EP0226177B1 - Internally-meshing gears machine - Google Patents

Internally-meshing gears machine Download PDF

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Publication number
EP0226177B1
EP0226177B1 EP86117212A EP86117212A EP0226177B1 EP 0226177 B1 EP0226177 B1 EP 0226177B1 EP 86117212 A EP86117212 A EP 86117212A EP 86117212 A EP86117212 A EP 86117212A EP 0226177 B1 EP0226177 B1 EP 0226177B1
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EP
European Patent Office
Prior art keywords
internal
gear
pinion
support element
casing
Prior art date
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Expired
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EP86117212A
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German (de)
French (fr)
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EP0226177A1 (en
Inventor
Klaus-Dieter Buchmüller
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.)
Eckerle Rexroth GmbH and Co KG
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Otto Eckerle GmbH and Co KG
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Publication of EP0226177A1 publication Critical patent/EP0226177A1/en
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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
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/101—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with a crescent-shaped filler element, located between the inner and outer intermeshing members

Definitions

  • the invention relates to an internal gear machine, in particular an internal gear pump, with the features according to the preamble of claim 1.
  • the filler pin for supporting the longitudinally divided filler is rotatably mounted about its longitudinal axis.
  • the filler parts are both displaceable in the radial direction on the support surface of the filler pin, and can also perform a pivoting movement about the longitudinal axis of the filler pin via the rotatability of the filler pin.
  • An extensive sealing of the filler parts on the tooth heads of the assigned gears is thus achieved even with relative movements, wear and the like.
  • the rotatable mounting of the filler pin must be extremely precise so that the intended purpose is achieved; otherwise the filler pin and / or the filler supported thereon would not be guided correctly and could therefore not carry out the desired compensatory movements.
  • the precise double-ended mounting of the filler pin in turn requires that the housing walls in which the filler pin is supported, i.e. the opposite housing parts, very precisely aligned with each other and connected to each other in this aligned position. This requires a considerable manufacturing and assembly effort, which is reflected in the production price of the internal gear machine, which increases costs.
  • the invention is therefore based on the object of designing an internal gear machine of the type specified at the outset such that a particular precision in the connection of the parts forming the housing to one another can be dispensed with without impairing the compensation and sealing action of the filler.
  • the invention proposes two basic configurations, each of which is specified in the characterizing part of claims 1 and 3.
  • the filler parts are supported on an intermediate piece which has the support surface on one side and a sliding surface on the other side, with which the intermediate piece can pivot on the at least partially cylindrical bearing surface of the support element.
  • the radial displacement movements of the filler parts take place in the compensation of radial gaps on the support surface, while the pivoting movements are brought about by the adjustment of the intermediate piece on the bearing surface.
  • the support element for the filler is only independent with one housing wall, an exact alignment of the two housing walls with one another is not necessary simply because of the mounting of the filler support element.
  • This also applies in general if the pinion is mounted on both sides in the housing, since the pinion bearing does not require the same precision as the bearing of the filler pin.
  • special precision in the alignment of the housing parts with respect to one another can be dispensed with if, in addition, the pinion is also only supported on one side (overhung) in the housing or outside it, so that when the housing parts are connected to one another there is also no pinion bearing Needs to be considered.
  • the housing wall which is free of bearing elements, is only supported in a sealing manner on the end faces of the support element and the pinion.
  • the support surface on which the convex end faces of the filler parts are supported in the first basic embodiment of the invention is expediently flat so as not to impede the radial displaceability of the filler parts.
  • a slightly concave curvature can also be considered, provided that this does not lead to a noticeable displacement of the filler parts in the circumferential direction during the radial displacement, since this reduces the stress at the contact point between the filler parts and the support surface.
  • an expedient embodiment can consist in the support element being a cylindrical pin or pin which is pressed into a bore in the housing wall and which is partially surrounded by the corresponding partially hollow-cylindrical sliding surface of the intermediate piece.
  • the support surface of the intermediate piece can also be partially withdrawn because it is less loaded in the basic second embodiment of the invention.
  • an internally toothed ring gear 3 is slidably mounted in a bore 1 of a housing 2.
  • the housing 2 consists of a middle housing ring 2a and two housing plates 2b and 2c placed thereon on the end faces, which are tightly clamped to one another and to the housing ring 2a by screws 6.
  • the housing plate 2b has an axial bore for the passage and possibly for the mounting of a pinion shaft 4, via which a pinion 5 can be driven which is in engagement with the ring gear 3.
  • the pinion 5 is thus supported on one side via its pinion shaft 4; its right end face (in FIG. 2) lies sealingly against the inner wall of the housing plate 2c during operation.
  • the pinion shaft 4 can be mounted in the axial bore of the housing plate 2b, which is not shown in detail, but also outside of it, in the latter case the housing bore only containing a seal.
  • a filler piece designated as a whole by 7, which is composed of two filler piece parts 7a and 7b.
  • the filler parts 7a, 7b lie alongside one another along a separating surface 8 and are supported with their end faces 10, 11 facing the suction chamber on a flat surface 12 of a support element 13.
  • the support element 13 which essentially corresponds to the so-called “filler pin” of known internal gear machines, passes through the sickle-shaped suction space in which the filler 7 is arranged in the axial direction and is formed in one piece with the housing plate 2b (see FIG. 2). Its sides facing the ring gear 3 or the pinion 5 are designed accordingly in accordance with the top rice diameter thereof.
  • the end faces 10, 11 of the filler parts 7a, 7b are partially cylindrically curved, the cylinder axis or axis of curvature running parallel to the axis of the gearwheels 3 and 5 and to the “longitudinal axis” of the support element 13.
  • the filler part 7a is shell-shaped and has a pressure equalization bore, not specified, which leads to a space in the filler part 7b in which two mutually parallel sealing rollers are mounted.
  • the mode of operation of this training is known and does not require any detailed explanation at this point.
  • the ring gear 3 has radially through bores 3a which serve for the inflow and outflow of the flow medium conveyed through housing channels, which are not identified in any more detail.
  • FIGS. 3 and 4 has the same structure as that according to FIGS. 1 and 2, with the exception of the support of the filling piece. For this reason, the housing is omitted from the drawing and corresponding parts are provided with the same reference numerals.
  • the filler parts 17a, 17b have flat end faces 20, 21 on the suction chamber side, which abut the likewise flat support surface 22 of an intermediate piece 23.
  • the intermediate piece 23 has essentially the shape of a flat cuboid and has on its side opposite the support surface 23 a partially cylindrical longitudinal groove which forms a sliding surface 24. With this sliding surface, the intermediate piece 23 is mounted on the circumference of a cylindrical pin 25 which is pressed into a bore 26 in the housing plate 2b.
  • the filler parts 7a, 7b are supported with their convex end faces 10, 11 on the support surface 12 of the support element 13 and, due to the compressive forces acting on them, can carry out compensatory movements in the radial direction by opening them the support surface 12 are moved.
  • the end faces 10, 11 owing to the convex shape of the end faces 10, 11, they can carry out rolling or rolling movements on this support surface 12, which result in pivoting of the filler parts 7a, 7b. In this way, the filler 7 can follow the relative movements that occur during operation and prevent the occurrence of radial gaps between parts that lie tightly against one another.
  • the filler parts 17a, 17 are displaceable in the radial direction (inwards or outwards) on the support surface 22.
  • a pivoting adjustment of the filler 17 is possible due to the rotatable mounting of the intermediate piece 23 on the pin 25.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Description

Die Erfindung betrifft eine Innenzahnradmaschine, insbesondere eine Innenzahnradpumpe, mit den Merkmalen gemäss dem Oberbegriff des Anspruches 1.The invention relates to an internal gear machine, in particular an internal gear pump, with the features according to the preamble of claim 1.

Bei einer bekannten Innenzahnradmaschine der vorstehend angegebenen Art (DE-A-29 42 417) ist der Füllstückstift zur Abstützung des längsgeteilten Füllstückes um seine Längsachse drehbar gelagert. Hierdurch wird erreicht, dass die Füllstückteile sowohl in radialer Richtung auf der Stützfläche des Füllstückstiftes verschiebbar sind, als auch über die Drehbarkeit des Füllstückstiftes eine Verschwenkbewegung um die Längsachse des Füllstückstiftes ausführen können. Damit wird eine weitgehende Dichtanlage der Füllstückteile an den Zahnköpfen der zugeordneten Zahnräder auch bei Relativbewegungen, Verschleiss und dgl. erreicht. Die drehbare Lagerung des Füllstückstiftes muss jedoch äusserst präzise sein, damit der angestrebte Zweck erreicht wird; andernfalls würde der Füllstückstift und/oder das darauf abgestützte Füllstück nicht richtig geführt und könnte daher die erwünschten Ausgleichsbewegungen nicht ausführen. Die präzise beidendige Lagerung des Füllstückstiftes erfordert wiederum, dass die Gehäusewandungen, in denen sich der Füllstückstift abstützt, d.h. die einander gegenüberliegenden Gehäuseteile, sehr genau zueinander ausgerichtet und in dieser ausgerichteten Lage miteinander verbunden werden. Dies erfordert einen beträchtlichen Herstelluhgs- und Montageaufwand, der sich im Erstellungspreis der Innenzahnradmaschine kostenerhöhend niederschlägt.In a known internal gear machine of the type specified above (DE-A-29 42 417), the filler pin for supporting the longitudinally divided filler is rotatably mounted about its longitudinal axis. In this way it is achieved that the filler parts are both displaceable in the radial direction on the support surface of the filler pin, and can also perform a pivoting movement about the longitudinal axis of the filler pin via the rotatability of the filler pin. An extensive sealing of the filler parts on the tooth heads of the assigned gears is thus achieved even with relative movements, wear and the like. However, the rotatable mounting of the filler pin must be extremely precise so that the intended purpose is achieved; otherwise the filler pin and / or the filler supported thereon would not be guided correctly and could therefore not carry out the desired compensatory movements. The precise double-ended mounting of the filler pin in turn requires that the housing walls in which the filler pin is supported, i.e. the opposite housing parts, very precisely aligned with each other and connected to each other in this aligned position. This requires a considerable manufacturing and assembly effort, which is reflected in the production price of the internal gear machine, which increases costs.

Der Erfindung liegt deshalb die Aufgabe zugrunde, eine Innenzahnradmaschine der eingangs angegebenen Artso auszubilden, dass ohne Beeinträchtigung der Kompensations- und Dichtwirkung des Füllstückes auf eine besondere Präzision bei der Verbindung der das Gehäuse bildenden Teile miteinander verzichtet werden kann.The invention is therefore based on the object of designing an internal gear machine of the type specified at the outset such that a particular precision in the connection of the parts forming the housing to one another can be dispensed with without impairing the compensation and sealing action of the filler.

Zur Lösung dieser Aufgabe schlägt die Erfindung zwei grundsätzlich Ausgestaltungen vor, die jeweils im Kennzeichen der Ansprüche 1 und 3 angegeben sind.To achieve this object, the invention proposes two basic configurations, each of which is specified in the characterizing part of claims 1 and 3.

Gemeinsam ist den beiden grundsätzlichen Ausführungen, dass an die Stelle eines drehbar gelagerten Füllstückstiftes ein Abstützelement tritt, welches undrehbar fest mit nur einer Gehäusewand verbunden ist. infolge dieser festen einseitigen Verbindung, die in einer zweckmässigen Ausführungsform durch einstückige Ausbildung des Abstützelements mit der Gehäusewand erreicht werden kann, kommen Spiele aufgrund von Lagertoleranzen in Wegfall und auch die elastischen Verformungen können klein gehalten werden. Um nun die erwünschte Schwenkbeweglichkeit der Füllstückteile zu realisieren, stützen sich bei der ersten grundsätzlichen Ausführungsform die Füllstückteile mit konvex gekrümmten Stirnseiten auf der Stützfläche des Abstützelements ab, so dass sie auf dieser in radialer Richtung - wie bisher - verschiebbar sind, zugleich aber Wälzbewegungen ausführen können. Diese Wälzbewegungen um die Krümmungsachse bewirken die notwendige Verschwenkung der Füllstückteile um diese Achse und damit die individuelle Anlage an den Zahnköpfen. Bei der zweiten grundsätzlichen Ausführungsform stützen sich die Füllstückteile an einem Zwischenstück ab, das auf der einen Seite die Stützfläche und auf der anderen Seite eine Gleitfläche aufweist, mit dem das Zwischenstück auf der zumindest teilzylindrischen Lagerfläche des Abstützelements verschwenken kann. Bei dieser Ausführungsform erfolgen die radialen Verschiebebewegungen der Füllstückteile bei der Kompensation von Radialspalten auf der Stützfläche, während die Verschwenkbewegungen durch die Verstellung des Zwischenstückes auf der Lagerfläche bewirkt werden.What the two basic designs have in common is that a rotatable filler pin is replaced by a support element which is non-rotatably connected to only one housing wall. As a result of this fixed one-sided connection, which can be achieved in an expedient embodiment by integrally forming the support element with the housing wall, games are eliminated due to bearing tolerances and the elastic deformations can also be kept small. In order to realize the desired pivoting mobility of the filler parts, in the first basic embodiment the filler parts are supported with convexly curved end faces on the support surface of the support element, so that they can be moved in the radial direction - as before - but at the same time can carry out rolling movements . These rolling movements around the axis of curvature bring about the necessary pivoting of the filler parts about this axis and thus the individual contact with the tooth tips. In the second basic embodiment, the filler parts are supported on an intermediate piece which has the support surface on one side and a sliding surface on the other side, with which the intermediate piece can pivot on the at least partially cylindrical bearing surface of the support element. In this embodiment, the radial displacement movements of the filler parts take place in the compensation of radial gaps on the support surface, while the pivoting movements are brought about by the adjustment of the intermediate piece on the bearing surface.

Da bei beiden grundsätzlichen Ausführungsformen der Erfindung das Abstützelement für das Füllstück nur mit einer Gehäusewand unabhängig ist, bedarf es einer exakten Ausrichtung der beiden Gehäusewände zueinander allein wegen der Lagerung des Füllstück-Abstützelementes nicht. Dies gilt allgemein auch dann, wenn das Ritzel zu beiden Seiten im Gehäuse gelagert ist, da die Ritzellagerung nicht die gleiche Präzision wie die Lagerung des Füllstückstiftes erforderlich macht. In gesteigertem Masse jedoch kann auf eine besondere Präzision bei der Ausrichtung der Gehäuseteile zueinander verzichtet werden, wenn darüber hinaus das Ritzel ebenfalls nur einseitig (fliegend) im Gehäuse oder ausserhalb davon gelagert ist, so dass bei der Verbindung der Gehäuseteile miteinander auch auf die Ritzellagerung keine Rücksicht genommen zu werden braucht. In beiden Fällen stützt sich die von Lagerelementen freie Gehäusewand lediglich abdichtend an den Stirnseiten des Abstützelements und des Ritzels ab.Since in both basic embodiments of the invention the support element for the filler is only independent with one housing wall, an exact alignment of the two housing walls with one another is not necessary simply because of the mounting of the filler support element. This also applies in general if the pinion is mounted on both sides in the housing, since the pinion bearing does not require the same precision as the bearing of the filler pin. To an increased extent, however, special precision in the alignment of the housing parts with respect to one another can be dispensed with if, in addition, the pinion is also only supported on one side (overhung) in the housing or outside it, so that when the housing parts are connected to one another there is also no pinion bearing Needs to be considered. In both cases, the housing wall, which is free of bearing elements, is only supported in a sealing manner on the end faces of the support element and the pinion.

Die Stützfläche, auf der sich die konvexen Stirnseiten der Füllstückteile bei der ersten grundsätzlichen Ausführungsform der Erfindung abstützen, ist zweckmässigerweise eben, um die radiale Verschieblichkeit der Füllstückteile nicht zu behindern. Jedoch kann auch eine geringfügig konkave Krümmung erwogen werden, sofern diese nicht zu einer merklichen Verschiebung der Füllstückteile in Umfangsrichtung bei der Radialverschiebung führt, weil hierduch die Beanspruchung an der Kontaktstelle zwischen Füllstückteilen und Stützfläche herabgesetzt wird. Bei der zweiten grundsätzlichen Ausführungsform kann einezweckmässige Ausbildung darin bestehen, dass das Abstützelement ein in eine Bohrung der Gehäusewand eingepresster zylindrischer Zapfen oder Stift ist, der teilweise von der entsprechend teil-hohlzylindrischen Gleitfläche des Zwischenstücks umfasst ist. Die Stützfläche des Zwischenstückes kann darüber hinaus teilweise zurückgenommen sein, weil diese bei der grundsätzlichen zweiten Ausführungsform der Erfindung geringer belastet ist.The support surface on which the convex end faces of the filler parts are supported in the first basic embodiment of the invention is expediently flat so as not to impede the radial displaceability of the filler parts. However, a slightly concave curvature can also be considered, provided that this does not lead to a noticeable displacement of the filler parts in the circumferential direction during the radial displacement, since this reduces the stress at the contact point between the filler parts and the support surface. In the second basic embodiment, an expedient embodiment can consist in the support element being a cylindrical pin or pin which is pressed into a bore in the housing wall and which is partially surrounded by the corresponding partially hollow-cylindrical sliding surface of the intermediate piece. The support surface of the intermediate piece can also be partially withdrawn because it is less loaded in the basic second embodiment of the invention.

Ausführungsbeispiele der vorliegenden Erfindung sind nachfolgend anhand der beiliegenden Zeichnungen näher erläutert. In den Zeichnungen zeigen:

  • Fig.1 eine Seitenansicht bei geöffnetem Gehäuse eines Beispiels für die grundsätzliche erste Ausführungsform der Erfindung;
  • Fig. 2 einen Schnitt längs der Linie 11-11 in Fig. 1 ;
  • Fig. 3 eine Seitenansicht eines Beispiels für die grundsätzliche zweite Ausführungsform der Erfindung, bei der aus Vereinfachungsgründen das Gehäuse nicht gezeichnet ist, und
  • Fig. 4 einen Teilschnitt längs der Linie IV-IV in Fig. 3.
Exemplary embodiments of the present invention are explained in more detail below with reference to the accompanying drawings. The drawings show:
  • 1 shows a side view with the housing open of an example of the basic first off embodiment of the invention;
  • 2 shows a section along the line 11-11 in Fig. 1.
  • Fig. 3 is a side view of an example of the basic second embodiment of the invention, in which the housing is not drawn for reasons of simplicity, and
  • 4 shows a partial section along the line IV-IV in FIG. 3.

Bei der in Fig. 1 dargestellten Innenzahnradpumpe ist in einer Bohrung 1 eines Gehäuses 2 ein innenverzahntes Hohlrad 3 gleitend gelagert. Das Gehäuse 2 besteht aus einem mittleren Gehäusering 2a und zwei stirnseitig darauf aufgesetzten Gehäuseplatten 2b und 2c, die miteinander und mit dem Gehäusering 2a durch Schrauben 6 dicht verspannt sind. Die Gehäuseplatte 2b weist eine Axialbohrung zur Hindurchführung und ggf. zur Lagerung einer Ritzelwelle 4 auf, über die ein Ritzel 5 antreibbar ist, das mit dem Hohlrad 3 in Eingriff steht. Das Ritzel 5 ist über seine Ritzelwelle 4 somit einseitig gelagert; seine (in Fig. 2) rechte Stirnseite liegt im Betrieb abdichtend an der Innenwand der Gehäuseplatte 2c an. Die Ritzelwelle 4 kann in der hierzu nicht näher gezeigten Axialbohrung der Gehäuseplatte 2b, aber auch ausserhalb davon gelagert sein, wobei im letzteren Fall die Gehäusebohrung lediglich eine Abdichtung enthält.In the internal gear pump shown in Fig. 1, an internally toothed ring gear 3 is slidably mounted in a bore 1 of a housing 2. The housing 2 consists of a middle housing ring 2a and two housing plates 2b and 2c placed thereon on the end faces, which are tightly clamped to one another and to the housing ring 2a by screws 6. The housing plate 2b has an axial bore for the passage and possibly for the mounting of a pinion shaft 4, via which a pinion 5 can be driven which is in engagement with the ring gear 3. The pinion 5 is thus supported on one side via its pinion shaft 4; its right end face (in FIG. 2) lies sealingly against the inner wall of the housing plate 2c during operation. The pinion shaft 4 can be mounted in the axial bore of the housing plate 2b, which is not shown in detail, but also outside of it, in the latter case the housing bore only containing a seal.

In dem zwischen den Zahnrädern 3 und 5 befindlichen sichelförmigen Raum ist ein im Ganzen mit 7 bezeichnetes Füllstück angeordnet, das aus zwei Füllstückteilen 7a und 7b zusammengesetzt ist. Die Füllstückteile 7a, 7b liegen längs einer Trennfläche 8 aneinander und stützen sich mit ihren dem Saugraum zugewendeten Stirnseiten 10, 11 an einer ebenen Fläche 12 eines Abstützelements 13 ab. Das Abstützelement 13, das im wesentlichen dem sog. « Füllstückstift» bekannter Innenzahnradmaschinen entspricht, durchsetzt den sichelförmigen Saugraum, in dem das Füllstück 7 angeordnet ist, in axialer Richtung und ist einstükkig mit der Gehäuseplatte 2b ausgebildet (vgl. Fig. 2). Seine dem Hohlrad 3 bzw. dem Ritzel 5 zugewendeten Seiten sind in Anpassung an den Kopfreisdurchmesser derselben entsprechend ausgeführt.In the crescent-shaped space located between the gears 3 and 5 there is arranged a filler piece, designated as a whole by 7, which is composed of two filler piece parts 7a and 7b. The filler parts 7a, 7b lie alongside one another along a separating surface 8 and are supported with their end faces 10, 11 facing the suction chamber on a flat surface 12 of a support element 13. The support element 13, which essentially corresponds to the so-called “filler pin” of known internal gear machines, passes through the sickle-shaped suction space in which the filler 7 is arranged in the axial direction and is formed in one piece with the housing plate 2b (see FIG. 2). Its sides facing the ring gear 3 or the pinion 5 are designed accordingly in accordance with the top rice diameter thereof.

Die Stirnflächen 10, 11 der Füllstückteile 7a, 7b sind teilzylindrisch konvex gekrümmt, wobei die Zylinderachse oder Krümmungsachse parallel zu der Achse der Zahnräder 3 und 5 und zur «Längsachse» des Abstützelements 13 verläuft.The end faces 10, 11 of the filler parts 7a, 7b are partially cylindrically curved, the cylinder axis or axis of curvature running parallel to the axis of the gearwheels 3 and 5 and to the “longitudinal axis” of the support element 13.

Das Füllstückteil 7a ist schalenförmig ausgebildet und weist eine nicht näher bezeichnete Druckausgleichsbohrung auf, die zu einem Raum in dem Füllstückteil 7b führt, in welchem zwei zueinander parallele Dichtwalzen gelagert sind. Die Wirkungsweise dieser Ausbildung ist bekannt und bedarf an dieser Stelle keiner ins Detail gehenden Erläuterung.The filler part 7a is shell-shaped and has a pressure equalization bore, not specified, which leads to a space in the filler part 7b in which two mutually parallel sealing rollers are mounted. The mode of operation of this training is known and does not require any detailed explanation at this point.

Das Hohlrad 3 weist ausgehend von dem Grund seiner Zahnlücken radial durchgehende Bohrungen 3a auf, die für den Zu- und Abfluss des durch nicht näher bezeichnete Gehäusekanäle geförderten Strömungsmediums dienen.Starting from the bottom of its tooth gaps, the ring gear 3 has radially through bores 3a which serve for the inflow and outflow of the flow medium conveyed through housing channels, which are not identified in any more detail.

Die Ausführungsform gemäss den Fig. 3 und 4 ist mit Ausnahme der Abstützung des Füllstückes gleich aufgebaut wie diejenige gemäss den Fig. 1 und 2. Aus diesem Grund ist in der zeichnerischen Darstellung davon das Gehäuse weggelassen und übereinstimmende Teile sind mit gleichen Bezugszeichen versehen.The embodiment according to FIGS. 3 and 4 has the same structure as that according to FIGS. 1 and 2, with the exception of the support of the filling piece. For this reason, the housing is omitted from the drawing and corresponding parts are provided with the same reference numerals.

Abweichend von dem zuvor beschriebenen Ausführungsbeispiel weisen die Füllstückteile 17a, 17b ebene saugraumseitige Stirnflächen 20, 21 auf, die an der ebenfalls ebenen Stützfläche 22 eines Zwischenstückes 23 anliegen. Das Zwischenstück 23 hat im wesentlichen die Gestalt eines flachen Quaders und weist auf seiner der Stützfläche 23 gegenüberliegenden Seite eine teilzylindrische Längsnut auf, die eine Gleitfläche 24 bildet. Mit dieser Gleitfläche ist das Zwischenstück 23 auf dem Umfang eines zylindrischen Zapfens 25 gelagert, der in eine Bohrung 26 der Ge" häuseplatte 2b eingepresst ist.In a departure from the exemplary embodiment described above, the filler parts 17a, 17b have flat end faces 20, 21 on the suction chamber side, which abut the likewise flat support surface 22 of an intermediate piece 23. The intermediate piece 23 has essentially the shape of a flat cuboid and has on its side opposite the support surface 23 a partially cylindrical longitudinal groove which forms a sliding surface 24. With this sliding surface, the intermediate piece 23 is mounted on the circumference of a cylindrical pin 25 which is pressed into a bore 26 in the housing plate 2b.

Beim Betrieb des Ausführungsbeispiels gemäss den Fig. 1, 2 stützen sich die Füllstückteile 7a, 7b mit ihren konvexen Stirnflächen 10, 11 an der Stützfläche 12 des Abstützelements 13 ab und können aufgrund der an ihnen wirkenden Druckkräfte Ausgleichsbewegungen in radialer Richtung ausführen, indem sie auf der Stützfläche 12 verschoben werden. Darüber hinaus können sie aufgrund der konvexen Gestalt der Stirnflächen 10, 11 auf dieser Stützfläche 12 Abwälz- oder Rollbewegungen ausführen, die eine Verschwenkung der Füllstückteile 7a, 7b ergeben. Auf diese Weise kann das Füllstück 7 den während des Betriebes auftretenden Relativbewegungen folgen und das Auftreten von Radialspalten zwischen dichtend aneinanderliegenden Teilen verhindern.1, 2, the filler parts 7a, 7b are supported with their convex end faces 10, 11 on the support surface 12 of the support element 13 and, due to the compressive forces acting on them, can carry out compensatory movements in the radial direction by opening them the support surface 12 are moved. In addition, owing to the convex shape of the end faces 10, 11, they can carry out rolling or rolling movements on this support surface 12, which result in pivoting of the filler parts 7a, 7b. In this way, the filler 7 can follow the relative movements that occur during operation and prevent the occurrence of radial gaps between parts that lie tightly against one another.

Bei der Ausführungsform gemäss den Fig. 3 und 4 sind die Füllstückteile 17a, 17 in radialer Richtung (nach innen oder aussen) auf der Stützfläche 22 verschiebbar. Darüber hinaus ist eine Schwenkeinstellung des Füllstückes 17 aufgrund der drehbaren Lagerung des Zwischenstückes 23 auf dem Zapfen 25 möglich.In the embodiment according to FIGS. 3 and 4, the filler parts 17a, 17 are displaceable in the radial direction (inwards or outwards) on the support surface 22. In addition, a pivoting adjustment of the filler 17 is possible due to the rotatable mounting of the intermediate piece 23 on the pin 25.

Im Rahmen der Erfindung sind Abwandlungen von den vorstehend beschriebenen Ausführungsbeispielen möglich. So ist es nicht erforderlich, die Krümmung der Stirnseiten 10,11 der Füllstückteile 7a und 7b kreiszylindrisch auszuführen; es ist auch eine Krümmung mit nicht konstantem Krümmungsradius denkbar, um die notwendige Abwälz- und Verschwenkbewegung zu erhalten. Entsprechendes gilt für die Lagerfläche des Zapfens 25 und die darauf gleitende Gleitfläche 24 des Zwischenstückes 23. Die hier beschriebene Innenzahnradmaschine kann vollständig aus Kunststoff gefertigt sein, wobei sich die einstückige Ausbildung des Abstützelements 13 bzw. 23 mit der zugehörigen Gehäusewand anbietet.Modifications of the exemplary embodiments described above are possible within the scope of the invention. So it is not necessary to make the curvature of the end faces 10, 11 of the filler parts 7a and 7b circular cylindrical; a curvature with a non-constant radius of curvature is also conceivable in order to obtain the necessary rolling and pivoting movement. The same applies to the bearing surface of the pin 25 and the sliding surface 24 of the intermediate piece 23 sliding thereon. The internal gear machine described here can be made entirely of plastic, the integral construction of the support element 13 or 23 with the associated housing wall being available.

Claims (6)

1. An internal-gear machine, in particular an internal-gear pump, comprising a casing (2), an annular gear (3) which is mounted rotatably with its periphery in the casing, an externally toothed pinion (5) meshing with the annular gear, and a sickle-shaped filling member (7) which is divided along a substantially circumferentially extending junction surface, the portions of the filling member being supported with their end faces which are on the suction side against a support surface of a support element (13) which extends axially through the space between the annular gear and the pinion, in such a way that they are displaceable in a radial direction against the support surface and are pivotable about a pivot axis extending parallel to the axis of the pinion, characterised in that the support element (13) is fixedly connected only to one casing wall (2b) and the end faces (10, 11 ) of the filling member portions (7a, 7b) have a convex curvature with an axis of curvature extending parallel to the pivot axis.
2. An internal-gear machine according to claim 1, characterised in that the support element (13) is in one piece with the casing wall (2b).
3. An internal-gear machine, in particular an internal-gear pump, comprising a casing (2), an annular gear (3) which is mounted rotatably with its periphery in the casing, an externally toothed pinion (5) meshing with the annular gear, and a sickle-shaped filling member (7) which is divided along a substantially circumferentially extending junction surface, the portions of the filling member being supported with their end faces which are on the suction side against a support surface of a support element which extends axially through the space between the annular gear and the pinion, in such a way that they are displaceable in a radial direction and are pivotable about a pivot axis extending parallel to the axis of the pinion, characterised in that the support element is formed by a pin (25) which is fixedly connected to only one casing wall (2b), with an at least part-cylindrical bearing surface, and by an intermediate member (23) which has the support surface (22) for the filling member portions (17a, 17b) and which bears pivotably against the bearing surface with a sliding surface (24) which is of complementary curvature to the bearing surface.
4. An internal-gear machine according to claim 3, characterised in that the cylindrical pin (25) is pressed into a bore (26) in the casing wall (2b).
5. An internal-gear machine according to one of claims 1 to 4, characterised in that the support surface (12, 22) is flat.
6. An internal-gear machine according to claim 3 or claim 4, characterised in that the support surface (22) is partially set back at the intermediate portion (23).
EP86117212A 1985-12-18 1986-12-10 Internally-meshing gears machine Expired EP0226177B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3544857 1985-12-18
DE3544857A DE3544857C2 (en) 1985-12-18 1985-12-18 Internal gear machine

Publications (2)

Publication Number Publication Date
EP0226177A1 EP0226177A1 (en) 1987-06-24
EP0226177B1 true EP0226177B1 (en) 1989-03-01

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ID=6288807

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86117212A Expired EP0226177B1 (en) 1985-12-18 1986-12-10 Internally-meshing gears machine

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US (2) US4778363A (en)
EP (1) EP0226177B1 (en)
DE (2) DE3544857C2 (en)

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DE3723557A1 (en) * 1987-07-16 1989-01-26 Eckerle Otto Gmbh & Co INTERNAL GEAR MACHINE
CH682836A5 (en) * 1990-02-19 1993-11-30 Bucher Maschf Gmbh Internal gear machine.
DE4104397C2 (en) * 1990-03-09 1993-12-16 Voith Gmbh J M Internal gear pump
US5197869A (en) * 1991-03-22 1993-03-30 The Gorman-Rupp Company Rotary gear transfer pump having pressure balancing lubrication, bearing and mounting means
DE4336966A1 (en) * 1993-10-29 1995-05-04 Otto Eckerle Internal gear machine
US6945723B1 (en) * 2000-09-21 2005-09-20 L'oréal Packaging and application device
KR100412612B1 (en) * 2001-12-15 2003-12-31 현대자동차주식회사 Oil pump
DE102007054808A1 (en) * 2007-11-16 2009-05-20 Robert Bosch Gmbh Pump assembly for synchronous pressurization of two fluid circuits
CN102865224A (en) * 2011-07-05 2013-01-09 冀珂 Ultra-high molecular polyethylene gear pump
JP6190938B1 (en) * 2016-10-11 2017-08-30 大同機械製造株式会社 Internal gear pump

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US2482713A (en) * 1944-06-27 1949-09-20 Bergen Engineering And Sales C Rotary internal gear pump
DE1403924A1 (en) * 1961-01-24 1968-11-28 Oilenergetic Establishment Fill piece for internal runner gear machines
GB1129605A (en) * 1965-01-22 1968-10-09 Harald Hagenes Hydraulic gear pumps and motors
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JPS52694A (en) * 1975-06-12 1977-01-06 Kato Yukio Filtration device for fish farming
DE2606082A1 (en) * 1976-02-16 1977-08-25 Otto Eckerle HIGH PRESSURE GEAR PUMP OR MOTOR
DE2733712A1 (en) * 1976-07-27 1978-02-02 Eckerle Otto High pressure gear pump or motor - has eccentrically offset gears meshing internally with deflector in space between
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DE3416400C2 (en) * 1984-05-03 1993-10-07 Schwaebische Huettenwerke Gmbh Motor vehicle oil pump

Also Published As

Publication number Publication date
DE3544857C2 (en) 1994-09-29
US4780071A (en) 1988-10-25
DE3544857A1 (en) 1987-06-19
DE3662214D1 (en) 1989-04-06
EP0226177A1 (en) 1987-06-24
US4778363A (en) 1988-10-18

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