EP2662570B1 - Vacuum pump - Google Patents

Vacuum pump Download PDF

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Publication number
EP2662570B1
EP2662570B1 EP13002418.5A EP13002418A EP2662570B1 EP 2662570 B1 EP2662570 B1 EP 2662570B1 EP 13002418 A EP13002418 A EP 13002418A EP 2662570 B1 EP2662570 B1 EP 2662570B1
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EP
European Patent Office
Prior art keywords
drive shaft
orbiter
working chamber
vacuum pump
drive
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Not-in-force
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EP13002418.5A
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German (de)
French (fr)
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EP2662570A1 (en
Inventor
Franz Pawellek
Conrad Nickel
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Nidec GPM GmbH
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Nidec GPM GmbH
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Publication of EP2662570A1 publication Critical patent/EP2662570A1/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
    • 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
    • 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
    • F04C18/32—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/332—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and 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
    • 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
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement

Definitions

  • the invention relates to a vacuum pump with a cylindrical working chamber in which between a suction port and an outflow opening a slider is arranged, which slides in a guide slot of an eccentric rotary piston.
  • This solution has, with increasing volumetric efficiency, ie with the necessary increasing sealing of the working gap, between the inner wall of the cylindrical working chamber and the outer circumference of the piston drum sliding along this inner wall, by the required increase in the pressure between the piston drum and the inner wall of the cylindrical working chamber, a decreasing with increasing volumetric efficiency mechanical efficiency.
  • the reason for this is that with increasing contact pressure also increases the friction losses between the circulating in the cylindrical working chamber piston drum and the inner wall of the cylindrical working chamber.
  • FR 1 346 509 is another known as a vacuum pump using rotary piston pump with an eccentrically mounted, rotating in a working chamber rotary pistons whose provided with a pendulum head slider with the pendulum head in a arranged in the inner wall of the working chamber, between the suction port and the outflow bearing groove is mounted so oscillating, that this slider "immersed” during the orbital movement of the rotary piston with its pendulum shaft in a radially arranged in the rotary piston, formed by guide webs guide slot.
  • this solution has the disadvantage that with increasing sealing, ie with increasing contact pressure between the inner wall of the cylindrical working chamber and sliding along this inner wall along the outer periphery of the Exzenterfelkolbens, the friction losses between the circulating in the cylindrical working chamber piston drum and the inner wall of the cylindrical working chamber increase, so even in this in the DE 10 2006 016 791 B4 as well as in the WO 2009/021474 A1 solution presented worsens with increasing volumetric efficiency of mechanical efficiency.
  • the object of the invention is now a working by means of an eccentric orbital vacuum pump with a cylindrical working chamber in which between a suction port and an outflow opening a slide is arranged, which slides in a guide slot of an eccentric rotary, to develop the aforementioned disadvantages of the prior art does not have, in particular at high volumetric efficiency characterized by a very high mechanical efficiency, also achieved in a single-stage compression a high vacuum, it is simple and robust, with minimal material use manufacturing technology is easy to manufacture and assemble, at the same time the manufacturing and maintenance costs significantly lowers, the tightness between the Exzenterfelkolben and the inner wall of the cylindrical working chamber substantially increased, minimizing the wear of the assemblies, even at very high speeds, ie In the case of direct drive via the crankshaft, a high level of reliability, with a long service life and low susceptibility to soiling, is guaranteed, and in addition, in special designs, pump speeds which also vary with respect to the engine-side drive speed. Eccentric piston speeds, able to realize.
  • FIG. 1 shows the vacuum pump according to the invention in a partial section, with a pump housing 1, a drive shaft 2, arranged in the pump housing 1 working chamber 3 with a cylindrical inner wall 4, connected to the drive shaft 2, eccentrically arranged bearing pin 5, a rotatably mounted on the bearing pin 5, in the working chamber 3 rotating piston drum, the orbiter 6, with a cylinder jacket 7, a arranged in Orbiter 6 guide slot 8, and arranged in the working chamber 3 suction port 9 and arranged in the working chamber 3 outflow opening 10, with a between the suction port 9 and the outflow opening 10 arranged locking slide 11 which is slidably mounted in the guide slot 8 of the orbiter 6, with a pivotally mounted in the pump housing 1 locking slide 11, and arranged in a central orbiter 6 guide web 13 in which provided with oil pockets 14 guide slot 8 is.
  • an oil-lubricated design is arranged in the working chamber 3 as lubricant oil, and that in this embodiment between the cylindrical inner wall 4 of the working chamber 3 and the cylinder jacket 7 of the orbiter 6, a working gap 12 of approx 0.4 mm is arranged, which is completely closed during circulation of the orbiter 6 in the working chamber 3 with the lubricant oil used in oil-lubricated series.
  • the working gap 12 in the range of 0.05 mm to 0.8 mm.
  • the arrangement according to the invention surprisingly causes, during the circulation of the cylindrical orbiter 6 in the oil-lubricated cylindrical working chamber 3 between the cylinder jacket 7 of the rotating orbiter 6 and the cylindrical inner wall 4 of the working chamber 3, a working gap 12 reliably sealing oil wedge builds on the orbiter 6 "floating up" during its circulation in the working chamber 3.
  • FIG. 1 illustrated embodiment of the solution according to the invention also characterized in that in the guide of the locking slide 11, here in the guide bar 13, oil pockets 14 are arranged, which ensure a smooth, wear-minimized and reliable working stroke of the locking slide 11 in the guide slot 8.
  • the arrangement of the invention is simple and robust, characterized by a minimal use of material, at the same time significantly reduces the required manufacturing accuracy, therefore, manufacturing technology is easy to produce and also easy to install, and thus allows that compared to the previous solution to the DE 10 2006 016 791 B4 with increased tightness, between the orbiter 6 and the inner wall 4 of the cylindrical working chamber 3, the manufacturing cost, significantly reduced, but also the wear, due to the reduction of friction as well as the reduction of soil susceptibility due to the working gap of the invention can be minimized.
  • the solution according to the invention in conjunction with the marked reduction in susceptibility to soiling, also causes, by means of the present solution, even at very high speeds, i. With direct drive via the crankshaft, a high level of reliability can be ensured with a long service life, so that the maintenance effort in this area of use also drops significantly.
  • the Figure 2 A shows the vacuum pump according to the invention with a pivotally mounted in the pump housing 1 locking slide 11, a centrally arranged in Orbiter 6 guide web 13, arranged in Orbiter 6 support plate 15 and a non-rotatably connected to the drive shaft 2 eccentric disc 16 in an exploded view.
  • FIG. 2B is the vacuum pump according to the invention, according to the FIG. 2 A shown in a partial section.
  • FIG. 2C The side view of the vacuum pump according to the invention according to the FIGS. 2 A and 2 B is in the FIG. 2C shown in section.
  • Such a support plate 15 causes a higher stability of the orbiter 6, so that such support disks 15 both to reduce the wall thicknesses of the orbiter 6, or if necessary, to increase the stability of the orbiter 6, for example when using the vacuum pump according to the invention at high speeds, ie at speeds up to the range of 8,000 rpm, in order to avoid elastic deformations of the orbiter 6 even in this speed range and to ensure optimal functioning of the vacuum pump according to the invention.
  • This design of an eccentric disc 16 with bearing pin 5 is particularly appropriate when the shaft diameter of the drive shaft 2 for the arrangement of the bearing pin 5 is not sufficient to achieve the necessary for the vacuum pump to be used eccentricity.
  • the Figure 3 A shows the vacuum pump according to the invention with a pivotally mounted in the pump housing 1 locking slide 11, a centrally arranged in the orbiter 6 guide web 13, with a plurality of orbiter according to the invention arranged support webs 17 with a direct connection of the bearing pin 5 to the cylinder head 18 mounted in the drive shaft 2, here the camshaft , in a partial section.
  • FIG. 3B is the vacuum pump according to the invention according to the Figure 3 A shown in the side view.
  • FIGS. 3A and 2 B illustrated embodiment of the solution according to the invention is also characterized in that in the interior of the orbiter 6, alternatively to that in connection with the Figures 2 A . 2 B , and 2C explained supporting disk 15, supporting webs 17 are arranged.
  • support webs 17 causes a higher stability of the orbiter 6, so that the support webs 17 can be used both to reduce the wall thicknesses of the orbiter 6, as well as to reduce the elastic deformations, or to increase the stability of the orbiter 6.
  • the Figure 4 A shows the vacuum pump according to the invention with a pivotally mounted in the pump housing 1 locking slide 11, a centrally arranged in the orbiter 6 guide web 13, with a plurality arranged in the orbiter 6 support webs 17 and the inventive connection of the bearing pin 5 via an adapter 19 to the stored in the cylinder head 16 Drive shaft 2, here the camshaft, in a partial section.
  • FIG. 4B shows the vacuum pump according to the invention according to the Figure 4 A in the side view in section.
  • This adapter 19 is arranged in connection with a transitional fit the front side in the drive shaft 2 and according to the invention designed as a plug-in solution to avoid the required force in the previous embodiment, for pressing the bearing pin 5 in the cylinder head 18 mounted in the drive shaft 2 to avoid.
  • FIGS. 5 A and 5 B show a further of the possible embodiments of the solution according to the invention.
  • the Figure 5 A shows the vacuum pump according to the invention in the design of a tandem pump with the bearing pin 5 receiving eccentric disk 16 in plan view.
  • Characteristic of this design is that the eccentric disc 16 is rotatably mounted on the drive shaft 2 and between the drive shaft 2 and the bearing pin 5 bearing eccentric disc 16, for transmitting a defined drive torque, a slip clutch 20, in the design shown here, a tolerance ring arranged is.
  • This design of the solution according to the invention allows the inclusion of larger tolerances in the production of passing in operative connection shaft hub connection, at the same time ensures the compensation of thermal expansion, but also allows easy and quick installation, at the same time decouples the transmission of vibrations occurring and also ensures a limitation of torque transmission.
  • This design of the solution according to the invention is also particularly advantageous when the vacuum pump of the respective motor vehicle, from Space reasons, or else had to be arranged for noise reduction in the oil pan, and there at engine standstill with oil "full” can run.
  • the integrated friction clutch 20 guarantees a “slow”, component-preserving and systematic oil-discharging start-up of the vacuum pump, even under the extreme operating conditions of a vacuum pump "fully” running when the engine is at a standstill.
  • FIG. 6 is another of the possible embodiments of the solution according to the invention in plan view, shown in section.
  • FIG. 6 shows the vacuum pump according to the invention in the design of a tandem pump with an inventively by means of a sliding bearing 24 rotatably mounted on the drive shaft 2 arranged eccentric disk 16 with the bearing pin 5, and one next to the sliding bearing 24 between the drive shaft 2 and the eccentric disk 16 arranged overrunning clutch 21, wherein the so mounted on the drive shaft 2 eccentric 16 an electric drive 22 acts whose rotor is rigidly connected to the eccentric disc 16, and whose stator is rigidly connected to the pump housing 1.
  • a drive wheel 23 e.g. a sprocket, or a pulley arranged.
  • FIG. 6 illustrated design of the vacuum pump according to the invention allows the drive of the vacuum pump on the one hand by means of the rotatably connected to the drive shaft 2 drive wheel 23, and on the other hand, in "stationary or too slow-running" drive shaft 2, solely by means of the electric drive 22nd
  • FIG. 7 is another of the possible embodiments of the solution according to the invention in plan view, shown in section.
  • FIG. 7 illustrated vacuum pump according to the invention in the form of a tandem pump with a drive wheel 23, characterized inter alia by a non-rotatably connected to the drive shaft 2 eccentric disc 16 with a bearing pin 5, a separately adjacent to the eccentric disc 16 on the drive shaft 2 rotatably mounted inner ring of a passing freewheel 21, a acting on the associated outer ring of the overrunning clutch 21 electric drive 22 whose rotor is rigidly connected to the outer ring of the overrunning clutch 21 and whose stator is rigidly connected to the pump housing 1 from.
  • a drive wheel 23 e.g. a sprocket, or a pulley arranged.
  • Characteristic of this design is that between the drive shaft 2 and the drive wheel 23, a further overrunning clutch 21 is arranged.
  • FIG. 7 illustrated design thus allows the drive of the entire tandem pump on the one hand on the drive wheel 23, but on the other hand in "stationary" drive wheel 23 and the electric drive 22, for example, at start / stop operation of the engine.
  • FIGS. 8A and 8B Yet another of the possible embodiments of the solution according to the invention is shown.
  • FIG. 8A shows the vacuum pump according to the invention with a pivotally mounted in the pump housing 1 locking slide 11, a decentralized arranged in the Orbiter 6 guide web 13, guided through the pump housing 1 through drive shaft 2 with a arranged in the orbiter 6 supporting disk 15 in a sectional view.
  • FIG. 8B shows this vacuum pump according to the invention from the FIG. 8A in the side view in section.
  • This design for a by the vacuum pump "passed" drive shaft 2 is characteristic, allows the transmission of higher drive torque, the drive of another, the vacuum pump adjacent unit, z. B. a further pump, but also at the same time a, connected to the decentralized management of the locking slide, significant reduction of the required space of the vacuum pump.
  • FIGS. 9A and 9B show yet another of the possible embodiments of the inventive solution.
  • FIG. 9A the vacuum pump according to the invention in the form of a tandem pump with a pivotally mounted in the pump housing 1 locking slide 11 is shown in section.
  • the pivotally mounted in the pump housing 1 locking slide 11 is slidably mounted in a decentralized arranged in the orbiter 6 guide web 13.
  • a plurality of support webs 17 are arranged in the orbiter 6 next to the guide web 13 in this inventive design.
  • eccentric disc 16 is arranged in the eccentric one the orbiter 6 on both sides superior bearing pin 5 is fixed, on the opposite side of the orbiter 6, on which the orbiter 6 there superior bearing pin 9, a second eccentric disc 16 is arranged.
  • FIG. 9B shows the vacuum pump according to the invention from the FIG. 9A in a plan view in a sectional view. Due to the drive shaft 2 "passed" through the vacuum pump, this design also makes it possible to drive a further unit adjacent to the vacuum pump, for example a third pump.
  • FIG. 10 now shows a comparison of the characteristics of different types of currently used in motor vehicles, comparable in the chamber volume vacuum pumps.
  • the power consumption P of the respective vacuum pump is plotted in watts above the associated pump speed n in rpm.
  • the characteristic I describes the power consumption of the vacuum pump according to the invention presented here.
  • the characteristic II describes the power consumption of a piston pump used as a vacuum pump.
  • the characteristic III describes the power consumption of a monoerielpumpe with a plastic wing
  • the characteristic IV the power consumption of a Monoerielpumpe with a steel wing.
  • the vacuum pump according to the invention is as intended for use in the high speed range, i. Also suitable for direct drive via the crankshaft with up to more than 7000 rpm, optimally suited.
  • FIG. 11 shows in a comparison of the power consumption of a monoerielpumpe with plastic wing, characteristic III, and the power consumption of the vacuum pump according to the invention, characteristic I (with comparable working chamber sizes).
  • the drive speed was continuously increased to over 6,000 rpm and as a result the power consumption of the monoerielpumpe with plastic wing, as a characteristic III, the power consumption of the vacuum pump according to the invention compared.

Description

Die Erfindung betrifft eine Vakuumpumpe mit einer zylindrischen Arbeitskammer in der zwischen einer Ansaugöffnung und einer Ausströmöffnung ein Schieber angeordnet ist, der in einem Führungsschlitz eines Exzenterdrehkolbens gleitet.The invention relates to a vacuum pump with a cylindrical working chamber in which between a suction port and an outflow opening a slider is arranged, which slides in a guide slot of an eccentric rotary piston.

Im Stand der Technik sind derartige Drehkolbenpumpen, bei denen ein mit dem Gehäuse verbundener Schieber in einer von einem Exzenter angetriebenen Kolbentrommel verschiebbar gelagert ist, und deren Kolbentrommel an der zylindrischen Innenwand einer Arbeitskammer angepresst entlang gleitet, mehrfach vorbeschrieben.In the prior art, such rotary lobe pumps, in which a slide connected to the housing is slidably mounted in a piston drum driven by an eccentric, and whose piston drum is pressed against the cylindrical inner wall of a working chamber, are repeatedly described above.

Aus der DE 42 67 55 A ist eine Bauform bekannt, bei der der Schieber im Pumpengehäuse zwischen der Einströmöffnung und der Ausströmöffnung pendelnd gelagert ist und dieser während der Umlaufbewegung der Kolbentrommel in einen tangential in der Kolbentrommel angeordneten Schlitz eintaucht. Der Kurbelarm ist bei dieser Lösung an einer kreisförmigen Scheibe angeordnet.From the DE 42 67 55 A is known a design in which the slide is mounted oscillating in the pump housing between the inlet opening and the outflow opening and this dips during the orbital movement of the piston drum in a tangentially arranged in the piston drum slot. The crank arm is arranged in this solution on a circular disc.

Diese Lösung weist mit zunehmendem volumetrischen Wirkungsgrad, d.h. mit der hierfür erforderlichen zunehmenden Abdichtungen des Arbeitsspaltes, zwischen der Innenwandung der zylindrischen Arbeitskammer und dem an dieser Innenwandung entlang gleitenden Außenumfang der Kolbentrommel, durch die hierzu erforderliche Erhöhung der Pressung zwischen der Kolbentrommel und der Innenwandung der zylindrischen Arbeitskammer, einen bei zunehmendem volumetrischen Wirkungsgrad abnehmenden mechanischen Wirkungsgrad auf. Ursache hierfür ist, dass mit zunehmender Anpresskraft sich auch die Reibungsverluste zwischen der in der zylindrischen Arbeitskammer umlaufenden Kolbentrommel und der Innenwandung der zylindrischen Arbeitskammer erhöhen.This solution has, with increasing volumetric efficiency, ie with the necessary increasing sealing of the working gap, between the inner wall of the cylindrical working chamber and the outer circumference of the piston drum sliding along this inner wall, by the required increase in the pressure between the piston drum and the inner wall of the cylindrical working chamber, a decreasing with increasing volumetric efficiency mechanical efficiency. The reason for this is that with increasing contact pressure also increases the friction losses between the circulating in the cylindrical working chamber piston drum and the inner wall of the cylindrical working chamber.

In der AT 20 02 47 B wird nun zur Erzielung eines hohen Vakuums, bei gleichzeitiger Reduzierung der Reibungsverluste vorgeschlagen, an der Innenwandung der zylindrischen Arbeitskammer oder am Außenumfang der Kolbentrommel, über den Umfang verteilt, in achsparallele Nuten unter Federdruck stehende Leisten aus selbstschmierenden Werkstoffen anzuordnen. Diese Lösung ist jedoch mit einem sehr hohen Fertigungsaufwand verbunden, und kann zudem keine optimale Spaltabdichtung gewährleisten. Darüber hinaus ist diese Bauform sehr arbeits- und materialintensiv und verfügt zwangsläufig über sehr große Unwuchtmasse, wodurch diese Vakuumpumpe keinesfalls für hohe Drehzahlen geeignet ist.In the AT 20 02 47 B is now proposed to achieve a high vacuum, while reducing the friction losses, on the inner wall of the cylindrical working chamber or on the outer circumference of the piston drum, distributed over the circumference, to arrange in axially parallel grooves under spring pressure ledges made of self-lubricating materials. However, this solution is associated with a very high production cost, and also can not ensure optimum gap sealing. In addition, this design is very labor and material intensive and inevitably has very large imbalance mass, making this vacuum pump is by no means suitable for high speeds.

Aus der FR 1 346 509 ist eine weitere als Vakuumpumpe Einsatz findende Rotationskolbenpumpe mit einem exzentrisch gelagerten, in einer Arbeitskammer umlaufenden Drehkolben bekannt, deren mit einem Pendelkopf versehener Schieber mit dem Pendelkopf in einer in der Innenwandung der Arbeitskammer, zwischen der Ansaugöffnung und der Ausströmöffnung angeordneten Lagerrille derart pendelnd gelagert ist, dass dieser Schieber während der Umlaufbewegung des Drehkolbens mit seinem Pendelschaft in einen radial im Drehkolben angeordneten, von Führungsstegen gebildeten Führungsschlitz "eintaucht".From the FR 1 346 509 is another known as a vacuum pump using rotary piston pump with an eccentrically mounted, rotating in a working chamber rotary pistons whose provided with a pendulum head slider with the pendulum head in a arranged in the inner wall of the working chamber, between the suction port and the outflow bearing groove is mounted so oscillating, that this slider "immersed" during the orbital movement of the rotary piston with its pendulum shaft in a radially arranged in the rotary piston, formed by guide webs guide slot.

Doch auch bei dieser Lösung erhöhen sich mit zunehmender Anpresskraft zwischen der Innenwandung der zylindrischen Arbeitskammer und dem an dieser Innenwandung entlang gleitenden Außenumfang des Exzenterdrehkolbens, der Kolbentrommel, wiederum die Reibungsverluste, so dass mit zunehmendem volumetrischen Wirkungsgrad sich auch bei dieser Lösung der mechanische Wirkungsgrad verschlechtert.But even with this solution increase with increasing contact pressure between the inner wall of the cylindrical working chamber and the sliding along this inner wall along the outer periphery of the Exzenterdrehkolbens, the piston drum, in turn, the friction losses, so that with increasing volumetric efficiency, the mechanical efficiency deteriorates even with this solution.

Eine weitere Bauform einer ebenfalls als Vakuumpumpe Einsatz findenden Rotationskolbenpumpe, deren Schieber wiederum pendelnd im Pumpengehäuse zwischen der Einströmöffnung und der Ausströmöffnung gelagert ist und der während der Umlaufbewegung der Kolbentrommel in einen in der Kolbentrommel radial durchgehend angeordneten Schlitz eintaucht, wird in der DE 1 915 574 A vorbeschrieben. Um auch in der unteren Totpunktlage einen stetigen Kontakt der Kolbentrommel mit der Innenwandung der zylindrischen Arbeitskammer zu gewährleisten, werden dort die unterschiedlichsten Bauformen vorgeschlagen.Another design of a likewise used as a vacuum pump rotary piston pump, the slider is in turn mounted swinging in the pump housing between the inlet and the discharge and immersed during the orbital motion of the piston drum in a radially continuous in the piston drum slot is in the DE 1 915 574 A described above. In order to ensure a constant contact of the piston drum with the inner wall of the cylindrical working chamber in the bottom dead center, the most diverse designs are proposed there.

Doch auch bei all diesen Lösungen bewirkt die für einen hohen volumetrischen Wirkungsgrad erforderliche Anpresskraft, zwischen dem Exzenterdrehkolben und der Innenwandung der zylindrischen Arbeitskammer, zwangsläufig Reibungsverluste, so dass mit zunehmendem volumetrischen Wirkungsgrad sich auch bei diesen Lösungen der mechanische Wirkungsgrad verschlechtert. Eine andere Bauform einer Drehkolbenpumpe mit einem fest im Gehäuse angeordneten Schieber wurde, in der DE 22 62 574 A vorgestellt. Bei dieser Bauform wird vorgeschlagen den Schieber aus Bronze herzustellen, und die Seitenwände des Schiebers über die gesamte Länge konkav zu gestalten. Der Exzenter-Drehkolben hingegen soll aus Kunststoff gefertigt werden.But even with all these solutions causes the required for a high volumetric efficiency contact force between the Exzenterdrehkolben and the inner wall of the cylindrical working chamber, inevitably friction losses, so that deteriorates with increasing volumetric efficiency, even in these solutions, the mechanical efficiency. Another design of a rotary lobe pump with a fixed arranged in the housing slide was in the DE 22 62 574 A presented. In this design, it is proposed to make the slider made of bronze, and to make the side walls of the slider over the entire length concave. The eccentric rotary piston, however, should be made of plastic.

Auch bei dieser Lösung treten zwischen der Innenwandung der zylindrischen Arbeitskammer und dem an dieser Innenwandung entlang gleitenden Außenumfang des Exzenterdrehkolbens wiederum hohe Reibungsverluste auf, woraus mit steigendem volumetrischen Wirkungsgrad wiederum zwingend deutliche Verluste beim mechanischen Wirkungsgrad resultieren.In this solution, too, high friction losses occur between the inner wall of the cylindrical working chamber and the outer circumference of the eccentric rotary piston sliding along this inner wall, which in turn inevitably leads to significant losses in mechanical efficiency with increasing volumetric efficiency.

Zudem kann, infolge der lediglich sehr schmalen (linienförmigen) Berührungslinie zwischen dem starr im Gehäuse angeordneten Schieber und dem Exzenter-Drehkolben, mittels dieser Lösung keine optimale Spaltabdichtung gewährleistet werden, worauf zudem weitere Verluste beim volumetrischen Wirkungsgrad zurückzuführen sind.In addition, due to the only very narrow (line-shaped) contact line between the rigidly arranged in the housing slide and the eccentric rotary piston, no optimal gap seal can be ensured by means of this solution, which also further losses in volumetric efficiency are due.

Von der Anmelderin, wurde in der DE 10 2006 016 791 B4 , wie auch in der WO 2009/021474 A1 eine zwischenzeitlich bewährte Lösung einer Vakuumpumpe mit einer zylindrischen Arbeitskammer in der zwischen einer Ansaugöffnung und einer Ausströmöffnung ein Schieber angeordnet ist, der in einem Führungsschlitz eines Exzelter-Drehkolbens gleitet, vorgestellt, welche bereits in einer einstufigen Verdichtung ein hohes Vakuum erreicht und selbst bei sehr hohen Drehzahlen eine hohe Zuverlässigkeit und eine hohe Lebensdauer gewährleistet.By the applicant, was in the DE 10 2006 016 791 B4 as well as in the WO 2009/021474 A1 a meanwhile proven solution of a vacuum pump with a cylindrical working chamber in which between a suction port and an outflow opening a slide is arranged, which slides in a guide slot of an eccentric rotary piston, presented, which reaches a high vacuum even in a single-stage compression and even at very high Speeds ensuring high reliability and long life.

Bei dieser Lösung wird eine definierte Verformung des Exzenterdrehkolbens bewirkt, so dass während des gesamten Exzenterumlaufes dieser mit einer radialen Vorspannung stets dichtend an der Innenwand der zylindrischen Arbeitskammer anliegt.In this solution, a defined deformation of the Exzenterdrehkolbens is effected, so that during the entire eccentric revolution of this always bears with a radial bias sealingly against the inner wall of the cylindrical working chamber.

Auch diese Lösung hat den Nachteil, dass mit zunehmender Abdichtung, d.h. mit zunehmender Anpresskraft zwischen der Innenwandung der zylindrischen Arbeitskammer und dem an dieser Innenwandung entlang gleitenden Außenumfang des Exzenterdrehkolbens, sich die Reibungsverluste zwischen der in der zylindrischen Arbeitskammer umlaufenden Kolbentrommel und der Innenwandung der zylindrischen Arbeitskammer erhöhen, so dass auch bei dieser in der DE 10 2006 016 791 B4 , wie auch in der WO 2009/021474 A1 vorgestellten Lösung sich mit zunehmendem volumetrischen Wirkungsgrad der mechanische Wirkungsgrad verschlechtert.Also, this solution has the disadvantage that with increasing sealing, ie with increasing contact pressure between the inner wall of the cylindrical working chamber and sliding along this inner wall along the outer periphery of the Exzenterdrehkolbens, the friction losses between the circulating in the cylindrical working chamber piston drum and the inner wall of the cylindrical working chamber increase, so even in this in the DE 10 2006 016 791 B4 as well as in the WO 2009/021474 A1 solution presented worsens with increasing volumetric efficiency of mechanical efficiency.

Zusammenfassend ist daher festzustellen, dass alle zuvor genannten Bauformen zur Erzielung eines hohen volumetrischen Wirkungsgrades, zwischen dem/dem Exzenterdrehkolben und der/den zugeordneten Innenwandung/en der jeweiligen zylindrischen Arbeitskammern, eine die Dichtheit zwischen diesen Bauteilen gewährleistende Anpresskraft erfordern. Diese zwingend erforderliche, die Dichtheit gewährleistende Anpresskraft bewirkt jedoch als Normalkraft, beim Umlauf des Exzenterdrehkolbens in der Arbeitskammer, stets entgegen der Verschiebung wirkende Reibkräfte aus denen zwangsläufig Reibungsverluste der Vakuumpumpe resultieren, so dass mit zunehmendem volumetrischen Wirkungsgrad sich bei all diesen vorgenannten Lösungen der mechanische Wirkungsgrad verschlechtert.In summary, therefore, it should be noted that all the aforementioned designs to achieve a high volumetric efficiency, between the / the eccentric rotary piston and / the associated Innenwandung / s of the respective cylindrical working chambers, a tightness between these components guaranteeing contact force require. However, this absolutely necessary, the tightness ensuring pressing force causes as a normal force, during rotation of the Exzenterdrehkolbens in the working chamber, always counteracting the displacement frictional forces from which inevitably frictional losses of the vacuum pump result, so that with increasing volumetric efficiency, the mechanical efficiency deteriorates in all of these aforementioned solutions.

Die Aufgabe der Erfindung besteht nun darin eine mittels einer exzentrischen Umlaufbewegung arbeitende Vakuumpumpe mit einer zylindrischen Arbeitskammer in der zwischen einer Ansaugöffnung und einer Ausströmöffnung ein Schieber angeordnet ist, der in einem Führungsschlitz eines Exzenterdrehkolbens gleitet, zu entwickeln, die die vorgenannten Nachteile des Standes der Technik nicht aufweist, sich insbesondere bei hohem volumetrischen Wirkungsgrad durch einen sehr hohen mechanische Wirkungsgrad auszeichnet, zudem bereits in einer einstufigen Verdichtung ein hohes Vakuum erreicht, dabei einfach und robust aufgebaut ist, bei minimalem Materialeinsatz fertigungstechnisch einfach herstell- und montierbar ist, gleichzeitig den Fertigungs- und Instandhaltungsaufwand deutlich senkt, die Dichtheit zwischen dem Exzenterdrehkolben und der Innenwandung der zylindrischen Arbeitskammer wesentlich erhöht, den Verschleiß der Baugruppen minimiert, die selbst bei sehr hohen Drehzahlen, d.h. bei Direktantrieb über die Kurbelwelle, eine hohe Zuverlässigkeit, bei hoher Lebensdauer und geringer Schmutzanfälligkeit gewährleistet, und die zudem aber in speziellen Bauformen auch gegenüber der motorseitigen Antriebsdrehzahl variierende Pumpendrehzahlen, d.h. Exzenterkolbendrehzahlen, zu realisieren vermag.The object of the invention is now a working by means of an eccentric orbital vacuum pump with a cylindrical working chamber in which between a suction port and an outflow opening a slide is arranged, which slides in a guide slot of an eccentric rotary, to develop the aforementioned disadvantages of the prior art does not have, in particular at high volumetric efficiency characterized by a very high mechanical efficiency, also achieved in a single-stage compression a high vacuum, it is simple and robust, with minimal material use manufacturing technology is easy to manufacture and assemble, at the same time the manufacturing and maintenance costs significantly lowers, the tightness between the Exzenterdrehkolben and the inner wall of the cylindrical working chamber substantially increased, minimizing the wear of the assemblies, even at very high speeds, ie In the case of direct drive via the crankshaft, a high level of reliability, with a long service life and low susceptibility to soiling, is guaranteed, and in addition, in special designs, pump speeds which also vary with respect to the engine-side drive speed. Eccentric piston speeds, able to realize.

Erfindungsgemäß wird diese Aufgabe durch eine Vakuumpumpe nach den Merkmalen des Hauptanspruches der Erfindung gelöst.According to the invention this object is achieved by a vacuum pump according to the features of the main claim of the invention.

Vorteilhafte Ausführungen, Einzelheiten und Merkmale der Erfindung ergeben sich aus den Unteransprüchen sowie aus der nachfolgenden Beschreibung der erfindungsgemäßen Ausführungsbeispiele in Verbindung mit den Zeichnungen zur erfindungsgemäßen Lösung.Advantageous embodiments, details and features of the invention will become apparent from the dependent claims and from the following description of the Embodiments of the invention in conjunction with the drawings for the solution according to the invention.

Nachfolgend soll nun die Erfindung an Hand von 9 Ausführungsbeispiele in Verbindung mit den zugehörigen Figuren näher erläutert werden.Below, the invention will now be explained in more detail with reference to 9 embodiments in conjunction with the accompanying figures.

Die Figur 1 zeigt die erfindungsgemäße Vakuumpumpe in einem Teilschnitt, mit einem Pumpengehäuse 1, einer Antriebswelle 2, einer im Pumpengehäuse 1 angeordneten Arbeitskammer 3 mit einer zylinderförmigen Innenwandung 4, einem mit der Antriebswelle 2 verbundenen, exzentrisch angeordneten Lagerbolzen 5, einer drehbar auf dem Lagerbolzen 5 gelagerten, in der Arbeitskammer 3 umlaufenden Kolbentrommel, dem Orbiter 6, mit einem Zylindermantel 7, einem im Orbiter 6 angeordneten Führungsschlitz 8, sowie einer in der Arbeitskammer 3 angeordneten Ansaugöffnung 9 und einer in der Arbeitskammer 3 angeordneten Ausströmöffnung 10, mit einem zwischen der Ansaugöffnung 9 und der Ausströmöffnung 10 angeordneten Sperrschieber 11 der im Führungsschlitz 8 des Orbiters 6 verschiebbar, gleitend gelagert ist, mit einem schwenkbar, im Pumpengehäuse 1 gelagerten Sperrschieber 11, und einem im Orbiter 6 zentral angeordneten Führungssteg 13 in dem der mit Öltaschen 14 versehene Führungsschlitz 8 angeordnet ist. Erfindungswesentlich ist, dass in der in dieser Figur vorgestellten Bauform, einer ölgeschmierten Bauform in der Arbeitskammer 3 als Schmiermittel Öl angeordnet ist, und dass in diesem Ausführungsbeispiel zwischen der zylinderförmigen Innenwandung 4 der Arbeitskammer 3 und dem Zylindermantel 7 des Orbiters 6 ein Arbeitsspalt 12 von ca. 0,4 mm angeordnet ist der während Umlauf des Orbiters 6 in der Arbeitskammer 3 vollständig mit dem bei ölgeschmierten Baureihen eingesetzten Schmiermittel Öl verschlossen wird.The FIG. 1 shows the vacuum pump according to the invention in a partial section, with a pump housing 1, a drive shaft 2, arranged in the pump housing 1 working chamber 3 with a cylindrical inner wall 4, connected to the drive shaft 2, eccentrically arranged bearing pin 5, a rotatably mounted on the bearing pin 5, in the working chamber 3 rotating piston drum, the orbiter 6, with a cylinder jacket 7, a arranged in Orbiter 6 guide slot 8, and arranged in the working chamber 3 suction port 9 and arranged in the working chamber 3 outflow opening 10, with a between the suction port 9 and the outflow opening 10 arranged locking slide 11 which is slidably mounted in the guide slot 8 of the orbiter 6, with a pivotally mounted in the pump housing 1 locking slide 11, and arranged in a central orbiter 6 guide web 13 in which provided with oil pockets 14 guide slot 8 is. It is essential to the invention that, in the design presented in this figure, an oil-lubricated design is arranged in the working chamber 3 as lubricant oil, and that in this embodiment between the cylindrical inner wall 4 of the working chamber 3 and the cylinder jacket 7 of the orbiter 6, a working gap 12 of approx 0.4 mm is arranged, which is completely closed during circulation of the orbiter 6 in the working chamber 3 with the lubricant oil used in oil-lubricated series.

Bei anderen Bauformen der erfindungsgemäßen Lösung liegt der Arbeitsspalt 12, in Abhängigkeit vom jeweils eingesetzten Schmiermittel, im Bereich von 0,05 mm bis 0,8 mm.In other designs of the solution according to the invention, the working gap 12, depending on the particular lubricant used, in the range of 0.05 mm to 0.8 mm.

Die erfindungsgemäße Anordnung bewirkt überraschenderweise, dass sich während des Umlaufs des zylindrischen Orbiters 6 in der ölgeschmierten zylinderförmigen Arbeitskammer 3 zwischen dem Zylindermantel 7 des umlaufenden Orbiters 6 und der zylinderförmigen Innenwandung 4 der Arbeitskammer 3 ein den Arbeitsspalt 12 zuverlässig abdichtender Ölkeil aufbaut, auf dem der Orbiter 6 während seines Umlaufes in der Arbeitskammer 3 "dichtend aufschwimmt".The arrangement according to the invention surprisingly causes, during the circulation of the cylindrical orbiter 6 in the oil-lubricated cylindrical working chamber 3 between the cylinder jacket 7 of the rotating orbiter 6 and the cylindrical inner wall 4 of the working chamber 3, a working gap 12 reliably sealing oil wedge builds on the orbiter 6 "floating up" during its circulation in the working chamber 3.

Erfindungsgemäß bewirkt dieser Ölkeil neben seiner Dichtfunktion, aber gleichzeitig auch, dass in Folge der erfindungsgemäßen Anordnung des Arbeitsspaltes 12 keine direkte radiale Berührung der miteinander in Wirkverbindung tretenden Bauteile mehr stattfinden kann, und entlang des Arbeitsspaltes 12 über die gesamte Zylinderlänge des Orbiters 6 erfindungsgemäß ausschließlich Ölreibung, mit nur sehr geringen Reibungsverlusten auftritt.According to the invention causes this oil wedge in addition to its sealing function, but at the same time that no direct radial contact of passing together active components can take place due to the inventive arrangement of the working gap 12, and along the working gap 12 over the entire cylinder length of the orbiter 6 according to the invention exclusively oil friction , occurs with very little friction losses.

Wobei der Arbeitsdruck in dem, die Reibungsverluste erfindungsgemäß minimierenden Ölkeil während des Umlaufes des Orbiters 6 in der ölgeschmierten Arbeitskammer 3, infolge des ständig zwischen den Zylindern erneut in den Ölspalt "nachgepressten" Öls erhöht wird, so dass trotz des ständig durch den Arbeitsspalt 12 hindurchtretenden Öl's der Orbiter 6 auf dem erfindungsgemäß sich aufbauenden Ölkeil in der Arbeitskammer 3 "abdichtend" aufschwimmt und dabei gleichzeitig den Arbeitsspalt 12 zwischen dem Zylindermantel 7 des Orbiters 6 und der Innenwandung 4 der Arbeitskammer 3 zuverlässig abdichtet.Wherein the working pressure in the invention, the friction losses minimizing oil wedge during orbit 6 in the oil-lubricated working chamber 3, as a result of constantly re-injected between the cylinders in the oil gap "oil" is increased, so that despite the constantly passing through the working gap 12 Oil of the orbiter 6 "floats" on the oil wedge constituting the invention in the working chamber 3 and at the same time reliably seals the working gap 12 between the cylinder jacket 7 of the orbiter 6 and the inner wall 4 of the working chamber 3.

Mittels dieser hier vorliegenden erfindungsgemäßen Lösung kann bereits in einer einstufigen Verdichtung mit hohem volumetrischen Wirkungsgrad ein hohes Vakuum bei hohem mechanischen Wirkungsgrad erreicht werden. Dabei zeichnet sich diese in der Figur 1 dargestellte Ausführungsform der erfindungsgemäßen Lösung auch dadurch aus, dass in der Führung des Sperrschiebers 11, hier im Führungssteg 13, Öltaschen 14 angeordnet sind, welche einen leichtgängigen, verschleißminimierten und zuverlässigen Arbeitshub des Sperrschiebers 11 im Führungsschlitz 8 gewährleisten.By means of this solution according to the present invention, a high vacuum with high mechanical efficiency can already be achieved in a one-stage compression with high volumetric efficiency. This is characterized in the FIG. 1 illustrated embodiment of the solution according to the invention also characterized in that in the guide of the locking slide 11, here in the guide bar 13, oil pockets 14 are arranged, which ensure a smooth, wear-minimized and reliable working stroke of the locking slide 11 in the guide slot 8.

Die erfindungsgemäße Anordnung ist einfach und robust aufgebaut, zeichnet sich durch einen minimalen Materialeinsatz aus, senkt gleichzeitig deutlich die erforderliche Fertigungsgenauigkeit, ist daher fertigungstechnisch einfach herstellbar und zudem auch einfach montierbar, und ermöglicht so, dass gegenüber der Vorgängerlösung nach der DE 10 2006 016 791 B4 bei erhöhter Dichtheit, zwischen dem Orbiter 6 und der Innenwandung 4 der zylindrischen Arbeitskammer 3, der Fertigungsaufwand, deutlich gesenkt, aber auch der Verschleiß, wegen der Reduzierung der Reibung wie auch der Reduzierung der Schmutzanfälligkeit in Folge des erfindungsgemäßen Arbeitsspaltes minimiert werden kann.The arrangement of the invention is simple and robust, characterized by a minimal use of material, at the same time significantly reduces the required manufacturing accuracy, therefore, manufacturing technology is easy to produce and also easy to install, and thus allows that compared to the previous solution to the DE 10 2006 016 791 B4 with increased tightness, between the orbiter 6 and the inner wall 4 of the cylindrical working chamber 3, the manufacturing cost, significantly reduced, but also the wear, due to the reduction of friction as well as the reduction of soil susceptibility due to the working gap of the invention can be minimized.

Die erfindungsgemäße Lösung bewirkt in Verbindung mit der deutlichen Verringerung der Schmutzanfälligkeit auch, dass mittels der hier vorliegenden Lösung selbst bei sehr hohen Drehzahlen, d.h. bei Direktantrieb über die Kurbelwelle, eine hohe Zuverlässigkeit, bei hoher Lebensdauer gewährleistet werden kann, so dass auch der Instandhaltungsaufwand in diesem Einsatzbereich deutlich sinkt.The solution according to the invention, in conjunction with the marked reduction in susceptibility to soiling, also causes, by means of the present solution, even at very high speeds, i. With direct drive via the crankshaft, a high level of reliability can be ensured with a long service life, so that the maintenance effort in this area of use also drops significantly.

Für alle nachfolgend vorgestellten Ausführungsbeispiele der erfindungsgemäßen Lösung sind, neben weiteren, im Zusammenhang mit der jeweiligen Bauform vorgestellten Merkmalen, stets die vorgenannten, in Verbindung mit der Figur 1, erläuterten erfindungsgemäßen Merkmale charakteristisch.For all embodiments presented below the solution according to the invention are, in addition to other features presented in connection with the respective design features, always the aforementioned, in conjunction with the FIG. 1 , Characteristics of the invention explained characteristic.

In den Figuren 2 A, 2 B und 2 C ist eine der möglichen Ausführungsformen der erfindungsgemäßen Lösung dargestellt.In the Figures 2 A . 2 B and 2C is one of the possible embodiments of the solution according to the invention shown.

Die Figur 2 A zeigt die erfindungsgemäße Vakuumpumpe mit einem schwenkbar, im Pumpengehäuse 1 gelagerten Sperrschieber 11, einem im Orbiter 6 zentral angeordneten Führungssteg 13, einer im Orbiter 6 angeordneten Stützscheibe 15 und einer drehfest mit der Antriebswelle 2 verbundenen Exzenterscheibe 16 in einer Explosivdarstellung.The Figure 2 A shows the vacuum pump according to the invention with a pivotally mounted in the pump housing 1 locking slide 11, a centrally arranged in Orbiter 6 guide web 13, arranged in Orbiter 6 support plate 15 and a non-rotatably connected to the drive shaft 2 eccentric disc 16 in an exploded view.

In der Figur 2 B ist die erfindungsgemäße Vakuumpumpe, gemäß der Figur 2 A in einem Teilschnitt dargestellt.In the FIG. 2B is the vacuum pump according to the invention, according to the FIG. 2 A shown in a partial section.

Die Seitenansicht der erfindungsgemäßen Vakuumpumpe nach den Figuren 2 A und 2 B ist in der Figur 2 C im Schnitt dargestellt.The side view of the vacuum pump according to the invention according to the FIGS. 2 A and 2 B is in the FIG. 2C shown in section.

Diese in den Figuren 2 A, 2 B und 2 C dargestellte Ausführungsform der erfindungsgemäßen Lösung ist insbesondere auch dadurch gekennzeichnet, dass im Inneren des Orbiters 6 eine Stützscheibe 15 angeordnet ist.These in the Figures 2 A . 2 B and 2C illustrated embodiment of the solution according to the invention is particularly characterized in that inside the orbiter 6, a support plate 15 is arranged.

Die Anordnung einer solchen Stützscheibe 15 bewirkt eine höhere Stabilität des Orbiters 6, so dass derartige Stützscheiben 15 sowohl zur Reduzierung der Wandstärken des Orbiters 6, oder bei Bedarf auch zur Erhöhung der Stabilität des Orbiters 6, beispielsweise beim Einsatz der erfindungsgemäßen Vakuumpumpe bei hohen Drehzahlen, d.h. bei Drehzahlen bis in den Bereich von 8.000 U/min, um auch in diesem Drehzahlbereich elastische Verformungen des Orbiters 6 zu vermeiden und eine optimale Funktion der erfindungsgemäße Vakuumpumpe zu gewährleisten.The arrangement of such a support plate 15 causes a higher stability of the orbiter 6, so that such support disks 15 both to reduce the wall thicknesses of the orbiter 6, or if necessary, to increase the stability of the orbiter 6, for example when using the vacuum pump according to the invention at high speeds, ie at speeds up to the range of 8,000 rpm, in order to avoid elastic deformations of the orbiter 6 even in this speed range and to ensure optimal functioning of the vacuum pump according to the invention.

Neben den, analog zur Ausführung gemäß Figur 1, in der Führung des Sperrschiebers 11, dem Führungssteg 13 angeordneten Öltaschen 14, zeichnet sich diese in den Figuren 2 A, 2 B und 2 C dargestellte Ausführungsform insbesondere durch die drehfeste Anordnung einer, den Lagerbolzen 5 exzentrisch aufnehmenden, Exzenterscheibe 16 an der Antriebswelle 2 aus.In addition to, analogous to the execution according to FIG. 1 , in the leadership of the locking slide 11, the guide bar 13 arranged oil pockets 14, it is characterized in the Figures 2 A . 2 B and 2C illustrated embodiment, in particular by the rotationally fixed arrangement of one, the bearing pin 5 eccentrically receiving, eccentric disk 16 on the drive shaft 2 from.

Diese Bauform einer Exzenterscheibe 16 mit Lagerbolzen 5 bietet sich insbesondere dann an, wenn der Wellendurchmesser der Antriebwelle 2 für die Anordnung des Lagerbolzens 5 nicht ausreicht, um die für die einzusetzende Vakuumpumpe notwendige Exzentrizität zu erzielen.This design of an eccentric disc 16 with bearing pin 5 is particularly appropriate when the shaft diameter of the drive shaft 2 for the arrangement of the bearing pin 5 is not sufficient to achieve the necessary for the vacuum pump to be used eccentricity.

Bei den oftmals in Verbindung mit Vakuumpumpen Einsatz findenden Öl-Tandempumpen beträgt der Welledurchmesser der Antriebswelle 2 ca. 12 bis 15 mm. Mit der drehfesten Anordnung einer Exzenterscheibe 16 an der Antriebswelle 2 kann jede gewünschte Exzentrizität des Lagerbolzens 5 gegenüber der Wellenachse der Antriebswelle 2 realisiert werden.In the often used in conjunction with vacuum pumps oil tandem pumps of the shaft diameter of the drive shaft 2 is about 12 to 15 mm. With the rotationally fixed arrangement of an eccentric disk 16 on the drive shaft 2, any desired eccentricity of the bearing pin 5 relative to the shaft axis of the drive shaft 2 can be realized.

In den Figuren 3 A und 3 B ist eine weitere der möglichen Ausführungsformen der erfindungsgemäßen Lösung dargestellt.In the Figures 3 A and 3 B is shown another of the possible embodiments of the inventive solution.

Die Figur 3 A zeigt die erfindungsgemäße Vakuumpumpe mit einem schwenkbar, im Pumpengehäuse 1 gelagerten Sperrschieber 11, einem im Orbiter 6 zentral angeordneten Führungssteg 13, mit mehreren im Orbiter erfindungsgemäß angeordneten Stützstegen 17 mit einer Direktanbindung des Lagerbolzens 5 an die im Zylinderkopf 18 gelagerte Antriebswelle 2, hier die Nockenwelle, in einem Teilschnitt.The Figure 3 A shows the vacuum pump according to the invention with a pivotally mounted in the pump housing 1 locking slide 11, a centrally arranged in the orbiter 6 guide web 13, with a plurality of orbiter according to the invention arranged support webs 17 with a direct connection of the bearing pin 5 to the cylinder head 18 mounted in the drive shaft 2, here the camshaft , in a partial section.

In der Figur 3 B ist die erfindungsgemäße Vakuumpumpe gemäß der Figur 3 A in der Seitenansicht dargestellt.In the FIG. 3B is the vacuum pump according to the invention according to the Figure 3 A shown in the side view.

Diese in den Figuren 3 A und 2 B dargestellte Ausführungsform der erfindungsgemäßen Lösung ist zudem dadurch gekennzeichnet, dass im Inneren des Orbiters 6, alternativ zu der in Verbindung mit den Figuren 2 A, 2 B, und 2 C erläuterten Stützscheibe 15, Stützstege 17 angeordnet sind.These in the FIGS. 3A and 2 B illustrated embodiment of the solution according to the invention is also characterized in that in the interior of the orbiter 6, alternatively to that in connection with the Figures 2 A . 2 B , and 2C explained supporting disk 15, supporting webs 17 are arranged.

Auch die Anordnung von derartigen Stützstegen 17 bewirkt eine höhere Stabilität des Orbiters 6, so dass die Stützstege 17 sowohl zur Reduzierung der Wandstärken des Orbiters 6, wie auch zur Reduzierung der elastischen Verformungen, bzw. zur Erhöhung der Stabilität des Orbiters 6 eingesetzt werden können.The arrangement of such support webs 17 causes a higher stability of the orbiter 6, so that the support webs 17 can be used both to reduce the wall thicknesses of the orbiter 6, as well as to reduce the elastic deformations, or to increase the stability of the orbiter 6.

Die in diesem Ausführungsbeispiel dargestellte Direktanbindung des Lagerbolzens 5 an die im Zylinderkopf 18 gelagerte Antriebswelle 2, hier die Nockenwelle, ermöglicht den Entfall einer Kupplung und damit durch eine Reduzierung der erforderlichen Bauteile eine deutliche Einsparung bei den Fertigungs- und Montagekosten.The illustrated in this embodiment, direct connection of the bearing pin 5 to the cylinder head 18 mounted in the drive shaft 2, here the camshaft, allows the elimination of a clutch and thus by reducing the required components a significant savings in manufacturing and assembly costs.

In den Figuren 4 A und 4 B ist nun eine weitere der möglichen Ausführungsformen der erfindungsgemäßen Lösung dargestellt.In the Figures 4 A and 4 B Now, another of the possible embodiments of the solution according to the invention is shown.

Die Figur 4 A zeigt dabei die erfindungsgemäße Vakuumpumpe mit einem schwenkbar, im Pumpengehäuse 1 gelagerten Sperrschieber 11, einem im Orbiter 6 zentral angeordneten Führungssteg 13, mit mehreren im Orbiter 6 angeordneten Stützstegen 17 und der erfindungsgemäßen Anbindung des Lagerbolzens 5 über einen Adapter 19 an die im Zylinderkopf 16 gelagerte Antriebswelle 2, hier die Nockenwelle, in einem Teilschnitt.The Figure 4 A shows the vacuum pump according to the invention with a pivotally mounted in the pump housing 1 locking slide 11, a centrally arranged in the orbiter 6 guide web 13, with a plurality arranged in the orbiter 6 support webs 17 and the inventive connection of the bearing pin 5 via an adapter 19 to the stored in the cylinder head 16 Drive shaft 2, here the camshaft, in a partial section.

Die Figur 4 B zeigt die erfindungsgemäße Vakuumpumpe gemäß der Figur 4 A in der Seitenansicht im Schnitt.The FIG. 4B shows the vacuum pump according to the invention according to the Figure 4 A in the side view in section.

Für diese in den Figuren 4 A und 4 B dargestellte Ausführungsform der erfindungsgemäßen Lösung ist zudem kennzeichnend, dass der Lagerbolzen 5 in einem mit einem Zentrierbolzen versehenen Adapter 19 drehfest angeordnet ist.For these in the Figures 4 A and 4 B illustrated embodiment of the solution according to the invention is also characteristic that the bearing pin 5 is rotatably disposed in a provided with a centering pin adapter 19.

Dieser Adapter 19 ist in Verbindung mit einer Übergangspassung stirnseitig in der Antriebswelle 2 angeordnet und erfindungsgemäß als Stecklösung ausgeführt, um die im voran gegangenen Ausführungsbeispiel erforderliche Einpresskraft, zum Einpressen des Lagerbolzens 5 in die im Zylinderkopf 18 gelagerte Antriebswelle 2, zu vermeiden.This adapter 19 is arranged in connection with a transitional fit the front side in the drive shaft 2 and according to the invention designed as a plug-in solution to avoid the required force in the previous embodiment, for pressing the bearing pin 5 in the cylinder head 18 mounted in the drive shaft 2 to avoid.

Die Figuren 5 A und 5 B zeigen eine weitere der möglichen Ausführungsformen der erfindungsgemäßen Lösung.The FIGS. 5 A and 5 B show a further of the possible embodiments of the solution according to the invention.

Die Figur 5 A zeigt dabei die erfindungsgemäße Vakuumpumpe in der Bauform einer Tandempumpe mit einer den Lagerbolzen 5 aufnehmenden Exzenterscheibe 16 in der Draufsicht.The Figure 5 A shows the vacuum pump according to the invention in the design of a tandem pump with the bearing pin 5 receiving eccentric disk 16 in plan view.

Für diese Bauform ist kennzeichnend, dass die Exzenterscheibe 16 drehbar auf der Antriebswelle 2 angeordnet ist und zwischen der Antriebswelle 2 und der den Lagerbolzen 5 tragenden Exzenterscheibe 16, zur Übertragung eines definierten Antriebsmomentes, eine Rutschkupplung 20, in der hier dargestellten Bauform ein Toleranzring, angeordnet ist.Characteristic of this design is that the eccentric disc 16 is rotatably mounted on the drive shaft 2 and between the drive shaft 2 and the bearing pin 5 bearing eccentric disc 16, for transmitting a defined drive torque, a slip clutch 20, in the design shown here, a tolerance ring arranged is.

Die Einzelheit X der erfindungsgemäße Vakuumpumpe nach Figur 5 A ist in der Figur 5 B dargestellt.The detail X of the vacuum pump according to the invention Figure 5 A is in the FIG. 5B shown.

Diese Bauform der erfindungsgemäßen Lösung ermöglicht die Einbeziehung größerer Toleranzen bei der Herstellung der in Wirkverbindung tretenden Wellen-Nabenverbindung, gewährleistet gleichzeitig den Ausgleich von Wärmedehnungen, ermöglicht aber auch eine einfache und schnelle Montage, entkoppelt zugleich die Übertragung von auftretende Schwingungen und gewährleistet zudem eine Begrenzung der Drehmomentübertragung.This design of the solution according to the invention allows the inclusion of larger tolerances in the production of passing in operative connection shaft hub connection, at the same time ensures the compensation of thermal expansion, but also allows easy and quick installation, at the same time decouples the transmission of vibrations occurring and also ensures a limitation of torque transmission.

Diese Bauform der erfindungsgemäßen Lösung ist zudem dann besonders vorteilhaft, wenn die Vakuumpumpe des jeweiligen Kraftfahrzeuges, aus Platzgründen, oder aber auch zur Geräuschminderung in der Ölwanne angeordnet werden musste, und dort bei Motorstillstand mit Öl "voll" laufen kann.This design of the solution according to the invention is also particularly advantageous when the vacuum pump of the respective motor vehicle, from Space reasons, or else had to be arranged for noise reduction in the oil pan, and there at engine standstill with oil "full" can run.

Diese erfindungsgemäße, in der Bauform nach den Figuren 5 A und 5 B integrierte Rutschkupplung 20 gewährleistet auch unter den extremen Einsatzbedingungen einer bei Motorstillstand mit Öl "voll" gelaufenen Vakuumpumpe, stets einen "langsamen", bauteilschonenden und systematisch ölaustragenden Anlauf der Vakuumpumpe.This invention, according to the design FIGS. 5 A and 5 B The integrated friction clutch 20 guarantees a "slow", component-preserving and systematic oil-discharging start-up of the vacuum pump, even under the extreme operating conditions of a vacuum pump "fully" running when the engine is at a standstill.

In der Figur 6 ist eine weitere der möglichen Ausführungsformen der erfindungsgemäßen Lösung in der Draufsicht, im Schnitt dargestellt.In the FIG. 6 is another of the possible embodiments of the solution according to the invention in plan view, shown in section.

Die Figur 6 zeigt die erfindungsgemäße Vakuumpumpe in der Bauform einer Tandempumpe mit einer erfindungsgemäß mittels eines Gleitlagers 24 drehbar auf der Antriebswelle 2 angeordneten Exzenterscheibe 16 mit dem Lagerbolzen 5, und einem neben dem Gleitlager 24 zwischen der Antriebswelle 2 und der Exzenterscheibe 16 angeordneten Überholfreilauf 21, wobei auf die so auf der Antriebswelle 2 gelagerte Exzenterscheibe 16 ein Elektroantrieb 22 einwirkt, dessen Rotor starr mit der Exzenterscheibe 16, und dessen Stator starr mit dem Pumpengehäuse 1 verbunden ist.The FIG. 6 shows the vacuum pump according to the invention in the design of a tandem pump with an inventively by means of a sliding bearing 24 rotatably mounted on the drive shaft 2 arranged eccentric disk 16 with the bearing pin 5, and one next to the sliding bearing 24 between the drive shaft 2 and the eccentric disk 16 arranged overrunning clutch 21, wherein the so mounted on the drive shaft 2 eccentric 16 an electric drive 22 acts whose rotor is rigidly connected to the eccentric disc 16, and whose stator is rigidly connected to the pump housing 1.

Dabei ist starr auf der Antriebswelle 2 ein Antriebsrad 23, z.B. ein Kettenrad, oder eine Riemenscheibe, angeordnet.In this case, rigidly on the drive shaft 2, a drive wheel 23, e.g. a sprocket, or a pulley arranged.

Diese in der Figur 6 dargestellte Bauform der erfindungsgemäßen Vakuumpumpe ermöglicht den Antrieb der Vakuumpumpe einerseits mittels des drehfest mit der Antriebswelle 2 verbundenen Antriebsrades 23, und andererseits, bei "stehender oder zu langsam laufender" Antriebswelle 2, allein mittels des Elektroantriebes 22.This in the FIG. 6 illustrated design of the vacuum pump according to the invention allows the drive of the vacuum pump on the one hand by means of the rotatably connected to the drive shaft 2 drive wheel 23, and on the other hand, in "stationary or too slow-running" drive shaft 2, solely by means of the electric drive 22nd

Mittels des Elektroantriebes 22 kann die Exzenterscheibe 16, infolge des erfindungsgemäß angeordneten Überholfreilaufes 21, die Drehzahl des Antriebsrades 23 "überholen".By means of the electric drive 22, the eccentric disc 16, as a result of the inventively arranged overrunning clutch 21, the speed of the drive wheel 23 "overtake".

In der Figur 7 ist eine weitere der möglichen Ausführungsformen der erfindungsgemäßen Lösung in der Draufsicht, im Schnitt dargestellt.In the FIG. 7 is another of the possible embodiments of the solution according to the invention in plan view, shown in section.

Diese in der Figur 7 dargestellte erfindungsgemäße Vakuumpumpe in der Bauform einer Tandempumpe mit einem Antriebsrad 23, zeichnet sich unter anderem durch eine drehfest mit der Antriebswelle 2 verbundene Exzenterscheibe 16 mit einem Lagerbolzen 5, einem separat neben der Exzenterscheibe 16 auf der Antriebswelle 2 drehfest angeordneten Innenring eines Überholfreilaufes 21, einem auf dem zugeordneten Außenring des Überholfreilaufes 21 einwirkenden Elektroantrieb 22, dessen Rotor starr mit dem Außenring des Überholfreilaufes 21 und dessen Stator starr mit dem Pumpengehäuse 1 verbunden ist, aus.This in the FIG. 7 illustrated vacuum pump according to the invention in the form of a tandem pump with a drive wheel 23, characterized inter alia by a non-rotatably connected to the drive shaft 2 eccentric disc 16 with a bearing pin 5, a separately adjacent to the eccentric disc 16 on the drive shaft 2 rotatably mounted inner ring of a passing freewheel 21, a acting on the associated outer ring of the overrunning clutch 21 electric drive 22 whose rotor is rigidly connected to the outer ring of the overrunning clutch 21 and whose stator is rigidly connected to the pump housing 1 from.

Auch in dieser Bauform ist auf der Antriebswelle 2 ein Antriebsrad 23, z.B. einem Kettenrad, oder einer Riemenscheibe angeordnet.Also in this design is on the drive shaft 2, a drive wheel 23, e.g. a sprocket, or a pulley arranged.

Für diese Bauform ist zudem kennzeichnend, dass zwischen der Antriebswelle 2 und dem Antriebsrad 23 ein weiterer Überholfreilauf 21 angeordnet ist.Characteristic of this design is that between the drive shaft 2 and the drive wheel 23, a further overrunning clutch 21 is arranged.

Diese in der Figur 7 dargestellte Bauform ermöglicht somit den Antrieb der gesamten Tandempumpe einerseits über das Antriebsrad 23, aber andererseits bei "stehendem" Antriebsrad 23 auch über den Elektroantrieb 22, zum Beispiel bei Start/Stop Betrieb des Motors.This in the FIG. 7 illustrated design thus allows the drive of the entire tandem pump on the one hand on the drive wheel 23, but on the other hand in "stationary" drive wheel 23 and the electric drive 22, for example, at start / stop operation of the engine.

Selbstverständlich kann auch bei der in der Figur 7 dargestellten Bauform der erfindungsgemäßen Lösung der Elektroantrieb 22, bei zu langsam laufendem Antriebsrad 23, die Drehzahl des Antriebsrades 23 "überholen" und so den Antrieb der gesamten Tandempumpe übernehmen.Of course, also in the in the FIG. 7 illustrated design of the inventive solution of the electric drive 22, with too slowly running drive wheel 23, the speed of the drive wheel 23 "overtake" and so take over the drive of the entire tandem pump.

In den Figuren 8 A und 8 B ist noch eine weitere der möglichen Ausführungsformen der erfindungsgemäßen Lösung dargestellt.In the FIGS. 8A and 8B Yet another of the possible embodiments of the solution according to the invention is shown.

Die Figur 8 A zeigt dabei die erfindungsgemäße Vakuumpumpe mit einem schwenkbar, im Pumpengehäuse 1 gelagerten Sperrschieber 11, einem im Orbiter 6 dezentral angeordneten Führungssteg 13, einer durch das Pumpengehäuse 1 hindurch geführten Antriebswelle 2 mit einer im Orbiter 6 angeordneten Stützscheibe 15 in einer Schnittdarstellung.The FIG. 8A shows the vacuum pump according to the invention with a pivotally mounted in the pump housing 1 locking slide 11, a decentralized arranged in the Orbiter 6 guide web 13, guided through the pump housing 1 through drive shaft 2 with a arranged in the orbiter 6 supporting disk 15 in a sectional view.

Die Figur 8 B zeigt diese erfindungsgemäße Vakuumpumpe aus der Figur 8 A in der Seitenansicht im Schnitt.The FIG. 8B shows this vacuum pump according to the invention from the FIG. 8A in the side view in section.

Diese Bauform, für die eine durch die Vakuumpumpe "hindurchgeführten" Antriebswelle 2 kennzeichnend ist, ermöglicht die Übertragung höherer Antriebsmomente, den Antrieb eines weiteren, der Vakuumpumpe benachbarten Aggregates, z. B. einer weiteren Pumpe, wie aber auch gleichzeitig eine, mit der dezentralen Führung des Sperrschiebers verbundene, deutliche Verkleinerung des erforderlichen Bauraumes der Vakuumpumpe.This design, for a by the vacuum pump "passed" drive shaft 2 is characteristic, allows the transmission of higher drive torque, the drive of another, the vacuum pump adjacent unit, z. B. a further pump, but also at the same time a, connected to the decentralized management of the locking slide, significant reduction of the required space of the vacuum pump.

Die Figuren 9 A und 9 B zeigen noch eine weitere der möglichen Ausführungsformen der erfindungsgemäßen Lösung.The FIGS. 9A and 9B show yet another of the possible embodiments of the inventive solution.

In der Figur 9 A ist die erfindungsgemäße Vakuumpumpe in der Bauform einer Tandempumpe mit einem schwenkbar, im Pumpengehäuse 1 gelagerten Sperrschieber 11 im Schnitt dargestellt.In the FIG. 9A the vacuum pump according to the invention in the form of a tandem pump with a pivotally mounted in the pump housing 1 locking slide 11 is shown in section.

Auch in dieser Bauform ist der schwenkbar, im Pumpengehäuse 1 gelagerte Sperrschieber 11 in einem im Orbiter 6 dezentral angeordneten Führungssteg 13 verschiebbar gelagert. Zur Gewährleistung der Stabilität sind bei dieser erfindungsgemäßen Bauform im Orbiter 6 neben dem Führungssteg 13 mehrere Stützstege 17 angeordnet.Also in this design, the pivotally mounted in the pump housing 1 locking slide 11 is slidably mounted in a decentralized arranged in the orbiter 6 guide web 13. To ensure stability, a plurality of support webs 17 are arranged in the orbiter 6 next to the guide web 13 in this inventive design.

Kennzeichnend ist auch, dass auf einer Seite des Orbiters 6 eine drehfest mit der Antriebswelle 2 verbundene Exzenterscheibe 16 angeordnet ist, in der exzentrisch ein den Orbiter 6 beidseitig überragender Lagerbolzen 5 befestigt ist, wobei auf der gegenüberliegenden Seite des Orbiters 6, am dem den Orbiter 6 dort überragenden Lagerbolzen 9, eine zweite Exzenterscheibe 16 angeordnet ist.It is also characteristic that on one side of the orbiter 6 a non-rotatably connected to the drive shaft 2 eccentric disc 16 is arranged in the eccentric one the orbiter 6 on both sides superior bearing pin 5 is fixed, on the opposite side of the orbiter 6, on which the orbiter 6 there superior bearing pin 9, a second eccentric disc 16 is arranged.

Erfindungsgemäß ist zentrisch und drehfest an dieser zweiten Exzenterscheibe 16, dem Orbiter 6 gegenüberliegend, eine das Pumpengehäuse 1 überragende weiteren Antriebswelle 2 angeordnet. Die Figur 9 B zeigt die erfindungsgemäße Vakuumpumpe aus der Figur 9 A in der Draufsicht in einer Schnittdarstellung. Auch diese Bauform ermöglicht auf Grund der durch die Vakuumpumpe "hindurchgeführten" Antriebswelle 2, den Antrieb eines weiteren, der Vakuumpumpe benachbarten Aggregates, beispielsweise einer dritten Pumpe.In accordance with the invention, a further drive shaft 2 protruding beyond the pump housing 1 is arranged centrically and non-rotatably on this second eccentric disk 16, opposite the orbiter 6. The FIG. 9B shows the vacuum pump according to the invention from the FIG. 9A in a plan view in a sectional view. Due to the drive shaft 2 "passed" through the vacuum pump, this design also makes it possible to drive a further unit adjacent to the vacuum pump, for example a third pump.

Die Figur 10 zeigt nun eine Gegenüberstellung der Kennlinien unterschiedlicher Bauformen von gegenwärtig in Kraftfahrzeugen eingesetzten, im Kammervolumen vergleichbaren Vakuumpumpen.The FIG. 10 now shows a comparison of the characteristics of different types of currently used in motor vehicles, comparable in the chamber volume vacuum pumps.

Bei diesen Kennlinien ist die Leistungsaufnahme P der jeweiligen Vakuumpumpe in Watt über der zugehörigen Pumpendrehzahl n in U/min angetragen.In these curves, the power consumption P of the respective vacuum pump is plotted in watts above the associated pump speed n in rpm.

Die Kennlinie I beschreibt die Leistungsaufnahme der hier vorgestellten erfindungsgemäßen Vakuumpumpe.The characteristic I describes the power consumption of the vacuum pump according to the invention presented here.

Die Kennlinie II beschreibt die Leistungsaufnahme einer als Vakuumpumpe eingesetzten Kolbenpumpe.The characteristic II describes the power consumption of a piston pump used as a vacuum pump.

Die Kennlinie III beschreibt die Leistungsaufnahme einer Monoflügelpumpe mit einem Kunststoffflügel, und die Kennlinie IV die Leistungsaufnahme einer Monoflügelpumpe mit einem Stahlflügel.The characteristic III describes the power consumption of a monoflügelpumpe with a plastic wing, and the characteristic IV the power consumption of a Monoflügelpumpe with a steel wing.

Die optimale Lage der Kennlinie I der hier vorgestellten erfindungsgemäßen Vakuumpumpe, resultiert aus dem in seinem Bewegungsablauf zwangsgeführten, und berührungsfrei entlang der Innenwandung 4 der Arbeitskammer 3 auf einem Ölkeil entlang gleitenden Orbiter 6, der keine Normalkraftkomponente gegenüber der Arbeitskammerwandung erzeugt, so dass die Reibleistung lediglich aus der Ölreibung im Dichtspalt resultiert und daher mit steigender Drehzahl nur geringfügig zunimmt.The optimum position of the characteristic curve I of the vacuum pump according to the invention presented here results from the forcibly guided movement in its motion, and contactless along the inner wall 4 of the working chamber 3 on an oil wedge sliding orbiter 6, which generates no normal force component against the Arbeitskammerwandung, so that the friction only resulting from the oil friction in the sealing gap and therefore increases only slightly with increasing speed.

Daher ist die erfindungsgemäße Vakuumpumpe wie vorgesehen für den Einsatz im Hochdrehzahlbereich, d.h. auch für den Direktantrieb über die Kurbelwelle mit bis über 7000 U/min, optimal geeignet.Therefore, the vacuum pump according to the invention is as intended for use in the high speed range, i. Also suitable for direct drive via the crankshaft with up to more than 7000 rpm, optimally suited.

Die Lage der Kennlinie III der Monoflügelpumpe mit Kunststoffflügel, wie auch die der Kennlinie IV, einer Monoflügelpumpe mit einem Stahlflügel, resultieren daraus, dass deren Flügel beim Umlauf durch die auf den Flügel einwirkende Zentrifugalkraft dichtend an die Innenwand der Arbeitskammer gepresst werden. Mit steigender Drehzahl nimmt daher die die Reibkraft erzeugende Normalkraft, die Anpresskraft und mit dieser dann auch die Reibleistung überproportional zu.The position of the characteristic curve III of the monoflügelpumpe with plastic wings, as well as the characteristic IV, a monoflügelpumpe with a steel wing, resulting from the fact that the wings are pressed while passing through the centrifugal force acting on the wing sealingly against the inner wall of the working chamber. With increasing speed therefore increases the frictional force generating normal force, the contact pressure and with this then the friction too disproportionately.

Nicht nur die Flügel sind bei diesen Bauformen mit zunehmender Drehzahl einem starken Verschleiß unterworfen, auch die Antriebsdrehzahl selbst wird durch die stark ansteigende Reibleistung begrenzt, so dass derartige Monoflügelpumpen nie von der Kurbelwelle direkt angetrieben werden können, sondern stets nur an die Nockenwelle angebunden, bzw. untersetzt angetrieben werden, so dass deren maximale Antriebsdrehzahl zwangsläufig stets nur im Bereich von 3.500 U/min liegt.Not only the wings are subjected to heavy wear in these designs with increasing speed, the drive speed itself is limited by the sharply increasing friction, so that such Monoflügelpumpen can never be directly driven by the crankshaft, but always connected to the camshaft, or . are driven underpowered, so that their maximum drive speed is inevitably always only in the range of 3,500 rev / min.

Die Figur 11 zeigt in eine Gegenüberstellung die Leistungsaufnahme einer Monoflügelpumpe mit Kunststoffflügel, Kennlinie III, und die Leistungsaufnahme der erfindungsgemäßen Vakuumpumpe, Kennlinie I (mit vergleichbaren Arbeitskammergrößen). In den in diesem Zusammenhang seitens der Anmelderin durchgeführten Tests wurde die Antriebsdrehzahl kontinuierlich bis auf über 6.000 U/min erhöht und im Ergebnis die Leistungsaufnahme der Monoflügelpumpe mit Kunststoffflügel, als Kennlinie III, der Leistungsaufnahme der erfindungsgemäßen Vakuumpumpe gegenüber gestellt.The FIG. 11 shows in a comparison of the power consumption of a monoflügelpumpe with plastic wing, characteristic III, and the power consumption of the vacuum pump according to the invention, characteristic I (with comparable working chamber sizes). In the tests carried out in this context by the applicant, the drive speed was continuously increased to over 6,000 rpm and as a result the power consumption of the monoflügelpumpe with plastic wing, as a characteristic III, the power consumption of the vacuum pump according to the invention compared.

Da die im Test eingesetzte Monoflügelpumpe mit Kunststoffflügel, Kennlinie III, bei ca. 6000 U/min aus Verschleißgründen ausfiel, werden die Leistungsaufnahmen bei 6.000 U/min miteinander verglichen.Since the single-wing pump with plastic wing, curve III, used in the test failed at about 6000 rpm for reasons of wear, the power consumption at 6,000 rpm is compared with each other.

Diese belegen jedoch eindeutig, dass die erfindungsgemäße Vakuumpumpe mit dem auf dem erfindungsgemäßen Ölkeil umlaufenden Orbiter 6, welche bei 6.000 U/min lediglich eine Leistungsaufnahme von ca. 200 W aufwies, gegenüber der Monoflügelpumpe mit Kunststoffflügel, die bei 6.000 U/min eine Leistungsaufnahme von ca. 2.000 W aufwies, über einen wesentlich besseren mechanischen Wirkungsgrad verfügt.However, these clearly show that the vacuum pump according to the invention with the circulating on the oil wedge Orbiter 6, which only had a power consumption of about 200 W at 6,000 rev / min, compared to the monoflügelpumpe with plastic wings, which at 6,000 rev / min power consumption of about 2,000 W, has a much better mechanical efficiency.

Mit der erfindungsgemäßen Lösung ist es somit gelungen eine mittels einer exzentrischen Umlaufbewegung arbeitende Vakuumpumpe mit einer zylindrischen Arbeitskammer in der zwischen einer Ansaugöffnung und einer Ausströmöffnung ein Schieber angeordnet ist, der in einem Führungsschlitz eines Exzenter-Drehkolbens gleitet, zu entwickeln, die einfach und robust aufgebaut ist, und die Dichtheit zwischen dem Exzenter-Drehkolben und der Innenwandung der zylindrischen Arbeitskammer wesentlich erhöht, gleichzeitig den Verschleiß der Baugruppen minimiert, und die selbst bei sehr hohen Drehzahlen (bis 7.000 U/min), d.h. bei Direktantrieb über die Kurbelwelle eines Kraftfahrzeuges, eine hohe Zuverlässigkeit bei hoher Lebensdauer und geringer Schmutzanfälligkeit gewährleistet, sich dabei insbesondere bei hohem volumetrischen Wirkungsgrad auch durch einen sehr hohen mechanischen Wirkungsgrad, mit einer wesentlich geringeren Leistungsaufnahme gegenüber herkömmlichen Vakuumpumpen mit gleichen Kammergrößen, auszeichnet und bereits in einer einstufigen Verdichtung ein hohes Vakuum erzielt, zudem bei minimalem Materialeinsatz fertigungstechnisch einfach herstell- und montierbar ist und den erforderlichen Fertigungs- und Instandhaltungsaufwand gleichzeitig deutlich senkt.With the solution according to the invention, it is thus possible to operate a working by means of an eccentric orbital vacuum pump with a cylindrical working chamber in between a suction port and an outflow opening a slider which slides in a guide slot of an eccentric rotary piston to develop, which is simple and robust is, and the tightness between the eccentric rotary piston and the Increased significantly inner wall of the cylindrical working chamber, while minimizing wear of the assemblies, and even at very high speeds (up to 7,000 rev / min), ie direct drive via the crankshaft of a motor vehicle, a high reliability with high durability and low susceptibility to dirt ensures in particular at high volumetric efficiency also characterized by a very high mechanical efficiency, with a much lower power compared to conventional vacuum pumps with the same chamber sizes, and already achieved in a single-stage compression a high vacuum, also easy to manufacture and assemble with minimal use of materials production and at the same time significantly reduces the required production and maintenance costs.

BezugszeichenzusammenstellungREFERENCE SYMBOL

11
Pumpengehäusepump housing
22
Antriebswelledrive shaft
33
Arbeitskammerworking chamber
44
Innenwandunginner wall
55
Lagerbolzenbearing bolt
66
OrbiterOrbiter
77
Zylindermantelcylinder surface
88th
Führungsschlitzguide slot
99
Ansaugöffnungsuction
1010
Ausströmöffnungoutflow
1111
Sperrschieberblocking slide
1212
Arbeitsspaltworking gap
1313
Führungsstegguide web
1414
Öltaschenoil pockets
1515
Stützscheibesupport disc
1616
Exzenterscheibeeccentric
1717
Stützstegesupporting webs
1818
Zylinderkopfcylinder head
1919
Adapteradapter
2020
Rutschkupplungslip clutch
2121
Überholfreilaufoverrunning clutch
2222
Elektroantriebelectric drive
2323
Antriebsraddrive wheel
2424
Gleitlagerbearings

Claims (5)

  1. Vacuum pump with a pump housing (1), a driveshaft (2) a working chamber (3) with cylindrical inside walls (4) located in a pump housing (1) an offset disc (16) located on the drive shaft (2) with a bearing bolt (5) located on this in an offset position, a cylindrical barrel rotating in the working chamber (3) and rotatably mounted on the bearing bolt (5), the orbiter (6) with a cylinder jacket (7), a guide slot (8) located in the orbiter (6) as well as an intake orifice (9) located in the working chamber (3) and a discharge orifice (10) located in the working chamber (3), with a gate valve (11) located between the intake orifice (9) and the discharge orifice (10) which moves and glides in the guide slot (8) of the orbiter (6) and a drive wheel (23) located on the drive shaft (2) outside of the pump housing (1), characterized in
    - that a friction clutch (20) is used for rotatable location of the offset disc (16) on the drive shaft (2) or is rotatably located on the drive shaft (2) in a sliding bearing (24) or is located torque-proof on the drive shaft (2), and
    - that an overrunning clutch (21) is also located next to the sliding bearing (24) between the drive shaft (2) and the offset disc (16) when the offset disc (16) is located rotatably in a sliding bearing (24), whereby an electrical drive (22) acts on the offset disc (16) mounted on the drive shaft (2) whose rotor is rigidly connected with the offset disc (16) and whose stator is connected rigidly with the pump housing (1) and
    - that an inside ring of an overrunning clutch (21) with an electrical drive (22) acting on the associated outside ring of ,the overrunning clutch (21) is also located torque-proof next to the offset disc (16) on the drive shaft (2) when the offset disc (16) is located torque-proof on the drive shaft (2) and whose stator is connected rigidly with the pump housing (1), whereby an overrunning clutch (21) is simultaneously located between the drive shaft (2) and the drive wheel (23).
  2. Vacuum pump according to claim 1, characterized in that a support disc (15) is located in the orbiter (6) and a guide bar (13) is located decentrally.
  3. Vacuum pump according to claim 2, characteritzed in that a guide bar (13) is located decentrally in the orbiter (6) with several support bars (17).
  4. Vacuum pump according to claim 1 characterized in that a lubricant is located in the working chamber (3) and that a working gap (12) of 0.05 mm to 0.8 mm is located between the cylindrical inside wall (4) of the working chamber (3) and the cylinder jacket (7) of the orbiter (6), whereby the rotation of the orbiter (6) in the working chamber (3) of the working gap (12) is completely sealed with lubricant in oil-lubricated production series.
  5. Vacuum pump according to claim 1, characterized in that the bearing bolt (5) is located torque-proof in an adapter (19) with a centering bolt.
EP13002418.5A 2012-05-11 2013-05-07 Vacuum pump Not-in-force EP2662570B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201210009419 DE102012009419B3 (en) 2012-05-11 2012-05-11 "Vacuum pump"

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EP2662570A1 EP2662570A1 (en) 2013-11-13
EP2662570B1 true EP2662570B1 (en) 2015-12-09

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JP3361821B2 (en) * 1998-04-29 2003-01-07 チュンキュング キム Fluid pump
DE102006016791B4 (en) * 2006-04-10 2008-01-31 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt vacuum pump
ES2361506T3 (en) * 2007-08-11 2011-06-17 Geräte- Und Pumpenbau Gmbh, Dr. Eugen Schmidt PENDULAR SLIDING VACUUM PUMP.
CN101328890B (en) * 2008-07-22 2010-12-08 温岭市鑫磊空压机有限公司 Translation type rotary compressing device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106050648A (en) * 2016-07-25 2016-10-26 刘清泉 Disc pump

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DE102012009419B3 (en) 2013-07-25

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