EP0363420B1 - Pump - Google Patents

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Publication number
EP0363420B1
EP0363420B1 EP88905368A EP88905368A EP0363420B1 EP 0363420 B1 EP0363420 B1 EP 0363420B1 EP 88905368 A EP88905368 A EP 88905368A EP 88905368 A EP88905368 A EP 88905368A EP 0363420 B1 EP0363420 B1 EP 0363420B1
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EP
European Patent Office
Prior art keywords
rotors
rotor
pump
longitudinal axis
transverse axes
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
Application number
EP88905368A
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German (de)
French (fr)
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EP0363420A1 (en
EP0363420B2 (en
Inventor
Paul G. Langer
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.)
Herold and Co GmbH
Original Assignee
Herold and Co GmbH
BSA Maschinenfabrik Paul G Langer GmbH
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Application filed by Herold and Co GmbH, BSA Maschinenfabrik Paul G Langer GmbH filed Critical Herold and Co GmbH
Priority to AT88905368T priority Critical patent/ATE61083T1/en
Publication of EP0363420A1 publication Critical patent/EP0363420A1/en
Application granted granted Critical
Publication of EP0363420B1 publication Critical patent/EP0363420B1/en
Publication of EP0363420B2 publication Critical patent/EP0363420B2/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps 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 toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps 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 toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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
    • F01C1/126—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 with elements extending radially from the rotor body not necessarily cooperating with corresponding recesses in the other rotor, e.g. lobes, Roots type

Definitions

  • the invention relates to a pump with a housing formed from two intersecting cylinder sections, wherein at least one inlet and outlet opening is provided in the cutting area opposite each other and in each cylinder section a rotor rotatable about its central longitudinal axis is arranged, the larger transverse axes of the rotor in at least a phase of movement are approximately perpendicular to each other and the runners roll tightly against each other and against the inner wall of the housing, and wherein the surface lines of each rotor starting from the intersection of the large transverse axis run obliquely in opposite directions to the respective central longitudinal axis, with the rotation of the two in each phase Runner a uniformly increasing suction volume in front of the inlet opening and a uniformly smaller suction volume in front of the outlet opening is formed.
  • Roots pumps which are presumed to be known, are referred to as Roots pumps or Roots housings and have long been proven in practical use.
  • the rotors of conventional Roots pumps of this type have lateral surfaces which run parallel to the central longitudinal axis of the rotor and thus perpendicular to the flow direction defined by the inlet and outlet openings. Due to this construction of conventional pumps of this type, the pumped medium pulsates relatively strongly as a function of the respective rotational angle position of the rotor.
  • the object of the invention is to improve a pump of the generic type while preserving its basic advantages in such a way that a pulsation-free, uniform flow of the pumped medium is achieved with a high delivery capacity while avoiding dead spaces.
  • each runner comprises two approximately club-shaped sections which are connected to one another at their narrower end by a constriction, the runners having such a configuration and being arranged relative to one another that when the large transverse axes of the two runners are perpendicular to one another stand, the club-shaped section of one runner engages in the constriction of the other runner and the two runners roll against each other in a sealing manner.
  • the two halves of each runner are twisted relative to one another about the central longitudinal axis in the embodiment according to the invention, so that these oblique surface lines are created.
  • the two runners are in turn arranged on the two axes of rotation so that the surface lines in the sealing area of the two runners each run parallel to one another. This means that the lateral surfaces of the runners can roll against one another in a sealing manner, as is provided in conventionally known runners.
  • the configuration of the runners according to the invention can be produced with modern CNC-controlled machines with a reasonable effort compared to the considerable achievable advantages.
  • the rotor configuration according to the invention avoids cavities which increase the drive resistance in the rolling motion of the rotors to one another and relative to the housing and enables very substantial delivery rates to be achieved in relation to the pump volume and the required drive power.
  • the construction according to the invention enables a contact-free flow and return as well as the pumping of both gaseous and liquid media.
  • a pump shown in the drawing has a pump housing 1, which consists of two intersecting cylinder sections 2, 3.
  • an inlet opening 4 and an outlet opening 5 are provided on the surface of the cylinder.
  • the inlet opening 4 and the outlet opening 5 are located diametrically opposite one another, as can be seen in FIG. 1b, and have an approximately trapezoidal cross section. Deviating from this, however, a rectangular cross section can also be provided for these openings 4, 5.
  • a runner 6, 7 is arranged in the interior of each cylinder section 2, 3, the central longitudinal axis 8 or 9 of which runs parallel to the central longitudinal axis of the respective cylinder section 2 or 3.
  • the rotors 6 and 7 are driven in rotation in the opposite direction (arrows 16, 11) about their central longitudinal axes 8 and 9.
  • the coordinated drive of both runners 6, 7 can e.g. by meshing gears on the axles 8, 9, which are accommodated in the housing part 12, are accomplished.
  • Each runner 6 or 7 comprises, in a manner known per se, two approximately club-shaped sections 13 which are connected via a constriction 14, i.e. the runners have such a configuration that when the large transverse axes 15 and 16 of the two runners 6 and 7 are perpendicular to one another, the club-shaped section 13 of one runner engages in the constriction 14 of the other runner and the two runners seal against one another can pass on.
  • 1b shows a movement phase where the transverse axes 15, 16 are just perpendicular to one another and the club-like section 13 of the rotor 7 engages in the constriction 14 of the rotor 6. Based on this situation shown in FIG. 1 b, it is conceivable how the two runners 6, 7 roll against each other during a rotary movement in the direction of the arrows 10, 11.
  • the pump according to the invention essentially corresponds to a conventional Roots pump.
  • the generatrices 17 run helically, which cannot be seen in detail in the drawing.
  • This configuration ensures that in each phase of the rotary movement of the two rotors 6 and 7, a uniformly increasing suction volume is built up in front of the inlet opening 4 and a uniformly decreasing suction volume in front of the outlet opening 5, whereby a completely even flow with a large throughput is achieved in relation to the volume and the drive power of the pump.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

In order to achieve uniform throughput and high performance in a Roots-type pump, the surface-generating lines (17) of each runner (6 resp. 7) originating from the point of intersection (18) of the major transverse axis (15 resp. 6) are inclined in opposite directions to the corresponding median longitudinal axis (8 resp. 9).

Description

Technisches Gebiet :Technical field:

Die Erfindung betrifft eine Pumpe mit einem aus zwei sich schneidenden Zylinderabschnitten gebildeten Gehäuse, wobei im Schnittbereich einander gegenüberliegend wenigstens je eine Einlaß- und Auslaßöffnung vorgesehen ist und in jedem Zylinderabschnitt ein um dessen Mittellängsachse drehbarer Läufer angeordnet ist, wobei die größeren Querachsen der Läufer in wenigstens einer Bewegungsphase jeweils etwa senkrecht zueinander stehen und die Läufer sich dichtend aneinander und gegen die Gehäuseinnenwand abwälzen, und wobei die von dem Schnittpunkt der großen Querachse ausgehenden Mantellinien jedes Läufers in einander entgegengesetzter Richtung schräg zur jeweiligen Mittellängsachse verlaufen, wobei in jeder Phase der Drehbewegung der beiden Läufer ein sich gleichmäßig vergrößerndes Ansaugvolumen vor der Einlaßöffnung und ein sich gleichmäßig verkleinemdes Ansaugvolumen vor der Auslaßöffnung ausgebildet wird.The invention relates to a pump with a housing formed from two intersecting cylinder sections, wherein at least one inlet and outlet opening is provided in the cutting area opposite each other and in each cylinder section a rotor rotatable about its central longitudinal axis is arranged, the larger transverse axes of the rotor in at least a phase of movement are approximately perpendicular to each other and the runners roll tightly against each other and against the inner wall of the housing, and wherein the surface lines of each rotor starting from the intersection of the large transverse axis run obliquely in opposite directions to the respective central longitudinal axis, with the rotation of the two in each phase Runner a uniformly increasing suction volume in front of the inlet opening and a uniformly smaller suction volume in front of the outlet opening is formed.

Stand der Technik :State of the art :

Derartige gattungsgemäß als bekannt vorausgesetzte Pumpen werden als Roots-Pumpen bzw. Roots-Gehäuse bezeichnet und und sind im praktischen Einsatz seit langem bewährt.Pumps of this type, which are presumed to be known, are referred to as Roots pumps or Roots housings and have long been proven in practical use.

Die Läufer herkömmlicher derartiger Roots-Pumpen weisen Mantelflächen auf, welche zur Mittellängsachse des Läufers parallel verlaufen und damit senkrecht zur durch die Ein- und Auslaßöffnungen definierten Durchströmungsrichtung. Aufgrund dieses Aufbaus herkömmlicher derartiger Pumpen pulsiert das gepumpte Medium relativ stark in Abhängigkeit von der jeweiligen Drehwinkelstellung der Läufer.The rotors of conventional Roots pumps of this type have lateral surfaces which run parallel to the central longitudinal axis of the rotor and thus perpendicular to the flow direction defined by the inlet and outlet openings. Due to this construction of conventional pumps of this type, the pumped medium pulsates relatively strongly as a function of the respective rotational angle position of the rotor.

Aus der GB-A-382 953 ist eine gattungsgemäße Pumpe bekannt, bei welcher aufgrund der dort vorgeschlagenen Läuferkonfigurationen jedoch ein erhöhter Laufwiderstand aufgrund von Flüssigkeitskompressionen in Toträumen in Kauf genommen werden muß.From GB-A-382 953 a generic pump is known, in which due to the rotor configurations proposed there an increased running resistance due to fluid compression in dead spaces has to be accepted.

Aus der DE-A-35 02 839 ist eine Pumpe mit zwei Läufern bekannt, welche zwei zueinander parallele Drehachsen aufweisen, wobei die Dichtflächen jeweils schräg zu den Drehachsen verlaufen. Bei dieser vorbekannten Pumpe ist die Auslaß- und Einlaßöffnung in der axialen Verlängerung der Drehachsen angeordnet. Die Konfiguration der Läufer ist relativ kompliziert.From DE-A-35 02 839 a pump with two rotors is known, which have two mutually parallel axes of rotation, the sealing surfaces each being inclined to the axes of rotation. In this known pump, the outlet and inlet opening is arranged in the axial extension of the axes of rotation. The configuration of the runners is relatively complicated.

Darstellung der Erfindung:Presentation of the invention:

Hiervon ausgehend liegt der Erfindung die Aufgabe zugrunde, eine Pumpe der gattungsgemäßen Art unter Wahrung ihrer prinzipiellen Vorteile so zu verbessern, daß eine pulsationsfreie, gleichmäßige Strömung des geförderten Mediums bei hoher Förderkapazität unter Vermeidung von Toträumen erzielt wird.Proceeding from this, the object of the invention is to improve a pump of the generic type while preserving its basic advantages in such a way that a pulsation-free, uniform flow of the pumped medium is achieved with a high delivery capacity while avoiding dead spaces.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß jeder Läufer zwei etwa keulenförmige Abschnitte umfaßt, welche an ihrem schmäleren Ende über eine Einschnürung miteinanderverbunden sind, wobei die Läufer eine derartige Konfiguration aufweisen und relativ zueinander angeordnet sind, daß wenn die großen Querachsen der beiden Läufer senkrecht zueinander stehen, der keulenförmige Abschnitt des einen Läufers in die Einschnürung des anderen Läufers eingreift und die beiden Läufer sich dichtend aneinander abwälzen.This object is achieved in that each runner comprises two approximately club-shaped sections which are connected to one another at their narrower end by a constriction, the runners having such a configuration and being arranged relative to one another that when the large transverse axes of the two runners are perpendicular to one another stand, the club-shaped section of one runner engages in the constriction of the other runner and the two runners roll against each other in a sealing manner.

Im Vergleich zu den zu der Mittellängsachse parallel verlaufenden Mantellinien herkömmlicher Läufer sind also bei der erfindungsgemäßen Ausgestaltung die beiden Hälften jedes Läufers um die Mittellängsachse gegeneinander verwunden, so daß diese schräg verlaufenden Mantellinien entstehen. Die beiden Läufer sind ihrerseits auf den beiden drehachsen so ängeordnet, daß die Mantellinien im Dichtbereich der beiden Läufer jeweils parallel zueinander verlaufen. Dies bedeutet, daß sich die Mantelflächen der Läufer ebenso dichtend aneinander abwälzen können, wie dies bei herkömmlicherweise bekannten Läufern vorgesehen ist. Demgegenüber wird aber durch die erfindungsgemäße Verwindung erreicht, daß in Längsrichtung der Einlaßöffnung gesehen in jeder Phase der Drehbewegung mit praktisch gleichbleibender Saugkraft angesaugt und ausgestoßen wird, so daß eine äußerst gleichmäßige Durchströmung und Förderung erzielt wird, wie sie für manche Anwendungszwecke gefordert wird.In comparison to the surface lines of conventional runners running parallel to the central longitudinal axis, the two halves of each runner are twisted relative to one another about the central longitudinal axis in the embodiment according to the invention, so that these oblique surface lines are created. The two runners are in turn arranged on the two axes of rotation so that the surface lines in the sealing area of the two runners each run parallel to one another. This means that the lateral surfaces of the runners can roll against one another in a sealing manner, as is provided in conventionally known runners. In contrast, however, is achieved by the twisting according to the invention that seen in the longitudinal direction of the inlet opening in each phase of the rotary movement is sucked in and expelled with a practically constant suction force, so that an extremely uniform flow and delivery is achieved, as is required for some applications.

Die erfindungsgemäße Konfiguration der Läufer läßt sich mit zeitgemäßen CNC-gesteuerten Maschinen mit im Vergleich zu den erheblichen erzielbaren Vorteilen vertretbarem Aufwand herstellen.The configuration of the runners according to the invention can be produced with modern CNC-controlled machines with a reasonable effort compared to the considerable achievable advantages.

Die erfindungsgemäße Läuferkonfiguration vermeidet den Antriebswiderstand erhöhende Hohlräume in derAbwälzbewegung der Läuferzueinander und relativ zu dem Gehäuse und ermöglicht die Erzielung ganz erheblicher Fördermengen bezogen auf das Pumpenvolumen und die erforderliche Antriebsleistung.The rotor configuration according to the invention avoids cavities which increase the drive resistance in the rolling motion of the rotors to one another and relative to the housing and enables very substantial delivery rates to be achieved in relation to the pump volume and the required drive power.

Die erfindungsgemäße Konstruktion ermöglicht einen berührungsfreien Vor- und Rücklauf sowie das Pumpen sowohl gasförmiger als auch flüssiger Medien.The construction according to the invention enables a contact-free flow and return as well as the pumping of both gaseous and liquid media.

Durch das Vorsehen von einander diametral gegenüberliegend angeordneten Einlaß- und Auslaßöffnungen mit jeweils trapezförmigem Querschnitt wird eine sehr hohe pulsationsfreie Durchströmung des Pumpeninnenraums erreicht.The provision of diametrically opposed inlet and outlet openings, each with a trapezoidal cross section, results in a very high pulsation-free flow through the pump interior.

Kurze Beschreibung der Zeichnungen:Brief description of the drawings:

Weitere Merkmale, Vorteile und Einzelheiten der Erfindung ergeben sich aus der folgenden Beschreibung einer bevorzugten Ausführungsform anhand der Zeichnung. Dabei zeigen

  • Fig. 1a und 1c Seitenansichten des Pumpengehäuses mit der Auslaß- bzw. Einlaßöffnung.
  • Fig. 1 b eine Aufsicht auf das Pumpengehäuse mit den darin angeordneten Läufern (schematisch) bei abgenommenem Gehäusedeckel, und
  • Fig. 2 eine perspektivische Darstellung der beiden Läufer.
Further features, advantages and details of the invention result from the following description of a preferred embodiment with reference to the drawing. Show
  • 1a and 1c side views of the pump housing with the outlet or inlet opening.
  • Fig. 1 b is a plan view of the pump housing with the runners arranged therein (schematic) with the housing cover removed, and
  • Fig. 2 is a perspective view of the two runners.

Bester Weg zur Ausführung der Erfindung :Best way to carry out the invention:

Eine in der Zeichnung dargestellte Pumpe weist ein Pumpengehäuse 1 auf, welches aus zwei sich schneidenden Zylinderabschnitten 2, 3 besteht.A pump shown in the drawing has a pump housing 1, which consists of two intersecting cylinder sections 2, 3.

Im Schnittbereich derZylinderabschnitte 2, 3 sind an der Zylindermantelfläche eine Einlaßöffnung 4 und eine Auslaßöffnung 5 vorgesehen. Die Einlaßöffnung 4 und die Auslaßöffnung 5 liegen sich - wie aus Fig. 1 b ersichtlich diametral gegenüber und weisen einen etwa trapezförmigen Querschnitt auf. Hiervon abweichend kann für diese Öffnungen 4, 5 jedoch auch ein rechteckiger Querschnitt vorgesehen sein.In the cutting area of the cylinder sections 2, 3, an inlet opening 4 and an outlet opening 5 are provided on the surface of the cylinder. The inlet opening 4 and the outlet opening 5 are located diametrically opposite one another, as can be seen in FIG. 1b, and have an approximately trapezoidal cross section. Deviating from this, however, a rectangular cross section can also be provided for these openings 4, 5.

Im Inneren jedes Zylinderabschnitts 2, 3 ist ein Läufer 6, 7 angeordnet, dessen Mittellängsachse 8 bzw. 9 parallel zur Mittellängsachse des jeweiligen Zylinderabschnitts 2 bzw. 3 verläuft.A runner 6, 7 is arranged in the interior of each cylinder section 2, 3, the central longitudinal axis 8 or 9 of which runs parallel to the central longitudinal axis of the respective cylinder section 2 or 3.

Die Läufer 6 bzw. 7 sind um ihre Mittellängsachsen 8 bzw. 9 in entgegengesetzter Richtung (Pfeile 16,11) drehangetrieben. Der koordinierte Antrieb beider Läufer 6, 7 kann in an sich bekannter Weise z.B. durch auf den Achsen 8, 9 sitzende, ineinandergreifende Zahnräder, welche in dem Gehäuseteil 12 untergebracht sind, bewerkstelligt werden.The rotors 6 and 7 are driven in rotation in the opposite direction (arrows 16, 11) about their central longitudinal axes 8 and 9. The coordinated drive of both runners 6, 7 can e.g. by meshing gears on the axles 8, 9, which are accommodated in the housing part 12, are accomplished.

Jeder Läufer 6 bzw. 7 umfaßt in an sich bekannter Weise zwei etwa keulenfönnige Abschnitte 13, welche über eine Einschnürung 14 verbunden sind, d.h. die Läufer weisen eine solche Konfiguration auf, daß wenn die großen Querachsen 15 bzw. 16 der beiden Läufer 6 bzw. 7 senkrecht zueinander stehen, der keulenförmige Abschnitt 13 des einen Läufers in die Einschnürung 14 des anderen Läufers eingreift und die beiden Läufer sich dichtend aneinander abwälzen können. In Fig. 1b ist eine Bewegungsphase dargestellt, wo die Querachsen 15, 16 gerade aufeinander senkrecht stehen und der keulenartige Abschnitt 13 des Läufers 7 in die Einschnürung 14 des Läufers 6 eingreift. Ausgehend von dieser in Fig. 1 b dargestellten Situation ist es vorstellbar, wie sich die beiden Läufer 6, 7 bei einer Drehbewegung in Richtung der Pfeile 10, 11 aneinander abwälzen.Each runner 6 or 7 comprises, in a manner known per se, two approximately club-shaped sections 13 which are connected via a constriction 14, i.e. the runners have such a configuration that when the large transverse axes 15 and 16 of the two runners 6 and 7 are perpendicular to one another, the club-shaped section 13 of one runner engages in the constriction 14 of the other runner and the two runners seal against one another can pass on. 1b shows a movement phase where the transverse axes 15, 16 are just perpendicular to one another and the club-like section 13 of the rotor 7 engages in the constriction 14 of the rotor 6. Based on this situation shown in FIG. 1 b, it is conceivable how the two runners 6, 7 roll against each other during a rotary movement in the direction of the arrows 10, 11.

Die äußeren Mantellinien 17 der Läufer 6, 7 ausgehend vom Schnittpunkt 18 der großen Querachsen 15 bzw. 16 mit der Mantelfläche 19 der Läufer 6, 7 läuft längs der Innenwand 20 der Zylinderabschnitte 2, 3 dichtend ab.The outer surface lines 17 of the runners 6, 7, starting from the point of intersection 18 of the large transverse axes 15 and 16 with the lateral surface 19 of the runners 6, 7, run sealingly along the inner wall 20 of the cylinder sections 2, 3.

Soweit wie vorstehend beschrieben entspricht die erfindungsgemäße Pumpe im wesentlichen einer herkömmlichen Roots-Pumpe.As far as described above, the pump according to the invention essentially corresponds to a conventional Roots pump.

Demgegenüber ist erfindungsgemäß vorgesehen, daß - wie insbesondere aus Fig. 2 ersichtlich - die äußeren Mantellinien 17 schräg gegen die Mittellängsachse 8 bzw. 9 verlaufen, wobei die äußeren Mantellinien 17 an den einander gegenübergesetzten Seiten eines Läufers 6 bzw. 7 in entgegengesetzte Richtung gegen die Mittellängslinie 8 bzw. 9 versetzt sind.In contrast, it is provided according to the invention that - as can be seen in particular from FIG. 2 - the outer surface lines 17 run obliquely against the central longitudinal axis 8 or 9, the outer surface lines 17 on the opposite sides of a rotor 6 or 7 in the opposite direction against the Central longitudinal line 8 and 9 are offset.

Die Mantellinien 17 verlaufen, was in der Zeichnung im einzelnen nicht erkennbar ist, schraubenförmig.The generatrices 17 run helically, which cannot be seen in detail in the drawing.

Durch diese Konfiguration wird, wie die Aufsicht gemäß Fig. 1 veranschaulicht, erreicht, daß in jeder Phase der Drehbewegung der beiden Läufer 6 bzw. 7 ein sich gleichmäßig vergrößerndes Ansaugvolumen vorder Einlaßöffnung 4 und ein sich gleichförmig verkleinerndes Ansaugvolumen vor der Auslaßöffnung 5 aufgebaut wird, wodurch eine völlig gleichmäßige Durchströmung bei großem Durchsatz bezogen auf das Volumen und die Antriebsleistung der Pumpe erzielt wird.This configuration, as the top view according to FIG. 1 illustrates, ensures that in each phase of the rotary movement of the two rotors 6 and 7, a uniformly increasing suction volume is built up in front of the inlet opening 4 and a uniformly decreasing suction volume in front of the outlet opening 5, whereby a completely even flow with a large throughput is achieved in relation to the volume and the drive power of the pump.

Claims (2)

1. A pump with a housing consisting of two intersecting cylinder portions, the area of intersection comprising oppositely disposed and in each case one inlet and outlet aperture and in that there is in each cylinder portion and rotatable about its median longitudinal axis a rotor, the greater transverse axes of the rotors being substantially at right-angles to each other at least in one movement phase, the rotors rolling on each other and in respect of the interior wall of the housing in sealing-tight fashion, the generatrices of each rotor emanating from the point of intersection of the major transverse axes extending in mutually opposite directions and obliquely to the relevant median longitudinal axis, and in that in each phase of the rotary movement of the two rotors there is an evenly increasing induction volume upstream of the inlet aperture and an evenly diminishing induction volume upstream of the outlet orifice, characterised in that each rotor (6 or 7) comprises two substantially lobar portions (13) which at their narrower end are connected to each other by a restricted portion (14), the rotors (6 or 7) having such a configuration and being disposed relatively to each other that when the major transverse axes (15,16) of the two rotors (6, 7) are at right-angles to each other, the lobar portion (13) of one rotor engages the restriction portion (14) of the other rotor, while the two rotors roll on each other in a seaiing-tight fashion.
2. A pump according to claim 1, characterised in that the inlet aperture (4) and the outlet orifice (5) are diametrally opposed to each other and in that each has a trapezoidal cross-section.
EP88905368A 1987-06-05 1988-06-04 Pump Expired - Lifetime EP0363420B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88905368T ATE61083T1 (en) 1987-06-05 1988-06-04 PUMP.

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE3718866 1987-06-05
DE19873718866 DE3718866A1 (en) 1987-06-05 1987-06-05 PUMP
PCT/EP1988/000498 WO1988009877A1 (en) 1987-06-05 1988-06-04 Pump

Publications (3)

Publication Number Publication Date
EP0363420A1 EP0363420A1 (en) 1990-04-18
EP0363420B1 true EP0363420B1 (en) 1991-02-27
EP0363420B2 EP0363420B2 (en) 1996-02-07

Family

ID=6329129

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88905368A Expired - Lifetime EP0363420B2 (en) 1987-06-05 1988-06-04 Pump

Country Status (3)

Country Link
EP (1) EP0363420B2 (en)
DE (2) DE3718866A1 (en)
WO (1) WO1988009877A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4121684C2 (en) * 1991-06-29 1999-04-01 Herold & Co Gmbh pump

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006041633A1 (en) 2006-09-05 2008-03-13 Herold & Co. Gmbh pump

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1142734A (en) * 1913-04-30 1915-06-08 Charles W Sidwell Pump.
FR718487A (en) * 1930-06-11 1932-01-25 Commercial Patents Inc Multiple rotary piston hydraulic pump or motor acting simultaneously
GB382953A (en) 1930-06-11 1932-11-10 Commercial Patents Inc Fluid apparatus provided with co-operating rotary pistons
US2982221A (en) * 1958-07-02 1961-05-02 Joseph E Whitfield Gear pump
DE3502839A1 (en) 1985-01-29 1986-07-31 Bsa Maschinenfabrik Paul G. Langer Gmbh, 8581 Marktschorgast Pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4121684C2 (en) * 1991-06-29 1999-04-01 Herold & Co Gmbh pump

Also Published As

Publication number Publication date
EP0363420A1 (en) 1990-04-18
WO1988009877A1 (en) 1988-12-15
DE3861857D1 (en) 1991-04-04
EP0363420B2 (en) 1996-02-07
DE3718866A1 (en) 1988-12-22

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