EP2662570A1 - Vacuum pump - Google Patents
Vacuum pump Download PDFInfo
- Publication number
- EP2662570A1 EP2662570A1 EP13002418.5A EP13002418A EP2662570A1 EP 2662570 A1 EP2662570 A1 EP 2662570A1 EP 13002418 A EP13002418 A EP 13002418A EP 2662570 A1 EP2662570 A1 EP 2662570A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- drive shaft
- orbiter
- working chamber
- vacuum pump
- eccentric disc
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000000314 lubricant Substances 0.000 claims description 5
- 238000004519 manufacturing process Methods 0.000 description 12
- 238000007789 sealing Methods 0.000 description 6
- 239000000463 material Substances 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000033001 locomotion Effects 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 238000012423 maintenance Methods 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000000712 assembly Effects 0.000 description 2
- 238000000429 assembly Methods 0.000 description 2
- 230000005489 elastic deformation Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 229910000906 Bronze Inorganic materials 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 239000010974 bronze Substances 0.000 description 1
- KUNSUQLRTQLHQQ-UHFFFAOYSA-N copper tin Chemical compound [Cu].[Sn] KUNSUQLRTQLHQQ-UHFFFAOYSA-N 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000002689 soil Substances 0.000 description 1
- 230000009897 systematic effect Effects 0.000 description 1
Images
Classifications
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- 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
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- 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
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- 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 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 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 Exzenternavkolben 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.
- FIGS. 2A . 2B and 2C is one of the possible embodiments of the solution according to the invention shown.
- 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.
- FIG. 2B is the vacuum pump according to the invention, according to the Figure 2 A shown in a partial section.
- FIGS. 2A and 2B 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.
- 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.
- 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.
- 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.
- FIGS. 3A and 3B is shown another of the possible embodiments of the inventive solution.
- 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.
- FIG. 3B is the vacuum pump according to the invention according to the FIG. 3A shown in the side view.
- 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.
- 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.
- FIGS. 4A and 4B Now, another of the possible embodiments of the solution according to the invention is shown.
- 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.
- FIG. 4B shows the vacuum pump according to the invention according to the FIG. 4A in the side view in section.
- 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.
- FIGS. 5A and 5B show a further of the possible embodiments of the solution according to the invention.
- 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.
- FIG. 5A 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.
- 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.
- 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.
- 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.
- 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 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 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.
- 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.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
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
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
Aus der
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
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
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
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
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 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.
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
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.It is essential to the invention that, in the design presented in this figure, an oil-lubricated design is arranged in the working
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
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
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
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
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.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.
Dabei zeichnet sich diese in der
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
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
In den
Die
In der
Die Seitenansicht der erfindungsgemäßen Vakuumpumpe nach den
Diese in den
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
Neben den, analog zur Ausführung gemäß
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
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
In den
Die
In der
Diese in den
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
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
In den
Die
Die
Für diese in den
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
Die
Die
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
Die Einzelheit X der erfindungsgemäße Vakuumpumpe nach
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
In der
Die
Dabei ist starr auf der Antriebswelle 2 ein Antriebsrad 23, z.B. ein Kettenrad, oder eine Riemenscheibe, angeordnet.In this case, rigidly on the
Diese in der
Mittels des Elektroantriebes 22 kann die Exzenterscheibe 16, infolge des erfindungsgemäß angeordneten Überholfreilaufes 21, die Drehzahl des Antriebsrades 23 "überholen".By means of the
In der
Diese in der
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
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
Diese in der
Selbstverständlich kann auch bei der in der
In den
Die
Die
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"
Die
In der
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
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
Erfindungsgemäß ist zentrisch und drehfest an dieser zweiten Exzenterscheibe 16, dem Orbiter 6 gegenüberliegend, eine das Pumpengehäuse 1 überragende weiteren Antriebswelle 2 angeordnet. Die
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 I of the vacuum pump according to the invention presented here results from the forcibly guided movement in its course and contactless along the
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 input speed is inevitably always only in the range of 3,500 rev / min.
Die
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
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.
- 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)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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DE201210009419 DE102012009419B3 (en) | 2012-05-11 | 2012-05-11 | "Vacuum pump" |
Publications (2)
Publication Number | Publication Date |
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EP2662570A1 true EP2662570A1 (en) | 2013-11-13 |
EP2662570B1 EP2662570B1 (en) | 2015-12-09 |
Family
ID=48236658
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP13002418.5A Not-in-force EP2662570B1 (en) | 2012-05-11 | 2013-05-07 | Vacuum pump |
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EP (1) | EP2662570B1 (en) |
DE (1) | DE102012009419B3 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN113217381A (en) * | 2020-01-21 | 2021-08-06 | 尼得科Gpm有限公司 | Orbital vacuum pump capable of idle running |
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DE102014202979A1 (en) | 2014-02-18 | 2015-08-20 | Volkswagen Aktiengesellschaft | pump |
DE102015010846B4 (en) | 2015-08-19 | 2017-04-13 | Nidec Gpm Gmbh | Electric motor driven vacuum pump |
CN106050648B (en) * | 2016-07-25 | 2018-08-17 | 王鼎兴 | Disc pump |
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KR100321687B1 (en) * | 1998-04-29 | 2002-03-18 | 김천경 | Fluid pump |
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- 2012-05-11 DE DE201210009419 patent/DE102012009419B3/en not_active Expired - Fee Related
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DE426755C (en) | 1926-03-18 | Johan Hjalmar Syrjaenen | Sealing of the drive shaft of rotary lobe pumps for liquids or gases | |
AT200247B (en) | 1954-07-21 | 1958-10-25 | Franz Zgoll | Rotary lobe pump |
FR1346509A (en) | 1962-11-27 | 1963-12-20 | Mechanical device intended for the suction and delivery or compression of fluids | |
DE1915574A1 (en) | 1968-03-29 | 1969-10-09 | Peter Sadler | Rotary piston pump |
DE2262574A1 (en) | 1972-12-21 | 1974-06-27 | Theisen Alois | SELF-PRIMING ROTARY LISTON PUMP |
DE102006016791B4 (en) | 2006-04-10 | 2008-01-31 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | vacuum pump |
WO2009021474A1 (en) * | 2007-08-11 | 2009-02-19 | Geräte-und Pumpenbau GmbH Dr. Eugen Schmidt | Pendulum slide vacuum pump |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN113217381A (en) * | 2020-01-21 | 2021-08-06 | 尼得科Gpm有限公司 | Orbital vacuum pump capable of idle running |
Also Published As
Publication number | Publication date |
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EP2662570B1 (en) | 2015-12-09 |
DE102012009419B3 (en) | 2013-07-25 |
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