EP0640766B1 - Internal gear pump - Google Patents

Internal gear pump Download PDF

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Publication number
EP0640766B1
EP0640766B1 EP94113166A EP94113166A EP0640766B1 EP 0640766 B1 EP0640766 B1 EP 0640766B1 EP 94113166 A EP94113166 A EP 94113166A EP 94113166 A EP94113166 A EP 94113166A EP 0640766 B1 EP0640766 B1 EP 0640766B1
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EP
European Patent Office
Prior art keywords
segment
internal gear
stop
gear pump
axial
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Expired - Lifetime
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EP94113166A
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German (de)
French (fr)
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EP0640766A1 (en
Inventor
Gerd Hundt
Peter Peiz
Franz Arbogast
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JM Voith GmbH
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JM Voith GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/10—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth equivalents, e.g. rollers, than the inner member
    • 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 pump with an internally toothed ring gear, two axial disks arranged on both sides of the ring gear, a driven, externally toothed pinion arranged eccentrically to the ring gear and in engagement with the ring gear, and a circumferentially divided, crescent-shaped, floating bearing piece, that with its blunt end abuts against an axial support bolt and its first segment facing the teeth of the pinion has a greater radial thickness than its second segment facing the teeth of the ring gear, the first segment in the dividing surface having at least one axially extending groove for receiving a Has sealing element, according to the preamble of claim 1.
  • the filler is divided into two segments in the circumferential direction. This division ensures that, due to the pressure prevailing between the segments, the segments are pressed separately from one another onto the tooth tips of the assigned gears and in this way the radial bearing changes of the pinion and ring gear can be compensated for as a function of pressure, speed and viscosity.
  • the contact force on the tooth heads is dimensioned such that no wear occurs on the filler parts under normal operating conditions. In practice, however, it has been shown that in extreme operating conditions, such as heavy pollution or air bubbles present in the oil, the force ratios are changed primarily on the segment facing the pinion, so that this segment is one experiences severe abrasion, which then leads to the breakage of the segment and thus to the total failure of the pump.
  • the stop is expediently designed according to the invention as a mechanical stop and arranged in the region of the pointed end of the first segment in connection with the axial disks, wherein according to a further advantageous embodiment of the invention a second mechanical stop in the region of the blunt end of the first segment in connection with the axial disks can be trained.
  • the stop or stops after a certain removal quantity prevent or prevent further removal.
  • the thrust forces generated are then absorbed by the axial disk bearing on the pinion shaft.
  • the stop is expediently designed as a pin fitted into an axial bore in the axial disk, which pin engages in a corresponding axial bore in the first segment, which, however, has a larger diameter than the pin. It is also conceivable that the stop is fitted into the first segment in a kinematic reversal and engages in a larger diameter bore in the axial disk. With this embodiment of the invention, the allowable removal quantity is determined by the difference in diameter of the two bores. The stop does not function in normal operation.
  • a further embodiment of the invention advantageously provides that the stop is designed as a hydraulic stop in the form of at least one blind groove which is arranged in the side faces of the axial disks facing the first segment and is connected with its open end to the pressure build-up side of the pump.
  • the blind end being arranged such that it opens to the pressure side of the pump when limited removal has taken place.
  • the at least one blind groove it is also possible for the at least one blind groove to be arranged on one side or on both sides of the first segment, it being possible for the connection to the pressure side to always be present and for the removal to open a connection to the pressure build-up area.
  • This design of the stop is based on the hydraulic conditions of the pump.
  • the blind grooves introduced into the axial disks or the first segment are covered in normal operation by the axial surface of the first segment or the axial disks and are inoperative.
  • the pressure build-up control on the first segment is influenced in such a way that, under the prevailing extreme operating conditions, there is a relief between the tooth tips of the pinion and the first segment and therefore no further erosion takes place.
  • a further advantageous embodiment of the invention provides that a connection is formed between the first segment and the second segment to limit the gap width in the region of the division area after limited removal.
  • the gap between the first and second segments increases. With the loose, mechanical connection between the two segments it is achieved that after the initial removal on the first segment, a further increase in gap is prevented by the connection.
  • a limitation for a rotary movement of the support bolt is provided to limit the removal of the surface of the first segment facing the teeth of the pinion.
  • the boundary can be designed as a stop element on the contact surface of the blunt end of the filler piece on the support bolt on the back of one of the axial disks or in the bearing cover. The same effect is achieved if the limitation is formed by means of a snug fit of the support bolt in the axial disks or the bearing caps.
  • the first segment is not removed parallel to the surface facing the tooth tips of the pinion, but a torque is generated on the first segment or the filler, which causes the greatest removal at the tip end of the first segment he follows.
  • the support bolt adapts to the new conditions and rotates, as a result of which the entire contact surface of the blunt end of the filler piece lies against the support bolt.
  • the contact of the first segment on the contact surface of the support bolt changes from a flat contact to a linear contact.
  • the force F with which the first segment is pressed against the support bolt generates a moment Md around the contact point, which counteracts the removal of the first segment by the tooth tips of the pinion.
  • the internal gear pump 10 shown in the figures generally comprises an internally toothed ring gear 12, two axial disks 13 arranged on the two sides of the ring gear 12, a driven, externally toothed pinion 14 arranged eccentrically to the ring gear 12 and in engagement with the ring gear 12, and one in the circumferential direction divided, sickle-shaped, floating filler 16, which abuts with its blunt end 36 against an axial support pin 17.
  • the filler 16 has a first segment 18 facing the teeth of the pinion 14 and a second segment 20 facing the teeth of the ring gear 12.
  • the first segment 18 has a greater radial thickness than the second segment 20.
  • axially extending grooves 24 are provided for receiving sealing elements 26.
  • the first segment 18 has a stop 28 for limitation at its tip end 32 of the removal 54 of the surface 30 of the first segment 18 facing the teeth of the pinion 14.
  • This stop 28 consists, as shown in Fig. 1a, of a pin 40, which is fitted with its one portion in an axial bore 38 of an axial disc 13. With its other section, the pin 40 is arranged in an axial bore 42 in the first segment 18, this bore 42 having a larger diameter than the axial bore 38 in the axial disk 13.
  • an arrangement in kinematic reversal is also conceivable, ie the fit is in this case in the first segment 18, and the larger diameter bore is arranged in the axial disk 13.
  • FIG. 2 Another embodiment of the invention is shown in FIG. 2.
  • a second mechanical stop 34 is provided in the region of the blunt end 36 of the first segment 18. This second stop 34 is designed in accordance with the first stop 28.
  • the stop is designed as a hydraulic stop 44.
  • This hydraulic stop 44 consists of at least one blind groove 46 which is formed in the side faces of the axial disks facing the first segment.
  • the open end 52 of the blind groove 46 is connected to the pressure build-up side 50 of the internal gear pump 10.
  • the blind end 48 is covered by the side surface of the first segment 18 in normal operation. Only after the removal 54 of the surface 30 of the first segment 18 facing the teeth of the pinion 14 does the blind groove 46 forming the hydraulic stop 44 become free at its blind end 48 and with the pressure side 50 of the by the inevitable displacement of the dividing surface 22 Internal gear pump connected.
  • the pressure build-up on the first segment 18 is influenced in such a way that, under extreme conditions, relief occurs between the teeth of the pinion 14 and the first segment 18, so that no further erosion takes place.
  • a plurality of blind grooves 46 or control grooves can also be provided in the axial disks 13. It is also possible, in a kinematic reversal, to arrange the blind grooves in the side faces on one side or on both sides of the first segment 18 (see FIG. 4), the blind groove now being connected to the pressure side 50 and, after removal 54 has taken place, a connection to the pressure build-up side opens .
  • the closed end of the blind groove is expediently designed as a radius, because the size of the connection (of the opening) then automatically adjusts to the prevailing hydraulic conditions.
  • the removal on the inside of the filler continues until a sufficient cross-section is available to achieve the hydraulic balance.
  • FIG. 5 Another embodiment of the invention is shown in FIG. 5.
  • a connection 58 is provided between the first segment 18 and the second segment 20 to limit the width of the gap 70 in the region of the dividing surface 22. If ablation takes place on the first segment 18, the gap between the first segment 18 and the second segment 20 increases.
  • FIGS. 6 to 9 Another embodiment of the internal gear pump is shown in FIGS. 6 to 9. It has been shown that a Removal on the first segment 18 does not take place parallel to the surface facing the tooth heads of the pinion 14, but instead, as a result of a torque acting on the first segment 18, there is an increased removal on the tip end 32 of the first segment 18. As the removal progresses from the pointed end 32 of the first segment 18, the support bolt 17 adapts to the new conditions and rotates, so that the entire contact surface 64 of the blunt end 36 of the filler piece 16 bears against the support bolt 17. In order to limit the removal on the first segment 18, a limitation 60 is provided for the rotary movement of the support bolt 17 in this embodiment of the internal gear pump 10.
  • the boundary 60 is designed as a stop element 62.
  • the stop element 62 can either be formed in the rear of the axial disks 13 (see FIG. 7a) or in the bearing caps 66 (see FIG. 7b).
  • Another possibility of forming the limit 60 consists in a snug fit with which the support bolt 17 is fitted either in the axial disks 13 or the bearing cover 66 (see FIGS. 8 and 9).

Abstract

Internal gear pump with an internal gear, a thrust plate arranged on each side of the internal gear, a powered external pinion arranged eccentrically relative to the internal gear and meshing with it, and a sickle-shaped, floating filler part split in peripheral direction and bearing with its blunt end on an axial support pin. The first segment of the filler part that faces the teeth of the pinion has a greater radial thickness than its second segment facing the teeth of the internal gear. The first segment features in the parting interface at least one axially extending groove for accommodation of a sealing element. The first segment features at least one stop for restricting wear on the surface facing the teeth of the pinion.

Description

Die Erfindung betrifft eine Innenzahnradpumpe mit einem innenverzahnten Hohlrad, zwei an den beiden Seiten des Hohlrades angeordneten Axialscheiben, einem zum Hohlrad exzentrisch angeordneten und mit dem Hohlrad in Eingriff stehenden, angetriebenen, außenverzahnten Ritzel und einem in Umfangsrichtung geteilten, sichelförmigen, schwimmend gelagerten Füllstück, das mit seinem stumpfen Ende gegen einen axialen Stützbolzen anliegt und dessen erstes, den Zähnen des Ritzels zugewandtes Segment eine größere radiale Dicke als dessen zweites, den Zähnen des Hohlrades zugewandtes Segment aufweist, wobei das erste Segment in der Teilungsfläche mindestens eine axial verlaufende Nut zur Aufnahme eines Dichtelements aufweist, gemäß dem Oberbegriff des Anspruchs 1.The invention relates to an internal gear pump with an internally toothed ring gear, two axial disks arranged on both sides of the ring gear, a driven, externally toothed pinion arranged eccentrically to the ring gear and in engagement with the ring gear, and a circumferentially divided, crescent-shaped, floating bearing piece, that with its blunt end abuts against an axial support bolt and its first segment facing the teeth of the pinion has a greater radial thickness than its second segment facing the teeth of the ring gear, the first segment in the dividing surface having at least one axially extending groove for receiving a Has sealing element, according to the preamble of claim 1.

Eine Innenzahnradpumpe der vorstehend beschriebenen Art ist bekannt (DE-OS 26 06 082, DE-OS 25 33 646).An internal gear pump of the type described above is known (DE-OS 26 06 082, DE-OS 25 33 646).

Bei dieser bekannten Innenzahnradpumpe ist das Füllstück in Umfangsrichtung in zwei Segmente unterteilt. Durch diese Teilung wird erreicht, daß aufgrund des zwischen den Segmenten herrschenden Drucks die Segmente getrennt voneinander an die Zahnköpfe der zugeordneten Zahnräder angedrückt werden und auf diese Weise die radialen Lagerveränderungen von Ritzel und Hohlrad in Abhängigkeit von Druck, Drehzahl und Viskosität kompensiert werden können.In this known internal gear pump, the filler is divided into two segments in the circumferential direction. This division ensures that, due to the pressure prevailing between the segments, the segments are pressed separately from one another onto the tooth tips of the assigned gears and in this way the radial bearing changes of the pinion and ring gear can be compensated for as a function of pressure, speed and viscosity.

Die Anlagekraft an die Zahnköpfe ist so bemessen, daß bei normalen Betriebsbedingungen keinerlei Abtrag an den Füllstückteilen erfolgt. In der Praxis hat sich jedoch gezeigt, daß bei extremen Betriebsbedingungen, wie z.B. bei starker Verschmutzung oder im Öl vorhandenen Luftblasen, die Kraftverhältnisse vorrangig am dem Ritzel zugewandten Segment verändert werden, so daß dieses Segment einen starken Abtrag erfährt, der dann zum Bruch des Segments und somit zum Totalausfall der Pumpe führt.The contact force on the tooth heads is dimensioned such that no wear occurs on the filler parts under normal operating conditions. In practice, however, it has been shown that in extreme operating conditions, such as heavy pollution or air bubbles present in the oil, the force ratios are changed primarily on the segment facing the pinion, so that this segment is one experiences severe abrasion, which then leads to the breakage of the segment and thus to the total failure of the pump.

Es ist daher Aufgabe der vorliegenden Erfindung, den Abtrag an dem dem Ritzel zugewandten ersten Segment zu begrenzen, um dadurch den Bruch und somit einen Totalausfall der Pumpe zu verhindern.It is therefore an object of the present invention to limit the removal on the first segment facing the pinion in order to prevent the breakage and thus a total failure of the pump.

Diese Aufgabe wird erfindungsgemäß durch die im Anspruch 1 gekennzeichnete Erfindung gelöst, d.h. dadurch, daß das erste Segment mindestens einen Anschlag zur Begrenzung eines Abtrags der den Zähnen des Ritzels zugewandten Fläche aufweist.This object is achieved according to the invention by the invention characterized in claim 1, i.e. characterized in that the first segment has at least one stop to limit removal of the surface facing the teeth of the pinion.

Mit einem derartigen Anschlag wird erreicht, daß nach einem erfolgten Erstabtrag an der den Zähnen des Ritzels zugewandten Fläche ein weiterer Abtrag verhindert wird.With such a stop it is achieved that after a first removal on the surface facing the teeth of the pinion a further removal is prevented.

Vorteilhafte Ausgestaltungen der Erfindung ergeben sich aus den Unteransprüchen.Advantageous refinements of the invention result from the subclaims.

Zweckmäßigerweise ist erfindungsgemäß der Anschlag als mechanischer Anschlag ausgebildet und im Bereich des spitzen Endes des ersten Segments in Verbindung mit den Axialscheiben angeordnet, wobei gemäß einer weiteren vorteilhaften Ausgestaltung der Erfindung ein zweiter mechanischer Anschlag im Bereich des stumpfen Endes des ersten Segments in Verbindung mit den Axialscheiben ausgebildet sein kann.The stop is expediently designed according to the invention as a mechanical stop and arranged in the region of the pointed end of the first segment in connection with the axial disks, wherein according to a further advantageous embodiment of the invention a second mechanical stop in the region of the blunt end of the first segment in connection with the axial disks can be trained.

Tritt nun ein Erstabtrag am ersten Segment ein, so verhindert bzw. verhindern der bzw. die Anschläge nach einer bestimmten Abtragsmenge einen weiteren Abtrag. Die entstehenden Schubkräfte werden dann von der Axialscheibenlagerung auf der Ritzelwelle aufgenommen.If an initial removal occurs on the first segment, the stop or stops after a certain removal quantity prevent or prevent further removal. The thrust forces generated are then absorbed by the axial disk bearing on the pinion shaft.

Zweckmäßigerweise ist gemäß einer weiteren vorteilhaften Ausgestaltung der Erfindung der Anschlag als ein in eine Axialbohrung in der Axialscheibe eingepaßter Stift ausgebildet, der in eine entsprechende axiale Bohrung im ersten Segment, die jedoch einen größeren Durchmesser als der Stift aufweist, eingreift. Es ist ebenfalls denkbar, daß in kinematischer Umkehr der Anschlag in das erste Segment eingepaßt ist und in eine Bohrung größeren Durchmessers in der Axialscheibe eingreift. Mit dieser Ausgestaltung der Erfindung wird durch die Durchmesserdifferenz der beiden Bohrungen die erlaubte Abtragsmenge bestimmt. Im Normalbetrieb ist der Anschlag außer Funktion.According to a further advantageous embodiment of the invention, the stop is expediently designed as a pin fitted into an axial bore in the axial disk, which pin engages in a corresponding axial bore in the first segment, which, however, has a larger diameter than the pin. It is also conceivable that the stop is fitted into the first segment in a kinematic reversal and engages in a larger diameter bore in the axial disk. With this embodiment of the invention, the allowable removal quantity is determined by the difference in diameter of the two bores. The stop does not function in normal operation.

Eine weitere Ausgestaltung der Erfindung sieht in vorteilhafter Weise vor, daß der Anschlag als hydraulischer Anschlag in Form von mindestens einer in den dem ersten Segment zugewandten Seitenflächen der Axialscheiben angeordneten Blindnut ausgebildet ist, die mit ihrem offenen Ende mit der Druckaufbauseite der Pumpe in Verbindung steht, wobei das blinde Ende so angeordnet ist, daß es sich bei erfolgtem begrenzten Abtrag zur Druckseite der Pumpe öffnet. In kinematischer Umkehr ist es ebenfalls möglich, daß die mindestens eine Blindnut einseitig oder beidseitig am ersten Segment angeordnet ist, wobei die Verbindung mit der Druckseite immer vorhanden sein kann und sich durch den Abtrag dann eine Verbindung zum Druckaufbaubereich öffnet.A further embodiment of the invention advantageously provides that the stop is designed as a hydraulic stop in the form of at least one blind groove which is arranged in the side faces of the axial disks facing the first segment and is connected with its open end to the pressure build-up side of the pump. the blind end being arranged such that it opens to the pressure side of the pump when limited removal has taken place. In kinematic reversal, it is also possible for the at least one blind groove to be arranged on one side or on both sides of the first segment, it being possible for the connection to the pressure side to always be present and for the removal to open a connection to the pressure build-up area.

Diese Ausbildung des Anschlags beruht auf den hydraulischen Verhältnissen der Pumpe. Die in die Axialscheiben bzw. dem ersten Segment eingebrachten Blindnuten sind im Normalbetrieb durch die axiale Fläche des ersten Segments bzw. die Axialscheiben abgedeckt und außer Funktion.This design of the stop is based on the hydraulic conditions of the pump. The blind grooves introduced into the axial disks or the first segment are covered in normal operation by the axial surface of the first segment or the axial disks and are inoperative.

Erst nach erfolgtem Abtrag auf der den Ritzelköpfen zugewandten Fläche des ersten Segments werden durch die zwangsläufige Verlagerung der Rückseite des ersten Segments die den hydraulischen Anschlag bildenden Blindnuten frei und mit der Druckseite der Pumpe bzw. dem Druckraum verbunden.Only after removal has occurred on the surface of the first segment facing the pinion heads by inevitable displacement of the back of the first segment, the blind grooves forming the hydraulic stop free and connected to the pressure side of the pump or the pressure chamber.

Durch den Einsatz zusätzlicher Blindnuten wird die Druckaufbausteuerung am ersten Segment so beeinflußt, daß bei den herrschenden extremen Betriebsbedingungen eine Entlastung zwischen den Zahnköpfen des Ritzels und dem ersten Segment stattfindet und somit kein weiterer Abtrag erfolgt.By using additional blind grooves, the pressure build-up control on the first segment is influenced in such a way that, under the prevailing extreme operating conditions, there is a relief between the tooth tips of the pinion and the first segment and therefore no further erosion takes place.

Eine weitere vorteilhafte Ausgestaltung der Erfindung sieht vor, daß zwischen dem ersten Segment und dem zweiten Segment eine Verbindung zur Begrenzung der Spaltbreite im Bereich der Teilungsfläche nach erfolgtem begrenzten Abtrag ausgebildet ist.A further advantageous embodiment of the invention provides that a connection is formed between the first segment and the second segment to limit the gap width in the region of the division area after limited removal.

Wenn am ersten Segment ein Abtrag erfolgt, wird der Spalt zwischen dem ersten und zweiten Segment immer größer. Mit der losen, mechanischen Verbindung zwischen den beiden Segmenten wird erreicht, daß nach erfolgtem Erstabtrag am ersten Segment eine weitere Spaltvergrößerung durch die Verbindung verhindert wird.If the first segment is removed, the gap between the first and second segments increases. With the loose, mechanical connection between the two segments it is achieved that after the initial removal on the first segment, a further increase in gap is prevented by the connection.

Schließlich ist gemäß einer weiteren Ausgestaltung der Erfindung vorgesehen, daß eine Begrenzung für eine Drehbewegung des Stützbolzens zur Begrenzung des Abtrags der den Zähnen des Ritzels zugewandten Fläche des ersten Segments vorgesehen ist. Dabei kann die Begrenzung als ein Anschlagselement an der Anlagefläche des stumpfen Endes des Füllstücks am Stützbolzen auf der Rückseite einer der Axialscheiben oder im Lagerdeckel ausgebildet sein. Die gleiche Wirkung erzielt man, wenn die Begrenzung mittels eines Paßsitzes des Stützbolzens in den Axialscheiben oder den Lagerdeckeln ausgebildet ist.Finally, according to a further embodiment of the invention, it is provided that a limitation for a rotary movement of the support bolt is provided to limit the removal of the surface of the first segment facing the teeth of the pinion. The boundary can be designed as a stop element on the contact surface of the blunt end of the filler piece on the support bolt on the back of one of the axial disks or in the bearing cover. The same effect is achieved if the limitation is formed by means of a snug fit of the support bolt in the axial disks or the bearing caps.

Wie die praktischen Erfahrungen zeigen, erfolgt ein Abtrag am ersten Segment nicht parallel zu der den Zahnköpfen des Ritzels zugewandten Fläche, sondern es entsteht ein Drehmoment auf das erste Segment bzw. das Füllstück, das bewirkt, daß der größte Abtrag am spitzen Ende des ersten Segments erfolgt. Bei fortschreitendem Abtrag von dem spitzen Ende des ersten Segments her paßt sich der Stützbolzen den neuen Gegebenheiten an und verdreht sich, wodurch immer die ganze Anlagefläche des stumpfen Endes des Füllstücks am Stützbolzen anliegt. Durch die Begrenzung der Drehung des Stützbolzens verändert sich bei einem Abtrag des ersten Segments von der Spitze ausgehend die Anlage des ersten Segments an der Anlagefläche des Stützbolzens von einer flächenmäßigen Anlage zu einer linearen Anlage. Die Kraft F, mit der das erste Segment an den Stützbolzen gepreßt wird, erzeugt ein Moment Md um den Anlagepunkt, welches dem Abtrag des ersten Segments durch die Zahnköpfe des Ritzels entgegenwirkt.As practical experience shows, the first segment is not removed parallel to the surface facing the tooth tips of the pinion, but a torque is generated on the first segment or the filler, which causes the greatest removal at the tip end of the first segment he follows. As the removal progresses from the pointed end of the first segment, the support bolt adapts to the new conditions and rotates, as a result of which the entire contact surface of the blunt end of the filler piece lies against the support bolt. By limiting the rotation of the support bolt, when the first segment is removed from the tip, the contact of the first segment on the contact surface of the support bolt changes from a flat contact to a linear contact. The force F with which the first segment is pressed against the support bolt generates a moment Md around the contact point, which counteracts the removal of the first segment by the tooth tips of the pinion.

Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden im folgenden näher beschrieben. Es zeigen:

Fig. 1
eine geschnittene Seitenansicht einer ersten Ausführungsform der Innenzahnradpumpe;
Fig. 1a
eine Schnittansicht längs der Linie A-B in Fig. 1 zur Darstellung des mechanischen Anschlags;
Fig. 2
eine geschnittene Seitenansicht einer zweiten Ausführungsform der Innenzahnradpumpe mit mechanischem Anschlag;
Fig. 3
eine geschnittene Seitenansicht einer dritten Ausführungsform der Innenzahnradpumpe mit hydraulischem Anschlag;
Fig. 4
eine geschnittene Seitenansicht einer vierten Ausführungsform der Innenzahnradpumpe mit hydraulischem Anschlag;
Fig. 5
eine geschnittene Seitenansicht einer fünften Ausführungsform der Innenzahnradpumpe mit einer Verbindung zwischen dem ersten und zweiten Segment;
Fig. 6
eine geschnittene Seitenansicht einer sechsten Ausführungsform der Innenzahnradpumpe mit einer Begrenzung für die Drehbewegung des Stützbolzens;
Fig. 7
eine geschnittene Seitenansicht einer siebten Ausführungsform der Innenzahnradpumpe mit einer Begrenzung für die Drehbewegung des Stützbolzens;
Fig. 7a,b
Schnittansichten längs der Linie C-D in Fig. 7 zur Darstellung zweier alternativer Ausbildungen der Begrenzungen;
Fig. 8
eine Detailansicht gemäß Detail "A" in Fig. 6 zur Darstellung des Paßsitzes in den Axialscheiben; und
Fig. 9
eine Detailansicht gemäß Detail "A" in Fig. 6 zur Darstellung des Paßsitzes in den Lagerdeckeln.
Embodiments of the invention are shown in the drawing and are described in more detail below. Show it:
Fig. 1
a sectional side view of a first embodiment of the internal gear pump;
Fig. 1a
a sectional view taken along line AB in Figure 1 to illustrate the mechanical stop.
Fig. 2
a sectional side view of a second embodiment of the internal gear pump with mechanical stop;
Fig. 3
a sectional side view of a third embodiment of the internal gear pump with hydraulic stop;
Fig. 4
a sectional side view of a fourth embodiment of the internal gear pump with hydraulic stop;
Fig. 5
a sectional side view of a fifth embodiment of the internal gear pump with a connection between the first and second segments;
Fig. 6
a sectional side view of a sixth embodiment of the internal gear pump with a limit for the rotational movement of the support bolt;
Fig. 7
a sectional side view of a seventh embodiment of the internal gear pump with a limit for the rotational movement of the support bolt;
7a, b
Sectional views along the line CD in FIG. 7 to show two alternative configurations of the boundaries;
Fig. 8
a detailed view according to detail "A" in Figure 6 to illustrate the snug fit in the axial washers. and
Fig. 9
a detailed view according to detail "A" in Fig. 6 to show the snug fit in the bearing caps.

Die in den Figuren dargestellte Innenzahnradpumpe 10 umfaßt allgemein ein innenverzahntes Hohlrad 12, zwei an den beiden Seiten des Hohlrades 12 angeordnete Axialscheiben 13, ein zum Hohlrad 12 exzentrisch angeordnetes und mit dem Hohlrad 12 in Eingriff stehendes, angetriebenes, außenverzahntes Ritzel 14 und ein im Umfangsrichtung eteiltes, sichelförmiges, schwimmend gelagertes Füllstück 16, das mit seinem stumpfen Ende 36 gegen einen axialen Stützbolzen 17 anliegt. Das Füllstück 16 weist ein erstes, den Zähnen des Ritzels 14 zugewandtes Segment 18 und ein zweites, den Zähnen des Hohlrades 12 zugewandtes Segment 20 auf. Das erste Segment 18 hat eine größere radiale Dicke als das zweite Segment 20. In der Teilungsfläche 22 zwischen den beiden Segmenten 18, 20 sind axial verlaufende Nuten 24 zur Aufnahme von Dichtelementen 26 vorgesehen.The internal gear pump 10 shown in the figures generally comprises an internally toothed ring gear 12, two axial disks 13 arranged on the two sides of the ring gear 12, a driven, externally toothed pinion 14 arranged eccentrically to the ring gear 12 and in engagement with the ring gear 12, and one in the circumferential direction divided, sickle-shaped, floating filler 16, which abuts with its blunt end 36 against an axial support pin 17. The filler 16 has a first segment 18 facing the teeth of the pinion 14 and a second segment 20 facing the teeth of the ring gear 12. The first segment 18 has a greater radial thickness than the second segment 20. In the dividing surface 22 between the two segments 18, 20, axially extending grooves 24 are provided for receiving sealing elements 26.

Wie in den Fig. 1, 1a gezeigt, weist das erste Segment 18 an seinem spitzen Ende 32 einen Anschlag 28 zur Begrenzung des Abtrags 54 der den Zähnen des Ritzels 14 zugewandten Fläche 30 des ersten Segments 18 auf. Dieser Anschlag 28 besteht, wie in Fig. 1a dargestellt, aus einem Stift 40, der mit seinem einen Abschnitt in eine Axialbohrung 38 einer Axialscheibe 13 eingepaßt ist. Mit seinem anderen Abschnitt ist der Stift 40 in einer axialen Bohrung 42 im ersten Segment 18 angeordnet, wobei diese Bohrung 42 einen größeren Durchmesser als die Axialbohrung 38 in der Axialscheibe 13 aufweist. Obwohl nicht in der Zeichnung dargestellt, ist ebenfalls eine Anordnung in kinematischer Umkehr denkbar, d.h. der Paßsitz befindet sich in diesem Fall im ersten Segment 18, und die Bohrung mit größerem Durchmesser ist in der Axialscheibe 13 angeordnet. Nach erfolgtem Erstabtrag werden die entstehenden Schubkräfte zwischen dem ersten Segment 18 und dem Ritzel 14 von der Axialscheibenlagerung 69 auf der Ritzelwelle aufgenommen.As shown in FIGS. 1, 1a, the first segment 18 has a stop 28 for limitation at its tip end 32 of the removal 54 of the surface 30 of the first segment 18 facing the teeth of the pinion 14. This stop 28 consists, as shown in Fig. 1a, of a pin 40, which is fitted with its one portion in an axial bore 38 of an axial disc 13. With its other section, the pin 40 is arranged in an axial bore 42 in the first segment 18, this bore 42 having a larger diameter than the axial bore 38 in the axial disk 13. Although not shown in the drawing, an arrangement in kinematic reversal is also conceivable, ie the fit is in this case in the first segment 18, and the larger diameter bore is arranged in the axial disk 13. After the first removal, the thrust forces generated between the first segment 18 and the pinion 14 are absorbed by the axial disk bearing 69 on the pinion shaft.

Eine weitere Ausführungsform der Erfindung ist in Fig. 2 dargestellt. Bei dieser Ausführungsform ist ein zweiter mechanischer Anschlag 34 im Bereich des stumpfen Endes 36 des ersten Segments 18 vorgesehen. Dieser zweite Anschlag 34 ist entsprechend dem ersten Anschlag 28 ausgebildet.Another embodiment of the invention is shown in FIG. 2. In this embodiment, a second mechanical stop 34 is provided in the region of the blunt end 36 of the first segment 18. This second stop 34 is designed in accordance with the first stop 28.

Bei der in Fig. 3 dargestellten Ausführungsform der Innenzahnradpumpe 10 ist der Anschlag als hydraulischer Anschlag 44 ausgebildet. Dieser hydraulische Anschlag 44 besteht aus mindestens einer Blindnut 46, die in die dem ersten Segment zugewandten Seitenflächen der Axialscheiben ausgebildet ist. Das offene Ende 52 der Blindnut 46 steht mit der Druckaufbauseite 50 der Innenzahnradpumpe 10 in Verbindung. Das blinde Ende 48 ist im Normalbetrieb von der Seitenfläche des ersten Segments 18 abgedeckt. Erst nach erfolgtem Abtrag 54 der den Zähnen des Ritzels 14 zugewandten Fläche 30 des ersten Segments 18 wird durch die zwangsläufige Verlagerung der Teilungsfläche 22 die den hydraulischen Anschlag 44 bildende Blindnut 46 an ihrem blinden Ende 48 frei und mit der Druckseite 50 der Innenzahnradpumpe verbunden. Hierdurch wird der Druckaufbau am ersten Segment 18 so beeinflußt, daß bei extremen Bedingungen eine Entlastung zwischen den Zähnen des Ritzels 14 und dem ersten Segment 18 stattfindet, so daß kein weiterer Abtrag erfolgt. Je nach den Anforderungen können ebenfalls mehrere Blindnuten 46 oder Steuernuten in den Axialscheiben 13 vorgesehen sein. Es ist ebenfalls möglich, in kinematischer Umkehr die Blindnuten in den Seitenflächen einseitig oder beidseitig am ersten Segment 18 anzuordnen (siehe Fig. 4), wobei jetzt die Blindnut mit der Druckseite 50 in Verbindung steht und sich nach erfolgtem Abtrag 54 eine Verbindung zur Druckaufbauseite öffnet.In the embodiment of the internal gear pump 10 shown in FIG. 3, the stop is designed as a hydraulic stop 44. This hydraulic stop 44 consists of at least one blind groove 46 which is formed in the side faces of the axial disks facing the first segment. The open end 52 of the blind groove 46 is connected to the pressure build-up side 50 of the internal gear pump 10. The blind end 48 is covered by the side surface of the first segment 18 in normal operation. Only after the removal 54 of the surface 30 of the first segment 18 facing the teeth of the pinion 14 does the blind groove 46 forming the hydraulic stop 44 become free at its blind end 48 and with the pressure side 50 of the by the inevitable displacement of the dividing surface 22 Internal gear pump connected. As a result, the pressure build-up on the first segment 18 is influenced in such a way that, under extreme conditions, relief occurs between the teeth of the pinion 14 and the first segment 18, so that no further erosion takes place. Depending on the requirements, a plurality of blind grooves 46 or control grooves can also be provided in the axial disks 13. It is also possible, in a kinematic reversal, to arrange the blind grooves in the side faces on one side or on both sides of the first segment 18 (see FIG. 4), the blind groove now being connected to the pressure side 50 and, after removal 54 has taken place, a connection to the pressure build-up side opens .

Zweckmäßigerweise wird das geschlossene Ende der Blindnut als Radius ausgeführt, weil sich dann die Größe der Verbindung (des Durchbruchs) automatisch auf die herrschenden hydraulischen Verhältnisse einstellt. Der Abtrag an der Innenseite des Füllstückes schreitet also so lange fort, bis ein ausreichender Querschnitt vorhanden ist, um das hydraulische Gleichgewicht zu erreichen.The closed end of the blind groove is expediently designed as a radius, because the size of the connection (of the opening) then automatically adjusts to the prevailing hydraulic conditions. The removal on the inside of the filler continues until a sufficient cross-section is available to achieve the hydraulic balance.

Eine weitere Ausführungsform der Erfindung ist in Fig. 5 dargestellt. Bei dieser Ausführungsform ist zwischen dem ersten Segment 18 und dem zweiten Segment 20 eine Verbindung 58 zur Begrenzung der Breite des Spalts 70 im Bereich der Teilungsfläche 22 vorgesehen. Wenn an dem ersten Segment 18 ein Abtrag erfolgt, wird der Spalt zwischen dem ersten Segment 18 und dem zweiten Segment 20 immer größer.Another embodiment of the invention is shown in FIG. 5. In this embodiment, a connection 58 is provided between the first segment 18 and the second segment 20 to limit the width of the gap 70 in the region of the dividing surface 22. If ablation takes place on the first segment 18, the gap between the first segment 18 and the second segment 20 increases.

Durch das Vorsehen einer losen, mechanischen Verbindung zwischen den beiden Segmenten 18, 20 wird eine weitere Vergrößerung des Spalts und somit ein weiterer Abtrag am ersten Segment 18 verhindert.The provision of a loose, mechanical connection between the two segments 18, 20 prevents a further enlargement of the gap and thus further removal of the first segment 18.

Eine weitere Ausführungsform der Innenzahnradpumpe ist in den Fig. 6 bis 9 dargestellt. Es hat sich gezeigt, daß ein Abtrag am ersten Segment 18 nicht parallel zu der den Zahnköpfen des Ritzels 14 zugewandten Fläche erfolgt, sondern daß infolge eines auf das erste Segment 18 einwirkenden Drehmoments ein verstärkter Abtrag am spitzen Ende 32 des ersten Segments 18 erfolgt. Bei fortschreitendem Abtrag vom spitzen Ende 32 des ersten Segments 18 her paßt sich der Stützbolzen 17 den neuen Gegebenheiten an und verdreht sich, so daß immer die ganze Anlagefläche 64 des stumpfen Endes 36 des Füllstücks 16 am Stützbolzen 17 anliegt. Um nun den Abtrag am ersten Segment 18 zu begrenzen, ist bei dieser Ausführungsform der Innenzahnradpumpe 10 eine Begrenzung 60 für die Drehbewegung des Stützbolzens 17 vorgesehen. Hierdurch verändert sich bei einem Abtrag des ersten Segments 18 vom spitzen Ende 32 ausgehend die Anlage des ersten Segments 18 an der Anlagefläche 64 des Stützbolzens 17 von einer flächenmäßigen Anlage in eine Linienanlage im Anlagepunkt 68. Die Kraft F, mit der das erste Segment 18 an den Stützbolzen 17 gepreßt wird, erzeugt ein Moment Md um den Punkt 68, welches dem Abtrag des ersten Segments 18 durch die Zähne des Ritzels 14 entgegenwirkt.Another embodiment of the internal gear pump is shown in FIGS. 6 to 9. It has been shown that a Removal on the first segment 18 does not take place parallel to the surface facing the tooth heads of the pinion 14, but instead, as a result of a torque acting on the first segment 18, there is an increased removal on the tip end 32 of the first segment 18. As the removal progresses from the pointed end 32 of the first segment 18, the support bolt 17 adapts to the new conditions and rotates, so that the entire contact surface 64 of the blunt end 36 of the filler piece 16 bears against the support bolt 17. In order to limit the removal on the first segment 18, a limitation 60 is provided for the rotary movement of the support bolt 17 in this embodiment of the internal gear pump 10. As a result, when the first segment 18 is removed from the pointed end 32, the contact of the first segment 18 on the contact surface 64 of the support bolt 17 changes from a planar contact to a line contact at the contact point 68. The force F with which the first segment 18 acts the support pin 17 is pressed, a moment Md around the point 68, which counteracts the removal of the first segment 18 by the teeth of the pinion 14.

In der in Fig. 7 dargestellten Ausführungsform ist die Begrenzung 60 als Anschlagselement 62 ausgebildet. Das Anschlagselement 62 kann entweder in der Rückseite der Axialscheiben 13 (siehe Fig. 7a) oder in den Lagerdeckeln 66 (siehe Fig. 7b) ausgebildet sein. Eine weitere Möglichkeit der Ausbildung der Begrenzung 60 besteht in einem Paßsitz, mit welchem der Stützbolzen 17 entweder in die Axialscheiben 13 oder die Lagerdeckel 66 eingepaßt ist (siehe Fig. 8 und 9).In the embodiment shown in FIG. 7, the boundary 60 is designed as a stop element 62. The stop element 62 can either be formed in the rear of the axial disks 13 (see FIG. 7a) or in the bearing caps 66 (see FIG. 7b). Another possibility of forming the limit 60 consists in a snug fit with which the support bolt 17 is fitted either in the axial disks 13 or the bearing cover 66 (see FIGS. 8 and 9).

Bei der beschriebenen Innenzahnradpumpe wird durch das Vorsehen eines Anschlags in einer der oben beschriebenen Ausführungsformen oder in deren Kombination nach einem bestimmten Abtrag der den Köpfen des Ritzels 14 zugewandten Fläche 30 des ersten Segments 18 dieser Abtrag 54 begrenzt, so daß kein weiterer Abtrag des ersten Segments 18 erfolgt und damit eine Zerstörung der Innenzahnradpumpe verhindert wird.In the internal gear pump described, by providing a stop in one of the above-described embodiments or in combination thereof, after a certain removal of the surface 30 of the first segment 18 facing the heads of the pinion 14, this removal 54 is limited, so that no further removal of the first segment 18 takes place and thus destruction of the internal gear pump is prevented.

Claims (11)

  1. Internal gear pump with an internally toothed hollow wheel, two axial discs arranged on both sides of the hollow wheel, a driven externally toothed pinion arranged off-centre relative to the hollow wheel and in engagement with the hollow wheel, and a sickle-shaped float mounted filler piece divided in peripheral direction, which rests at its blunt end on an axial support bolt, of which the first segment facing the teeth of the pinion has a greater radial thickness than the second segment facing the teeth of the hollow wheel, whereby the first segment in the divided surface has at least one axial groove for mounting a sealing element, characterised in that the first segment (18) has at least one stop (28, 34, 44, 58, 60) for restricting the wear (54) of the surface facing the teeth of the pinion (14).
  2. Internal gear pump according to claim 1, characterised in that the stop is designed as a mechanical stop (28) and is arranged in the region of the pointed end (32) of the first segment (18) in connection with the axial discs (13).
  3. Internal gear pump according to one of claims 1 to 2, characterised in that a second mechanical stop (34) is designed in the region of the blunt end (36) of the first segment (18) in connection with the axial discs (13).
  4. Internal gear pump according to one of claims 1 to 3, characterised in that the stop (28, 36) is designed as a pin (40) fitted into an axial bore (38) in the axial disc (13), which pin engages in a corresponding axial bore (42) in the first segment (18), which has a larger diameter than the pin (40).
  5. Internal gear pump according to one of claims 1 to 3, characterised in that the stop (28, 36) is designed as a pin (40) fitted into an axial bore in the first segment (18), which pin engages in a corresponding axial bore in the axial disc (13) which has a larger diameter than the pin (40).
  6. Internal gear pump according to claim 1, characterised in that the stop is designed as a hydraulic stop (44) in the form of at least one blind groove (46) facing the first segment (18) and arranged in the side surfaces of the axial discs (13), which connects at its open end (52) to the pressure build-up side (56) of the pump (10) and the blind end (48) is arranged so that with the successful restriction of wear (54) it opens to the pressure side (50) of the pump (10).
  7. Internal gear pump according to claim 1, characterised in that the stop is designed as a hydraulic stop (44) in the form of at least one blind groove (47) arranged on the side surfaces of the first segment (18) which with its open end (52) is in connection with the pressure side of the pump, and the blind end (48) is arranged so that it opens with the successful restriction of wear to the pressure side of the pump.
  8. Internal gear pump according to claim 1, characterised in that between the first segment (18) and the second segment (20) there is a connection (58) to the restriction of the gap width in the region of the divided surface (22) after the successful restriction of wear (54).
  9. Internal gear pump according to claim 1, characterised in that a restriction (60) is provided for a rotational movement of the support bolt (17) to restrict the wear of the surface (30) of the first segment (18) facing the teeth of the pinion (14).
  10. Internal gear pump according to claim 9, characterised in that the restriction (60) is designed as a stop element (62) on the bearing surface (64) of the blunt end (36) of the filler piece (16) on the support bolt (17) on the rear side of one of the axial discs (13) or in the bearing cap (66).
  11. Internal gear pump according to claim 9, characterised in that the restriction (60) is designed by means of a tight fit of the support bolt (17) in the axial discs (13) or the bearing caps (66).
EP94113166A 1993-08-26 1994-08-24 Internal gear pump Expired - Lifetime EP0640766B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4328733A DE4328733C1 (en) 1993-08-26 1993-08-26 Internal-gear pump
DE4328733 1993-08-26

Publications (2)

Publication Number Publication Date
EP0640766A1 EP0640766A1 (en) 1995-03-01
EP0640766B1 true EP0640766B1 (en) 1997-01-02

Family

ID=6496094

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94113166A Expired - Lifetime EP0640766B1 (en) 1993-08-26 1994-08-24 Internal gear pump

Country Status (6)

Country Link
US (1) US5499910A (en)
EP (1) EP0640766B1 (en)
JP (1) JPH07151067A (en)
KR (1) KR100191180B1 (en)
AT (1) ATE147138T1 (en)
DE (1) DE4328733C1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996037704A1 (en) * 1995-05-26 1996-11-28 J.M. Voith Gmbh Machine based on an internally geared wheel
DE19854155B4 (en) * 1997-12-03 2012-04-26 Schaeffler Technologies Gmbh & Co. Kg Hydraulic gear machine
DE10109769A1 (en) * 2001-03-01 2002-09-05 Eckerle Ind Elektronik Gmbh Internal gear pump without filler
DE202013103826U1 (en) 2013-05-13 2013-09-09 Eckerle Industrie-Elektronik Gmbh Internal gear machine with filler retainer
CN103939333B (en) * 2014-04-25 2016-06-01 福州大学 A kind of inside gearing pump with radial compensation
CN111828307A (en) * 2020-06-15 2020-10-27 南京威孚金宁有限公司 Pump body structure of internal gear pump and assembly process thereof

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1243025A (en) * 1967-09-01 1971-08-18 Otto Eckerle Improvements in and relating to hydraulic gear pumps
DE2313085C2 (en) * 1973-03-16 1984-05-24 Otto 7502 Malsch Eckerle Axially and radially compensated high pressure gear pump
DE2606082A1 (en) * 1976-02-16 1977-08-25 Otto Eckerle HIGH PRESSURE GEAR PUMP OR MOTOR
DE2533646C2 (en) * 1975-07-28 1986-04-17 Otto Sion Wallis Eckerle High pressure gear pump or motor
DE2641278A1 (en) * 1976-09-14 1978-03-16 Voith Getriebe Kg INTERNAL GEAR PUMP
DE2942417A1 (en) * 1979-10-19 1981-05-14 Otto Eckerle GmbH & Co KG, 7502 Malsch INTERNAL GEAR MACHINE

Also Published As

Publication number Publication date
JPH07151067A (en) 1995-06-13
KR100191180B1 (en) 1999-06-15
EP0640766A1 (en) 1995-03-01
KR950006257A (en) 1995-03-20
US5499910A (en) 1996-03-19
ATE147138T1 (en) 1997-01-15
DE4328733C1 (en) 1994-09-08

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