EP2662570A1 - Vacuum pump - Google Patents

Abstract

The pump has an overhauling freewheel arranged adjacent to a slide bearing between a drive shaft (2) and an eccentric disk. An electric drive works on the eccentric disk that is supported on the drive shaft. A rotor of the electric drive is rigidly connected with the eccentric disk, and a stator is rigidly connected with a pump housing (1). An inner ring of the freewheel is arranged on the disk adjacent to the drive shaft. The freewheel is arranged between the drive shaft and a drive wheel. A bearing bolt (5) is arranged in an adapter that has a centering bolt.

Description

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.

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.

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.

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 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.

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.

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.

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.

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.

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.

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.

By the applicant, was in the DE 10 2006 016 791 B4 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.

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.

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 solution presented worsens with increasing volumetric efficiency of mechanical efficiency.

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.

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 slider 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.

According to the invention this object is achieved by a vacuum pump according to the features of the main claim of the invention.

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.

Below, the invention will now be explained in more detail with reference to 9 embodiments in conjunction with the accompanying figures.

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.

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.

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.

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.

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.

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.

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.

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 the FIGS. 2A . 2B and 2C is one of the possible embodiments of the solution according to the invention shown.

The FIG. 2A 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 the FIG. 2B is the vacuum pump according to the invention, according to the Figure 2 A shown in a partial section.

The side view of the vacuum pump according to the invention according to the FIGS. 2A and 2B is in the Figure 2C shown in section.

These in the FIGS. 2A . 2B 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.

The arrangement of such a support plate 15 causes a higher stability of the orbiter 6, so that such support disks 15 both for reducing 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.

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 FIGS. 2A . 2B 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.

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.

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 the FIGS. 3A and 3B is shown another of the possible embodiments of the inventive solution.

The FIG. 3A 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 ribs 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 the FIG. 3B is the vacuum pump according to the invention according to the FIG. 3A shown in the side view.

These in the FIGS. 3A and 2B 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 FIGS. 2A . 2 B , and 2C explained supporting disk 15, supporting webs 17 are arranged.

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.

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 the FIGS. 4A and 4B Now, another of the possible embodiments of the solution according to the invention is shown.

The FIG. 4A 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.

The FIG. 4B shows the vacuum pump according to the invention according to the FIG. 4A in the side view in section.

For these in the FIGS. 4A and 4B 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.

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.

The FIGS. 5A and 5B show a further of the possible embodiments of the solution according to the invention.

The FIG. 5A 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.

The detail X of the vacuum pump according to the invention FIG. 5A is in the FIG. 5B shown.

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.

This invention, according to the design FIGS. 5A and 5B The integrated friction clutch 20 ensures a "slow", component-preserving and systematic oil-discharging start-up of the vacuum pump, even under the extreme operating conditions of a vacuum pump that has run "fully" when the engine is at a standstill.

In the FIG. 6 is another of the possible embodiments of the solution according to the invention in plan view, shown in section.

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.

In this case, rigidly on the drive shaft 2, a drive wheel 23, e.g. a sprocket, or a pulley arranged.

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

By means of the electric drive 22, the eccentric disc 16, as a result of the present invention arranged overrunning clutch 21, the speed of the drive wheel 23 "overtake".

In the FIG. 7 is another of the possible embodiments of the solution according to the invention in plan view, shown in section.

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.

Also in this design is on the drive shaft 2, 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.

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.

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 the Figures 8A and 8B Yet another of the possible embodiments of the solution according to the invention is shown.

The Figure 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.

The FIG. 8B shows this vacuum pump according to the invention from the Figure 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.

The Figures 9A and 9B show yet another of the possible embodiments of the inventive solution.

In the Figure 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.

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.

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.

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 Figure 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. 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.

In these curves, 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 monoflügelpumpe with a plastic wing, and the characteristic IV the power consumption of a Monoflügelpumpe with a steel wing.

The optimum position of the characteristic I of the vacuum pump according to the invention presented here results from the forcibly guided movement in its course 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.

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.

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.

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 input speed is inevitably always only in the range of 3,500 rev / min.

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.

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.

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.

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.

REFERENCE SYMBOL

1

pump housing

2

drive shaft

3

working chamber

4

inner wall

5

bearing bolt

6

Orbiter

7

cylinder surface

8th

guide slot

9

suction

10

outflow

11

blocking slide

12

working gap

13

guide web

14

oil pockets

15

support disc

16

eccentric

17

supporting webs

18

cylinder head

19

adapter

20

slip clutch

21

overrunning clutch

22

electric drive

23

drive wheel

24

bearings

Claims (5)

Vacuum pump with a pump housing (1), a drive shaft (2), a working chamber (3) arranged in the pump housing (1) with a cylindrical inner wall (4), an eccentric disc (16) arranged on the drive shaft (2) with one on this 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 in the orbiter (6) arranged guide slot (8) and a suction opening (9) arranged in the working chamber (3) and an outflow opening (10) arranged in the working chamber (3) with a locking slide (11) arranged in the guide slot between the suction opening (9) and the outflow opening (10) (8) of the orbiter (6) is slidably mounted, slidably mounted, and on the drive shaft (2) outside the bearing housing (1) arranged drive wheel (23), characterized - That the eccentric disc (16) by means of a slip clutch (20) on the drive shaft (2) rotatably, on the drive shaft (2) in a sliding bearing (24) rotatably or non-rotatably on the drive shaft (2) is arranged, and - That in a sliding bearing (24) rotatable arrangement of the eccentric disc (16) on the drive shaft (2) in addition to the sliding bearing (24) between the drive shaft (2) and the eccentric disc (16) an overrunning clutch (21) is arranged, on the drive shaft (2) mounted eccentric disc (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), and - That in a rotationally fixed arrangement of the eccentric disc (16) on the drive shaft (2) also separately next to the eccentric disc (16) on the drive shaft (2) rotationally fixed an inner ring of an overrunning clutch (21) with a on the associated outer ring of the overrunning clutch (21) acting electric drive (22) is arranged, the rotor rigid with the outer ring of the overrunning clutch (21) and the stator rigidly with the Pump housing (1) is connected, wherein at the same time between the drive shaft (2) and the drive wheel (23) an overrunning clutch (21) is arranged. Vacuum pump according to claim 1, characterized in that in the orbiter (6) a support disk (15) and decentralized a guide web (13) are arranged. Vacuum pump according to claim 2, characterized in that in the orbiter (6) a guide web (13) and a plurality of support webs (17) are arranged decentrally. Vacuum pump according to claim 1, characterized in that in the working chamber (3) a lubricant, and between the cylindrical inner wall (4) of the working chamber (3) and the cylinder jacket (7) of the orbiter (6) has a working gap (12) of 0, 05 mm to 0.8 mm are arranged, whereby due to the circulation of the orbiter (6) in the working chamber (3) of this working gap (12) completely closed with lubricant, in oil-lubricated series with oil. Vacuum pump according to claim 1, characterized in that the bearing pin (5) rotatably arranged in a provided with a centering pin adapter (19).

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