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EP1076760A1 - Rotating piston machine with three-blade rotors - Google Patents

Rotating piston machine with three-blade rotors

Info

Publication number
EP1076760A1
EP1076760A1 EP99948559A EP99948559A EP1076760A1 EP 1076760 A1 EP1076760 A1 EP 1076760A1 EP 99948559 A EP99948559 A EP 99948559A EP 99948559 A EP99948559 A EP 99948559A EP 1076760 A1 EP1076760 A1 EP 1076760A1
Authority
EP
European Patent Office
Prior art keywords
rotors
piston machine
chamber
rotary piston
machine 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.)
Granted
Application number
EP99948559A
Other languages
German (de)
French (fr)
Other versions
EP1076760B1 (en
Inventor
Reinhard Garczorz
Fritz-Martin Scholz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Rietschle Werner GmbH and Co KG
Werner Rietschle GmbH and Co KG
Original Assignee
Rietschle Werner GmbH and Co KG
Werner Rietschle GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Rietschle Werner GmbH and Co KG, Werner Rietschle GmbH and Co KG filed Critical Rietschle Werner GmbH and Co KG
Publication of EP1076760A1 publication Critical patent/EP1076760A1/en
Application granted granted Critical
Publication of EP1076760B1 publication Critical patent/EP1076760B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • 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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/122—Arrangements for supercharging the working space
    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/123—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially or approximately radially from the rotor body extending tooth-like elements, co-operating with recesses in the other rotor, e.g. one tooth

Definitions

  • the invention relates to a rotary piston machine with a chamber formed in a housing, in which three-bladed rotors rotate in opposite directions about parallel, mutually offset axes and mesh without contact and form separate cells with the peripheral wall of the chamber.
  • Blower known.
  • the inlet and outlet are aligned with each other on a line that is perpendicular to the axes of the rotors.
  • the volume flow is conveyed through the interlocking wings in the chamber and pushed out at the outlet without internal compression.
  • Such a rotary lobe machine is particularly suitable as a supercharger for relatively high volume flows.
  • the invention provides a rotary lobe machine with three-bladed rotors, which works with internal compression and internal expansion and is also suitable for generating pressure and vacuum, even with relatively small volume flows.
  • the claw-like wings of the rotors together with the chamber form a suction cell which increases their volume by the rotation of the rotors and a pressure cell which reduces their volume by the rotation of the rotors. Since the rotary lobe machine works with internal compression and at the same time with internal expansion, it is suitable for the simultaneous generation of pressure and negative pressure.
  • the rotors with the chamber form two charging cells which are initially separate from one another in the course of the rotation of the rotors and which are combined with one another to form the pressure cell during the further rotation of the rotors.
  • a media stream can be fed in via the charging cells, so that a corresponding - 2 -
  • the charging cells are essentially isobar and isochoric in the pump chamber before they are combined; the medium in the charging cells experiences essentially no change in pressure and no volume when the charging cells are displaced.
  • the geometry of the rotors is determined by the requirement to simultaneously separate the cells required for the generation of pressure and vacuum in the chamber. Since the rotors interact without contact with one another and also with the peripheral wall of the chamber, no wear occurs in the region of the chamber.
  • the sealing gap between the rotors can be kept very small by optimizing their geometry; in practical versions it is only a fraction of a millimeter, so that good pressure and vacuum values are guaranteed. These values become even better with increasing operating time, since the deposits that form over time lead to a reduction in the size of the sealing gaps.
  • the rotary piston machine according to the invention is particularly suitable for use as a pump for the simultaneous generation of compressed air and
  • Vacuum In this application, it is particularly suitable for use in the paper processing industry, especially when no - separate provision or adjustment of compressed air and vacuum is required.
  • Compressed air is e.g. needed to blow on a stack of paper to support sheet separation.
  • the pulsating generation of compressed air by such a pump proves to be expedient here, since the edges of the paper can be separated more easily by compressed air which occurs intermittently. In such applications, vacuum is also required to suck up the top sheet of paper.
  • FIG. 1 shows a longitudinal section of the rotary lobe machine according to the invention
  • Figure 2 is a view along line II-II in Figure 1;
  • Figure 3 is a view along line III-III in Figure 1;
  • Figures 4a to 4h are schematic views of different rotor positions to explain the mode of operation.
  • the rotary piston machine according to the invention is described below using the example of a pump for the simultaneous generation of compressed air and vacuum. However, the invention is not restricted to such an application.
  • the single-stage pump for the simultaneous generation of compressed air and negative pressure has a housing which consists of a load-bearing central part 10, a housing cover 12 placed on one side of the central part 10, a housing ring 14 attached to the other side of the central part 10 and one on the housing ring 14 adjoining cover plate 16 there.
  • a pump chamber 18 is formed between the middle part 10, the housing ring 14 and the cover plate 16.
  • housing cover 12 and the central part 10, two shafts 20, 22 are mounted parallel to one another and offset from one another in floating ball bearings.
  • a pinion 24, 26 is seated on each shaft 20, 22.
  • the pinions 24, 26 are in meshing engagement with one another, so that the shafts 20, 22 rotate in opposite directions synchronously with one another.
  • the lower shaft 22 is led out of the housing cover 12.
  • Each of the rotors 30, 32 is adjustably attached to the associated shaft 20 and 22, respectively.
  • each rotor 30, 32 has three blades 30a and 32a, respectively.
  • the pump chamber 18 has a side view in the form of two intersecting circles, which are joined together in the form of an "8".
  • the blades 30a of the rotor 30 have a shape that is different from the shape of the blades 32a of the rotor 32.
  • the geometry of the wings 30a, 32a and the pump chamber 18 is determined so that at - 4 -
  • the rotation of the rotors 30, 32 a plurality of separate cells are formed, as explained in more detail below with reference to FIGS. 4a to 4h, in that the vanes 30a, 32a contact-free with a sealing gap of a fraction of 1 mm one above the other and along the outer circumference of the pump chamber 18 slide.
  • the cover plate 16 is provided with a series of cutouts, which are closed off from the outside by an attached closure plate 36.
  • Two pipe sockets 42, 44 are screwed into the closure plate 36.
  • the upper pipe socket 42 forms the suction connection and is connected to a recess 50 of the cover plate 16.
  • the lower pipe socket 44 forms the pressure connection and is connected to a recess 52 in the cover plate 16.
  • Two further cutouts 54a, 54b in the cover plate 16 are open to the outside and form charging ports.
  • FIG. 4a shows the rotors 30, 32 in a rotational position in which their blades 30a, 32a form a closed cell 60, which is only connected to the recess 50, with the wall of the pump chamber 18. This cell 60 enlarges in the further
  • This cell 60 is therefore a suction cell.
  • FIG. 4c shows two cells 62a, 62b which are separate from one another and which arise immediately after the state shown in FIG. 4b in that the cell 60 has been separated into two sub-cells.
  • the cell 62a assigned to the rotor 30 already borders the recess 54a, and the cell 62b assigned to the rotor 32 approaches the recess 54b.
  • the cells 62a, 62b are connected to the recesses 54a and 54b leading to the atmosphere and are filled with air and charged to ambient pressure, so that the air mass flow is increased.
  • the cells 62a, 62b are thus charging cells.
  • the pressure cell 64 reduces its volume.
  • Cell 64 compressed air is pushed out via the recess 52 to the pipe socket 44, as illustrated in FIGS. 4g and 4h.
  • the pump chamber 18 is free of any lubricant, since the rotors 30, 32 operate without contact. To the drive side is the
  • This arrangement also facilitates cooling.
  • the housing can be equipped with cooling fins, and cooling air is guided from the cover plate 16 via the housing ring 14, the middle part 10 and the housing cover 12 by a cooling fan arranged on the side of the housing cover 12.
  • a resonance damper which is matched to the operating frequency of the pump, is used to dampen the operating noise. Due to the three-wing design of the rotors, this frequency is three times the speed of the shafts 20, 22. The increased operating frequency makes it easier to accommodate the resonance damper, since its length is reduced accordingly.
  • the described flying storage of the rotors is advantageous up to a volume flow of approximately 300 m3 / h. Pumps with larger
  • Volume flow is preferably formed with rotors mounted on both sides. In this case, connections are left out in both scite plates.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)

Abstract

The aim of the invention is to provide a means of producing pressure and negative pressure simultaneously with a single-stage rotating piston machine. To this end, said rotating piston machine has a chamber (18) which is situated in a housing and which is provided with a vacuum connection, a pressure connection and a loading connection. Two three-blade rotors (30, 32) are arranged in the pump chamber (18). These rotors (30, 32) function with internal compression and internal expansion and rotate in opposite directions about parallel axes which are offset from one another, intermeshing without touching. Together with the peripheral wall of the pump chamber (18), the rotors also form cells (60, 62a, 62b, 64) which are separate from another.

Description

Drehkolbenmaschine mit dreiflügcligen Rotoren Rotary lobe machine with three-bladed rotors
Die Erfindung betrifft eine Drehkolbenmaschine mit einer in einem Gehäuse gebildeten Kammer, in der dreiflügelige Rotoren um parallele, gegeneinander versetzte Achsen gegenläufig rotieren und berührungslos kämmen sowie mit der Umfangswandung der Kammer und miteinander getrennte Zellen bilden.The invention relates to a rotary piston machine with a chamber formed in a housing, in which three-bladed rotors rotate in opposite directions about parallel, mutually offset axes and mesh without contact and form separate cells with the peripheral wall of the chamber.
Drehkolbenmaschinen mit dreiflügeligen Rotoren sind als Roots-Rotary lobe machines with three-bladed rotors are
Gebläse bekannt. Bei derartigen Maschinen sind Einlaß und Auslaß miteinander fluchtend auf einer Linie angeordnet, die senkrecht zu den Achsen der Rotoren ist. Der Volumenstrom wird durch die ineinandergreifenden Flügel in der Kammer befördert und am Auslaß ohne innere Verdichtung ausgeschoben. Eine solche Drehkolbenmaschine ist besonders als Lader für relativ hohe Volumenströme geeignet.Blower known. In such machines, the inlet and outlet are aligned with each other on a line that is perpendicular to the axes of the rotors. The volume flow is conveyed through the interlocking wings in the chamber and pushed out at the outlet without internal compression. Such a rotary lobe machine is particularly suitable as a supercharger for relatively high volume flows.
Durch die Erfindung wird eine Drehkolbenmaschine mit dreiflügeligen Rotoren zur Verfügung gestellt, die mit innerer Verdichtung und innerer Expansion arbeitet und auch bei relativ kleinen Volumenströmen sowohl zur Druck- als auch zur Vakuumerzeugung geeignet ist.The invention provides a rotary lobe machine with three-bladed rotors, which works with internal compression and internal expansion and is also suitable for generating pressure and vacuum, even with relatively small volume flows.
Bei der erfindungsgemäßen Drchkolbenmaschine bilden die klauenartigen Flügel der Rotoren mit der Kammer gleichzeitig eine durch die Drehung der Rotoren ihr Volumen vergrößernde Saugzelle und eine durch die Drehung der Rotoren ihr Volumen verkleinernde Druckzelle. Da die Drehkolbenmaschine mit innerer Verdichtung und gleichzeitig mit innerer Expansion arbeitet, ist sie zur gleichzeitigen Erzeugung von Druck und Unterdruck geeignet.In the rotary piston machine according to the invention, the claw-like wings of the rotors together with the chamber form a suction cell which increases their volume by the rotation of the rotors and a pressure cell which reduces their volume by the rotation of the rotors. Since the rotary lobe machine works with internal compression and at the same time with internal expansion, it is suitable for the simultaneous generation of pressure and negative pressure.
In Weiterbildung der Erfindung bilden die Rotoren mit der Kammer zwei im Verlauf der Drehung der Rotoren zunächst voneinander getrennte Aufladezellen, die bei der weiteren Drehung der Rotoren miteinander zur Druckzelle vereinigt werden. Über die Aufladezellen kann ein Medienstrom eingespeist werden, so daß am Druckausgang ein entspre- - 2 -In a development of the invention, the rotors with the chamber form two charging cells which are initially separate from one another in the course of the rotation of the rotors and which are combined with one another to form the pressure cell during the further rotation of the rotors. A media stream can be fed in via the charging cells, so that a corresponding - 2 -
chend vergrößerter Volumenstrom zur Verfügung steht. Die Aufladezellen werden vor ihrer Vereinigung im wesentlichen isobar und isochor in der Pumpenkammer verschoben; das sich in den Aufladezellen befindliche Medium erfährt bei der Verschiebung der Aufladezellen im wesentlichen keine Druck- und keine Volumenänderung.accordingly increased volume flow is available. The charging cells are essentially isobar and isochoric in the pump chamber before they are combined; the medium in the charging cells experiences essentially no change in pressure and no volume when the charging cells are displaced.
Die Geometrie der Rotoren wird durch die Forderung bestimmt, in der Kammer gleichzeitig die für die Erzeugung von Druck und Vakuum erforderlichen Zellen voneinander abzugrenzen. Da die Rotoren berührungslos miteinander und auch mit der Um angswand der Kammer zusammenwirken, tritt im Bereich der Kammer keinerlei Verschleiß auf. Der Dichtspalt zwischen den Rotoren kann durch Optimierung ihrer Geometrie sehr klein gehalten werden; er beträgt bei praktischen Ausführungen nur Bruchteile eines Millimeters, so daß gute Druck- und Vakuumwerte gewährleistet sind. Diese Werte werden sogar mit zunehmender Betriebsdauer besser, da die sich mit der Zeit bildenden Ablagerungen zu einer Verkleinerung der Dichtspalte führen.The geometry of the rotors is determined by the requirement to simultaneously separate the cells required for the generation of pressure and vacuum in the chamber. Since the rotors interact without contact with one another and also with the peripheral wall of the chamber, no wear occurs in the region of the chamber. The sealing gap between the rotors can be kept very small by optimizing their geometry; in practical versions it is only a fraction of a millimeter, so that good pressure and vacuum values are guaranteed. These values become even better with increasing operating time, since the deposits that form over time lead to a reduction in the size of the sealing gaps.
Die erfindungsgemäße Drchkolbcnmaschine eignet sich besonders zur Verwendung als Pumpe für die gleichzeitige Erzeugung von Druckluft undThe rotary piston machine according to the invention is particularly suitable for use as a pump for the simultaneous generation of compressed air and
Vakuum. In dieser Anwendung ist sie besonders für den Einsatz im papierverarbeitenden Gewerbe geeignet, insbesondere dann, wenn keine - getrennte Bereitstellung oder Einstellung von Druckluft und Vakuum erforderlich ist. Druckluft wird z.B. zum seitlichen Anblasen eines Papierstapels für die Unterstützung der Bogentrennung benötigt. Die pulsierende Drucklufterzeugung durch eine solche Pumpe erweist sich hier als zweckmäßig, da die Papierkanten durch stoßweise auftretende Druckluft leichter getrennt werden können. Unterdruck ist bei derartigen Anwendungen gleichzeitig zum Ansaugen des obersten Papier- bogens erforderlich.Vacuum. In this application, it is particularly suitable for use in the paper processing industry, especially when no - separate provision or adjustment of compressed air and vacuum is required. Compressed air is e.g. needed to blow on a stack of paper to support sheet separation. The pulsating generation of compressed air by such a pump proves to be expedient here, since the edges of the paper can be separated more easily by compressed air which occurs intermittently. In such applications, vacuum is also required to suck up the top sheet of paper.
Weitere Vorteile und Merkmale der Erfindung ergeben sich aus der folgenden Beschreibung einer bevorzugten Ausführungsform und aus der Zeichnung, auf die Bezug genommen wird. In der Zeichnung zeigen:Further advantages and features of the invention result from the following description of a preferred embodiment and from the drawing, to which reference is made. The drawing shows:
Figur 1 einen Längsschnitt der erfindungsgemäßen Drehkolbenmaschine; - 3 -1 shows a longitudinal section of the rotary lobe machine according to the invention; - 3 -
Figur 2 eine Ansicht entlang Linie II-II in Figur 1 ;Figure 2 is a view along line II-II in Figure 1;
Figur 3 eine Ansicht entlang Linie III-III in Figur 1; undFigure 3 is a view along line III-III in Figure 1; and
Figuren 4a bis 4h schematische Ansichten verschiedener Rotorstellungen zur Erläuterung der Wirkungsweise.Figures 4a to 4h are schematic views of different rotor positions to explain the mode of operation.
Die erfindungsgemäße Drchkolbenmaschine wird nachfolgend am Beispiel einer Pumpe für gleichzeitige Erzeugung von Druckluft und Vakuum beschrieben. Auf eine solche Anwendung ist die Erfindung aber nicht beschränkt.The rotary piston machine according to the invention is described below using the example of a pump for the simultaneous generation of compressed air and vacuum. However, the invention is not restricted to such an application.
Die einstufig ausgebildete Pumpe zur gleichzeitigen Erzeugung von Druckluft und Unterdruck hat ein Gehäuse, das aus einem tragenden Mittelteil 10, einem auf der einen Seite des Mittelteils 10 aufgesetzten Gehäusedeckel 12, einem an die andere Seite des Mittelteils 10 angefügten Gehäuscring 14 und einer an den Gehäusering 14 anschließenden Deckelplatte 16 besteht. Zwischen dem Mittelteil 10, dem Gehäusering 14 und der Deckclplattc 16 ist eine Pumpenkammer 18 gebildet. In den einander gegenüberliegenden Wandungsleilen desThe single-stage pump for the simultaneous generation of compressed air and negative pressure has a housing which consists of a load-bearing central part 10, a housing cover 12 placed on one side of the central part 10, a housing ring 14 attached to the other side of the central part 10 and one on the housing ring 14 adjoining cover plate 16 there. A pump chamber 18 is formed between the middle part 10, the housing ring 14 and the cover plate 16. In the opposite wall lines of the
Gehäusedeckels 12 und des Mittelteils 10 sind zwei Wellen 20, 22 parallel zueinander und gegeneinander versetzt in Kugellagern fliegend gelagert. Auf jeder Welle 20, 22 sitzt ein Ritzel 24, 26. Die Ritzel 24, 26 stehen miteinander in Kämmeingriff, so daß die Wellen 20, 22 miteinander synchron entgegengesetzt rotieren. Für den Drehantrieb ist die untere Welle 22 aus dem Gehäusedeckel 12 herausgeführt.Housing cover 12 and the central part 10, two shafts 20, 22 are mounted parallel to one another and offset from one another in floating ball bearings. A pinion 24, 26 is seated on each shaft 20, 22. The pinions 24, 26 are in meshing engagement with one another, so that the shafts 20, 22 rotate in opposite directions synchronously with one another. For the rotary drive, the lower shaft 22 is led out of the housing cover 12.
Auf den in die Pumpenkammer 14 hineinragenden freien Enden der Wellen 20, 22 sind zwei Rotoren 30, 32 angeordnet. Da der durch die Rotoren 30, 32 gebildete Lastangriff nicht zwischen, sondern außerhalb der Lager liegt, ergibt sich eine fliegende Wellenlagerung. Jeder der Rotoren 30, 32 ist justierbar an der zugehörigen Welle 20 bzw. 22 befestigt. Wie aus Figur 2 ersichtlich ist. hat jeder Rotor 30, 32 drei Flügel 30a bzw. 32a. Die Pumpenkammer 18 hat in Seitenansicht die Form von zwei sich schneidenden Kreisen, die in Form einer "8" zusammengefügt sind. Die Flügel 30a des Rotors 30 haben eine Form, die von der Form der Flügel 32a des Rotors 32 verschieden ist. Die Geometrie der Flügel 30a, 32a und der Pumpenkammer 18 ist so bestimmt, daß bei - 4 -Two rotors 30, 32 are arranged on the free ends of the shafts 20, 22 projecting into the pump chamber 14. Since the load application formed by the rotors 30, 32 is not between, but outside of the bearings, there is a flying shaft bearing. Each of the rotors 30, 32 is adjustably attached to the associated shaft 20 and 22, respectively. As can be seen from Figure 2. each rotor 30, 32 has three blades 30a and 32a, respectively. The pump chamber 18 has a side view in the form of two intersecting circles, which are joined together in the form of an "8". The blades 30a of the rotor 30 have a shape that is different from the shape of the blades 32a of the rotor 32. The geometry of the wings 30a, 32a and the pump chamber 18 is determined so that at - 4 -
der Drehung der Rotoren 30, 32 mehrere voneinander getrennte Zellen gebildet werden, wie unter Bezugnahme auf die Figuren 4a bis 4h weiter unten näher erläutert, indem die Flügel 30a, 32a berührungsfrei mit einem Dichtspalt eines Bruchteils von 1 mm übereinander und entlang dem Außenumfang der Pumpenkammer 18 gleiten.the rotation of the rotors 30, 32 a plurality of separate cells are formed, as explained in more detail below with reference to FIGS. 4a to 4h, in that the vanes 30a, 32a contact-free with a sealing gap of a fraction of 1 mm one above the other and along the outer circumference of the pump chamber 18 slide.
Die Deckelplattc 16 ist mit einer Reihe von Aussparungen versehen, die nach außen durch eine aufgesetzte Vcrschlußplatle 36 abgeschlossen werden. In die Verschlußplattc 36 sind zwei Rohrstutzen 42, 44 eingeschraubt. Der obere Rohrstutzen 42 bildet den Sauganschluß und ist mit einer Aussparung 50 der Dcckelplatte 16 verbunden. Der untere Rohrstutzen 44 bildet den Druckanschluß und ist mit einer Aussparung 52 in der Deckclplatte 16 verbunden. Zwei weitere Aussparungen 54a, 54b in der Deckelplatte 16 sind nach außen zur Atmosphäre geöffnet und bilden Aufladcanschlüsse.The cover plate 16 is provided with a series of cutouts, which are closed off from the outside by an attached closure plate 36. Two pipe sockets 42, 44 are screwed into the closure plate 36. The upper pipe socket 42 forms the suction connection and is connected to a recess 50 of the cover plate 16. The lower pipe socket 44 forms the pressure connection and is connected to a recess 52 in the cover plate 16. Two further cutouts 54a, 54b in the cover plate 16 are open to the outside and form charging ports.
Figur 4a zeigt die Rotoren 30, 32 in einer Drehstcllung, bei der ihre Flügel 30a, 32a mit der Wandung der Pumpenkammer 18 eine abgeschlossene, nur mit der Aussparung 50 in Verbindung stehende, gemein- same Zelle 60 bilden. Diese Zelle 60 vergrößert bei der weiterenFIG. 4a shows the rotors 30, 32 in a rotational position in which their blades 30a, 32a form a closed cell 60, which is only connected to the recess 50, with the wall of the pump chamber 18. This cell 60 enlarges in the further
Drehung der Rotoren 30, 32 ihr Volumen, wie in Figur 4b ersichtlich. Es handelt sich bei dieser Zelle 60 also um eine Saugzelle.Rotation of the rotors 30, 32 their volume, as can be seen in Figure 4b. This cell 60 is therefore a suction cell.
Figur 4c zeigt zwei voneinander getrennte Zellen 62a, 62b, die unmittelbar nach dem in Figur 4b gezeigten Zustand entstehen, indem die Zelle 60 in zwei Teilzellen getrennt wurde. Die dem Rotor 30 zugeordnete Zelle 62a grenzt schon an die Aussparung 54a an, und die dem Rotor 32 zugeordnete Zelle 62b nähert sich der Aussparung 54b. InFIG. 4c shows two cells 62a, 62b which are separate from one another and which arise immediately after the state shown in FIG. 4b in that the cell 60 has been separated into two sub-cells. The cell 62a assigned to the rotor 30 already borders the recess 54a, and the cell 62b assigned to the rotor 32 approaches the recess 54b. In
Figur 4d sind die Zellen 62a, 62b mit den zur Atmosphäre führenden Aussparungen 54a bzw. 54b in Verbindung und werden mit Luft aufgefüllt und auf Umgebungsdruck aufgeladen, so daß der Luftmassenstrom erhöht wird. Es handelt sich bei den Zellen 62a, 62b somit um Aufladezellen.4d, the cells 62a, 62b are connected to the recesses 54a and 54b leading to the atmosphere and are filled with air and charged to ambient pressure, so that the air mass flow is increased. The cells 62a, 62b are thus charging cells.
Nachdem diese Aufladezellen 62a, 62b durch den nacheilenden Flügel 30a bzw. 32b von der zugehörigen Aussparung 54a bzw. 54b abgetrennt sind, wie in Figur 4e gezeigt, werden die Zellen 62a, 62b isobar und isochor verschoben, bis sie sich, wie in Figur 4f gezeigt, miteinander zu einer Druckzelle 64 vereinigen. Bei der weiteren Drehung der RotorenAfter these charging cells 62a, 62b have been separated from the associated recess 54a or 54b by the trailing wing 30a or 32b, as shown in FIG. 4e, the cells 62a, 62b are moved isobarically and isochorously until, as in FIG. 4f shown, combine with one another to form a pressure cell 64. As the rotors continue to rotate
30, 32 verkleinert die Druckzelle 64 ihr Volumen. Die in der Druck- - 5 -30, 32, the pressure cell 64 reduces its volume. The in the printing - 5 -
zelle 64 verdichtete Luft wird über die Aussparung 52 zum Rohrstutzen 44 ausgeschoben, wie in den Figuren 4g und 4h veranschaulicht ist.Cell 64 compressed air is pushed out via the recess 52 to the pipe socket 44, as illustrated in FIGS. 4g and 4h.
Die Pumpenkammer 18 ist frei von jeglichem Schmiermittel, da die Rotoren 30, 32 berührungsfrei arbeiten. Zur Antriebsseite hin ist dieThe pump chamber 18 is free of any lubricant, since the rotors 30, 32 operate without contact. To the drive side is the
Pumpenkammer 18 durch Dichtungen an den Wellen 20, 22 abgedichtet.Pump chamber 18 sealed by seals on the shafts 20, 22.
Durch die fliegende Anordnung der Rotoren 30, 32 auf den Wellen 20, 22, die zu einer fliegenden Lagerung führt, wird der Zugang zur Pumpenkammer erleichtert, da für einen Zugang lediglich die Deckelplatte 16 abzunehmen ist. Auch die Kühlung wird durch diese Anordnung erleichtert. Zur Kühlung kann das Gehäuse mit Kühlrippen ausgestattet werden, und durch ein auf der Seite des Gehäuscdeckels 12 angeordnetes Kühlgebläse wird kühlende Luft von der Deckelplatte 16 her über den Gehäusering 14, das Mittelteil 10 und den Gehäuscdeckel 12 geführt.The flying arrangement of the rotors 30, 32 on the shafts 20, 22, which leads to a flying bearing, facilitates access to the pump chamber, since only the cover plate 16 has to be removed for access. This arrangement also facilitates cooling. For cooling, the housing can be equipped with cooling fins, and cooling air is guided from the cover plate 16 via the housing ring 14, the middle part 10 and the housing cover 12 by a cooling fan arranged on the side of the housing cover 12.
Zur Dämpfung der Betriebsgeräusche dient ein Resonanz-Dämpfer, der auf die Betriebsfrequenz der Pumpe abgestimmt ist. Diese Frequenz beträgt aufgrund der dreiflügeligen Ausbildung der Rotoren die dreifache Drehzahl der Wellen 20, 22. Die erhöhte Betriebsfrequenz erleichtert die Unterbringung des Resonanz-Dämpfers, da dessen Länge entsprechend verkleinert wird.A resonance damper, which is matched to the operating frequency of the pump, is used to dampen the operating noise. Due to the three-wing design of the rotors, this frequency is three times the speed of the shafts 20, 22. The increased operating frequency makes it easier to accommodate the resonance damper, since its length is reduced accordingly.
Die beschriebene fliegende Lagerung der Rotoren ist bis zu einem Volumenstrom von etwa 300 m3/h vorteilhaft. Pumpen mit größeremThe described flying storage of the rotors is advantageous up to a volume flow of approximately 300 m3 / h. Pumps with larger
Volumenstrom werden vorzugsweise mit beidseitig gelagerten Rotoren ausgebildet. In diesem Falle sind in beiden Scitenplatten Anschlüsse ausgespart. Volume flow is preferably formed with rotors mounted on both sides. In this case, connections are left out in both scite plates.

Claims

Patentansprüche claims
1. Drehkolbenmaschinc mit einer in einem Gehäuse gebildeten Kammer (18), in der dreiflügeligc Rotoren (30, 32) um parallele, gegeneinander versetzte Achsen gegenläufig rotieren und berührungslos kämmen sowie mit der Umfangswandung der Kammer (18) voneinander getrennte Zellen (60, 62a, 62b, 64) bilden, dadurch gekennzeichnet, daß die klauenartigen Flügel der Rotoren (30, 32) mit der Kammer (18) gleichzeitig eine durch die Drehung der Rotoren (30, 32) ihr Volumen vergrößernde Saugzelle (60) und eine durch die Drehung der Rotoren1. Rotary piston machine with a chamber (18) formed in a housing, in which three-bladed rotors (30, 32) rotate in opposite directions about parallel, mutually offset axes and mesh without contact, and cells (60, 62a) separated from one another with the peripheral wall of the chamber (18) , 62b, 64), characterized in that the claw-like wings of the rotors (30, 32) with the chamber (18) simultaneously a suction cell (60) which increases their volume due to the rotation of the rotors (30, 32) and one through which Rotation of the rotors
(30, 32) ihr Volumen verkleinernde Druckzelle (64) bilden.(30, 32) form their volume-reducing pressure cell (64).
2. Drehkolbenmaschine nach Anspruch 1, dadurch gekennzeichnet, daß die Rotoren (30, 32) mit der Kammer zwei im Verlauf der Drehung der Rotoren zunächst voneinander getrennte Aufladezellen (62a, 62b) bilden, die bei der weiteren Drehung der Rotoren miteinander zur Druckzelle (64) vereinigt werden.2. Rotary piston machine according to claim 1, characterized in that the rotors (30, 32) with the chamber form two charging cells (62a, 62b) which are initially separated from one another in the course of the rotation of the rotors and which together form the pressure cell during the further rotation of the rotors ( 64) can be combined.
3. Drehkolbenmaschine nach Anspruch 1 oder 2, dadurch gekenn- zeichnet, daß ein Sauganschluß durch eine Seitenplatte des Gehäuses geführt ist und in der Kammer im Bereich der Saugzclle mündet.3. Rotary piston machine according to claim 1 or 2, characterized in that a suction connection is guided through a side plate of the housing and opens into the chamber in the area of the suction cylinder.
4. Drehkolbenmaschine nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß ein Druckanschluß durch eine Seitenplatte des Gehäuses geführt ist und in der Kammer im Bereich der Druckzelle mündet.4. Rotary piston machine according to one of the preceding claims, characterized in that a pressure connection is guided through a side plate of the housing and opens into the chamber in the region of the pressure cell.
5. Drehkolbenmaschine nach Anspruch 4, dadurch gekennzeichnet, daß mindestens eine Aufladczclle (62a, 62b) einen zugeordneten Aufladeanschluß (54a, 54b) aufweist.5. Rotary piston machine according to claim 4, characterized in that at least one Aufladczclle (62a, 62b) has an associated charging port (54a, 54b).
6. Drehkolbenmaschinc nach Anspruch 4 oder 5, dadurch gekennzeichnet, daß die Aufladezellen (62a. 62b) vor ihrer Vereinigung im wesentlichen isobar und isochor in der Kammer (18) verschoben werden.6. Rotary piston machine according to claim 4 or 5, characterized in that the charging cells (62a. 62b) are displaced essentially isobar and isochoric in the chamber (18) before they are combined.
7. Drehkolbenmaschinc nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die Kammer (18) schmicrmittelfrei ist.7. Rotary piston machine according to one of the preceding claims, characterized in that the chamber (18) is free of lubricant.
8. Drehkolbenmaschinc nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die Kammer (18) zwischen zwei parallelen Seitenplatten -(10, 16) begrenzt ist und in wenigstens einer der8. Rotary piston machine according to one of the preceding claims, characterized in that the chamber (18) between two parallel side plates - (10, 16) is limited and in at least one of the
Seitenplatten (16) die Anschlüsse (50, 52, 54a, 54b) ausgespart sind.Side plates (16) the connections (50, 52, 54a, 54b) are recessed.
9. Drehkolbenmaschinc nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die Wellen (20, 22) fliegend gelagert und die Rotoren (30, 32) auf freien Enden der Wellen (20, 22) angeordnet sind.9. Rotary piston machine according to one of the preceding claims, characterized in that the shafts (20, 22) are overhung and the rotors (30, 32) are arranged on free ends of the shafts (20, 22).
10. Drehkolbenmaschine nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die Wellen (20, 22) durch zwei miteinander in Kämmeingriff stehende Ritzel (24, 26) synchronisiert sind und wenigstens einer der Rotoren (30, 32) justierbar auf der zugeordneten Welle (20, 22) befestigt ist.10. Rotary piston machine according to one of the preceding claims, characterized in that the shafts (20, 22) by two meshing pinions (24, 26) are synchronized and at least one of the rotors (30, 32) adjustable on the associated shaft ( 20, 22) is attached.
11. Drehkolbenmaschinc nach einem der vorstehenden Ansprüche, gekennzeichnet durch ihre Verwendung als Pumpe zur gleichzeitigen11. Rotary piston machine according to one of the preceding claims, characterized by its use as a pump for simultaneous
Erzeugung von Druck und Unterdruck. Generation of pressure and negative pressure.
EP99948559A 1998-04-30 1999-04-28 Rotating piston machine with three-blade rotors Expired - Lifetime EP1076760B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19819538A DE19819538C2 (en) 1998-04-30 1998-04-30 Pressure suction pump
DE19819538 1998-04-30
PCT/EP1999/002881 WO1999057419A1 (en) 1998-04-30 1999-04-28 Rotating piston machine with three-blade rotors

Publications (2)

Publication Number Publication Date
EP1076760A1 true EP1076760A1 (en) 2001-02-21
EP1076760B1 EP1076760B1 (en) 2003-07-02

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EP99948559A Expired - Lifetime EP1076760B1 (en) 1998-04-30 1999-04-28 Rotating piston machine with three-blade rotors
EP99923485A Expired - Lifetime EP1075601B1 (en) 1998-04-30 1999-04-28 Vacuum pump

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EP99923485A Expired - Lifetime EP1075601B1 (en) 1998-04-30 1999-04-28 Vacuum pump

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US (2) US6364642B1 (en)
EP (2) EP1076760B1 (en)
JP (2) JP2002513887A (en)
KR (2) KR100556077B1 (en)
CN (2) CN1105820C (en)
DE (3) DE19819538C2 (en)
WO (2) WO1999057439A1 (en)

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Also Published As

Publication number Publication date
WO1999057419A1 (en) 1999-11-11
EP1076760B1 (en) 2003-07-02
CN1105820C (en) 2003-04-16
CN1299434A (en) 2001-06-13
KR20010043093A (en) 2001-05-25
JP2002513887A (en) 2002-05-14
DE19819538A1 (en) 1999-11-11
DE59906193D1 (en) 2003-08-07
CN1299444A (en) 2001-06-13
JP2002513880A (en) 2002-05-14
WO1999057439A1 (en) 1999-11-11
EP1075601A1 (en) 2001-02-14
DE19819538C2 (en) 2000-02-17
KR100608527B1 (en) 2006-08-09
US6364642B1 (en) 2002-04-02
KR100556077B1 (en) 2006-03-07
CN1128935C (en) 2003-11-26
US6439865B1 (en) 2002-08-27
EP1075601B1 (en) 2002-09-18
DE59902761D1 (en) 2002-10-24
KR20010043094A (en) 2001-05-25

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