material. This results in addition to the Warmzentritation still a Reibzentri für.
  • shaft 3 and rotor 1 are equipped with a cooling channel system for reducing the temperature problems.
  • the shaft 3 has a central bore 16.
  • this bore 16 is a pipe section 17 which extends into the hollow bore 6 in and serves to supply a coolant.
  • the hollow bore 6 form hollow (thin-walled) and / or lightweight, mounted on the pipe section 17 internals 18 an outer annular channel 19, inter alia via the bore 7 with an outer annular channel 21 in the hollow bore 5, formed by the shaft 3 and the inner wall the hollow bore 5, is connected.
  • a reverse flow direction of the coolant may also be useful.
  • the rotors 1, 2 bearing side with collar 25, 26 equipped which include the shafts 3, 4 from the outside. If the rotor material has a greater coefficient of expansion than the shafts, external centering of this type can cause play between the rotors and the shaft as temperatures increase. To avoid this, rings 27, 28 are provided, which in turn comprise the collars 25, 26. If the material of the rings 27, 28 has an expansion coefficient which is equal to or even smaller than the coefficient of expansion of the shaft material, the rings 27, 28 prevent expansion of the collars 25, 26 and thus the undesirable play with increasing temperatures.
  • a cooling system according to the Figure 1 corresponding cooling system is provided.
  • the annular channels 21, 22 extend into the region of the collar 25, 26. They reduce the maximum operating temperatures occurring and thus also eliminate the risk of games.
  • the rings 27, 28 are equipped with annular grooves in which piston rings, not shown, are located. They form together with housing-fixed rings 29, 30 labyrinth seals 31, 32, which have the task of preventing the ingress of lubricant vapors from the bearings 33, 34 in the delivery chambers 35, 36 of the screw pump.
  • the disc 38 may be equipped with an axially directed collar 43 which engages in the hollow bore 5. This can be achieved at the same time a hot centering. For this it is necessary that rotor 1, shaft 3 and disc 38 are mounted without clearance in the warm state. Because of the mentioned ratios of the expansion coefficients, this attachment remains free of play with decreasing temperatures. This also applies to a rotor / shaft attachment without disc 38th
  • the attachment of the rotor on the shaft can also be done by means of a press-fit connection. If the rotor consists of aluminum and the shaft of steel, then it is expedient that the ambient temperature at which this press-fit connection is produced corresponds approximately to the maximum temperature of the rotors (1, 2) which occurs during operation of the twin-shaft vacuum pump.
  • a compound of this type is free of play in all operating temperatures occurring during operation of the two-shaft vacuum pump.
  • FIG. 3 shows the possibility of arranging the rotor-side bearing 33 in a bearing-side recess 47 in the rotor 3.
  • the cooling channel system (bore 16 in the shaft 3, pipe section 17) extends to the bearing 33 to keep the bearing temperatures low.
  • the two shaft bearings 33, 51 have an O-arrangement, as shown in FIG.
  • the force application point moves through the pressure angle in the direction of the rotor's center of gravity.
  • a floating bearing 33 on the rotor side and a fixed bearing 51 on the side facing away from the rotor of the shaft 3 is expedient.
  • FIG. 5 shows this arrangement.
  • the force application point is located in the middle of the camp.

Description

Die Erfindung betrifft eine Zweiwellenvakuumpumpe, insbesondere Schraubenvakuumpumpe, mit den Merkmalen des Oberbegriffs des neuen Patentanspruchs 1.The invention relates to a two-shaft vacuum pump, in particular screw vacuum pump, having the features of the preamble of the new patent claim 1.

Die Entwickler und Hersteller von Pumpen der genannten Art, insbesondere Schraubenvakuumpumpen, verfolgen das Ziel, dass solche Pumpen bei vertretbaren Herstellkosten mit möglichst hohen Drehzahlen und möglichst kleinen Spaltleckagen betrieben werden können, um den Zweck - Vakuumerzeugung - möglichst effektiv zu erreichen. Voraussetzungen dafür sind eine präzise Lagerung und eine - auch im warmen Zustand - spielfreie Befestigung der Rotoren auf den Wellen. Bezüglich der Lagerung ist zu berücksichtigen, dass die Rotoren fliegend gelagert sein sollen. Das geschieht üblicherweise mit Hilfe von jeweils zwei Lagern, zwischen denen sich ein Antriebsmotor befindet. Gerade bei Schraubenvakuumpumpen hat sich diese Art der Lagerung als zweckmäßig erwiesen, da ihre Vorteile - keine Dichtung an der Saugseite, kostengünstiger als zweiflutige Lösungen - die Nachteile - höhere Anforderungen an Welle und Lagerung - überwiegen.The developers and manufacturers of pumps of the type mentioned, in particular screw vacuum pumps, pursue the goal that such pumps can be operated at reasonable manufacturing costs with the highest possible speeds and the smallest possible gap leakage in order to achieve the purpose - vacuum generation - as effectively as possible. Prerequisites for this are a precise bearing and - even when warm - play-free attachment of the rotors on the shafts. With regard to storage, it should be noted that the rotors are to be cantilevered. This usually happens with the help of two bearings, between which there is a drive motor. Especially with screw vacuum pumps, this type of storage has proven to be useful, since its advantages - no seal on the suction side, more cost-effective than double-flow solutions - the disadvantages - higher demands on shaft and bearing - outweigh.

Die fliegende Lagerung ist Ursache für Probleme mit der spielfreien Befestigung der Rotoren auf ihren Wellen. Es ist bekannt, dass es bei einer fliegenden Lagerung zweckmäßig ist, wenn sich der Schwerpunkt des rotierenden Systems möglichst in der Nähe des rotorseitigen Lagers befindet. Dieses lässt sich dadurch erreichen, dass ein möglichst leichter Werkstoff für den Rotor gewählt wird, z. B. Aluminium. Aluminium hat jedoch einen wesentlichen höheren Wärmeausdehnungskoeffizienten (ca. 23 x 10-6/K) als Stahl (12 x 10-6/K), der bei fliegenden Lagerungen als Wellenwerkstoff besonders geeignet ist. Stahl hat ein hohes Elastizitätsmodul, weshalb die Herstellung steifer Wellen möglich ist. Bei der Werkstoffpaarung Stahl / Aluminium ist es schwierig, eine bei allen Betriebstemperaturen (zwischen Umgebungstemperatur und etwa 200° C) spielfreie Befestigung des Rotors auf der Welle zu realisieren. Es besteht zwar die Möglichkeit, von der Ausdehnungsproblematik her günstigere Werkstoffe wie Stahl, Ti oder Keramik für den Rotor einzusetzen. Diese führen jedoch zu sehr schweren (Stahl) oder teuren Rotoren (Ti, Keramik). Auch kommt Aluminium auf Grund des geringen E-Moduls nicht als Wellenwerkstoff in Frage.The flying bearing is the cause of problems with the play-free mounting of the rotors on their shafts. It is known that it is expedient for a flying bearing when the center of gravity of the rotating system is as close as possible to the rotor-side bearing. This can be achieved by choosing the lightest possible material for the rotor, for. As aluminum. However, aluminum has a significantly higher coefficient of thermal expansion (about 23 x 10 -6 / K) than steel (12 x 10 -6 / K), which is particularly suitable as a shaft material for flying bearings. Steel has a high modulus of elasticity, which makes it possible to produce stiff waves. With the material combination steel / aluminum, it is difficult to realize a clearance-free mounting of the rotor on the shaft at all operating temperatures (between ambient temperature and about 200 ° C.). Although it is possible to use the expansion problem ago cheaper materials such as steel, Ti or ceramic for the rotor. However, these lead to very heavy (steel) or expensive rotors (Ti, ceramics). Also aluminum is due to the low modulus of elasticity not as a shaft material in question.

Aus der EP 480 629 A1 ist eine Vakuumpumpe mit den Merkmalen des Oberbegriffs des Anspruchs 1 bekannt. Die Rotoren sind mit jeweils einem Bolzen an ihren zugehörigen Wellen befestigt. Auf eine auch im warmen Zustand spielfreie Befestigung der Rotoren auf ihren Wellen wird nicht eingegangen.From the EP 480 629 A1 a vacuum pump with the features of the preamble of claim 1 is known. The rotors are fastened to their respective shafts with one bolt each. On a play-free mounting of the rotors on their shafts in the warm state is not discussed.

Die JP-08 261183 offenbart eine Schraubenmaschine mit rotierenden Einheiten, die eine Stahlwelle und einen zweiteiligen hohlen Rotor aus Aluminium besitzen. Bestandteil eines jeden Rotors ist eine zentrale Hülse, die auf der zugehörigen Welle fixiert ist. Die Hülse trägt ein äußeres Bauteil mit der Schraubenkontur. Die Welle ragt beidseitig aus dem Rotor heraus.The JP-08 261183 discloses a rotary unit screw machine having a steel shaft and a two-piece hollow rotor made of aluminum. Part of each rotor is a central sleeve, which is fixed on the associated shaft. The sleeve carries an outer component with the screw contour. The shaft projects out of the rotor on both sides.

DE 198 39 501 A1 offenbart eine Schraubenspindelpumpe, die auch als Vakuumpumpe einsetzbar ist. Sie besitzt hohle Rotoren, die auf ruhenden Zapfen gelagert sind. DE 198 39 501 A1 discloses a screw pump which can also be used as a vacuum pump. It has hollow rotors, which are mounted on stationary pins.

In der US 52 95 788 ist eine rotierende Einheit für eine Schraubenmaschine offenbart. Sie besitzt eine Stahlwelle und einen Aluminium-Rotor. Rotor und Welle sind sowohl kraftschlüssig als auch formschlüssig miteinander verbunden. Eine Pressverbindung besteht in Höhe des relativ kurzen Wellenabschnittes 18. Diese kraftschlüssige Verbindung wird dadurch hergestellt, dass die Welle in die zentrale Bohrung des Rotors durch Anwendung von Kraft eingepresst wird (vgl. Spalte 3, Zeilen 6 bis 8). Die aufzuwendende Kraft muss offensichtlich hoch sein. Es wird deshalb empfohlen, während des Pressvorgangs Schmiermittel zu verwenden (vgl. Spalte 3, Zeilen 34 bis 38). In Höhe von "serrated", Abschnitten 19, 20 bestehende Verbindungsmittel können als formschlüssig angesehen werden. Darüber hinaus besteht eine in Bezug auf Drehmomente kraftschlüssige Verbindung, die einen Bohrungen in Welle und Rotor durchsetzenden Stift umfasst.In the US 52 95 788 discloses a rotating unit for a screw machine. It has a steel shaft and an aluminum rotor. Rotor and shaft are connected to each other both positively and positively. A positive connection is made by pressing the shaft into the central bore of the rotor by application of force (see column 3, lines 6 to 8). The force required must obviously be high. It is therefore recommended to use lubricants during the pressing process (see column 3, lines 34 to 38). In the amount of "serrated", sections 19, 20 existing connection means can be regarded as positive. In addition, there is a force-locking connection with respect to torque, which comprises a bore in the shaft and rotor passing through pin.

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, eine Vakuumpumpe mit den gattungsgemäßen Merkmalen zu schaffen, die die Ziele der Hersteller und Entwickler dieser Vakuumpumpen optimal erfüllen, d. h., dass ihre Rotoren mit einer für Schraubenvakuumpumpen günstigen fliegenden Lagerung ausgerüstet sind, dass die Materialauswahl für ihre Rotoren und Wellen hohe Drehzahlen zulassen und dass aufgrund der Auswahl sowohl des Wellenwerkstoffs als auch der Rotor-/Welle-Verbindungen ein Betrieb der Pumpe mit kleinen Spaltleckagen möglich ist.The present invention has for its object to provide a vacuum pump with the generic features that optimally meet the objectives of the manufacturer and developer of these vacuum pumps, d. their rotors are equipped with a flying bearing favorable for screw vacuum pumps, that allow the material selection for their rotors and shafts high speeds and that due to the selection of both the shaft material and the rotor / shaft connections operation of the pump with small Gap leakage is possible.

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

Dadurch, dass die Wellen aus einem Werkstoff mit einem möglichst hohen Elastizitätsmodul (z. B. Stahl) bestehen und dass Mittel zur Sicherung einer spielfreien Befestigung der Rotoren auf den Wellen bei allen Betriebstemperaturen der Pumpe vorgesehen sind, ist eine präzise Führung der Wellen und damit der Rotoren sicher gestellt. Die Spalte zwischen den Rotoren selbst und ihren Gehäusewandungen können klein gehalten werden. Darüber hinaus erlaubt der im Vergleich zum Wellenwerkstoff leichte Rotorwerkstoff das Betreiben der Pumpen mit hohen Drehzahlen.The fact that the shafts are made of a material with the highest possible modulus of elasticity (eg steel) and that means for securing a play-free fastening of the rotors on the shafts are provided at all operating temperatures of the pump, is a precise guidance of the shafts and thus the rotors ensured. The gaps between the rotors themselves and their housing walls can be kept small. In addition, the rotor material, which is lightweight compared to the shaft material, allows the pumps to be operated at high speeds.

Zusätzlich können weitere Mittel zur Sicherung der spielfreien Befestigung der Rotoren auf ihren Wellen vorgesehen sein. Bei größeren Differenzen der Ausdehnungskoeffizienten der beteiligten Werkstoffe können die Rotoren und die Wellen so ausgebildet sein, dass die Spielfreiheit zusätzlich durch Warmzentrierung, Kaltzentrierung und/oder Reibzentrierung sichergestellt ist. Auch Bandagen, die die größere Ausdehnung des auf der Stahlwelle befestigten Aluminiumrotors verhindern, sind möglich. Schließlich kann unterstützt oder allein - eine Kühlung vorhanden sein, die Temperaturschwankungen der Fügestellen begrenzt oder verhindert.In addition, further means for securing the backlash-free attachment of the rotors can be provided on their shafts. For larger differences in the expansion coefficients of the materials involved, the rotors and the shafts can be designed so that the backlash is additionally ensured by hot centering, cold centering and / or Reibzentrierung. Also bandages that prevent the greater extent of the mounted on the steel shaft aluminum rotor are possible. Finally, it can be supported or alone - a cooling system that limits or prevents temperature fluctuations of the joints.

Um zu erreichen, dass der Schwerpunkt der jeweils aus einem Rotor und einer Welle bestehenden Systeme zur Erzielung hoher Drehzahlen möglichst nahe beim rotorseitigen Lager liegt, können verschiedene Maßnahmen zweckmäßig sein:

  • Hohlbohrung im Rotor, in welche die Stahlwelle nur teilweise eingreift; falls es zur Führung einer Kühlflüssigkeit nötig ist, können dazu Bauteile mit geringen Dichten (z.B. Kunststoffe) in der Bohrung untergebracht sein.
  • Kurze Rotoren; dieses wird bei Schraubenpumpen in an sich bekannter Weise durch geeignete Steigungsänderung und/oder durch tief eingeschnittene Rotorprofile erreicht.
  • Unterbringung des rotorseitigen Wellenlagers in einer lagerseitigen Aussparung im Rotor.
  • O-Anordnung der beiden Wellenlager und/oder Loslager an der Rotorseite und Festlager an der dem Rotor abgewandten Seite der Welle.
In order to achieve that the center of gravity of each of a rotor and a shaft existing systems to achieve high speeds as close as possible to the rotor side bearing, various measures may be appropriate:
  • Hollow bore in the rotor, in which the steel shaft only partially engages; if it is necessary to guide a coolant, components with low densities (eg plastics) can be accommodated in the bore.
  • Short rotors; this is achieved in screw pumps in a conventional manner by suitable change in pitch and / or by deeply cut rotor profiles.
  • Housing the rotor-side shaft bearing in a bearing-side recess in the rotor.
  • O arrangement of the two shaft bearings and / or floating bearing on the rotor side and fixed bearing on the side facing away from the rotor of the shaft.

Weitere Vorteile und Einzelheiten sollen an Hand von in den Figuren 1 bis 5 schematisch dargestellten Ausführungsbeispielen erläutert werden. Es zeigen:Further advantages and details will be explained with reference to embodiments schematically illustrated in Figures 1 to 5. Show it:

In den Figuren sind die Rotoren mit 1 (bzw. 1 und 2 in Figur 2) und deren Wellen mit 3 (bzw. 3, 4) bezeichnet. Die Rotoren sind fliegend gelagert und mit axialen Hohlbohrungen ausgerüstet, in die hinein sich die freien Enden der Wellen 3, 4 erstrecken. Auf diesen Wellenenden sind die Rotoren 1, 2 jeweils spielfrei befestigt.In the figures, the rotors are denoted by 1 (or 1 and 2 in Figure 2) and their shafts with 3 (or 3, 4). The rotors are cantilevered and equipped with axial hollow holes into which the free ends of the shafts 3, 4 extend. On these shaft ends, the rotors 1, 2 are fixed without play.

Beim Ausführungsbeispiel nach Figur 1 weist der Rotor 1 zwei stirnseitige Hohlbohrungen 5 und 6 auf, die etwa in der Mitte des Rotors 1 über eine engere Bohrung 7 miteinander verbunden sind. Im zusammengebauten Zustand ist die saugseitige Öffnung der Hohlbohrung 6 mit einer Scheibe 8 dicht verschlossen, die z. B. - wie dargestellt - in die Öffnung der Hohlbohrung mit Hilfe eines Gewindes 9 eingeschraubt ist.In the embodiment of Figure 1, the rotor 1 has two end-side hollow holes 5 and 6, which are connected approximately in the middle of the rotor 1 via a narrower bore 7. In the assembled state, the suction-side opening of the hollow bore 6 is sealed with a disc 8, the z. B. - as shown - is screwed into the opening of the hollow bore by means of a thread 9.

In der lagerseitigen Hohlbohrung 5 endet bereits die Welle 1, die stirnseitig mit einem axial gerichteten Kragen 11 ausgerüstet ist. Im Bereich der engeren, die Hohlbohrungen 5 und 6 miteinander verbindenden Bohrung 7 ist der ringförmige, sich nach innen erstreckende Vorsprung 12 mit einem axial gerichteten Kragen 13 ausgerüstet, dessen Richtung und Durchmesser so gewählt sind, dass er dem Kragen 11 der Welle 1 von innen anliegt. Besteht die Welle 3 aus Stahl und der Rotor 1 aus Aluminium mit einem im Vergleich zu Stahl größeren Ausdehnungskoeffizienten und liegen die Kragen 11, 13 bei Umgebungstemperatur einander spielfrei an, ergibt sich eine Innenzentrierung, die auch bei höheren Temperaturen spielfrei bleibt.In the bearing-side hollow bore 5 already ends the shaft 1, which is frontally equipped with an axially directed collar 11. In the area of the narrower, the hollow bores 5 and 6 interconnecting bore 7 of the annular, inwardly extending projection 12 is equipped with an axially directed collar 13, whose direction and diameter are chosen so that it the collar 11 of the shaft 1 from the inside is applied. If the shaft 3 made of steel and the rotor 1 made of aluminum with a larger expansion coefficient compared to steel and are the collar 11, 13th At ambient temperature each other without clearance, resulting in an internal centering, which remains free of play even at higher temperatures.

Zur Verbindung von Rotor 1 und Welle 3 sind axiale Bolzen 14 vorgesehen, die von der Hohlbohrung 6 her zugänglich sind. Sie durchsetzen den Vorsprung 12 des Rotors 1 und sind in den Kragen 11 der Welle eingeschraubt. Zweckmäßig ist den Bolzenköpfen ein Ring 15 zugeordnet, der aus dem Wellenwerkstoff besteht. Dadurch ergibt sich neben der Warmzentrierung noch eine Reibzentrierung.For connecting rotor 1 and shaft 3 axial bolts 14 are provided, which are accessible from the hollow bore 6 ago. They enforce the projection 12 of the rotor 1 and are screwed into the collar 11 of the shaft. Appropriately, the bolt heads associated with a ring 15, which consists of the shaft material. This results in addition to the Warmzentrierung still a Reibzentrierung.

Im übrigen sind Welle 3 und Rotor 1 zur Reduzierung der Temperaturprobleme mit einem Kühlkanalsystem ausgerüstet. Dazu weist die Welle 3 eine zentrale Bohrung 16 auf. In dieser Bohrung 16 befindet sich ein Rohrabschnitt 17, der sich bis in die Hohlbohrung 6 hinein erstreckt und der Zuführung eines Kühlmittels dient. In der Hohlbohrung 6 bilden hohle (dünnwandige) und/oder leichte, auf dem Rohrabschnitt 17 befestigte Einbauten 18 einen äußeren Ringkanal 19, der u.a. über die Bohrung 7 mit einem äußeren Ringkanal 21 in der Hohlbohrung 5, gebildet von der Welle 3 und der Innenwandung der Hohlbohrung 5, verbunden ist. Über diese Ringkanäle 19, 21 und danach über den in der Welle befindlichen Ringkanal 23, gebildet vom Rohrabschnitt 17 und der Innenwandung der Bohrung 16, strömt das Kühlmittel zurück. Eine umgekehrte Strömungsrichtung des Kühlmittels kann ebenfalls sinnvoll sein.Incidentally, shaft 3 and rotor 1 are equipped with a cooling channel system for reducing the temperature problems. For this purpose, the shaft 3 has a central bore 16. In this bore 16 is a pipe section 17 which extends into the hollow bore 6 in and serves to supply a coolant. In the hollow bore 6 form hollow (thin-walled) and / or lightweight, mounted on the pipe section 17 internals 18 an outer annular channel 19, inter alia via the bore 7 with an outer annular channel 21 in the hollow bore 5, formed by the shaft 3 and the inner wall the hollow bore 5, is connected. About this annular channels 19, 21 and then on the located in the shaft ring channel 23, formed by the pipe section 17 and the inner wall of the bore 16, the coolant flows back. A reverse flow direction of the coolant may also be useful.

In Figur 2 sind die Rotoren 1, 2 lagerseitig mit Kragen 25, 26 ausgerüstet, die die Wellen 3, 4 von außen umfassen. Hat der Rotorwerkstoff einen größeren Ausdehnungskoeffizienten als die Wellen, kann es bei einer Außenzentrierung dieser Art zu Spielen zwischen Rotoren und Welle kommen, wenn die Temperaturen ansteigen. Um das zu vermeiden, sind Ringe 27, 28 vorgesehen, die ihrerseits die Kragen 25, 26 umfassen. Hat der Werkstoff der Ringe 27, 28 einen Ausdehnungskoeffizienten, der gleich oder sogar kleiner als der Ausdehnungskoeffizient des Wellenwerkstoffes ist, verhindern die Ringe 27, 28 bei ansteigenden Temperaturen eine Ausdehnung der Kragen 25, 26 und damit die unerwünschten Spiele.In Figure 2, the rotors 1, 2 bearing side with collar 25, 26 equipped, which include the shafts 3, 4 from the outside. If the rotor material has a greater coefficient of expansion than the shafts, external centering of this type can cause play between the rotors and the shaft as temperatures increase. To avoid this, rings 27, 28 are provided, which in turn comprise the collars 25, 26. If the material of the rings 27, 28 has an expansion coefficient which is equal to or even smaller than the coefficient of expansion of the shaft material, the rings 27, 28 prevent expansion of the collars 25, 26 and thus the undesirable play with increasing temperatures.

Ein dem Kühlsystem nach Figur 1 entsprechendes Kühlsystem ist vorgesehen. Die Ringkanäle 21, 22 erstrecken sich bis in den Bereich der Kragen 25, 26. Sie reduzieren die maximal auftretenden Betriebstemperaturen und beseitigen damit ebenfalls die Gefahr von Spielen.A cooling system according to the Figure 1 corresponding cooling system is provided. The annular channels 21, 22 extend into the region of the collar 25, 26. They reduce the maximum operating temperatures occurring and thus also eliminate the risk of games.

Von außen sind die Ringe 27, 28 mit ringförmigen Nuten ausgerüstet, in denen sich nicht dargestellte Kolbenringe befinden. Sie bilden gemeinsam mit gehäusefesten Ringen 29, 30 Labyrinthdichtungen 31, 32, die die Aufgabe haben, das Eindringen von Schmiermitteldämpfen von den Lagern 33, 34 in die Förderräume 35, 36 der Schraubenpumpe zu verhindern.From the outside, the rings 27, 28 are equipped with annular grooves in which piston rings, not shown, are located. They form together with housing-fixed rings 29, 30 labyrinth seals 31, 32, which have the task of preventing the ingress of lubricant vapors from the bearings 33, 34 in the delivery chambers 35, 36 of the screw pump.

Beim Ausführungsbeispiel nach Figur 3 ist eine Reibzentrierung realisiert. Dazu dient eine Scheibe 38, die zunächst die Aufgabe hat, die saugseitige Öffnung der Hohlbohrung 5 zu verschließen. Die Scheibe 38 ist über Bolzen sowohl mit der Welle 3 (Bolzen 39) als auch mit dem Rotor (mehrere Bolzen 41) fest verbunden. Hat das Rotormaterial einen größeren Ausdehnungskoeffizienten als die Welle 3 und besteht die Scheibe 38 beispielsweise aus dem Wellenwerkstoff, dann verhindert die feste Bolzenverbindung bei ansteigenden Temperaturen die Entstehung eines Spiels.In the embodiment of Figure 3 a Reibzentrierung is realized. The purpose of a disc 38, which initially has the task to close the suction-side opening of the hollow bore 5. The disc 38 is over Bolt with both the shaft 3 (bolt 39) and with the rotor (several bolts 41) firmly connected. If the rotor material has a greater coefficient of expansion than the shaft 3, and if the disk 38 consists, for example, of the shaft material, then the solid bolt connection prevents the formation of a clearance in the event of rising temperatures.

Wie in Figur 3 dargestellt, kann die Scheibe 38 mit einem axial gerichteten Kragen 43 ausgerüstet sein, der in die Hohlbohrung 5 eingreift. Dadurch kann gleichzeitig eine Warmzentrierung erreicht werden. Dazu ist es erforderlich, dass Rotor 1, Welle 3 und Scheibe 38 im warmen Zustand spielfrei montiert werden. Wegen der erwähnten Verhältnisse der Ausdehnungskoeffizienten bleibt diese Befestigung bei abnehmenden Temperaturen spielfrei. Dieses gilt auch für eine Rotor-/Welle-Befestigung ohne Scheibe 38.As shown in Figure 3, the disc 38 may be equipped with an axially directed collar 43 which engages in the hollow bore 5. This can be achieved at the same time a hot centering. For this it is necessary that rotor 1, shaft 3 and disc 38 are mounted without clearance in the warm state. Because of the mentioned ratios of the expansion coefficients, this attachment remains free of play with decreasing temperatures. This also applies to a rotor / shaft attachment without disc 38th

Die Befestigung des Rotors auf der Welle kann auch mittels einer Presssitzverbindung erfolgen. Bestehen der Rotor aus Aluminium und die Welle aus Stahl, dann ist es dabei zweckmäßig, dass die Umgebungstemperatur, bei welcher diese Presssitzverbindung hergestellt wird, etwa der maximalen Temperatur der Rotoren (1, 2) entspricht, die beim Betrieb der Zweiwellenvakuumpumpe auftritt.The attachment of the rotor on the shaft can also be done by means of a press-fit connection. If the rotor consists of aluminum and the shaft of steel, then it is expedient that the ambient temperature at which this press-fit connection is produced corresponds approximately to the maximum temperature of the rotors (1, 2) which occurs during operation of the twin-shaft vacuum pump.

Eine Verbindung dieser Art ist bei allen während des Betriebs der Zweiwellenvakuumpumpe auftretenden Betriebstemperaturen spielfrei.A compound of this type is free of play in all operating temperatures occurring during operation of the two-shaft vacuum pump.

In Figur 3 ist noch dargestellt, dass Kragen 43 und Stirnseite der Welle 3 einander aufliegen, vorzugsweise innerhalb einer äußeren Aussparung 44 in der Welle 3. Zwischen den einander zugewandten Auflageflächen von Kragen 43 und Welle 3 befindet sich ein Passring 45. Durch Einlegen von Passringen 45 mit verschiedenen Dicken - oder auch durch Kragen 43 mit verschiedenen Höhen - kann die axiale Position des Rotors 1 zur Welle 3 bestimmt werden. Dadurch besteht die Möglichkeit, das Flanke-Flanke-Spiel des Rotors 1 zum zweiten, nicht dargestellten Rotor einzustellen. Die Scheibe 38 kann gleichzeitig zum Wuchtausgleich und/oder zur Drehmomentenübertragung (z.B. als Zahnscheibe) dienen.In Figure 3 is still shown that collar 43 and end face of the shaft 3 rest on each other, preferably within an outer recess 44 in the shaft 3. Between the facing bearing surfaces of collar 43 and shaft 3 is a fitting ring 45. By inserting pass rings 45 with different thicknesses - or by collar 43 with different heights - the axial position of the rotor 1 to the shaft 3 can be determined. This makes it possible to adjust the edge-flank clearance of the rotor 1 to the second rotor, not shown. The disc 38 can simultaneously serve for balancing and / or for the transmission of torque (for example as a toothed disc).

Figur 3 zeigt schließlich die Möglichkeit, das rotorseitige Lager 33 in einer lagerseitigen Aussparung 47 im Rotor 3 anzuordnen. In die Aussparung 47 greift ein sich axial erstreckender Lagerträger 48 ein. Das Kühlkanalsystem (Bohrung 16 in der Welle 3, Rohrabschnitt 17) erstreckt sich bis zum Lager 33, um die Lagertemperaturen niedrig zu halten.Finally, FIG. 3 shows the possibility of arranging the rotor-side bearing 33 in a bearing-side recess 47 in the rotor 3. In the recess 47 engages an axially extending bearing support 48 a. The cooling channel system (bore 16 in the shaft 3, pipe section 17) extends to the bearing 33 to keep the bearing temperatures low.

Um die gewünschten hohen Drehzahlen sicher zu erreichen, ist es zweckmäßig, wenn die beiden Wellenlager 33, 51 eine O-Anordnung aufweisen, wie sie in Figur 4 dargestellt ist. Bei Lagern dieser Art wandert der Kraftangriffspunkt durch den Druckwinkel in Richtung Rotorschwerpunkt. Unter diesem Gesichtspunkt ist auch ein Loslager 33 an der Rotorseite und ein Festlager 51 an der dem Rotor abgewandten Seite der Welle 3 zweckmäßig. Figur 5 zeigt diese Anordnung. Der Kraftangriffspunkt liegt in der Lagermitte.In order to safely achieve the desired high speeds, it is expedient if the two shaft bearings 33, 51 have an O-arrangement, as shown in FIG. In bearings of this type, the force application point moves through the pressure angle in the direction of the rotor's center of gravity. From this point of view, a floating bearing 33 on the rotor side and a fixed bearing 51 on the side facing away from the rotor of the shaft 3 is expedient. FIG. 5 shows this arrangement. The force application point is located in the middle of the camp.

Claims (13)

  1. Two-shaft vacuum pump, in particular a screw-type vacuum pump, comprising two shafts (3, 4) and two interacting rotors (1, 2) fastened on the shafts,
    each of the rotors (1, 2) has a hollow bore (5), each of the hollow bores (5) is at least partially penetrated by the associated shaft (3, 4), the rotors (1, 2) are over-mounted at their discharge end by means of the shafts (3, 4),
    characterized by the following features:
    the shafts (3, 4) are made of steel,
    the rotors (1, 2) are made of aluminium, for the purpose of a backlash-free fastening of the rotors (1, 2) on the shafts (3, 4) an interference fit connection is provided,
    the interference fit connection is produced by temperature application, wherein the ambient temperature is selected in such a way that it corresponds approximately to the maximum temperature of the rotors (1, 2) that arises during operation of the pump, so that the rotor/shaft connection is free of backlash at all operating temperatures of the rotors.
  2. Pump according to claim 1, characterized in that hot-centring means are additionally provided, which comprise axially extending collar portions (13) on the rotor (1, 2) and/or (11) on the shaft (3, 4) and engage in such a way into one another that the collar portion (13) of the rotor (1, 2) is inside.
  3. Pump according to claim 1, characterized in that friction-centring means are additionally provided and comprise axially oriented bolts (14, 39, 41), by means of which rotor (1, 2) and shaft (3, 4) are connected to one another.
  4. Pump according to claim 1, characterized in that the rotor (1, 2) has a hollow bore and that a disk (38) disposed at the suction side of the rotor is provided.
  5. Pump according to claim 4, characterized in that the disk (38) is equipped with a collar (43), which engages into the hollow bore (5) of the rotor (1, 2) and effects cold centring.
  6. Pump according to claim 5, characterized in that collar (43) and shaft (3) are supported one on the other, namely via an adjusting ring (45).
  7. Pump according to claim 1, characterized in that the rotor (1, 2) is equipped with a collar (25, 26) that encompasses the shaft (3, 4), and that a banding (27, 28) is provided, which in turn encompasses the collar (25, 26).
  8. Pump according to one of the preceding claims, characterized in that a cooling device is situated at the level of the fitting points between shaft (3, 4) and rotor (1, 2).
  9. Pump according to one of the preceding claims, characterized in that the shaft (3, 4) only partially penetrates the hollow space.
  10. Pump according to claims 8 and 9, characterized in that in the hollow space not occupied by the shaft (3, 4) lightweight components (18) carrying a coolant flow are situated.
  11. Pump according to one of the preceding claims, characterized in that the rotors (1, 2) are as short as possible in axial direction and that the thread has a pitch that decreases from the suction side to the discharge end.
  12. Pump according to one of the preceding claims, characterized in that the rotor-side bearing (33) is situated in a recess (47) in the rotor (1, 2).
  13. Method of manufacturing a unit, comprising a rotor (1, 2) and a shaft (3, 4), for a two-shaft vacuum pump, in particular a screw-type vacuum pump, comprising two shafts (3, 4) and two interacting rotors (1, 2) fastened on the shafts, having the following features:
    - each of the rotors (1, 2) has a hollow bore (5),
    - each of the hollow bores (5) is at least partially penetrated by the associated shaft (3, 4),
    - the rotors (1, 2) are over-mounted at their discharge end by means of the shafts (3, 4), characterized in that for the purpose of a backlash-free fastening of the rotors (1, 2) on the shafts (3, 4) aluminium is used as rotor material and steel as shaft material, that between rotor (1, 2) and shaft (3, 4) an interference fit connection is produced by temperature application and that the ambient temperature, at which said interference fit connection is produced, corresponds approximately to the maximum temperature of the rotors (1, 2) that arises during operation of the screw-type vacuum pump.
EP01960473A 2000-08-10 2001-07-06 Two-shaft vacuum pump Expired - Lifetime EP1307657B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10039006 2000-08-10
DE10039006A DE10039006A1 (en) 2000-08-10 2000-08-10 Two-shaft vacuum pump
PCT/EP2001/007739 WO2002012726A1 (en) 2000-08-10 2001-07-06 Two-shaft vacuum pump

Publications (2)

Publication Number Publication Date
EP1307657A1 EP1307657A1 (en) 2003-05-07
EP1307657B1 true EP1307657B1 (en) 2007-12-12

Family

ID=7651941

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01960473A Expired - Lifetime EP1307657B1 (en) 2000-08-10 2001-07-06 Two-shaft vacuum pump

Country Status (9)

Country Link
US (1) US6863511B2 (en)
EP (1) EP1307657B1 (en)
JP (1) JP4944347B2 (en)
KR (1) KR100948988B1 (en)
CN (1) CN1273741C (en)
AU (1) AU2001281962A1 (en)
DE (2) DE10039006A1 (en)
TW (1) TW538199B (en)
WO (1) WO2002012726A1 (en)

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US20040091380A1 (en) 2004-05-13
CN1273741C (en) 2006-09-06
DE50113380D1 (en) 2008-01-24
JP4944347B2 (en) 2012-05-30
JP2004506140A (en) 2004-02-26
US6863511B2 (en) 2005-03-08
EP1307657A1 (en) 2003-05-07
KR20030027009A (en) 2003-04-03
CN1446291A (en) 2003-10-01
KR100948988B1 (en) 2010-03-23
AU2001281962A1 (en) 2002-02-18
WO2002012726A1 (en) 2002-02-14
TW538199B (en) 2003-06-21
DE10039006A1 (en) 2002-02-21

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