EP0692634B1 - Rotary piston pump - Google Patents
Rotary piston pump Download PDFInfo
- Publication number
- EP0692634B1 EP0692634B1 EP95108460A EP95108460A EP0692634B1 EP 0692634 B1 EP0692634 B1 EP 0692634B1 EP 95108460 A EP95108460 A EP 95108460A EP 95108460 A EP95108460 A EP 95108460A EP 0692634 B1 EP0692634 B1 EP 0692634B1
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- EP
- European Patent Office
- Prior art keywords
- vane
- rotor
- piston pump
- rotary piston
- pump according
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0881—Construction of vanes or vane holders the vanes consisting of two or more parts
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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
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
Definitions
- the invention relates to a rotary lobe pump with an inevitably guided slide of unchangeable length according to the preamble of patent claim 1.
- Such a rotary lobe pump can be driven by a vehicle drive machine and can convey a fluid, in particular air for generating vacuum or compressed air for vehicle auxiliary units.
- Such a pump is known from DE-A1-25 23 190, in which a single slide is slidably guided in a guide slot of the rotor.
- the housing is designed with a cross-section that is circumscribed by a self-contained curve according to the information from R. Plank and J. Kuprianoff: Circulation Compressors for Chillers, VDI-Zeitschrift Volume 79, No. 12 from 03/23/35, p. 369 to 372 (basis of calculation and kinematic analysis of a rotary lobe compressor with an inevitably guided slide of constant length ').
- DE-A1-38 13 132 is a compressor which no longer meets today's standards with regard to a construction suitable for production.
- a pump according to the preamble of claim 1 is described in document FR-E-31237.
- Fig. 1 shows a rotary lobe pump 1 with an open cylinder pot 2, which provides an insight into a pump chamber 3, in which a rotor 4 is arranged with a slide 7 of unchangeable length guided in a slot 6 running over the center of the rotor 5 5.
- the rotary lobe pump 1 is intended to be driven by a vehicle drive machine, for example an internal combustion engine, to provide vacuum for vehicle auxiliary units.
- the cylinder pot 2 has a cross-sectional area which is characteristic of this type of pump and which is circumscribed by a closed cylinder wall curve 8, the secants 9 of which intersect the center of rotation 5 of the rotor are substantially equal to the slide length between the points of contact of the slide 7 with the curve 8, the cylinder pot 2, a flange body 10 and the rotor 4 delimit the pump chamber 3, into which air is pushed by the slide 7 on the one hand and air is pushed out of the slide 7 on the other hand.
- the pump 1 is connected to an oil circuit system, not shown, here it can be that of the drive machine, the oil of which is conveyed with the air and lubricates and seals the pump.
- the slide 7 has at its ends a pivot bearing 11, each of which supports a slide shoe 12, the theoretical slide length in the position in which the cylinder, rotor and slide symmetry axes lie one above the other, plus the slide length measured via the pivot bearings 11 plus twice the thickness of the sliding block 13 between the pivot wall and the cylinder wall.
- the sliding shoes 12 have a curvature of the outer surface which lies between the curvature of the outer rotor wall 14 and the greatest curvature of the cylinder wall curve 8.
- the cylinder cup 2 is designed as a deep-drawn pressed part and is screwed against the flange body 10 by means of an integrally formed flange collar 15.
- the slide length is advantageously shorter than the theoretical slide length between 0.01 and 1%, so that there is a gap between the slide shoe and cylinder wall, and the curvature of the outer slide shoe surface is equal to or slightly larger than the largest curvature of the cylinder wall curve 8, whereby the sliding shoe surface at the ends of the curvature merges into a chamfer or rounding, which is shown as radius 16, so that the sliding shoe 12 is symmetrical and can be installed to the left or to the right.
- This measure enables the pump 1 to be operated in both directions of rotation.
- the slide 7 with the slide shoe 12 dips into a rotor recess 17.
- a recess 18 arranged on each side of the slide shoe 12 forms a chamber within the rotor recess 17 for receiving lubricating oil, which rotates in front of the slide shoe 12 as a so-called oil roller when the oil circulation system is connected.
- the slide shoe 12 has a width 19 which corresponds approximately to three to five times the slide thickness 20. So that the slide pivot bearing 11 can work directly out of the slide blank, d. H. the maximum possible slide pivot bearing diameter is then equal to the slide thickness.
- the gap formed by the shortened slide length is changed to a convergent gap 21, which causes the build-up of oil pressures or a lubricating oil film between the slide shoe and cylinder surface during air delivery and oil lubrication becomes.
- Fig. 2 shows a section through the pump 1, from which the flange body 10 can be seen, in which the rotor 4 is rotatably mounted with a pin 22. It is provided that, starting from the cylinder wall, the cylinder pot 2 has a bead 24 which runs into a cylinder end wall 23.
- the rotor 5 has a recess 25 which is closed by the cylinder end wall 23 and is connected to the oil circulation system by the hollow bearing journal 22.
- the enlarging pump chamber 3 has a suction opening 26 with a suction valve 27.
- An outlet opening 28 is arranged as close as possible before the dead center 29 of the slide-in movement and opens via a pressure valve 30 into a recess 31 in the flange body 10 which is open towards the drive machine.
- the pressure valve 30 is advantageously designed as a tongue valve, the fastening surface 32 and the valve closing surface 33 of which are connected in one piece to the spring strip 34, the center line 35 of which, as a straight line, intersects the center of gravity of the fastening and valve surface, as can be seen from FIG. 3, which is a view from below 1 and the arrangement and design of the pressure valve 30. With this design, the reed valve is only loaded by pure bending, so that a long service life can be expected.
- FIGS. 4 to 6 show alternative embodiments of the bead 24 according to FIGS. 1 and 2.
- Fig. 4 shows an embodiment in which the bead 24 is formed obliquely upwards, Fig. 5 to the right and Fig. 6 upwards.
- FIG. 7 shows an enlargement from FIG. 1, in which the cylinder wall curve 8, the rotor 4, the slide 7 with the rotary bearing 11 and the slide shoe 12 are shown.
- the convergent gap 21 would be set by pivoting on the pivot bearing 11 under the supporting force between the slide shoe 12 and the pivot bearing 11 and the slide shoe and cylinder surface at the point of contact.
- the new rotary lobe pump has an improved volumetric efficiency, less wear and is suitable for economical production.
- the pump 1 shown is provided for emptying the vacuum container (not shown), the air extracted from it being conveyed with the lubricating oil via the recess 31 into the drive machine.
- the pump 1 can also be operated as a compressor for providing compressed air, in which case the outlet opening 28 or the recess 31 is connected to a compressed air container and the suction opening 26 to the atmosphere.
- a suitable material pairing between cylinder pot 2 and sliding shoe 12 an unlubricated operation can also be achieved.
- the pump according to the invention is also suitable for conveying a liquid, in which case a corresponding arrangement of the suction and outlet openings 25, 26 must be made for conveying without internal compression.
Description
Die Erfindung betrifft eine Drehkolbenpumpe mit einem zwangsläufig geführten Schieber unveränderlicher Länge nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a rotary lobe pump with an inevitably guided slide of unchangeable length according to the preamble of patent claim 1.
Eine solche Drehkolbenpumpe kann von einer Fahrzeugantriebsmaschine angetrieben werden und ein Fluid fördern, insbesondere Luft zur Vakuum- oder Drucklufterzeugung für Fahrzeughilfsaggregate.Such a rotary lobe pump can be driven by a vehicle drive machine and can convey a fluid, in particular air for generating vacuum or compressed air for vehicle auxiliary units.
Aus der DE-A1-25 23 190 ist eine solche Pumpe bekannt, bei der ein einziger Schieber in einem Führungsschlitz des Rotors gleitend geführt ist. Das Gehäuse ist mit einem Querschnitt ausgeführt, das von einer in sich geschlossenen Kurve umschrieben ist gemäß den Angaben aus R. Plank und J. Kuprianoff: Umlaufverdichter für Kältemaschinen, VDI-Zeitschrift Band 79, Nr. 12 vom 23.03.35, S. 369 bis 372 (Berechnungsgrundlage und kinematische Analyse eines Drehkolbenverdichters mit zwangsläufig geführtem Schieber unveränderlicher Länge').Such a pump is known from DE-A1-25 23 190, in which a single slide is slidably guided in a guide slot of the rotor. The housing is designed with a cross-section that is circumscribed by a self-contained curve according to the information from R. Plank and J. Kuprianoff: Circulation Compressors for Chillers, VDI-Zeitschrift Volume 79, No. 12 from 03/23/35, p. 369 to 372 (basis of calculation and kinematic analysis of a rotary lobe compressor with an inevitably guided slide of constant length ').
Durch Ausgestaltung des Gehäusequerschnitts in der dort angegebenen Form als eine Pascalsche Spirale und durch die spitze Ausgestaltung der Schieberenden wird die Konstruktion eines Drehkolbenverdichters mit nur einem Schieber geometrisch möglich.By designing the housing cross-section in the form given there as a Pascal spiral and by the pointed design of the slide ends, the design of a rotary piston compressor with only one slide is geometrically possible.
Der Nachteil dieses Verdichters ist darin zu sehen, daß sich Gehäuse und Rotor im Bereich des unteren Totpunktes, in dem das eine Schieberende vollständig in den Rotor eingefahren ist, nur linienmäßig berühren. Bei einer solch kurzen Dichtstrecke kommt es in diesem Bereich zu einer Undichtigkeit zwischen Druck- und Saugzone der Pumpe mit einer dementsprechenden Verschlechterung des volumetrischen Wirkungsgrades.The disadvantage of this compressor can be seen in the fact that the housing and the rotor only touch one another linearly in the area of the bottom dead center, in which the one slide end is fully inserted into the rotor. With such a short sealing section, there is a leak in this area between the pressure and suction zones of the pump, with a corresponding deterioration in the volumetric efficiency.
Aus der DE-A1-38 13 132 ist daher vorgesehen, daß in Abweichung von der Pascalschen Spirale der Krümmungsradius des Gehäusequerschnitts in dem Dichtbereich im wesentlichen gleich dem Krümmungsradius des Rotors ausgeführt ist, womit der Dichtspalt länger wird.From DE-A1-38 13 132 it is therefore provided that, in deviation from the Pascal spiral, the radius of curvature of the housing cross section in the sealing region is essentially the same as the radius of curvature of the rotor, thus making the sealing gap longer.
Nun ist jedoch der volumetrische Wirkungsgrad eines solchen Verdichters auch durch die zwischen Schieber und Zylinderwand bestehende kurze Dichtstrecke beeinträchtigt, und diese Beeinträchtigung liegt hier sogar zweifach vor, da der Schieber zwei Berührungspunkte mit der Zylinderwandung hat.Now, however, the volumetric efficiency of such a compressor is also impaired by the short sealing distance existing between the slide and the cylinder wall, and this impairment is present here twice, since the slide has two points of contact with the cylinder wall.
Darüber hinaus liegt mit dem Gegenstand der DE-A1-38 13 132 ein Verdichter vor, der den heutigen Maßstäben bezüglich einer fertigungsgerechten Konstruktion nicht mehr genügt.In addition, the subject of DE-A1-38 13 132 is a compressor which no longer meets today's standards with regard to a construction suitable for production.
Eine Pumpe nach dem Oberbegriff des Anspruchs 1 ist im Dokument FR-E-31237 beschrieben.A pump according to the preamble of claim 1 is described in document FR-E-31237.
Es ist daher Aufgabe der Erfindung, ausgehend von einer gattungsgemäßen Drehkolbenpumpe, diese derart zu gestalten, daß der volumetrische Wirkungsgrad gegenüber anderen Pumpen verbessert, eine vorteilhafte kostensparende Fertigung und eine lange Lebensdauer erreicht werden.It is therefore an object of the invention, starting from a generic rotary lobe pump, to design it in such a way that the volumetric efficiency is improved compared to other pumps, advantageous cost-saving production and a long service life are achieved.
Diese Aufgabe ist mit den im Kennzeichen des Anspruchs 1 angegebenen Merkmalen gelöst worden. Vorteilhafte Weiterbildungen sind mit den Unteransprüchen angegeben.This object has been achieved with the features specified in the characterizing part of claim 1. Advantageous further developments are specified in the subclaims.
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird nachfolgend beschrieben.An embodiment of the invention is shown in the drawing and is described below.
Es zeigt:
- Fig. 1 einen Einblick in eine aufgeschnittene Drehkolbenpumpe,
- Fig. 2 einen Längsschnitt der Pumpe nach Fig. 1,
- Fig. 3 eine Druntersicht der Fig. 1,
- Fig. 4 bis 6 Ausführungen alternativer Art einer Einzelheit aus Fig. 1,
- Fig. 7 eine Vergrößerung aus Fig. 1.
- 1 shows an insight into a cut-open rotary lobe pump,
- 2 shows a longitudinal section of the pump according to FIG. 1,
- 3 is a bottom view of FIG. 1,
- 4 to 6 versions of an alternative type of detail from FIG. 1,
- 7 is an enlargement of FIG. 1st
Fig. 1 zeigt eine Drehkolbenpumpe 1 mit einem geöffneten Zylindertopf 2, der einen Einblick in eine Pumpenkammer 3 gewährt, in der ein Rotor 4 mit einem in einem über die Rotordrehmitte 5 verlaufenden Schlitz 6 geführten Schieber 7 unveränderlicher Länge angeordnet ist. Die Drehkolbenpumpe 1 soll durch eine Fahrzeugantriebsmaschine, zum Beispiel eine Brennkraftmaschine, zur Bereitstellung von Vakuum für Fahrzeughilfsaggregate angetrieben werden.Fig. 1 shows a rotary lobe pump 1 with an
Der Zylindertopf 2 weist eine für diesen Pumpentyp charakteristische Querschnittsfläche auf, die von einer geschlossenen Zylinderwandkurve 8 umschrieben ist, deren die Rotordrehmitte 5 schneidende Sekanten 9 im wesentlichen gleich der Schieberlänge zwischen den Berührungspunkten des Schiebers 7 mit der Kurve 8 sind, wobei der Zylindertopf 2, ein Flanschkörper 10 und der Rotor 4 die Pumpenkammer 3 begrenzen, in die einerseits des Schiebers 7 Luft hinein und aus der andererseits des Schiebers 7 Luft herausgedrückt wird. Die Pumpe 1 ist an ein nicht dargestelltes Ölkreislaufsystem angeschlossen, hier kann es sich um das der Antriebsmaschine handeln, deren Öl mit der Luft gefördert wird und die Pumpe schmiert und abdichtet.The
Der Schieber 7 weist an seinen Enden jeweils ein Drehlager 11 auf, das jeweils einen Gleitschuh 12 lagert, wobei sich die theoretische Schieberlänge in der Stellung, in der Zylinder-, Rotor- und Schiebersymmetrieachse übereinanderliegen, addiert aus der über die Drehlager 11 gemessenen Schieberlänge plus zweimal Gleitschuhwanddicke 13 zwischen Drehlager- und Zylinderwand.The
Die Gleitschuhe 12 weisen eine Krümmung der äußeren Fläche auf, die zwischen der Krümmung der äußeren Rotorwand 14 und der größten Krümmung der Zylinderwandkurve 8 liegt.The
Bei dieser Pumpe 1 ist der Zylindertopf 2 als Tiefziehpreßteil ausgebildet und mittels eines angeformten Flanschkragens 15 gegen den Flanschkörper 10 geschraubt.In this pump 1, the
Die Schieberlänge ist vorteilhafterweise gegenüber der theoretischen Schieberlänge zwischen 0,01 und 1 % kürzer ausgeführt, so daß sich zwischen Gleitschuh- und Zylinderwand ein Spalt ergibt, und die Krümmung der äußeren Gleitschuhfläche gleich der oder geringfügig größer der größten Krümmung der Zylinderwandkurve 8 ausgeführt, wobei die Gleitschuhfläche an den Enden der Krümmung in eine Fase oder Rundung übergeht, die als Radius 16 dargestellt ist, so daß der Gleitschuh 12 symmetrisch ist und links- oder rechtsherum eingebaut werden kann.
Durch diese Maßnahme kann die Pumpe 1 in beide Drehrichtungen betrieben werden. Bei einem Umlauf des Rotors 4 taucht der Schieber 7 mit Gleitschuh 12 in eine Rotorausnehmung 17 ein. Eine an jeder Seite des Gleitschuhes 12 angeordnete Ausnehmung 18 bildet innerhalb der Rotorausnehmung 17 eine Kammer zur Aufnahme von Schmieröl, das bei angeschlossenem Ölkreislaufsystem vor dem Gleitschuh 12 als sogenannte Ölwalze umläuft.The slide length is advantageously shorter than the theoretical slide length between 0.01 and 1%, so that there is a gap between the slide shoe and cylinder wall, and the curvature of the outer slide shoe surface is equal to or slightly larger than the largest curvature of the
This measure enables the pump 1 to be operated in both directions of rotation. When the
Wie aus Fig. 1 ersichtlich, ist vorgesehen, daß der Gleitschuh 12 eine Breite 19 aufweist, die in etwa der drei- bis fünffachen Schieberdicke 20 entspricht. Damit läßt sich das Schieberdrehlager 11 direkt aus dem Schieberrohling herausarbeiten, d. h. der maximal mögliche Schieberdrehlagerdurchmesser ist dann gleich groß der Schieberdicke. Durch Schwenken des Gleitschuhs 12 auf dem Schieberdrehlager 11, unter Auswandern des Berührungspunktes, wird der durch die verkürzte Schieberlänge gebildete Spalt zu einem konvergenten Spalt 21 verändert, wobei bei Luftförderung und Ölschmierung hierdurch der Aufbau von Öldrücken bzw. eines Schmierölfilmes zwischen Gleitschuh- und Zylinderfläche bewirkt wird.As can be seen from FIG. 1, it is provided that the
Fig. 2 zeigt einen Schnitt durch die Pumpe 1, aus dem der Flanschkörper 10 ersichtlich ist, in dem der Rotor 4 mit einem Zapfen 22 drehbar gelagert ist. Es ist vorgesehen, daß der Zylindertopf 2 ausgehend von der Zylinderwand eine in eine Zylinderstirnwand 23 auslaufende Sicke 24 aufweist.Fig. 2 shows a section through the pump 1, from which the
Hierdurch ist eine vorteilhafte Herstellung und eine ausreichende Versteifung des Zylindertopfes 2 gegeben. Der Rotor 5 weist eine Ausnehmung 25 auf, die von der Zylinderstirnwand 23 verschlossen und durch den hohl ausgeführten Lagerzapfen 22 mit dem Ölkreislaufsystem verbunden ist.This results in an advantageous production and a sufficient stiffening of the
Wie aus Fig. 1 ersichtlich, weist die sich vergrößernde Pumpenkammer 3 eine Ansaugöffnung 26 mit einem Saugventil 27 auf.As can be seen from FIG. 1, the
Eine Auslaßöffnung 28 ist so nah wie möglich vor dem Totpunkt 29 der Schiebereinfahrbewegung angeordnet und mündet über ein Druckventil 30 in eine Ausnehmung 31 des Flanschkörpers 10 ein, die zu der Antriebsmaschine hin offen ist.An outlet opening 28 is arranged as close as possible before the
Vorteilhafterweise ist das Druckventil 30 als Zungenventil ausgebildet, dessen Befestigungsfläche 32 und dessen Ventilschließfläche 33 über einen einstückig mit diesem ausgeführten Federstreifen 34 verbunden sind, dessen Mittellinie 35 als Gerade den Befestigungs- und Ventilflächenschwerpunkt schneidet, wie aus Fig. 3 ersichtlich ist, die eine Druntersicht der Fig. 1 bzw. die Anordnung und Ausführung des Druckventils 30 zeigt. Durch diese Ausbildung wird das Zungenventil nur durch reine Biegung belastet, so daß eine lange Lebensdauer zu erwarten ist.The
In den Fig. 4 bis 6 sind alternative Ausführungsformen der Sicke 24 nach Fig. 1 bzw. 2 dargestellt. Fig. 4 zeigt eine Ausführung bei der die Sicke 24 schräg nach oben, Fig. 5 nach rechts und Fig. 6 nach oben ausgebildet ist.4 to 6 show alternative embodiments of the
Fig. 7 zeigt eine Vergrößerung aus Fig. 1, in der die Zylinderwandkurve 8, der Rotor 4, der Schieber 7 mit Drehlager 11 und Gleitschuh 12 dargestellt sind. Bei in Pfeilrichtung drehendem Rotor 4 würde sich durch Schwenken auf dem Drehlager 11 unter der Abstützkraft zwischen Gleitschuh 12 und Drehlager 11 sowie Gleitschuh- und Zylinderfläche im Berührungspunkt der konvergente Spalt 21 einstellen.FIG. 7 shows an enlargement from FIG. 1, in which the
Die neue Drehkolbenpumpe hat einen verbesserten volumetrischen Wirkungsgrad, geringeren Verschleiß und eignet sich für eine wirtschaftliche Fertigung.The new rotary lobe pump has an improved volumetric efficiency, less wear and is suitable for economical production.
Die dargestellte Pumpe 1 ist für die Entleerung des nicht dargestellten Vakuumbehälters vorgesehen, wobei die aus diesem abgesaugte Luft mit dem Schmieröl über die Ausnehmung 31 in die Antriebsmaschine gefördert wird. Die Pumpe 1 kann jedoch auch als Kompressor zur Bereitstellung von Druckluft betrieben werden, wobei dann die Auslaßöffnung 28 bzw. die Ausnehmung 31 an einen Druckluftbehälter und die Ansaugöffnung 26 an die Atmosphäre angeschlossen ist. Bei geeigneter Materialpaarung zwischen Zylindertopf 2 und Gleitschuh 12 ist auch ein ungeschmierter Betrieb erreichbar.The pump 1 shown is provided for emptying the vacuum container (not shown), the air extracted from it being conveyed with the lubricating oil via the
Die erfindungsgemäße Pumpe eignet sich auch für die Förderung einer Flüssigkeit, wobei dann eine entsprechende Anordnung der Ansaug- und Auslaßöffnung 25,26 für eine Förderung ohne innere Verdichtung getroffen werden muß.The pump according to the invention is also suitable for conveying a liquid, in which case a corresponding arrangement of the suction and
Claims (9)
- Rotary piston pump with a positively guided vane of an invariable length, consisting of a flanged body, a rotor mounted in the latter, the vane, which is guided in a slot extending over the rotational centre of the rotor, and a cylindrical pot whose cross-sectional area is circumscribed by a closed cylinder wall curve whose secants, which intersect the rotational centre of the rotor, are substantially equal to the vane length between the points of contact of the vane with the curve, characterised in that at each of its ends the vane (7) comprises a pivot bearing (11) which in each case supports a sliding block (12), the theoretical vane length being the sum of the vane length measured over the pivot bearings (11) plus twice the sliding block wall thickness (13) between the pivot bearing wall and the cylinder wall in the position in which the axes of symmetry of the cylinder, rotor and vane are superimposed, and that the curvature of the outer surface of the sliding blocks (12) lies between the curvature of the outer rotor wall (14) and the maximum curvature of the cylinder wall curve (8).
- Rotary piston pump according to claim 1, characterised in that the cylindrical pot (2) is formed as a deep-drawn part and is screwed against the flanged body (10) by means of a moulded-on flanged collar (15).
- Rotary piston pump according to claim 1 or 2,
characterised in that the vane length is between 0.01 and 1 % shorter than the theoretical vane length, the curvature of the outer sliding block surface is equal to or slightly greater than the maximum curvature of the cylinder wall curve (8), and the sliding block surface passes at the ends of the curvature into a chamfer or rounded portion (16). - Rotary piston pump according to claim 3, characterised in that the sliding block (12) is of a width (19) which corresponds approximately to three to five times the vane thickness (20) and, by pivoting on the pivot bearing (11) of the vane, with the point of contact shifting, the gap produced by shortening the vane is changed into a convergent gap (21) between the sliding block surface and the cylinder surface.
- Rotary piston pump according to one of the preceding claims, characterised in that, starting from the cylinder wall curve (8), the cylindrical pot (2) comprises a bead (24) which terminates in an end wall (23) of the cylinder.
- Rotary piston pump according to one of the preceding claims, characterised in that the rotor (4) comprises a recess (25) which is closed by the end cylinder wall (23) and communicates with an oil circulation system via a hollow pivot pin (22).
- Rotary piston pump according to claim 6, characterised in that the sliding block (12) moves into a rotor recess (17) and comprises a recess (18) which forms within the rotor recess (17) a chamber for accommodating lubricating oil.
- Rotary piston pump according to one of the preceding claims, characterised in that an outlet opening (28) is disposed as near as possible before the dead centre (29) of the vane entry movement and leads via a delivery valve (30) into a recess (31) in the flanged body (10), which recess is open towards the driving engine.
- Rotary piston pump according to claim 8, characterised in that the delivery valve (30) is formed as a tongue valve, the mounting face (32) and the valve closing face (33) of which are connected via a spring strip (34), which is integral with these and the centre line (35) of which, as a straight line, intersects the centre of gravity of the mounting and valve faces.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4425293 | 1994-07-16 | ||
| DE4425293A DE4425293A1 (en) | 1994-07-16 | 1994-07-16 | Rotary lobe pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0692634A1 EP0692634A1 (en) | 1996-01-17 |
| EP0692634B1 true EP0692634B1 (en) | 1997-09-03 |
Family
ID=6523434
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP95108460A Expired - Lifetime EP0692634B1 (en) | 1994-07-16 | 1995-06-02 | Rotary piston pump |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US5779463A (en) |
| EP (1) | EP0692634B1 (en) |
| JP (1) | JP4037919B2 (en) |
| DE (2) | DE4425293A1 (en) |
| ES (1) | ES2106597T3 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4305238B2 (en) * | 2004-03-23 | 2009-07-29 | ブラザー工業株式会社 | Pump and ink jet printer equipped with the pump |
| DE102004015083A1 (en) * | 2004-03-25 | 2005-10-13 | Endress + Hauser Wetzer Gmbh + Co Kg | Sampler for taking a defined sample amount of a fluid medium from a sample sampling point |
| GB0406897D0 (en) * | 2004-03-26 | 2004-04-28 | Wabco Automotive Uk Ltd | Vacuum pump oil pressure relief |
| EP2173971B1 (en) * | 2007-07-03 | 2016-12-21 | O.M.P. Officine Mazzocco Pagnoni S.r.l. | Vacuum pump for a motor vehicle engine |
| JP5421223B2 (en) * | 2009-12-29 | 2014-02-19 | 株式会社ヴァレオジャパン | Vane type compressor |
| CN102536832A (en) * | 2012-03-21 | 2012-07-04 | 重庆云海机械制造有限公司 | Vacuum pump |
| CN104131976A (en) * | 2014-08-18 | 2014-11-05 | 王喜来 | Rotation type air compressor |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR31237E (en) * | 1927-01-26 | |||
| US813024A (en) * | 1905-02-23 | 1906-02-20 | Jacob H Renner | Rotary engine. |
| US902501A (en) * | 1907-11-20 | 1908-10-27 | Fritz W Machlet | Pump, &c. |
| US1339347A (en) * | 1919-08-02 | 1920-05-04 | Jackson Harry | Pump |
| US3647328A (en) * | 1970-05-25 | 1972-03-07 | Crane Co | Slipper vane and valve combination for vane-type fluid pump |
| US3723034A (en) * | 1971-10-26 | 1973-03-27 | Battelle Development Corp | Vane end and tip assembly |
| IT1012857B (en) | 1974-05-28 | 1977-03-10 | Pirelli | FINALIZATION IN THE MANUFACTURE OF BUILT-IN ELECTRICAL CABLES |
| US4144005A (en) * | 1977-12-01 | 1979-03-13 | General Motors Corporation | Rotary through vane compressor |
| DE3734573C2 (en) * | 1986-10-18 | 1998-12-17 | Barmag Barmer Maschf | Vane vacuum pump |
| DE3813132A1 (en) | 1987-05-19 | 1988-12-15 | Barmag Barmer Maschf | Vane-cell pump |
| DE3832042C2 (en) * | 1987-10-05 | 1997-08-14 | Barmag Barmer Maschf | Vane pump |
| DE4018509A1 (en) * | 1989-06-24 | 1991-01-10 | Barmag Barmer Maschf | Vane cell pump with vanes in axial slots - uses method of connecting rotor to bearing shaft |
-
1994
- 1994-07-16 DE DE4425293A patent/DE4425293A1/en not_active Withdrawn
-
1995
- 1995-06-02 ES ES95108460T patent/ES2106597T3/en not_active Expired - Lifetime
- 1995-06-02 DE DE59500589T patent/DE59500589D1/en not_active Expired - Lifetime
- 1995-06-02 EP EP95108460A patent/EP0692634B1/en not_active Expired - Lifetime
- 1995-07-13 JP JP17748795A patent/JP4037919B2/en not_active Expired - Lifetime
- 1995-07-14 US US08/502,820 patent/US5779463A/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| ES2106597T3 (en) | 1997-11-01 |
| JP4037919B2 (en) | 2008-01-23 |
| JPH0849666A (en) | 1996-02-20 |
| EP0692634A1 (en) | 1996-01-17 |
| DE4425293A1 (en) | 1996-01-18 |
| DE59500589D1 (en) | 1997-10-09 |
| US5779463A (en) | 1998-07-14 |
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