EP0302190B1 - Internal-gear machine - Google Patents

Internal-gear machine Download PDF

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Publication number
EP0302190B1
EP0302190B1 EP88108387A EP88108387A EP0302190B1 EP 0302190 B1 EP0302190 B1 EP 0302190B1 EP 88108387 A EP88108387 A EP 88108387A EP 88108387 A EP88108387 A EP 88108387A EP 0302190 B1 EP0302190 B1 EP 0302190B1
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EP
European Patent Office
Prior art keywords
internal
filling portion
machine according
filler
gear machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP88108387A
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German (de)
French (fr)
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EP0302190A1 (en
Inventor
Otto Eckerle
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Eckerle Rexroth GmbH and Co KG
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Otto Eckerle GmbH and Co KG
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Publication of EP0302190A1 publication Critical patent/EP0302190A1/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 patent claim 1.
  • the filler piece is so flexibly mounted in internal gear machines (cf. DE-A-15 53 027; CH-A-601 670) that it can follow the movements of the meshing gears during operation in order to compensate for radial leakage gaps that arise due to the movement.
  • internal gear machines cf. DE-A-15 53 027; CH-A-601 670
  • Through a targeted control of the hydraulic forces acting on the filler which is carried out by means of pre-filling grooves or slots provided on the filler and / or on the surfaces lying against it (cf. DE-A-15 53 027), it is ensured that the filler is at least partially by the action of the hydraulic forces held in the optimal position for the seal, ie pressed against the tooth tips of the gears.
  • an internal gear machine according to the preamble of claim 1 is also known (DE-A-22 23 916), in which the filler piece is supported by a bearing journal which is rotatably supported on both ends in the opposite housing walls.
  • the bearing journal In its central section, the bearing journal is shaped into a bearing body which is approximately square in cross section, which is received in a groove of the filling piece which is adapted in cross section and in this way also supports the filling piece so that it can be displaced in the radial direction. Since the bearing body also passes axially through the bearing body in this case of the filler piece and is therefore limited in its possible cross section in accordance with the dimensions of the filler piece, high operating pressures cannot be used.
  • the invention is therefore based on the object to provide an internal gear machine of the type specified, in particular for the promotion of low-viscosity media, which is not subject to the restrictions described with regard to the level of the operating pressure, but without the risk of overloading the filler bearing and the risk of being pulled in of the filler in the tooth mesh is excluded with certainty.
  • the invention is based on the consideration that a greater freedom in the arrangement of the bearing body is obtained by relocating the filler bearing from the suction chamber end towards the filler tip, so that on the one hand the bearing body has the largest possible storage area and, as a result, a corresponding one low surface pressure can be realized, but on the other hand it can also be ensured that the resultant of the hydraulic forces acting on the filler from the pressure chamber also passes through the bearing surface without the pressure chamber having to be enlarged unnecessarily. It goes without saying that with increasing operating pressure there must be an interest in keeping the pressure space as small as possible in order to keep the load on the internal gear machine within limits.
  • the bearing journal is expediently arranged in the filler half facing the suction chamber end of the filler and, in the limit case, lies in the longitudinal center of the filler.
  • Favorable kinematic conditions for the radial gap compensation are also obtained if the axis of rotation of the bearing pin passes through the filler at a point closer to the circumferential surface of the ring gear.
  • the bearing body is designed asymmetrically with respect to the axis of rotation of the bearing pin, since it is offset relative to the filler piece relative to the filler piece in accordance with the eccentric arrangement of the bearing pin axis.
  • the storage of the filling piece which is offset towards the filling piece tip, allows greater freedom in the orientation of the bearing surface.
  • the bearing surface and the groove receiving the bearing body in the side surface of the filling piece will always be placed in such a way that an optimal distribution of the filling piece on the one hand in Direction of the pinion, on the other hand, forces urging in the direction of the ring gear.
  • this always enables a compromise, which leads to a relatively large storage area and the resulting low surface pressure.
  • the bearing body which is expediently one-piece with the journal, has two mutually parallel flat surfaces, of which the bearing surface facing the filler tip assumes the support of the filler against the hydraulic and other forces that are effective during operation, while the surface facing the suction chamber is the retention surface , which absorbs the forces acting on the filler from the suction chamber and the frictional forces exerted on the filler by the gearwheels. Since these opposing forces do not coincide in terms of direction, however, in particular in the case of a long filler piece in which the frictional force component is greater, it can be considered to allow the bearing surfaces on the bearing body to run at a corresponding angle to one another, this angle normally being in Direction towards the ring gear opens.
  • the cross-section of the bearing body is thus wedge-shaped in this case, the suction-space-side retention surface being positioned such that the pressure forces acting from the suction space and the frictional forces are directed perpendicularly or almost perpendicularly to this surface.
  • the play between the filler and this retaining surface can always be kept small even with a parallel arrangement of the bearing surface and the retaining surface. In the described embodiment of the bearing body with a wedge-shaped cross section, this is possible to a particular degree, since the play decreases when the filler moves in the direction of the ring gear due to the wedge shape.
  • the embodiment according to the invention can in principle also be used for multi-part filling pieces (cf. DE-A-26 06 082).
  • the groove provided on the side of the filler expediently penetrates all parts or segments of the filler.
  • the retaining surface of the bearing body is not a flat surface, but has a kink at the separation point between the sealing segment and segment carrier on. This takes into account the fact that the Segment carrier and forces acting on the sealing segment from the suction space and the frictional forces have different directions. In order to align the retaining surface in the sense already explained above so that these forces are absorbed vertically, this adjustment is necessary.
  • the internal gear pump according to FIG. 1 has a housing 1 (not shown in more detail), an internal gear or ring gear 2 mounted therein with its circumference, a pinion 3 mounted in the housing and equipped with a shaft (not shown), and a filling piece designated as 4 overall.
  • the ring gear 2 bears on its entire circumference in a known manner only partially indicated openings 5, which enables the pumped medium that enters through a suction opening 6 to get into the suction chamber 7 and out of the pressure chamber 8 exit again, after which it is discharged through a pressure connection 9.
  • the structure of the internal gear pump described so far is conventional and therefore requires no further explanation.
  • the filler 4 has the shape of a half-crescent or a comma and is made relatively long in the embodiment shown, so that it is in contact with nine teeth of the ring gear 2 on its outer circumferential surface in order to achieve the best possible for the purpose of conveying particularly thin media Get waterproofing.
  • the filler 4 is composed of a shell-shaped sealing segment 11 and a segment carrier 12, which abut one another along a separating surface 13 which extends in the circumferential direction and are sealed off from one another by two sealing rollers 14.
  • two lateral housing plates 15, which are only indicated in FIG. 2 blind bores 16 are formed for the rotatable mounting of one bearing pin 17 each.
  • the bearing pins 17 are assigned to the two side surfaces of the filler piece 4 and have bearing bodies 18 formed integrally thereon, which project in the direction of the filler piece from the end face of the bearing pins 17.
  • the bearing bodies 18 have two plane-parallel surfaces, of which the surface 19 facing the filler tip is the bearing surface for absorbing the forces acting from the pressure chamber 8 and the opposite surface 20 is the retaining surface for supporting the filler 4 against the forces acting from the suction chamber 7 .
  • the journals 17 are arranged relative to the filler 4 in such a way that the axis of rotation 10 of the journals 17 is offset in the direction of the tip of the filler 4 and is located at a point that the filler length is approximately in the ratio of 2 to 3 shares.
  • the axis of rotation 10 is close to the interface 13 between the sealing segment 11 and segment carrier 12, i.e. thus closer to the tooth tips of the ring gear 2.
  • grooves 21 corresponding to the bearing bodies 18 are incorporated, which are intended for receiving the bearing bodies 18 and their groove flanks on the bearing surface 19 and on of the retaining surface 20 and transfer the forces acting on the filler 4 to this.
  • the shape of the grooves 21 and the bearing bodies 18 engaging therein results from FIG. 1, from which it can be seen that, due to the eccentric arrangement of the axis of rotation 10 relative to the filler 4, the bearing bodies 18 are arranged eccentrically in relation to the end face of the journal 17 in the direction of the pinion 3 are. It can also be seen from FIG.
  • the bearing body 18 largely fills the grooves 21 of the filler 4, that is to say that they are at least approximately matched to the circumferential shape of the filler 4 on their circumferential boundary surfaces in order thereby to keep the surfaces 19 and 20 as large as possible.
  • the groove flanks of the grooves 21, as can also be seen in FIG. 1, run at an angle of approximately 30 degrees to the plane in which the axis of the pinion 3 and the axis of rotation 10 of the bearing pins 17 lie.
  • This position ensures that, on the one hand, the forces acting on the filler 4 from the pressure chamber 8 are distributed in such a way that the filler experiences an optimal sealing system on the ring gear 2 and on the pinion 3, and on the other hand the surface pressure which arises on the bearing surface 19 is as low as possible .
  • the direction of the resultant force of the hydraulic forces acting from the pressure chamber 8 is determined in a known manner by control slots (not shown) in the axial plates 15 and / or the side faces of the filler 4 (cf. DE-A-15 53 027).
  • the embodiment according to FIG. 2A differs from the embodiment described above only in that instead of two bearing journals 17 assigned to the two side surfaces of the filling piece 4, only a bearing journal 17 ′ which is arranged on one side and is provided with its bearing body 18 ′ in a groove 21 ′ arranged on one side is provided. of the filler engages.
  • FIG. 3 differs from the embodiment according to FIGS. 1 and 2 solely by the special design of the bearing body 28 on the bearing journal 27. For this reason, the other components of the internal gear pump are identified by the same reference numerals as in FIGS. 1 and 2 .
  • the bearing surface 29 is arranged, as in the first embodiment, at an angle of approximately 30 degrees to the plane containing the axis of rotation of the bearing journal 27 and the pinion 3, and is formed flat throughout.
  • the partial surfaces 30 'and 30 ⁇ meet in the area of the separating surface 13; the retention surface 30 is thus kinked.
  • This embodiment takes into account the fact that the forces acting from the suction space 7 act on the segment carrier 22 and the sealing segment 23 in different directions, so that it is necessary to incline them differently in the case of a vertical alignment of the respectively associated retaining surfaces.
  • FIG. 4 largely corresponds to that according to FIGS. 1 and 2; the only difference is that instead of a divided filler 4 an undivided filler 4 'is selected, in the axial side surfaces of which the bearing body receiving grooves are incorporated.

Description

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

Das Füllstück ist in Innenzahnradmaschinen (vgl. DE-A-15 53 027; CH-A-601 670) so beweglich gelagert, daß es im Betrieb den Bewegungen der miteinander kämmenden Zahnräder folgen kann, um hierdurch aufgrund der Bewegung entstehende radiale Leckspalte auszugleichen. Durch eine gezielte Steuerung der auf das Füllstück einwirkenden hydraulischen Kräfte, die mittels am Füllstück und/oder an den daran anliegenden Flächen vorgesehener Vorfüllnuten oder -schlitze erfolgt (vgl. DE-A-15 53 027) wird dafür gesorgt, daß das Füllstück zumindest teilweise durch das Einwirken der hydraulischen Kräfte in der für die Dichtung jeweils optimalen Lage gehalten, d.h. an die Zahnköpfe der Zahnräder angedrückt wird. Die Richtung und die Größe dieser Kräfte werden aufgrund der genannten Steuerung dabei durch die Höhe des im Druckraum herrschenden Betriebsdruckes sowie durch den Verlauf der durch die Steuerung bestimmten Trennfläche zwischen Saugraum und Druckraum bestimmt. Eindeutig bestimmt sind diese Kräfte jedoch genau genommen nur bei stationärem Betrieb der Zahnradmaschine. Herrscht hingegen kein Betriebsdruck im Druckraum oder treten Betriebszustände ein, bei denen der Druck im Saugraum sogar den Druck im Druckraum übersteigt (was beim Einsatz von vorgeschalteten Füllpumpen der Fall sein kann), dann wirken auf das Füllstück Kräfte ein, die dieses in Richtung auf den Zahneingriff der miteinander kämmenden Zahnräder drücken. In Verbindung mit den ohnehin in dieser Richtung auf das Füllstück einwirkenden Reibkräften zwischen Füllstück und Zahnköpfen besteht dabei die Gefahr, daß das Füllstück von den Zahnrädern mitgenommen wird und sich im Zahneingriff verkeilt. Dies hat die sofortige Blockierung und damit den Ausfall des angeschlossenen Geräts zur Folge.The filler piece is so flexibly mounted in internal gear machines (cf. DE-A-15 53 027; CH-A-601 670) that it can follow the movements of the meshing gears during operation in order to compensate for radial leakage gaps that arise due to the movement. Through a targeted control of the hydraulic forces acting on the filler, which is carried out by means of pre-filling grooves or slots provided on the filler and / or on the surfaces lying against it (cf. DE-A-15 53 027), it is ensured that the filler is at least partially by the action of the hydraulic forces held in the optimal position for the seal, ie pressed against the tooth tips of the gears. The direction and the magnitude of these forces are determined on the basis of the control mentioned, by the level of the operating pressure prevailing in the pressure chamber and by the course of the interface between the suction chamber and the pressure chamber determined by the control. However, these forces are clearly defined only when the gear machine is in stationary operation. If, on the other hand, there is no operating pressure in the pressure chamber or if there are operating states in which the pressure in the suction chamber even exceeds the pressure in the pressure chamber (which can be the case when using upstream filling pumps), then forces act on the filler that push it in the direction press the meshing of the meshing gears. In connection with the frictional forces acting in this direction on the filler piece between the filler piece and tooth heads, there is a risk that the filler piece will be carried along by the gears and wedged in meshing engagement. This results in immediate blocking and thus the failure of the connected device.

Um ein derartiges Verkeilen zu vermeiden, ist es bereits bekannt, das Füllstück in der eingangs angegebenen Art zu lagern, so daß es in beiden Umfangsrichtungen gehalten ist, ohne daß dadurch die freie Beweglichkeit zum Zweck der Radialspaltkompensation beeinträchtigt ist. Nachteilig ist bei dieser Ausführung jedoch, daß der das Füllstück durchsetzende Lagerzapfen entsprechend den Füllstückabmessungen in seinem Durchmesser begrenzt ist und daher hohe Betriebsdrücke nicht verträgt. Um höhere Betriebsdrücke verwirklichen zu können, ist man deshalb schon zu Lagerzapfen für das Füllstück übergegangen, die ganz außerhalb des Füllstückes verlaufen, eine Abstützfläche für das Füllstück aufweisen und aus diesem Grund stärker ausgeführt werden können. Um aber hierbei das Verkeilen zu vermeiden, wurde zusätzlich zur Rückhaltung des Füllstückes ein Federstift vorgesehen (DE-A-23 13 085). Bei den vorstehend geschilderten Betriebzuständen, in denen ein im Saugraum überwiegender Druck herrscht, kann aber auch durch den Federstift ein Hineinziehen des Füllstückes in den Zahneingriff bei laufender Maschine nicht mit Sicherheit ausgeschlossen werden. Dies gilt noch in verstärktem Maße in solchen Fällen, in denen das Fördermedium sehr dünnflüssig und gegebenenfalls zusätzlich noch nichtschmierend ist.In order to avoid such wedging, it is already known to store the filling piece in the manner specified at the outset, so that it is held in both circumferential directions without the free mobility for the purpose of radial gap compensation being impaired thereby. A disadvantage of this embodiment, however, is that the diameter of the bearing pin passing through the filler piece is limited in accordance with the filler piece dimensions and therefore cannot tolerate high operating pressures. In order to be able to achieve higher operating pressures, bearings for the filler piece have already been moved to, which run completely outside the filler piece, have a support surface for the filler piece and can therefore be made stronger. In order to avoid wedging, a spring pin was provided in addition to retaining the filler (DE-A-23 13 085). In the operating conditions described above, in which there is a predominant pressure in the suction chamber, a pulling of the filler into the tooth engagement while the machine is running cannot also be ruled out with certainty by the spring pin. This applies to an even greater extent in those cases in which the pumped medium is very thin and possibly additionally non-lubricating.

Denn bei solchen Fördermedien ist es aus Gründen der Abdichtung erforderlich, das Füllstück länger als an Innenzahnradmaschinen für Fördermedien von höherer Viskosität auszubilden, was aber den gleichzeitigen Eingriff einer höheren Zahl von Zahnköpfen mit dem Füllstück und eine daraus resultierende höhere Reibkraft zur Folge hat, die das Füllstück in den Zahneingriff zu ziehen sucht.Because with such conveying media it is necessary for sealing reasons to make the filler longer than on internal gear machines for conveying media of higher viscosity, but this results in the simultaneous engagement of a higher number of tooth tips with the filler and the resulting higher frictional force, which Trying to pull the filler into the tooth mesh.

Schließlich ist auch eine Innenzahnradmaschine gemäß dem Oberbegriff des Patentanspruches 1 bekannt (DE-A-22 23 916), bei der das Füllstück durch einen beidendig in den gegenüberliegenden Gehäusewandungen drehbar gelagerten Lagerzapfen abgestützt ist. Der Lagerzapfen ist in seinem mittleren Abschnitt zu einem im Querschnitt etwa quadratischen Lagerkörper geformt, der in einer im Querschnitt angepassten Nut des Füllstückes aufgenommen ist und auf diese Weise das Füllstück in radialer Richtung auch verschiebbar abstützt. Da auch bei dieser Füllstücklagerung der Lagerkörper das Füllstück axial durchsetzt und damit entsprechend den Füllstückabmessungen in seinem möglichen Querschnitt begrenzt ist, kann nicht mit hohen Betriebsdrücken gearbeitet werden. Darüber hinaus wird durch die Nut, welche von der dem Ritzel zugewendeten radialen Dichtfläche des Füllstückes her einspringt und die axiale Dicke des Füllstückes ganz durchsetzt, festigkeitsmässig gegenüber den vorstehend geschilderten Kräften, die in Richtung des Druckraumes wirken, eine Schwachstelle geschaffen. Dadurch ist die Betriebssicherheit dieser bekannten Innenzahnradmaschine beeinträchtigt.Finally, an internal gear machine according to the preamble of claim 1 is also known (DE-A-22 23 916), in which the filler piece is supported by a bearing journal which is rotatably supported on both ends in the opposite housing walls. In its central section, the bearing journal is shaped into a bearing body which is approximately square in cross section, which is received in a groove of the filling piece which is adapted in cross section and in this way also supports the filling piece so that it can be displaced in the radial direction. Since the bearing body also passes axially through the bearing body in this case of the filler piece and is therefore limited in its possible cross section in accordance with the dimensions of the filler piece, high operating pressures cannot be used. In addition, due to the groove which springs in from the radial sealing surface of the filler piece facing the pinion and completely penetrates the axial thickness of the filler piece, a weak point is created in terms of strength compared to the forces described above, which act in the direction of the pressure chamber. This affects the operational safety of this known internal gear machine.

Der Erfindung liegt daher die Aufgabe zugrunde, eine Innenzahnradmaschine der eingangs angegebenen Art zu schaffen, insbesondere zur Förderung dünnflüssiger Medien, die den geschilderten Beschränkungen bezüglich der Höhe des Betriebsdruckes nicht unterliegt, ohne daß aber die Gefahr einer Überbelastung der Füllstücklagerung besteht und die Gefahr eines Hineinziehens des Füllstückes in den Zahneingriff mit Sicherheit ausgeschlossen ist.The invention is therefore based on the object to provide an internal gear machine of the type specified, in particular for the promotion of low-viscosity media, which is not subject to the restrictions described with regard to the level of the operating pressure, but without the risk of overloading the filler bearing and the risk of being pulled in of the filler in the tooth mesh is excluded with certainty.

Erfindungsgemäß wird diese Aufgabe gelöst durch die Merkmale gemäß dem Kennzeichen des Patenanspruches 1.According to the invention, this object is achieved by the features according to the characterizing part of patent claim 1.

Die Erfindung geht dabei von der Überlegung aus, daß man durch eine Verlegung der Füllstücklagerung von dem saugraumseitigen Ende in Richtung auf die Füllstückspitze eine größere Freiheit bei der Anordnung des Lagerkörpers erhält, so daß einerseits an dem Lagerkörper eine möglichst große Lagerfläche und daraus resultierend eine entsprechend niedrige Flächenpressung verwirklicht werden kann, andererseits aber auch dafür gesorgt werden kann, daß die Resultierende der vom Druckraum her an dem Füllstück angreifenden hydraulischen Kräfte auch durch die Lagerfläche geht, ohne daß der Druckraum unnötig vergrößert werden muß. Es versteht sich, daß mit zunehmendem Betriebsdruck ein Interesse daran bestehen muß, den Druckraum möglichst klein zu halten, um hierdurch die Belastung der Innenzahnradmaschine in Grenzen zu halten. Insbesondere bei Füllstücken, die aus den oben angegebenen Gründen länger ausgebildet sein müssen, läßt sich eine Ausrichtung der hydraulischen Kraftresultierenden auf die Lagerfläche für das Füllstück aber nur unter Inkaufnahme einer Vergrößerung des Druckraumes erreichen, weil hierzu die Trennfläche zwischen Saugraum und Druckraum am Füllstück mittels der erwähnten Steuerung weiter von der Füllstückspitze entfernt angeordnet werden muß. Die erfindungsgemäße Ausbildung, bei der das Füllstück praktisch über seine Abstützung hinaus in Richtung Saugraum verlängert ist, erlaubt es jedoch, die Kraftresulierende auf die Lagerfläche des Lagerkörpers zu richten, ohne eine Vergrößerung des Druckraumes hinnehmen zu müssen. Weiterhin kann der Lagerkörper an dem Lagerzapfen beliebig an dessen Stirnseite, auch exzentrisch, je nach der Lage der Nut in der Seitenfläche des Füllstückes angeordnet sein, so daß jeweils eine maximale Abstützfläche zur Verfügung steht.The invention is based on the consideration that a greater freedom in the arrangement of the bearing body is obtained by relocating the filler bearing from the suction chamber end towards the filler tip, so that on the one hand the bearing body has the largest possible storage area and, as a result, a corresponding one low surface pressure can be realized, but on the other hand it can also be ensured that the resultant of the hydraulic forces acting on the filler from the pressure chamber also passes through the bearing surface without the pressure chamber having to be enlarged unnecessarily. It goes without saying that with increasing operating pressure there must be an interest in keeping the pressure space as small as possible in order to keep the load on the internal gear machine within limits. Especially with filler pieces, which must be longer for the reasons given above, an alignment of the hydraulic force results on the bearing surface for the filler piece can only be achieved by accepting an enlargement of the pressure chamber, because for this purpose the separating surface between the suction chamber and the pressure chamber on the filler piece by means of mentioned control must be placed further away from the filler tip. The design according to the invention, in which the filler is practically extended beyond its support in the direction of the suction chamber, however, allows the resultant force to be directed onto the bearing surface of the bearing body without having to accept an increase in the pressure chamber. Furthermore, the bearing body on the trunnion at its end face, also eccentrically, depending be arranged according to the position of the groove in the side surface of the filler piece, so that a maximum support surface is available in each case.

Es ist zwar bereits von Innenzahnradmaschinen, bei denen ein Füllstück in Form einer vollständigen Sichel mit zwei spitz zu laufenden Enden vorgesehen ist, bekannt, dieses Füllstück in der Längsmitte an einem Füllstückstift zu lagern. Infolge der symetrischen Ausbildung und der beidseitigen Verjüngung dieses Füllstückes ist aber die mittige Lagerung im Bereich der größten Füllstückdicke die einzig sinnvolle und entspricht bei den Innenzahnradmaschinen mit halbsichelförmigem Füllstück der bisher gebräuchlichen Lagerung am saugraumseitigen Füllstückende.It is already known from internal gear machines in which a filler piece is provided in the form of a complete sickle with two pointed ends, to store this filler piece in the longitudinal center on a filler pin. As a result of the symmetrical design and the tapering of this filler on both sides, the central bearing in the area of the greatest filler thickness is the only sensible one and corresponds to the hitherto customary storage at the end of the suction piece on the internal gear machines with a semi-crescent shaped filler.

Der Lagerzapfen ist zweckmäßigerweise in der dem saugraumseitigen Ende des Füllstückes zugewendeten Füllstückhälfte angeordnet und liegt im Grenzfall in der Längsmitte des Füllstückes. Günstige kinematische Verhältnisse für die Radialspaltkompensation erhält man darüber hinaus, wenn die Drehachse des Lagerzapfens das Füllstück an einer Stelle durchsetzt, die näher an dessen hohlradseitiger Umfangsfläche liegt. Bei dieser Ausführung ist der Lagerkörper bezüglich der Drehachse des Lagerzapfens unsymetrisch ausgestaltet, da er entsprechend der außermittigen Anordnung der Lagerzapfenachse relativ zum Füllstück zu letzterem hinversetzt ist.The bearing journal is expediently arranged in the filler half facing the suction chamber end of the filler and, in the limit case, lies in the longitudinal center of the filler. Favorable kinematic conditions for the radial gap compensation are also obtained if the axis of rotation of the bearing pin passes through the filler at a point closer to the circumferential surface of the ring gear. In this embodiment, the bearing body is designed asymmetrically with respect to the axis of rotation of the bearing pin, since it is offset relative to the filler piece relative to the filler piece in accordance with the eccentric arrangement of the bearing pin axis.

Wie bereits erwähnt, ermöglicht die zur Füllstückspitze hin versetzte Lagerung des Füllstückes eine größere Freiheit bei der Orientierung der Lagerfläche. In Verbindung mit der durch Steuerschlitze oder Vorfüllnuten erfolgenden Beeinflussung von Richtung und Größe der auf das Füllstück wirkenden hydraulischen Kraftresultierenden wird man aber die Lagerfläche und die den Lagerkörper aufnehmende Nut in der Seitenfläche des Füllstückes immer so legen, daß eine optimale Verteilung der das Füllstück einerseits in Richtung des Ritzels andererseits in Richtung des Hohlrades drängenden Kräfte erfolgt. Dies ermöglicht jedoch stets einen Kompromiß, der zu einer relativ großen Lagerfläche und daraus resultierender niedriger Flächenpressung führt.As already mentioned, the storage of the filling piece, which is offset towards the filling piece tip, allows greater freedom in the orientation of the bearing surface. In connection with the influencing of the direction and size of the hydraulic force results acting on the filling piece through control slots or pre-filling grooves, the bearing surface and the groove receiving the bearing body in the side surface of the filling piece will always be placed in such a way that an optimal distribution of the filling piece on the one hand in Direction of the pinion, on the other hand, forces urging in the direction of the ring gear. However, this always enables a compromise, which leads to a relatively large storage area and the resulting low surface pressure.

Der zweckmäßigerweise mit dem Lagerzapfen einstückige Lagerkörper weist in der einfachsten Ausführungsform zwei zueinander parallele ebene Fläche auf, von denen die der Füllstückspitze zugewendete Lagerfläche die Abstützung des Füllstückes gegenüber den im Betrieb wirksamen hydraulischen und sonstigen Kräften übernimmt, während die dem Saugraum zugewendete Fläche die Rückhaltefläche ist, die die vom Saugraum her auf das Füllstück wirkenden Kräfte sowie die von den Zahnrädern auf dieses ausgeübten Reibkräfte aufnimmt. Da sich richtungsmäßig diese einander entgegengesetzten Kräfte nicht decken, kann jedoch insbesondere bei einem lang ausgebildeten Füllstück, an dem der Reibkraftanteil größer ist, daran gedacht werden, die Lagerflächen an dem Lagerkörper unter einem entsprechenden Winkel zueinander verlaufen zu lassen, wobei dieser Winkel sich normalerweise in Richtung zum Hohlrad hin öffnet. Der Querschnitt des Lagerkörpers ist in diesem Fall somit keilförmig, wobei die saugraumseitige Rückhaltefläche so gelegt ist, daß die vom Saugraum her wirkenden Druckkräfte sowie die Reibkräfte senkrecht oder nahezu senkrecht zu dieser Fläche gerichtet sind. Das Spiel zwischen dem Füllstück und dieser Rückhaltefläche kann auch bei planparelleler Anordnung der Lagerfläche und der Rückhaltefläche stets klein gehalten werden. Bei der geschilderten Ausführungsform des Lagerkörpers mit keilförmigem Querschnitt ist dies in besonderem Maße möglich, da infolge der Keilform sich das Spiel bei Bewegungen des Füllstückes in Richtung Hohlrad verkleinert.In the simplest embodiment, the bearing body, which is expediently one-piece with the journal, has two mutually parallel flat surfaces, of which the bearing surface facing the filler tip assumes the support of the filler against the hydraulic and other forces that are effective during operation, while the surface facing the suction chamber is the retention surface , which absorbs the forces acting on the filler from the suction chamber and the frictional forces exerted on the filler by the gearwheels. Since these opposing forces do not coincide in terms of direction, however, in particular in the case of a long filler piece in which the frictional force component is greater, it can be considered to allow the bearing surfaces on the bearing body to run at a corresponding angle to one another, this angle normally being in Direction towards the ring gear opens. The cross-section of the bearing body is thus wedge-shaped in this case, the suction-space-side retention surface being positioned such that the pressure forces acting from the suction space and the frictional forces are directed perpendicularly or almost perpendicularly to this surface. The play between the filler and this retaining surface can always be kept small even with a parallel arrangement of the bearing surface and the retaining surface. In the described embodiment of the bearing body with a wedge-shaped cross section, this is possible to a particular degree, since the play decreases when the filler moves in the direction of the ring gear due to the wedge shape.

Die erfindungsgemäße Ausgestaltung kann grundsätzlich auch für mehrteilige Füllstücke Anwendung finden (vgl. DE-A-26 06 082). In diesem Fall durchsetzt zweckmäßigerweise die an der Seite des Füllstückes vorgesehene Nut (bzw. die an beiden Seiten des Füllstückes vorgesehenen Nuten) alle Füllstückteile oder -segmente. In einer besonders bevorzugten Ausführungsform des Füllstückes, bei der sich dieses aus einem verhältnismäßig dünnwandigen Dichtsegment und aus einem Segmentträger zusammensetzt, wobei das Dichtsegment am Hohlrad anliegt, ist die Rückhaltefläche des Lagerkörpers keine ebene Fläche, sondern weist einen Knick an der Trennstelle zwischen Dichtsegment und Segmentträger auf. Hierdurch wird dem Umstand Rechnung getragen, daß die auf den Segmentträger und auf das Dichtsegment vom Saugraum her wirkenden Kräfte sowie die Reibkräfte unterschiedliche Richtungen haben. Um in dem vorstehend bereits erläuterten Sinne die Rückhaltefläche so auszurichten, daß diese Kräfte senkrecht aufgenommen werden, ist diese Anpassung erforderlich.The embodiment according to the invention can in principle also be used for multi-part filling pieces (cf. DE-A-26 06 082). In this case, the groove provided on the side of the filler (or the grooves provided on both sides of the filler) expediently penetrates all parts or segments of the filler. In a particularly preferred embodiment of the filler piece, in which it is composed of a relatively thin-walled sealing segment and a segment carrier, the sealing segment resting on the ring gear, the retaining surface of the bearing body is not a flat surface, but has a kink at the separation point between the sealing segment and segment carrier on. This takes into account the fact that the Segment carrier and forces acting on the sealing segment from the suction space and the frictional forces have different directions. In order to align the retaining surface in the sense already explained above so that these forces are absorbed vertically, this adjustment is necessary.

Weitere vorteilhafte Ausgestaltungen ergeben sich aus anderen Unteransprüchen.Further advantageous configurations result from other subclaims.

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

  • Figur 1 Einen schematischen Querschnitt durch eine erste Ausführungsform einer erfindungsgemäßen Innenzahnradpumpe mit geteiltem Füllstück;
  • Figur 2 einen Teilschnitt längs der Linie II-II in Figur 1;
  • Figur 2A einen zu Figur 2 analogen Teilschnitt an einer modifizierten Ausführungsform mit nur einem Lagerzapfen;
  • Figur 3 einen zu Figur 1 analogen Querschnitt, jedoch nur teilweise, durch eine zweite Ausführungsform einer erfindungsgemäßen Innenzahnradpumpe, und
  • Figur 4 einen zu Figur 1 analogen Querschnitt durch eine dritte Ausführungsform einer erfindungsgemäßen Innenzahnradpumpe mit einem einteiligen Füllstück.
Embodiments of the present invention are explained below with reference to the accompanying drawings. The drawings show:
  • Figure 1 shows a schematic cross section through a first embodiment of an internal gear pump according to the invention with divided filler;
  • 2 shows a partial section along the line II-II in Figure 1;
  • FIG. 2A shows a partial section analogous to FIG. 2 on a modified embodiment with only one bearing journal;
  • 3 shows a cross section analogous to FIG. 1, but only partially, through a second embodiment of an internal gear pump according to the invention, and
  • 4 shows a cross section analogous to FIG. 1 through a third embodiment of an internal gear pump according to the invention with a one-piece filler.

Die Innenzahnradpumpe gemäß Figur 1 weist ein nicht näher gezeigtes Gehäuse 1, ein darin mit seinem Umfang gelagertes Innenzahnrad oder Hohlrad 2, ein im Gehäuse gelagertes und mit einer nicht gezeigten Welle ausgestattetes Ritzel 3 sowie ein im ganzen mit 4 bezeichnetes Füllstück auf. Das Hohlrad 2 trägt auf seinem ganzen Umfang in bekannter Weise nur zum Teil angedeutete Durchbrüche 5, die es dem Fördermedium, das über eine Ansaugöffnung 6 eintritt, ermöglicht in den Saugraum 7 zu gelangen und aus dem Druckraum 8 wieder auszutreten, wonach es durch einen Druckanschluß 9 abgeführt wird. Der bisher beschriebene Aufbau der Innenzahnradpumpe ist herkömmlicher Art und bedarf deshalb keiner näheren Erläuterung.The internal gear pump according to FIG. 1 has a housing 1 (not shown in more detail), an internal gear or ring gear 2 mounted therein with its circumference, a pinion 3 mounted in the housing and equipped with a shaft (not shown), and a filling piece designated as 4 overall. The ring gear 2 bears on its entire circumference in a known manner only partially indicated openings 5, which enables the pumped medium that enters through a suction opening 6 to get into the suction chamber 7 and out of the pressure chamber 8 exit again, after which it is discharged through a pressure connection 9. The structure of the internal gear pump described so far is conventional and therefore requires no further explanation.

Das Füllstück 4 hat die Form einer Halbsichel oder eines Kommas und ist in dem gezeigten Ausführungsbeispiel verhältnismäßig lang ausgeführt, so daß es auf seiner äußeren Umfangsfläche gleichzeitig mit neun Zähnen des Hohlrades 2 in Kontakt steht, um zum Zweck der Förderung besonders dünnflüssiger Medien eine möglichst gute Abdichtung zu erhalten. Das Füllstück 4 setzt sich zusammen aus einem schalenförmigen Dichtsegment 11 und einem Segmentträger 12, die längs einer sich in Umfangsrichtung erstreckenden Trennfläche 13 aneinanderliegen und gegeneinander durch zwei Dichtwalzen 14 abgedichtet sind. In zwei seitlichen Gehäuseplatten 15, die in Figur 2 nur angedeutet sind, sind Sackbohrungen 16 zur drehbaren Lagerung je eines Lagerzapfens 17 ausgebildet. Die Lagerzapfen 17 sind den beiden Seitenflächen des Füllstückes 4 zugeordnet und weisen einstückig daran ausgebildete Lagerkörper 18 auf, die in Richtung auf das Füllstück von der Stirnseite der Lagerzapfen 17 vorspringen. Die Lagerkörper 18 haben zwei planparallele Flächen, von denen die der Füllstückspitze zugewendete Fläche 19 die Lagerfläche zur Aufnahme der aus dem Druckraum 8 wirkenden Kräfte und die gegenüberliegende Fläche 20 die Rückhaltefläche zur Abstützung des Füllstückes 4 gegenüber den Kräften ist, die vom Saugraum 7 her wirken. Wie sich aus Figur 1 ergibt, sind die Lagerzapfen 17 so relativ zum Füllstück 4 angeordnet, daß die Drehachse 10 der Lagerzapfen 17 in Richtung zur Spitze des Füllstückes 4 hin versetzt ist und an einer Stelle liegt, die die Füllstücklänge etwa im Verhältnis von 2 zu 3 teilt. Außerdem liegt die Drehachse 10 nahe an der Trennfläche 13 zwischen Dichtsegment 11 und Segmentträger 12, d.h. somit näher an den Zahnköpfen des Hohlrades 2.The filler 4 has the shape of a half-crescent or a comma and is made relatively long in the embodiment shown, so that it is in contact with nine teeth of the ring gear 2 on its outer circumferential surface in order to achieve the best possible for the purpose of conveying particularly thin media Get waterproofing. The filler 4 is composed of a shell-shaped sealing segment 11 and a segment carrier 12, which abut one another along a separating surface 13 which extends in the circumferential direction and are sealed off from one another by two sealing rollers 14. In two lateral housing plates 15, which are only indicated in FIG. 2, blind bores 16 are formed for the rotatable mounting of one bearing pin 17 each. The bearing pins 17 are assigned to the two side surfaces of the filler piece 4 and have bearing bodies 18 formed integrally thereon, which project in the direction of the filler piece from the end face of the bearing pins 17. The bearing bodies 18 have two plane-parallel surfaces, of which the surface 19 facing the filler tip is the bearing surface for absorbing the forces acting from the pressure chamber 8 and the opposite surface 20 is the retaining surface for supporting the filler 4 against the forces acting from the suction chamber 7 . As can be seen from FIG. 1, the journals 17 are arranged relative to the filler 4 in such a way that the axis of rotation 10 of the journals 17 is offset in the direction of the tip of the filler 4 and is located at a point that the filler length is approximately in the ratio of 2 to 3 shares. In addition, the axis of rotation 10 is close to the interface 13 between the sealing segment 11 and segment carrier 12, i.e. thus closer to the tooth tips of the ring gear 2.

In den axialen Seitenflächen des Dichtsegments 11 und des Segmentträgers 12 sind zu den Lagerkörpern 18 korrespondierende Nuten 21 eingearbeitet, die zur Aufnahme der Lagerkörper 18 bestimmt sind und deren Nutflanken an der Lagerfläche 19 bzw. an der Rückhaltefläche 20 anliegen und auf diese die an dem Füllstück 4 angreifenden Kräfte übertragen. Die Gestalt der Nuten 21 und der darin eingreifenden Lagerkörper 18 ergibt sich aus Figur 1 daraus ist aus erkennbar, daß infolge der relativ zum Füllstück 4 außermittigen Anordnung der Drehachse 10 die Lagerkörper 18 gegenüber der Stirnseite der Lagerzapfen 17 in Richtung zum Ritzel 3 hin exzentrisch angeordnet sind. Weiterhin ist aus Figur 1 erkennbar, daß die Lagerkörper 18 die Nuten 21 des Füllstückes 4 weitgehend ausfüllen, d.h. an ihren umfangsseitigen Begrenzungsflächen der Umfangsform des Füllstückes 4 zumindest annähernd angepaßt sind, um hierdurch die Flächen 19 und 20 möglichst groß zu halten. Die Nutflanken der Nuten 21 verlaufen, wie ebenfalls aus Figur 1 zu entnehmen ist, unter einem Winkel von annähernd 30 Grad zu derjenigen Ebene, in welcher die Achse des Ritzels 3 sowie die Drehachse 10 der Lagerzapfen 17 liegen. Diese Lage gewährleistet, daß einerseits die vom Druckraum 8 her auf das Füllstück 4 wirkenden Kräfte so verteilt werden, daß das Füllstück eine optimale Dichtanlage an dem Hohlrad 2 und an dem Ritzel 3 erfährt, andererseits die an der Lagerfläche 19 sich einstellende Flächenpressung möglichst gering ist. Die Richtung der Kraftresultierenden der vom Druckraum 8 her wirksamen hydraulischen Kräfte wird in bekannter Weise durch nicht gezeigte Steuerschlitze in den Axialplatten 15 und/oder den Seitenflächen des Füllstückes 4 festgelegt (vgl. DE-A-15 53 027).In the axial side surfaces of the sealing segment 11 and the segment carrier 12, grooves 21 corresponding to the bearing bodies 18 are incorporated, which are intended for receiving the bearing bodies 18 and their groove flanks on the bearing surface 19 and on of the retaining surface 20 and transfer the forces acting on the filler 4 to this. The shape of the grooves 21 and the bearing bodies 18 engaging therein results from FIG. 1, from which it can be seen that, due to the eccentric arrangement of the axis of rotation 10 relative to the filler 4, the bearing bodies 18 are arranged eccentrically in relation to the end face of the journal 17 in the direction of the pinion 3 are. It can also be seen from FIG. 1 that the bearing body 18 largely fills the grooves 21 of the filler 4, that is to say that they are at least approximately matched to the circumferential shape of the filler 4 on their circumferential boundary surfaces in order thereby to keep the surfaces 19 and 20 as large as possible. The groove flanks of the grooves 21, as can also be seen in FIG. 1, run at an angle of approximately 30 degrees to the plane in which the axis of the pinion 3 and the axis of rotation 10 of the bearing pins 17 lie. This position ensures that, on the one hand, the forces acting on the filler 4 from the pressure chamber 8 are distributed in such a way that the filler experiences an optimal sealing system on the ring gear 2 and on the pinion 3, and on the other hand the surface pressure which arises on the bearing surface 19 is as low as possible . The direction of the resultant force of the hydraulic forces acting from the pressure chamber 8 is determined in a known manner by control slots (not shown) in the axial plates 15 and / or the side faces of the filler 4 (cf. DE-A-15 53 027).

Die Ausführungsform gemäß Figur 2A unterscheidet sich von der vorstehend beschriebenen Ausführungsform nur dadurch, daß anstelle zweier den beiden Seitenflächen des Füllstückes 4 zugeordneter Lagerzapfen 17 nur ein einseitig angeordneter Lagerzapfen 17′ vorgesehen ist, der mit seinem Lagerkörper 18′ in eine einseitig angeordnete Nut 21′ des Füllstückes eingreift.The embodiment according to FIG. 2A differs from the embodiment described above only in that instead of two bearing journals 17 assigned to the two side surfaces of the filling piece 4, only a bearing journal 17 ′ which is arranged on one side and is provided with its bearing body 18 ′ in a groove 21 ′ arranged on one side is provided. of the filler engages.

Die Ausführungsform gemäß Figur 3 unterscheidet sich von der Ausführungsform gemäß den Figuren 1 und 2 allein durch die besondere Ausgestaltung der Lagerkörper 28 an den Lagerzapfen 27. Aus diesem Grund sind die übrigen Komponenten der Innenzahnradpumpe mit den gleichen Bezugszeichen wie in den Figuren 1 und 2 bezeichnet.The embodiment according to FIG. 3 differs from the embodiment according to FIGS. 1 and 2 solely by the special design of the bearing body 28 on the bearing journal 27. For this reason, the other components of the internal gear pump are identified by the same reference numerals as in FIGS. 1 and 2 .

An dem Lagerkörper 28 ist die Lagerfläche 29 _ wie bei der ersten Ausführungsform _ unter einem Winkel von etwa 30 Grad zu der die Drehachse des Lagerzapfens 27 und des Ritzels 3 enthaltenen Ebene angeordnet und durchwegs eben ausgebildet. Die Rückhaltefläche 30 hingegen bildet zur Lagerfläche 29 einen spitzen Winkel und ist unterteilt in eine dem Segmentträger 22 zugeordnete Teifläche 30′ und in eine dem Dichtsegment 23 zugeordnete Teilfläche 30˝. Die Teiflächen 30′ und 30˝ treffen sich im Bereich der Trennfläche 13; die Rückhaltefläche 30 ist somit geknickt. Diese Ausführung trägt dem Umstand Rechnung, daß die vom Saugraum 7 her wirkenden Kräfte den Segmentträger 22 und das Dichtsegment 23 in unterschiedlichen Richtungen beaufschlagen, so daß es erforderlich ist, bei einer senkrechten Ausrichtung der jeweils zugehörigen Rückhalteflächen diese unterschiedlich zu neigen.On the bearing body 28, the bearing surface 29 is arranged, as in the first embodiment, at an angle of approximately 30 degrees to the plane containing the axis of rotation of the bearing journal 27 and the pinion 3, and is formed flat throughout. The retention surface 30, however, forms an acute angle to the bearing surface 29 and is divided into a partial surface 30 'assigned to the segment carrier 22 and a partial surface 30' assigned to the sealing segment 23. The partial surfaces 30 'and 30˝ meet in the area of the separating surface 13; the retention surface 30 is thus kinked. This embodiment takes into account the fact that the forces acting from the suction space 7 act on the segment carrier 22 and the sealing segment 23 in different directions, so that it is necessary to incline them differently in the case of a vertical alignment of the respectively associated retaining surfaces.

Die Ausführungsform gemäß Figur 4 entspricht weitgehend derjenigen gemäß den Figuren 1 und 2; der Unterschied besteht lediglich darin, daß anstelle eines geteilten Füllstückes 4 ein ungeteiltes Füllstück 4′ gewählt ist, in dessen axialen Seitenflächen die die Lagerkörper aufnehmenden Nuten eingearbeitet sind.The embodiment according to FIG. 4 largely corresponds to that according to FIGS. 1 and 2; the only difference is that instead of a divided filler 4 an undivided filler 4 'is selected, in the axial side surfaces of which the bearing body receiving grooves are incorporated.

Claims (12)

1. An internal-gear machine, in particular an internal-gear pump, comprising an internally toothed annular gear (2), an externally toothed pinion (3) meshing therewith, and a half-sickle-shaped filling portion (4, 4′) which extends in the circumferential direction and which bears with its radial surfaces sealingly against the tips of the teeth of the annular gear and the pinion and which subdivides the space between the annular gear and the pinion into a suction space (7) and a pressure space (8) and which faces with its tip towards the pressure space and which is rotatably and displaceably supported at a spacing from its end towards the suction space by a mounting trunnion (17, 17′) rotatably mounted in a bore (16) in the housing, and a mounting body (18, 18′, 28) of the mounting trunnion, which mounting body engages into a groove (21, 21′) in the filling portion, characterised in that associated with at least one axial side surface of the filling portion is a mounting trunnion which is mounted only at one side of the mounting body and said side surface has a groove (21, 21′) extending over the radial height of the filling portion.
2. An internal-gear machine according to claim 1 characterised in that a respective mounting trunnion (17, 27) with mounting body (18, 28) is arranged at each side of the filling portion (4, 4′) and each of the side surfaces of the filling portion (4, 4′) has a groove (21).
3. An internal-gear machine according to claim 1 or claim 2 characterised in that the mounting trunnion is arranged approximately at the longitudinal centre of the filling portion.
4. An internal-gear machine according to claim 1 or claim 2 characterised in that the mounting trunnion (17, 27) is arranged at a location in the longitudinal extent of the filling portion (4, 4′), which is closer to the end towards the suction space and which subdivides the arcuate length of the filling portion (4, 4′) in a ratio of two to three.
5. An internal-gear machine according to one of claims 1 to 4 characterised in that the axis of rotation (10) of the mounting trunnion (17, 27) passes through the filling portion (4, 4′) closer to the circumferential surface thereof at the side towards the annular gear.
6. An internal-gear machine according to one of claims 1 to 5 characterised in that the groove accommodating the mounting body (18, 28) extends in the side surface of the filling portion at an angle to the plane connecting the axis of the pinion and the axis of rotation (10) of the mounting trunnion.
7. An internal-gear machine according to claim 6 characterised in that the angle is about 30°.
8. An internal-gear machine according to one of claims 1 to 7 characterised in that the surfaces (29, 30) of the mounting body (28), which are on the pressure space side and the suction space side, and the associated sides of the groove, extend relative to each other at an acute angle which opens towards the annular gear.
9. An internal-gear machine according to claim 8 characterised in that the mounting surface (retaining surface 30) on the suction space side extends at least approximately parallel to the plane of separation, which is established by a slot control, between the pressure space (8) and the suction space (7).
10. An internal-gear machine according to one of claims 1 to 9 characterised in that the filling portion is divided along one or more separating surfaces (13) extending approximately in the circumferential direction.
11. An internal-gear machine according to claim 10 characterised in that the groove (21) in the side surface of the filling portion (4) passes through the side surfaces of all parts of the filling portion (11, 12; 22, 23).
12. An internal-gear machine according to claim 11 characterised in that the filling portion is subdivided into a shell-like sealing segment (23) and a segment carrier (22) and that the retaining surface (30) of the mounting body (28), at the suction space side, has a bend at the separating surface (13) between the sealing segment (23) and the segment carrier (22).
EP88108387A 1987-07-16 1988-05-26 Internal-gear machine Expired - Lifetime EP0302190B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3723557 1987-07-16
DE19873723557 DE3723557A1 (en) 1987-07-16 1987-07-16 INTERNAL GEAR MACHINE

Publications (2)

Publication Number Publication Date
EP0302190A1 EP0302190A1 (en) 1989-02-08
EP0302190B1 true EP0302190B1 (en) 1991-03-20

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US (1) US4893997A (en)
EP (1) EP0302190B1 (en)
JP (1) JPH0747955B2 (en)
DE (2) DE3723557A1 (en)

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DE2942417A1 (en) * 1979-10-19 1981-05-14 Otto Eckerle GmbH & Co KG, 7502 Malsch INTERNAL GEAR MACHINE
JPS5944511B2 (en) * 1979-12-17 1984-10-30 株式会社不二越 Internal gear pump/motor
DE3544857C2 (en) * 1985-12-18 1994-09-29 Eckerle Rexroth Gmbh Co Kg Internal gear machine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202013103826U1 (en) 2013-05-13 2013-09-09 Eckerle Industrie-Elektronik Gmbh Internal gear machine with filler retainer

Also Published As

Publication number Publication date
US4893997A (en) 1990-01-16
EP0302190A1 (en) 1989-02-08
JPH0747955B2 (en) 1995-05-24
DE3862079D1 (en) 1991-04-25
DE3723557A1 (en) 1989-01-26
JPS6445986A (en) 1989-02-20

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