EP0459112B1 - Rotary vane vacuum pump - Google Patents

Rotary vane vacuum pump Download PDF

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Publication number
EP0459112B1
EP0459112B1 EP91105560A EP91105560A EP0459112B1 EP 0459112 B1 EP0459112 B1 EP 0459112B1 EP 91105560 A EP91105560 A EP 91105560A EP 91105560 A EP91105560 A EP 91105560A EP 0459112 B1 EP0459112 B1 EP 0459112B1
Authority
EP
European Patent Office
Prior art keywords
shaft
rotor
coupling
shaft extension
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
EP91105560A
Other languages
German (de)
French (fr)
Other versions
EP0459112A1 (en
Inventor
Lutz Arndt
Peter Müller
Dieter Vorberg
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.)
Balzers und Leybold Deutschland Holding AG
Original Assignee
Leybold AG
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Filing date
Publication date
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Publication of EP0459112A1 publication Critical patent/EP0459112A1/en
Application granted granted Critical
Publication of EP0459112B1 publication Critical patent/EP0459112B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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
    • F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
    • F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/70—Interfitted members
    • Y10T403/7018—Interfitted members including separably interposed key
    • Y10T403/7021—Axially extending

Definitions

  • the invention relates to a rotary vane vacuum pump with a housing, with a rotor and with a drive motor coupled to the rotor, wherein both the rotor and the drive motor are each equipped with a shaft journal and both shaft journals are mounted in the area of their coupling in the housing.
  • connection of the drive motor to the rotor of a rotary vane vacuum pump and the oil sealing of the drive are usually realized with the help of a large number of components.
  • the coupling usually comprises two coupling halves and an elastomer element with feather keys and screw connections. Separate shields for the motor bearing and the rotor bearing as well as a clutch housing are provided. It is also necessary to equip the various shaft journals with shaft sealing rings. Shaft seal liners are usually used for this.
  • the individual components have to be manufactured separately, which is not only complex and therefore expensive, but can also lead to tolerance summations which impair the concentricity.
  • a rotary vane vacuum pump of the type mentioned is known.
  • the separately mounted motor shaft journal is equipped with a liner that is slidably mounted in a hole in the clutch housing.
  • the bushing is equipped with shaft sealing rings, between which there is a lubricant chamber.
  • the liner is connected to the bearing journal of the rotor via a pin coupling has an enlarged diameter.
  • runout deviations occur, which necessitates a soft mounting of the pin of the pin coupling in at least one of the parts to be coupled together. This further increases the cost of manufacture. Difficulties also arise with the lubrication of the rotor bearing journal.
  • the present invention has for its object to make the connection between the drive motor and the pump rotor much simpler and cheaper.
  • this object is achieved in that the drive-side shaft journal of the rotor has the same diameter as the shaft journal of the drive motor, that the shaft journal of the rotor and the shaft journal of the drive motor are jointly mounted directly in a bearing bore, that two form a lubricant chamber for sealing the bearing bore Shaft sealing rings are provided, one of which is assigned to the rotor shaft journal and the other to the motor shaft journal, and that the rotor shaft journal and motor shaft journal are coupled to one another on the end face.
  • a separate end plate with a bearing for the motor is no longer required in the area of the coupling.
  • the problem related to the lubrication of the rotor bearing no longer exists.
  • the sealing ring assigned to the rotor shaft journal is located in immediate vicinity of the rotor or scoop chamber itself, so that there is no difficulty in operating the lubricant chamber between the sealing rings with full lubrication and the immediately adjacent scoop chamber with insufficient lubrication.
  • the invention therefore even makes it possible to arrange the high-vacuum stage, operated with very little oil, of a two-stage vacuum pump directly next to the clutch and bearing area, which is operated with full lubrication.
  • FIGS. 1 and 2 show sections through a rotary vane vacuum pump designed according to the invention.
  • the two-stage vacuum pump 1 shown in the figures as an exemplary embodiment comprises the actual pump housing 2, the oil box 3 surrounding the pump housing, the drive motor 4 and the outer housing or the hood 5.
  • the pump housing 2 and the drive motor 4 are fastened to a shield, which is supported on the floor by a base plate 7.
  • Part of the pump housing 2 is the one-piece pump ring 8, the opening of which has three areas 11, 12, 13 with different designs.
  • the rotor system 14 Inside the pump ring 8 is the rotor system 14, which is also made in one piece, with the sections 14a, 14b, and 14c.
  • the two outer sections 14a and 14c are equipped with slide slots 15, 16 accessible from the end faces and form the anchors of the high vacuum or fore vacuum stage.
  • the length and diameter of the middle section 14b of the rotor system 14 correspond to the middle area 12 of the opening of the pump ring 8 in such a way that this area has the function of a sliding bearing for the rotor system 14.
  • the slide of the HV stage is designated by 18.
  • the area 11 of the pump ring 8 forms together with the front panel 19, the scoop 21 of the fore-vacuum (VV) stage.
  • the slide of the VV stage is designated 22.
  • the inlet channel of the HV stage is designated 23.
  • the channel leading from the outlet of the HV stage to the inlet of the VV stage is only shown in FIG. 2 and designated by 24.
  • the outlet valve 26 is assigned to the outlet channel 25 (FIG. 2) of the VV stage.
  • the outlet valve 26 is designed as a check valve and takes over the vacuum protection of the recipient in the event of a pump failure.
  • the valve 26 is arranged in the upper region of the pump housing 2. It is located at the bottom of a depression 27 which forms an oil sump during the operation of the vacuum pump.
  • the inlet port 31 of the vacuum pump shown is attached to the intermediate plate 6. It is connected to the inlet duct 23 of the HV stage via a bore 32 in the shield 6.
  • the outlet connector 33 is also provided on the shield 6. It communicates with the interior of the oil box 3 via a bore corresponding to the bore 32.
  • a dome 35 arranged on the front side of the oil box. Its central section 36 is transparent and serves to check the oil level in the oil box 3.
  • the dome 35 has an approximately semicircular cross section, the broad side of which faces the oil box 3. It extends over the entire height of the oil box 3 so that it can be equipped with the oil fill opening 37 and the oil drain opening 38.
  • the motor 4 is equipped with a blower 41 on its free end face.
  • the cooling air flow generated by this fan serves not only to cool the engine, but also to cool the oil box 3.
  • Both the motor housing and the oil box 3 are equipped with axially or horizontally running cooling fins 42 and 43, respectively.
  • the intermediate plate 6 also has the function of a clutch housing. It is provided with a bearing bore 51 in which a rotor shaft journal 52 arranged on the rotor system 14 and the shaft journal 53 of the drive motor 4 protrude and are mounted there. With the aid of a pin coupling 54, the two shaft journals 52, 53 are coupled on the end face. Instead of the pin coupling, interlocking projections could also be provided in the area of the end faces of the shaft journals 52, 53. Both the rotor and the motor shaft journal can be slidably mounted in the bearing bore 51.
  • the pin or pins 54 of the pin coupling which extend in the axial direction and are arranged outside the axis of rotation, can be firmly embedded in their bores in the rotor shaft journal 52 while they engage in the bores of the motor shaft journal 53 with little play.
  • the motor shaft journal 53 can be mounted exclusively in the pins of the pin coupling in this solution.
  • Each of the shaft journals 52, 53 is assigned a shaft sealing ring 55, 56, the seat of which is also located in the clutch housing. These form a lubricant chamber 57, which contains the clutch and can be operated with full lubrication via the oil bore 58. Since the shaft seal ring 55 on the rotor side is in the immediate vicinity of the HV stage, the performance of this stage operated with insufficient lubrication is not impaired by lubricating oil.
  • the position of the oil bore 58 is shown in FIG. 2 by a dash-dotted line 59. It penetrates - preferably inclined - the pump housing 2 and cuts the lubricant chamber 57 to be supplied with oil above the shaft journals 52, 53 or the coupling 54.
  • An axial groove 60 is expediently provided in the bearing and coupling housing 6 in this area. Oil enters the lubricant chamber 57 through the bore 58. Excess oil continues to flow through the bore 58 and flows into the deeper one located oil sump. The lubricating oil can never flow completely out of the lubricant chamber 57, so that the bearing and clutch according to the invention have particularly good emergency running properties.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)

Description

Die Erfindung bezieht sich auf eine Drehschiebervakuumpumpe mit einem Gehäuse, mit einem Rotor und mit einem mit dem Rotor gekuppelten Antriebsmotor, wobei sowohl der Rotor als auch der Antriebsmotor jeweils mit einem Wellenzapfen ausgerüstet sind und beide Wellenzapfen im Bereich ihrer Kupplung im Gehäuse gelagert sind.The invention relates to a rotary vane vacuum pump with a housing, with a rotor and with a drive motor coupled to the rotor, wherein both the rotor and the drive motor are each equipped with a shaft journal and both shaft journals are mounted in the area of their coupling in the housing.

Die Verbindung des Antriebsmotor mit dem Rotor einer Drehschiebervakuumpumpe sowie die Ölabdichtung des Antriebes werden in der Regel mit Hilfe einer Vielzahl von Bauteilen realisiert. Üblicherweise umfaßt die Kupplung zwei Kupplungshälften sowie ein Elastomerelement mit Paßfedern und Verschraubungen. Separate Schilde für das Motorlager und das Rotorlager sowie ein Kupplungsgehäuse sind vorgesehen. Weiterhin ist es erforderlich, die verschiedenen Wellenzapfen mit Wellendichtringen auszurüsten. Dazu werden üblicherweise Wellendichtringlaufbuchsen verwendet. Die einzelnen Bauteile müssen jeweils separat hergestellt werden, was nicht nur aufwendig und deshalb kostspielig ist, sondern auch zu Toleranz-Summationen führen kann, die den Rundlauf beeinträchtigen.The connection of the drive motor to the rotor of a rotary vane vacuum pump and the oil sealing of the drive are usually realized with the help of a large number of components. The coupling usually comprises two coupling halves and an elastomer element with feather keys and screw connections. Separate shields for the motor bearing and the rotor bearing as well as a clutch housing are provided. It is also necessary to equip the various shaft journals with shaft sealing rings. Shaft seal liners are usually used for this. The individual components have to be manufactured separately, which is not only complex and therefore expensive, but can also lead to tolerance summations which impair the concentricity.

Aus der DE-OS 23 54 039 ist eine Drehschiebervakuumpumpe der eingangs genannten Art bekannt. Der gesondert gelagerte Motorwellenzapfen ist mit einer Laufbuchse ausgerüstet, die in einer Bohrung im Kupplungsgehäuse gleitend gelagert ist. Die Buchse ist mit Wellendichtringen ausgerüstet, zwischen denen sich ein Schmiermittelraum befindet. Stirnseitig ist die Laufbuchse über eine Stiftkupplung mit dem Lagerzapfen des Rotors verbunden, der einen vergrößerten Durchmesser hat. Erfahrungen mit der bekannten Pumpe haben gezeigt, daß Rundlaufabweichungen auftreten, die eine weiche Lagerung des Stiftes der Stiftkupplung in mindestens einem der miteinander zu kuppelnden Teile erforderlich macht. Dadurch wird die Herstellung weiter verteuert. Außerdem treten Schwierigkeiten bei der Schmiermittelversorgung des Rotor-Lagerzapfens auf. Der Grund dafür liegt in der unmittelbaren Nähe des Schöpfraumes des Rotors zu den mit Schmieröl zu versorgenden Flächen der Rotorlagerung. Da es wünschenswert ist, die Gleitlagerungen mit einer Vollschmierung auszurüsten, tritt ständig Schmieröl in den Schöpfraum der Pumpe und beeinträchtigt die Pumpleistung.From DE-OS 23 54 039 a rotary vane vacuum pump of the type mentioned is known. The separately mounted motor shaft journal is equipped with a liner that is slidably mounted in a hole in the clutch housing. The bushing is equipped with shaft sealing rings, between which there is a lubricant chamber. On the face side, the liner is connected to the bearing journal of the rotor via a pin coupling has an enlarged diameter. Experience with the known pump has shown that runout deviations occur, which necessitates a soft mounting of the pin of the pin coupling in at least one of the parts to be coupled together. This further increases the cost of manufacture. Difficulties also arise with the lubrication of the rotor bearing journal. The reason for this lies in the immediate vicinity of the rotor's scooping area to the surfaces of the rotor bearing that are to be supplied with lubricating oil. Since it is desirable to equip the plain bearings with full lubrication, lubricating oil constantly enters the pump's pumping chamber and impairs the pump performance.

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, die Verbindung zwischen dem Antriebsmotor und dem Pumpenrotor wesentlich einfacher und kostengünstiger zu gestalten.The present invention has for its object to make the connection between the drive motor and the pump rotor much simpler and cheaper.

Erfindungsgemäß wird diese Aufgabe dadurch gelöst, daß der antriebsseitige Wellenzapfen des Rotors den gleichen Durchmesser wie der Wellenzapfen des Antriebsmotors hat, daß der Wellenzapfen des Rotors und der Wellenzapfen des Antriebsmotors gemeinsam unmittelbar in einer Lagerbohrung gelagert sind, daß zur Abdichtung der Lagerbohrung zwei einen Schmiermittelraum bildende Wellendichtringe vorgesehen sind, von denen einer dem Rotorwellenzapfen und der andere dem Motorwellenzapfen zugeordnet ist, und daß Rotorwellenzapfen und Motorwellenzapfen stirnseitig miteinander gekuppelt sind. Durch diese Merkmale ist die Anzahl der für die Lagerung und Kupplung von Motor und Rotor notwendigen Bauteile auf ein Minimum reduziert, wodurch nicht nur die beabsichtigte Reduzierung der Herstellkosten, sondern auch noch eine Reduzierung der von der Pumpe abgegebenen Geräusche erreicht wird. Ein gesonderter Lagerschild mit Lager für den Motor ist im Bereich der Kupplung nicht mehr erforderlich. Das sich auf die Schmierung des Rotorlagers beziehende Problem besteht nicht mehr. Der dem Rotorwellenzapfen zugeordnete Dichtring befindet sich in unmittelbarer Nähe des Rotors bzw. Schöpfraumes selbst, so daß keinerlei Schwierigkeit besteht, den Schmiermittelraum zwischen den Dichtringen mit einer Vollschmierung und den unmittelbar benachbarten Schöpfraum mit einer Mangelschmierung zu betreiben. Durch die Erfindung ist es deshalb sogar möglich, die mit sehr wenig Öl betriebene Hochvakuum-Stufe einer zweistufigen Vakuumpumpe unmittelbar neben dem mit Vollschmierung betriebenen Kupplungs- und Lagerbereich anzuordnen.According to the invention, this object is achieved in that the drive-side shaft journal of the rotor has the same diameter as the shaft journal of the drive motor, that the shaft journal of the rotor and the shaft journal of the drive motor are jointly mounted directly in a bearing bore, that two form a lubricant chamber for sealing the bearing bore Shaft sealing rings are provided, one of which is assigned to the rotor shaft journal and the other to the motor shaft journal, and that the rotor shaft journal and motor shaft journal are coupled to one another on the end face. These features reduce the number of components required for the mounting and coupling of the motor and rotor to a minimum, which not only achieves the intended reduction in manufacturing costs but also a reduction in the noise emitted by the pump. A separate end plate with a bearing for the motor is no longer required in the area of the coupling. The problem related to the lubrication of the rotor bearing no longer exists. The sealing ring assigned to the rotor shaft journal is located in immediate vicinity of the rotor or scoop chamber itself, so that there is no difficulty in operating the lubricant chamber between the sealing rings with full lubrication and the immediately adjacent scoop chamber with insufficient lubrication. The invention therefore even makes it possible to arrange the high-vacuum stage, operated with very little oil, of a two-stage vacuum pump directly next to the clutch and bearing area, which is operated with full lubrication.

Weitere Vorteile und Einzelheiten der Erfindung sollen anhand der Figuren 1 und 2 erläutert werden, die Schnitte durch eine erfindungsgemäß gestaltete Drehschiebervakuumpumpe zeigen.Further advantages and details of the invention will be explained with reference to FIGS. 1 and 2, which show sections through a rotary vane vacuum pump designed according to the invention.

Die in den Figuren als Ausführungsbeispiel dargestellte, zweistufige Vakuumpumpe 1 umfaßt das eigentliche Pumpengehäuse 2, den das Pumpengehäuse umgebenden Ölkasten 3, den Antriebsmotor 4 und das äußere Gehäuse bzw. die Haube 5. Das Pumpengehäuse 2 und der Antriebsmotor 4 sind an einem Schild befestigt, der sich über eine Grundplatte 7 auf dem Boden abstützt.The two-stage vacuum pump 1 shown in the figures as an exemplary embodiment comprises the actual pump housing 2, the oil box 3 surrounding the pump housing, the drive motor 4 and the outer housing or the hood 5. The pump housing 2 and the drive motor 4 are fastened to a shield, which is supported on the floor by a base plate 7.

Bestandteil des Pumpengehäuses 2 ist der einstückig ausgebildete Pumpenring 8, dessen Öffnung drei Bereiche 11, 12, 13 mit unterschiedlicher Gestaltung aufweist. Innerhalb des Pumpenringes 8 befindet sich das ebenfalls einstückig ausgebildete Rotorensystem 14, mit den Abschnitten 14a, 14b, und 14c. Die beiden äußeren Abschnitte 14a und 14c sind mit von den Stirnseiten her zugänglichen Schieberschlitzen 15, 16 ausgerüstet und bilden die Anker der Hochvakuum- bzw. Vorvakuumstufe.Part of the pump housing 2 is the one-piece pump ring 8, the opening of which has three areas 11, 12, 13 with different designs. Inside the pump ring 8 is the rotor system 14, which is also made in one piece, with the sections 14a, 14b, and 14c. The two outer sections 14a and 14c are equipped with slide slots 15, 16 accessible from the end faces and form the anchors of the high vacuum or fore vacuum stage.

Der mittlere Abschnitt 14b des Rotorensystems 14 entspricht in seiner Länge und seinem Durchmesser derart dem mittleren Bereich 12 der Öffnung des Pumpenringes 8, daß dieser Bereich die Funktion einer Gleitlagerung für das Rotorensystem 14 hat. Der gegenüber dem Bereich 12 vergrößerte Bereich 13 des Pumpenringes 8 bildet gemeinsam mit dem Schild 6 den Schöpfraum 17 der Hochvakuum( HV)-Stufe der Pumpe 1. Der Schieber der HV-Stufe ist mit 18 bezeichnet. Der Bereich 11 des Pumpenringes 8 bildet gemeinsam mit der Frontplatte 19 den Schöpfraum 21 der Vorvakuum(VV)-Stufe. Der Schieber der VV-Stufe ist mit 22 bezeichnet.The length and diameter of the middle section 14b of the rotor system 14 correspond to the middle area 12 of the opening of the pump ring 8 in such a way that this area has the function of a sliding bearing for the rotor system 14. The area 13 of the pump ring 8, which is enlarged compared to the area 12, forms, together with the shield 6, the scooping space 17 of the high vacuum (HV) stage of the pump 1. The slide of the HV stage is designated by 18. The area 11 of the pump ring 8 forms together with the front panel 19, the scoop 21 of the fore-vacuum (VV) stage. The slide of the VV stage is designated 22.

Der Einlaßkanal der HV-Stufe ist mit 23 bezeichnet. Der vom Auslaß der HV-Stufe zum Einlaß der VV-Stufe führende Kanal ist nur in Figur 2 eingezeichnet und mit 24 bezeichnet. Dem Auslaßkanal 25 (Figur 2) der VV-Stufe ist das Auslaßventil 26 zugeordnet. Das Auslaßventil 26 ist als Rückschlagventil ausgebildet und übernimmt die Vakuumsicherung des Rezipienten bei Ausfall der Pumpe. Das Ventil 26 ist im oberen Bereich des Pumpengehäuses 2 angeordnet. Es befindet sich am Boden einer Vertiefung 27, die während des Betriebs der Vakuumpumpe einen Ölzwischensumpf bildet.The inlet channel of the HV stage is designated 23. The channel leading from the outlet of the HV stage to the inlet of the VV stage is only shown in FIG. 2 and designated by 24. The outlet valve 26 is assigned to the outlet channel 25 (FIG. 2) of the VV stage. The outlet valve 26 is designed as a check valve and takes over the vacuum protection of the recipient in the event of a pump failure. The valve 26 is arranged in the upper region of the pump housing 2. It is located at the bottom of a depression 27 which forms an oil sump during the operation of the vacuum pump.

Der Einlaßstutzen 31 der dargestellten Vakuumpumpe ist am Zwischenschild 6 befestigt. Über eine Bohrung 32 im Schild 6 ist er an den Eintrittskanal 23 der HV-Stufe angeschlossen. Auch der Auslaßstutzen 33 ist am Schild 6 vorgesehen. Über eine der Bohrung 32 entsprechende Bohrung steht er mit dem Innenraum des Ölkastens 3 in Verbindung.The inlet port 31 of the vacuum pump shown is attached to the intermediate plate 6. It is connected to the inlet duct 23 of the HV stage via a bore 32 in the shield 6. The outlet connector 33 is also provided on the shield 6. It communicates with the interior of the oil box 3 via a bore corresponding to the bore 32.

Bestandteil des Ölkastens 3 ist noch ein stirnseitig am Ölkasten angeordneter Dom 35. Sein mittlerer Abschnitt 36 ist durchsichtig und dient der Kontrolle des Ölstandes im Ölkasten 3. Der Dom 35 hat einen etwa halbrunden Querschnitt, dessen Breitseite dem Ölkasten 3 zugewandt ist. Er erstreckt sich über die gesamte Höhe des Ölkastens 3, so daß er mit der Öleinfüllöffnung 37 und der Ölablaßöffnung 38 ausgerüstet werden kann.Another component of the oil box 3 is a dome 35 arranged on the front side of the oil box. Its central section 36 is transparent and serves to check the oil level in the oil box 3. The dome 35 has an approximately semicircular cross section, the broad side of which faces the oil box 3. It extends over the entire height of the oil box 3 so that it can be equipped with the oil fill opening 37 and the oil drain opening 38.

Der Motor 4 ist auf seiner freien Stirnseite mit einem Gebläse 41 ausgerüstet. Der von diesem Gebläse erzeugte Kühlluftstrom dient nicht nur der Kühlung des Motors, sondern auch der Kühlung des Ölkastens 3. Sowohl das Motorgehäuse als auch der Ölkasten 3 sind mit axial bzw. horizontal verlaufenden Kühlrippen 42 bzw. 43 ausgerüstet.The motor 4 is equipped with a blower 41 on its free end face. The cooling air flow generated by this fan serves not only to cool the engine, but also to cool the oil box 3. Both the motor housing and the oil box 3 are equipped with axially or horizontally running cooling fins 42 and 43, respectively.

Der Zwischenschild 6 hat außerdem noch die Funktion eines Kupplungsgehäuses. Er ist mit einer Lagerbohrung 51 versehen, in die ein am Rotorsystem 14 angeordneter Rotorwellenzapfen 52 und der Wellenzapfen 53 des Antriebsmotors 4 hineinragen und dort gelagert sind. Mit Hilfe einer Stiftkupplung 54 sind die beiden Wellenzapfen 52, 53 stirnseitig gekuppelt. Anstelle der Stiftkupplung könnten auch ineinandergreifende Vorsprünge im Bereich der Stirnseiten der Wellenzapfen 52, 53 vorgesehen sein. Sowohl der Rotor- als auch der Motor-Wellenzapfen können in der Lagerbohrung 51 gleitend gelagert sein. Es besteht aber auch die Möglichkeit, nur einen der beiden Wellenzapfen - vorzugsweise den Rotorwellenzapfen 52 - in der Lagerbohrung 51 gleitend zu lagern und den jeweils anderen Wellenzapfen - vorzugsweise den Motorwellenzapfen 53 - in den Kupplungselementen zu lagern. Beispielsweise können der oder die sich in axialer Richtung erstreckenden, außerhalb der Drehachse angeordneten Stifte 54 der Stiftkupplung in ihren Bohrungen im Rotorwellenzapfen 52 fest eingelassen sein, während sie in die Bohrungen des Motorwellenzapfens 53 mit geringem Spiel eingreifen. Bei in der Lagerbohrung 51 gleitend gelagertem Rotorwellenzapfen 52 kann bei dieser Lösung der Motorwellenzapfen 53 ausschließlich in den Stiften der Stiftkupplung gelagert sein.The intermediate plate 6 also has the function of a clutch housing. It is provided with a bearing bore 51 in which a rotor shaft journal 52 arranged on the rotor system 14 and the shaft journal 53 of the drive motor 4 protrude and are mounted there. With the aid of a pin coupling 54, the two shaft journals 52, 53 are coupled on the end face. Instead of the pin coupling, interlocking projections could also be provided in the area of the end faces of the shaft journals 52, 53. Both the rotor and the motor shaft journal can be slidably mounted in the bearing bore 51. However, there is also the possibility of slidingly mounting only one of the two shaft journals - preferably the rotor shaft journal 52 - in the bearing bore 51 and the other shaft journal - preferably the motor shaft journal 53 - in the coupling elements. For example, the pin or pins 54 of the pin coupling, which extend in the axial direction and are arranged outside the axis of rotation, can be firmly embedded in their bores in the rotor shaft journal 52 while they engage in the bores of the motor shaft journal 53 with little play. With the rotor shaft journal 52 slidably mounted in the bearing bore 51, the motor shaft journal 53 can be mounted exclusively in the pins of the pin coupling in this solution.

Jedem der Wellenzapfen 52, 53 ist ein Wellendichtring 55, 56 zugeordnet, deren Sitz sich ebenfalls im Kupplungsgehäuse befindet. Diese bilden einen Schmiermittelraum 57, der die Kupplung enthält und über die Öl-Bohrung 58 mit Vollschmierung betrieben werden kann. Da sich der rotorseitige Wellendichtring 55 in unmittelbarer Nähe der HV-Stufe befindet, ist die Leistungsfähigkeit dieser mit Mangelschmierung betriebenen Stufe durch Schmieröl nicht beeinträchtigt.Each of the shaft journals 52, 53 is assigned a shaft sealing ring 55, 56, the seat of which is also located in the clutch housing. These form a lubricant chamber 57, which contains the clutch and can be operated with full lubrication via the oil bore 58. Since the shaft seal ring 55 on the rotor side is in the immediate vicinity of the HV stage, the performance of this stage operated with insufficient lubrication is not impaired by lubricating oil.

Die Lage der Ölbohrung 58 ist in Figur 2 durch eine strichpunktierte Linie 59 dargstellt. Sie durchsetzt - vorzugsweise geneigt - das Pumpengehäuse 2 und schneidet den mit Öl zu versorgenden Schmiermittelraum 57 oberhalb der Wellenzapfen 52, 53 bzw. der Kupplung 54. Zweckmäßig ist in diesem Bereich noch eine Axialnut 60 im Lager- und Kupplungsgehäuse 6 vorgesehen. Durch die Bohrung 58 gelangt Öl in den Schmiermittelraum 57. Überschüssiges Öl strömt weiter durch die Bohrung 58 und fließt in den tiefer gelegenen Ölsumpf ab. Aus dem Schmiermittelraum 57 kann das Schmieröl niemals völlig abfließen, so daß die erfindungsgemäße Lagerung und Kupplung besonders gute Notlaufeigenschaften hat.The position of the oil bore 58 is shown in FIG. 2 by a dash-dotted line 59. It penetrates - preferably inclined - the pump housing 2 and cuts the lubricant chamber 57 to be supplied with oil above the shaft journals 52, 53 or the coupling 54. An axial groove 60 is expediently provided in the bearing and coupling housing 6 in this area. Oil enters the lubricant chamber 57 through the bore 58. Excess oil continues to flow through the bore 58 and flows into the deeper one located oil sump. The lubricating oil can never flow completely out of the lubricant chamber 57, so that the bearing and clutch according to the invention have particularly good emergency running properties.

Claims (7)

  1. Rotary vane vacuum pump (1) having a housing (2), having a rotor (14) and having a drive motor (4) coupled to the rotor, both the rotor and the drive motor each being fitted with a shaft extension (52, 53) and the two shaft extensions being supported in the region of their coupling in the housing, characterized in that the drive-side shaft extension (52) of the rotor (14) has the same diameter as the shaft extension (53) of the drive motor (4), that the two shaft extensions (52, 53) are jointly supported directly in a bearing bore (51), that for sealing off the bearing bore (51) two rotary shaft seals (55, 56) forming a lubricant chamber (57) are provided, one of which rotary shaft seals is associated with the rotor shaft extension (52) and the other is associated with the motor shaft extension (53), and that the two shaft extensions (52, 53) are coupled end to end with one another.
  2. Pump according to claim 1, characterized in that an intermediate guard plate (6) forms the joint bearing and coupling housing.
  3. Pump according to claim 1 or 2, characterized in that the lubricant chamber (57) is in communication with an oil bore (58) extending above the shaft extensions (52, 53).
  4. Pump according to claim 3, characterized in that the bearing and coupling housing (6) is provided above the shaft extensions (52, 53) with an axial groove (60) and that the bore (58) cuts the axial groove (60).
  5. Pump according to one of claims 1 to 4, characterized in that the coupling (54) takes the form of a pin coupling.
  6. Pump according to one of the preceding claims, characterized in that one of the two shaft extensions (52, 53) - preferably the rotor shaft extension (52) - is slidingly supported in the bearing bore (51) and that the other shaft extension - preferably the motor shaft extension (53) - is supported in the coupling elements.
  7. Pump according to claims 5 and 6, characterized in that the pin or pins (54) of the pin coupling are embedded in a fixed manner in their bores in the rotor shaft extension (52) and that the pin or pins (54) engage with play into the corresponding bores in the motor shaft extension (53).
EP91105560A 1990-05-29 1991-04-09 Rotary vane vacuum pump Expired - Lifetime EP0459112B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4017194A DE4017194A1 (en) 1990-05-29 1990-05-29 ROTARY VALVE VACUUM PUMP
DE4017194 1990-05-29

Publications (2)

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EP0459112A1 EP0459112A1 (en) 1991-12-04
EP0459112B1 true EP0459112B1 (en) 1994-05-18

Family

ID=6407369

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Application Number Title Priority Date Filing Date
EP91105560A Expired - Lifetime EP0459112B1 (en) 1990-05-29 1991-04-09 Rotary vane vacuum pump

Country Status (4)

Country Link
US (1) US5156532A (en)
EP (1) EP0459112B1 (en)
JP (1) JPH04231697A (en)
DE (3) DE4017194A1 (en)

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WO2018161472A1 (en) * 2017-03-07 2018-09-13 北京艾岗科技有限公司 Self-circulation lubricating cooling system of vertical vacuum pump

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CN101552507B (en) * 2009-05-14 2011-05-04 北京化工大学 Motor shaft split rotary seal device
WO2018161472A1 (en) * 2017-03-07 2018-09-13 北京艾岗科技有限公司 Self-circulation lubricating cooling system of vertical vacuum pump

Also Published As

Publication number Publication date
EP0459112A1 (en) 1991-12-04
US5156532A (en) 1992-10-20
DE59101642D1 (en) 1994-06-23
JPH04231697A (en) 1992-08-20
DE4017194A1 (en) 1991-12-05
DE9007544U1 (en) 1992-08-13

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