EP2235375B1 - Liquid pump - Google Patents

Liquid pump Download PDF

Info

Publication number
EP2235375B1
EP2235375B1 EP08863084.3A EP08863084A EP2235375B1 EP 2235375 B1 EP2235375 B1 EP 2235375B1 EP 08863084 A EP08863084 A EP 08863084A EP 2235375 B1 EP2235375 B1 EP 2235375B1
Authority
EP
European Patent Office
Prior art keywords
pressure
sealing unit
pump
liquid pump
unit
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.)
Not-in-force
Application number
EP08863084.3A
Other languages
German (de)
French (fr)
Other versions
EP2235375A1 (en
Inventor
Dirk Foerch
Martin Hochdoerffer
Harald Hermann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2235375A1 publication Critical patent/EP2235375A1/en
Application granted granted Critical
Publication of EP2235375B1 publication Critical patent/EP2235375B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C15/0038—Shaft sealings specially adapted for rotary-piston machines or pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms

Definitions

  • the invention relates to a liquid pump according to the preamble of independent claim 1.
  • liquid pumps designed as gear pumps consist of a rotatably arranged drive shaft which leads into a pump housing of the liquid pump.
  • a pump unit with at least one gear, which represents the pumping function.
  • the drive shaft is performed only on one side of the pump housing and transmits drive energy to the at least one gear.
  • This bushing must be sealed with a sealing unit designed, for example, as a radial shaft seal. If the liquid pump generates an operating pressure p B or if the liquid pump is charged with admission pressure p v , this sealing unit absorbs the resulting axial load by the sealing unit sealing the pump housing from the environment.
  • a liquid pump having a pump housing and a pump unit arranged in the pump unit for generating an operating pressure of the liquid.
  • a drive shaft which is carried out on the input / output side out of the pump housing is provided, which is mounted in the pump housing via bearing units.
  • the bushing is sealed by a sealing unit.
  • the liquid pump according to the invention according to the features of independent claim 1 has the advantage that an asymmetrical arrangement of the pressure fields is provided.
  • the charged by the form surfaces are thus different sizes.
  • the axial force in the fluid pump arising during the loading of the fluid pump with the admission pressure can be compensated. It creates a balance of forces on the drive shaft.
  • the storage units of the liquid pump only need to absorb radial forces, resulting in a simplification of the storage units and a resulting cost savings.
  • the fact that the sealing unit only has to absorb lower pressures, the sealing unit can be designed significantly cheaper.
  • the pressure field facing the sealing unit is preferably larger than the pressure field facing away from the sealing unit. This results in an optimal seal of the pump housing against the environment. If the pump unit has several gears, the area of the pressure fields can be distributed to the individual gears.
  • the pressure field facing the sealing unit is larger by a surface of the cross section of the drive shaft than the pressure field facing away from the sealing unit.
  • an enlargement of the sealing unit facing the pressure field is easy and inexpensive to achieve via a recess in a sealing surface of the liquid pump.
  • the charged by the form surfaces are thus different sizes. This creates a pressure-free surface relative to the sealing unit.
  • a symmetrical arrangement of the pressure fields related to an operating pressure of the fluid pump is provided. This results in interaction with the pressure fields of the form a balance of forces on the drive shaft.
  • the pressure-free surface is formed opposite the sealing unit.
  • a channel for connecting the recess is preferably provided with a space in the pump unit.
  • the pump unit is a gear transmission.
  • the space in the pump unit is a space between the teeth of two gears, i. around so-called interdental spaces.
  • the interdental spaces are to be used directly after the vertex, which creates a negative pressure by the expansion of the interstices.
  • a line for connecting the recess can be provided with a storage chamber, which also allows a simple and cost-effective implementation of a discharge.
  • Fig. 1 shows a liquid pump 10 according to the invention in the form of a gear pump with a pump housing 12 having an interior 46 with an inlet 48 a suction side and a discharge 50 a pressure side.
  • a rotatably arranged drive shaft 16 which drives a pump unit 14 arranged in the interior 46 of the pump housing 12, leads into the pump housing 12 via a shaft passage to be sealed.
  • the pump unit 14 serves to convey the liquid to produce a correspondingly high pressure level of the liquid, ie to produce an operating pressure p B.
  • the liquid is in this case pumped in the usual way from the suction side to the pressure side of the liquid pump 10.
  • the pump unit 14 preferably has a gear transmission, which as a rule at least two gears 38, 40 in accordance with Fig. 2 includes, one of which is driven via the drive shaft 16. Depending on the arrangement and size of the gears, this can preferably be an external gear, an internal gear, a toothed ring pump or a screw pump.
  • the liquid pump 10 usually evenly pumps the liquid to be pumped. There is a symmetrical arrangement of the pressure fields 30, 32 of the operating pressure p B before.
  • the drive shaft 16 is rotatably mounted in the pump housing 12 via bearing units 52, 54. Between the shaft passage and the drive shaft 16 designed as a shaft seal sealing unit 18 is arranged to seal the pump housing 12 to the drive shaft 16 to the outside or against the environment.
  • the shaft seal 18 is arranged with a fixed seat in a recess of the pump housing 12.
  • the shaft seal 18 is formed as a radial shaft seal, which presses radially on the surface of the drive shaft 16.
  • the oil seal 18 has a can be applied to the fluid pump 10 inlet pressure p v and the operating pressure occurring in the pump housing 12 p B be designed accordingly, that the shaft seal ring 18 must be sufficient to raise high radial forces, depending on the pressure level to perform its function.
  • the pressurized fluid in the area of the sealing unit 18 When the liquid pump 10 is pressurized with the admission pressure p v , the pressurized fluid in the area of the sealing unit 18 generates at least one pressure field 20 facing the sealing unit 18 and at least one pressure field 22 facing away from the sealing unit 18 at the sealing unit 18.
  • an asymmetrical arrangement of the pressure fields 20, 22 is provided according to the invention.
  • the pressure field 20 facing the sealing unit 18 is greater than the pressure field 22 facing away from the sealing unit 18.
  • the pressure field 20 facing the sealing unit 18 is preferably larger around the area of the cross section 24 of the drive shaft 16 than the pressure field 22 facing away from the sealing unit 18.
  • FIG. 2 An enlargement of the sealing unit 18 facing pressure field 20 is according to Fig. 2 achieved via a recess 26 in a sealing surface 28 of the liquid pump 10.
  • a channel 34 for connection of the recess 26 is provided with a space 36 in the pump unit 14.
  • the space 36 in the pump unit 14 is a space between the teeth of the two gears 38, 40.
  • a conduit 42 for connecting the recess to a storage chamber 44 is provided.
  • the relief measures can also be provided individually.

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Flüssigkeitspumpe nach dem Oberbegriff des unabhängigen Patentanspruchs 1.The invention relates to a liquid pump according to the preamble of independent claim 1.

Üblicherweise bestehen als Zahnradpumpen ausgeführte Flüssigkeitspumpen aus einer drehbar angeordneten Antriebswelle, welche in ein Pumpengehäuse der Flüssigkeitspumpe hineinführt. Im Pumpengehäuse befindet sich eine Pumpeneinheit mit mindestens einem Zahnrad, welches die Pumpfunktion darstellt. Die Antriebswelle ist nur auf einer Seite des Pumpengehäuses durchgeführt und überträgt Antriebsenergie auf das mindestens eine Zahnrad. Diese Durchführung muss mit einer beispielsweise als Radialwellendichtring ausgeführten Dichteinheit abgedichtet werden. Erzeugt die Flüssigkeitspumpe einen Betriebsdruck pB bzw. wird die Flüssigkeitspumpe mit Vordruck pv belastet, nimmt diese Dichteinheit die entstehende Axiallast auf, indem die Dichteinheit das Pumpengehäuse gegen die Umgebung abdichtet. Diese Axiallast F berechnet sich aus dem Dichtdurchmesser D der Welle und dem anstehenden Vordruck pv nach der Gleichung F = p v * D 2 * π / 4.

Figure imgb0001
Usually, liquid pumps designed as gear pumps consist of a rotatably arranged drive shaft which leads into a pump housing of the liquid pump. In the pump housing is a pump unit with at least one gear, which represents the pumping function. The drive shaft is performed only on one side of the pump housing and transmits drive energy to the at least one gear. This bushing must be sealed with a sealing unit designed, for example, as a radial shaft seal. If the liquid pump generates an operating pressure p B or if the liquid pump is charged with admission pressure p v , this sealing unit absorbs the resulting axial load by the sealing unit sealing the pump housing from the environment. This axial load F is calculated from the sealing diameter D of the shaft and the pending form p v according to the equation F = p v * D 2 * π / 4th
Figure imgb0001

So zeigt die DE 199 24 057 A1 eine Flüssigkeitspumpe mit einem Pumpengehäuse und einer im Pumpengehäuse angeordneten Pumpeneinheit zur Erzeugung eines Betriebsdrucks der Flüssigkeit. Zum Antreiben der Pumpeneinheit ist eine auf einer An-/Abtriebsseite aus dem Pumpengehäuse durchgeführte Antriebswelle vorgesehen, die über Lagereinheiten im Pumpengehäuse gelagert ist. Die Durchführung wird über eine Dichteinheit abgedichtet. Bei Belastung der Flüssigkeitspumpe erzeugt die unter Druck stehende Flüssigkeit im Bereich der Dichteinheit mindestens ein der Dichteinheit zugewandtes Druckfeld und mindestens ein der Dichteinheit abgewandtes Druckfeld an der Dichteinheit.That's how it shows DE 199 24 057 A1 a liquid pump having a pump housing and a pump unit arranged in the pump unit for generating an operating pressure of the liquid. For driving the pump unit, a drive shaft which is carried out on the input / output side out of the pump housing is provided, which is mounted in the pump housing via bearing units. The bushing is sealed by a sealing unit. When the liquid pump is loaded, the liquid under pressure generates at least one sealing unit facing the sealing unit in the region of the sealing unit Pressure field and at least one of the sealing unit facing away pressure field on the sealing unit.

Offenbarung der ErfindungDisclosure of the invention

Die erfindungsgemäße Flüssigkeitspumpe nach den Merkmalen des unabhängigen Patentanspruchs 1 hat demgegenüber den Vorteil, dass eine asymmetrische Anordnung der Druckfelder vorgesehen ist. Die durch den Vordruck belasteten Flächen sind somit unterschiedlich groß. Durch eine asymmetrische Anordnung der den Vordruck betreffenden Druckfelder kann die bei der Belastung der Flüssigkeitspumpe mit dem Vordruck entstehende Axialkraft in der Flüssigkeitspumpe kompensiert werden. Es entsteht ein Kräftegleichgewicht an der Antriebswelle. Die Lagereinheiten der Flüssigkeitspumpe müssen nur noch radiale Kräfte aufnehmen, was zu einer Vereinfachung der Lagereinheiten und einer daraus resultierenden Kostenersparnis führt. Vorteilhafterweise ergibt sich eine Reduktion der Druckbelastung an der Dichteinheit. Dadurch, dass die Dichteinheit nur noch geringere Drücke aufnehmen muss, kann die Dichteinheit deutlich kostengünstiger ausgelegt werden.The liquid pump according to the invention according to the features of independent claim 1 has the advantage that an asymmetrical arrangement of the pressure fields is provided. The charged by the form surfaces are thus different sizes. As a result of an asymmetrical arrangement of the pressure fields relating to the admission pressure, the axial force in the fluid pump arising during the loading of the fluid pump with the admission pressure can be compensated. It creates a balance of forces on the drive shaft. The storage units of the liquid pump only need to absorb radial forces, resulting in a simplification of the storage units and a resulting cost savings. Advantageously, there is a reduction of the pressure load on the sealing unit. The fact that the sealing unit only has to absorb lower pressures, the sealing unit can be designed significantly cheaper.

Durch die in den abhängigen Ansprüchen aufgeführten Maßnahmen und Weiterbildungen sind vorteilhafte Verbesserungen der im unabhängigen Patentanspruch angegebenen Flüssigkeitspumpe möglich.The measures and refinements recited in the dependent claims advantageous improvements of the independent claim liquid pump are possible.

Um eine asymmetrische Anordnung der Druckfelder zu erhalten, ist vorzugsweise das der Dichteinheit zugewandte Druckfeld größer als das der Dichteinheit abgewandte Druckfeld. Hierdurch ergibt sich eine optimale Abdichtung des Pumpengehäuses gegen die Umgebung. Weist die Pumpeneinheit mehrere Zahnräder auf, kann die Fläche der Druckfelder auf die einzelnen Zahnräder verteilt werden.In order to obtain an asymmetrical arrangement of the pressure fields, the pressure field facing the sealing unit is preferably larger than the pressure field facing away from the sealing unit. This results in an optimal seal of the pump housing against the environment. If the pump unit has several gears, the area of the pressure fields can be distributed to the individual gears.

Besonders vorteilhaft ist das der Dichteinheit zugewandte Druckfeld um eine Fläche des Querschnitts der Antriebswelle größer als das der Dichteinheit abgewandte Druckfeld.Particularly advantageously, the pressure field facing the sealing unit is larger by a surface of the cross section of the drive shaft than the pressure field facing away from the sealing unit.

Vorteilhafterweise ist eine Vergrößerung des der Dichteinheit zugewandten Druckfeldes einfach und kostengünstig über eine Vertiefung in einer Dichtfläche der Flüssigkeitspumpe zu erreichen. Die durch den Vordruck belasteten Flächen sind somit unterschiedlich groß. Hierbei entsteht eine druckfreie Fläche gegenüber der Dichteinheit.Advantageously, an enlargement of the sealing unit facing the pressure field is easy and inexpensive to achieve via a recess in a sealing surface of the liquid pump. The charged by the form surfaces are thus different sizes. This creates a pressure-free surface relative to the sealing unit.

Vorzugsweise ist eine symmetrische Anordnung der auf einen Betriebsdruck der Flüssigkeitspumpe bezogenen Druckfelder vorgesehen. Hierdurch ergibt sich im Zusammenwirken mit den Druckfeldern des Vordruckes ein Kräftegleichgewicht an der Antriebswelle.Preferably, a symmetrical arrangement of the pressure fields related to an operating pressure of the fluid pump is provided. This results in interaction with the pressure fields of the form a balance of forces on the drive shaft.

Dadurch, dass das der Dichteinheit abgewandte Druckfeld des Vordrucks kleiner als das der Antriebswelle zugewandte Druckfeld ausgelegt ist und die Druckfelder des Betriebsdrucks symmetrisch ausgelegt sind, entsteht die druckfreie Fläche gegenüber der Dichteinheit. Um diese druckfreie Fläche auf einfache und kostengünstige Weise zu entlasten, ist vorzugsweise ein Kanal zur Verbindung der Vertiefung mit einem Raum in der Pumpeneinheit vorgesehen.Because the pressure field of the pre-pressure facing away from the sealing unit is designed to be smaller than the pressure field facing the drive shaft and the pressure fields of the operating pressure are designed symmetrically, the pressure-free surface is formed opposite the sealing unit. In order to relieve this pressure-free surface in a simple and cost-effective manner, a channel for connecting the recess is preferably provided with a space in the pump unit.

Bei der Pumpeneinheit handelt es sich um ein Zahnradgetriebe. Vorteilhafterweise handelt es sich bei dem Raum in der Pumpeneinheit um einen Raum zwischen den Zähnen zweier Zahnräder, d.h. um sogenannte Zahnzwischenräume. Vorzugsweise sind die Zahnzwischenräume direkt nach dem Scheitelpunkt zu benutzen, wodurch durch die Ausdehnung der Zwischenräume ein Unterdruck entsteht.The pump unit is a gear transmission. Advantageously, the space in the pump unit is a space between the teeth of two gears, i. around so-called interdental spaces. Preferably, the interdental spaces are to be used directly after the vertex, which creates a negative pressure by the expansion of the interstices.

Ferner kann zur Entlastung der druckfreien Fläche auch eine Leitung zur Verbindung der Vertiefung mit einer Speicherkammer vorgesehen werden, welche ebenfalls eine einfache und kostengünstige Umsetzung einer Entlastung ermöglicht.Furthermore, to relieve the pressure-free surface and a line for connecting the recess can be provided with a storage chamber, which also allows a simple and cost-effective implementation of a discharge.

Vorteilhafte Ausführungsformen der Erfindung sind in den Zeichnungen dargestellt und werden nachfolgend beschrieben. In den Zeichnungen bezeichnen gleiche Bezugszeichen Komponenten bzw. Elemente, die gleiche bzw. analoge Funktionen ausführen.Advantageous embodiments of the invention are illustrated in the drawings and will be described below. In the drawings, like reference numerals designate components that perform the same or analog functions.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Fig. 1Fig. 1
zeigt einen schematischen Längsschnitt durch eine erfindungsgemäße Flüssigkeitspumpe.shows a schematic longitudinal section through a liquid pump according to the invention.
Fig. 2Fig. 2
zeigt einen schematischen Querschnitt durch die erfindungsgemäße Flüssigkeitspumpe.shows a schematic cross section through the liquid pump according to the invention.
Ausführungsformen der ErfindungEmbodiments of the invention

Fig. 1 zeigt eine erfindungsgemäße Flüssigkeitspumpe 10 in Form einer Zahnradpumpe mit einem Pumpengehäuse 12, das einen Innenraum 46 mit einem Zulauf 48 einer Saugseite und einem Ablauf 50 einer Druckseite aufweist. In das Pumpengehäuse 12 führt über einen abzudichtenden Wellendurchgang eine drehbar angeordnete Antriebswelle 16, welche eine im Innenraum 46 des Pumpengehäuses 12 angeordnete Pumpeneinheit 14 antreibt. Fig. 1 shows a liquid pump 10 according to the invention in the form of a gear pump with a pump housing 12 having an interior 46 with an inlet 48 a suction side and a discharge 50 a pressure side. A rotatably arranged drive shaft 16, which drives a pump unit 14 arranged in the interior 46 of the pump housing 12, leads into the pump housing 12 via a shaft passage to be sealed.

Die Pumpeneinheit 14 dient zur Förderung der Flüssigkeit unter Erzeugung eines entsprechend hohen Druckniveaus der Flüssigkeit, d.h. unter Erzeugung eines Betriebsdruckes pB. Die Flüssigkeit wird hierbei in üblicher Weise von der Saugseite zur Druckseite der Flüssigkeitspumpe 10 gepumpt. Hierzu weist die Pumpeneinheit 14 vorzugsweise ein Zahnradgetriebe auf, welches in der Regel mindestens zwei Zahnräder 38, 40 gemäß Fig. 2 umfasst, wovon eines über die Antriebswelle 16 angetrieben wird. Je nach Anordnung und Größe der Zahnräder kann es sich hierbei vorzugsweise um eine Außenzahnrad-, eine Innenzahnrad-, eine Zahnring- oder eine Schraubpumpe handeln. Die Flüssigkeitspumpe 10 fördert in der Regel gleichmäßig die zu pumpende Flüssigkeit. Es liegt eine symmetrische Anordnung der Druckfelder 30, 32 des Betriebsdruckes pB vor.The pump unit 14 serves to convey the liquid to produce a correspondingly high pressure level of the liquid, ie to produce an operating pressure p B. The liquid is in this case pumped in the usual way from the suction side to the pressure side of the liquid pump 10. For this purpose, the pump unit 14 preferably has a gear transmission, which as a rule at least two gears 38, 40 in accordance with Fig. 2 includes, one of which is driven via the drive shaft 16. Depending on the arrangement and size of the gears, this can preferably be an external gear, an internal gear, a toothed ring pump or a screw pump. The liquid pump 10 usually evenly pumps the liquid to be pumped. There is a symmetrical arrangement of the pressure fields 30, 32 of the operating pressure p B before.

Die Antriebswelle 16 ist über Lagereinheiten 52, 54 drehbar im Pumpengehäuse 12 gelagert. Zwischen dem Wellendurchgang und der Antriebswelle 16 ist eine als Wellendichtring ausgebildete Dichteinheit 18 angeordnet, um das Pumpengehäuse 12 an der Antriebswelle 16 nach außen bzw. gegen die Umgebung abzudichten. Der Wellendichtring 18 ist mit festem Sitz in einer Ausnehmung des Pumpengehäuses 12 angeordnet. Vorzugsweise ist der Wellendichtring 18 als Radialwellendichtring ausgebildet, der radial auf die Oberfläche der Antriebswelle 16 drückt. Der Wellendichtring 18 muss einem an die Flüssigkeitspumpe 10 anlegbaren Vordruck pv und dem im Pumpengehäuse 12 auftretenden Betriebsdruck pB entsprechend ausgelegt sein, d.h. der Wellendichtring 18 muss je nach Druckniveau zur Erfüllung seiner Funktion ausreichend große Radialkräfte aufbringen. Bei Belastung der Flüssigkeitspumpe 10 mit dem Vordruck pv erzeugt die unter Druck stehende Flüssigkeit im Bereich der Dichteinheit 18 mindestens ein der Dichteinheit 18 zugewandtes Druckfeld 20 und mindestens ein der Dichteinheit 18 abgewandtes Druckfeld 22 an der Dichteinheit 18.The drive shaft 16 is rotatably mounted in the pump housing 12 via bearing units 52, 54. Between the shaft passage and the drive shaft 16 designed as a shaft seal sealing unit 18 is arranged to seal the pump housing 12 to the drive shaft 16 to the outside or against the environment. The shaft seal 18 is arranged with a fixed seat in a recess of the pump housing 12. Preferably, the shaft seal 18 is formed as a radial shaft seal, which presses radially on the surface of the drive shaft 16. The oil seal 18 has a can be applied to the fluid pump 10 inlet pressure p v and the operating pressure occurring in the pump housing 12 p B be designed accordingly, that the shaft seal ring 18 must be sufficient to raise high radial forces, depending on the pressure level to perform its function. When the liquid pump 10 is pressurized with the admission pressure p v , the pressurized fluid in the area of the sealing unit 18 generates at least one pressure field 20 facing the sealing unit 18 and at least one pressure field 22 facing away from the sealing unit 18 at the sealing unit 18.

Um die durch den Vordruck pv verursachte axiale Kraft F direkt in der Flüssigkeitspumpe 10 zu kompensieren, ist erfindungsgemäß eine asymmetrische Anordnung der Druckfelder 20, 22 vorgesehen. Im vorliegenden Ausführungsbeispiel ist das der Dichteinheit 18 zugewandte Druckfeld 20 größer als das der Dichteinheit 18 abgewandte Druckfeld 22. Vorzugsweise ist das der Dichteinheit 18 zugewandte Druckfeld 20 um eine Fläche des Querschnitts 24 der Antriebswelle 16 größer als das der Dichteinheit 18 abgewandte Druckfeld 22 .In order to compensate for the axial force F caused by the form p v directly in the liquid pump 10, an asymmetrical arrangement of the pressure fields 20, 22 is provided according to the invention. In the present exemplary embodiment, the pressure field 20 facing the sealing unit 18 is greater than the pressure field 22 facing away from the sealing unit 18. The pressure field 20 facing the sealing unit 18 is preferably larger around the area of the cross section 24 of the drive shaft 16 than the pressure field 22 facing away from the sealing unit 18.

Eine Vergrößerung des der Dichteinheit 18 zugewandten Druckfeldes 20 wird gemäß Fig. 2 über eine Vertiefung 26 in einer Dichtfläche 28 der Flüssigkeitspumpe 10 erreicht. Zur Entlastung dieser eine druckfreie Fläche bildenden Vertiefung 26 ist ein Kanal 34 zur Verbindung der Vertiefung 26 mit einem Raum 36 in der Pumpeneinheit 14 vorgesehen. Vorzugsweise handelt es sich bei dem Raum 36 in der Pumpeneinheit 14 um einen Raum zwischen den Zähnen der beiden Zahnräder 38, 40. Ferner ist zusätzlich zur Entlastung der als Vertiefung ausgebildeten druckfreien Fläche 26 eine Leitung 42 zur Verbindung der Vertiefung mit einer Speicherkammer 44 vorgesehen. Selbstverständlich können die Maßnahmen zur Entlastung auch einzeln vorgesehen sein.An enlargement of the sealing unit 18 facing pressure field 20 is according to Fig. 2 achieved via a recess 26 in a sealing surface 28 of the liquid pump 10. To relieve this pressure-free surface forming recess 26, a channel 34 for connection of the recess 26 is provided with a space 36 in the pump unit 14. Preferably, the space 36 in the pump unit 14 is a space between the teeth of the two gears 38, 40. Further, in addition to relieving the depressurized surface 26 formed as a recess, a conduit 42 for connecting the recess to a storage chamber 44 is provided. Of course, the relief measures can also be provided individually.

Claims (9)

  1. Liquid pump (10) having a pump housing (12), a pump unit (14) for generating an operating pressure (pB), a drive shaft (16) which is guided through on a drive/output side out of the pump housing (12) for driving the pump unit (14), and a sealing unit (18) which seals the leadthrough, wherein, if the liquid pump (10) is loaded with a system pressure (pv), the pressurized liquid generates, in the region of the sealing unit (18), at least one pressure field (20) which faces the sealing unit (18) and at least one pressure field (22) at the sealing unit (18), which pressure field (22) faces away from the sealing unit (18), characterized by an asymmetrical arrangement of the pressure fields (20, 22).
  2. Liquid pump according to Claim 1, characterized in that the pressure field (20) which faces the sealing unit (18) is larger than the pressure field (22) which faces away from the sealing unit (18).
  3. Liquid pump according to Claim 1 or 2, characterized in that the pressure field (20) which faces the sealing unit (18) is larger by an area of the cross section (24) of the drive shaft (16) than the pressure field (22) which faces away from the sealing unit (18).
  4. Liquid pump according to one of Claims 1 to 3, characterized by a depression (26) in a sealing face (28).
  5. Liquid pump according to one of the preceding claims, characterized by a symmetrical arrangement of the pressure fields (30, 32) of the operating pressure (pB).
  6. Liquid pump according to one of the preceding claims, characterized by a channel (34) for connecting the depression (26) to a space (36) in the pump unit (14).
  7. Liquid pump according to one of the preceding claims, characterized in that the pump unit (14) is a gear mechanism.
  8. Liquid pump according to Claim 1, characterized in that the space (36) in the pump unit (14) is a space between the teeth of two gearwheels (38, 40).
  9. Liquid pump according to Claim 1, characterized by a line (42) for connecting the depression (26) to an accumulator chamber (44).
EP08863084.3A 2007-12-17 2008-10-23 Liquid pump Not-in-force EP2235375B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007060758A DE102007060758A1 (en) 2007-12-17 2007-12-17 liquid pump
PCT/EP2008/064384 WO2009077248A1 (en) 2007-12-17 2008-10-23 Liquid pump

Publications (2)

Publication Number Publication Date
EP2235375A1 EP2235375A1 (en) 2010-10-06
EP2235375B1 true EP2235375B1 (en) 2013-12-11

Family

ID=40525085

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08863084.3A Not-in-force EP2235375B1 (en) 2007-12-17 2008-10-23 Liquid pump

Country Status (6)

Country Link
US (1) US20100316520A1 (en)
EP (1) EP2235375B1 (en)
JP (1) JP5583025B2 (en)
CN (1) CN101896723B (en)
DE (1) DE102007060758A1 (en)
WO (1) WO2009077248A1 (en)

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2695566A (en) * 1950-05-19 1954-11-30 Borg Warner Pump, bushing graduated pressure responsive areas
US2932254A (en) * 1955-05-02 1960-04-12 Plessey Co Ltd Gear pump
FR1241958A (en) * 1958-11-15 1960-09-23 Bosch Gmbh Robert Hydraulic machine
US3050010A (en) * 1960-02-23 1962-08-21 Thompson Ramo Wooldridge Inc Pressure loaded pump
DE1553133A1 (en) * 1966-12-23 1970-07-30 Maag Zahnraeder & Maschinen Ag High pressure gear pump
JPS4965805U (en) * 1972-09-22 1974-06-08
DE2403319A1 (en) * 1974-01-24 1975-07-31 Bosch Gmbh Robert GEAR MACHINE
DE2610827A1 (en) * 1976-03-15 1977-09-29 Bosch Gmbh Robert GEAR MACHINE (PUMP OR MOTOR)
JPS6097391U (en) * 1983-12-08 1985-07-03 三菱重工業株式会社 rotating fluid machine
US4737087A (en) * 1984-12-10 1988-04-12 Barmag Ag Drive shaft seal for gear pump and method
CN1006321B (en) * 1987-03-05 1990-01-03 江苏工学院 Balance unit for pump axial force
US5022837A (en) * 1989-11-13 1991-06-11 Sta-Rite Industries, Inc. Seal arrangement for a gear machine
US5180297A (en) * 1991-03-22 1993-01-19 The Gorman-Rupp Company Fluid transfer pump with shaft seal structure
US6213173B1 (en) * 1998-04-15 2001-04-10 K. J. Manufacturing Co. Engine air purge apparatus and method
KR100298356B1 (en) * 1998-11-13 2001-11-22 윤종용 ATM 2 processing apparatus and method of ATM network
US6149415A (en) * 1999-02-11 2000-11-21 Viking Pump, Inc. Internal gear pump having a feed groove aligned with the roots of the idler teeth
DE19924057A1 (en) 1999-05-26 2000-11-30 Bosch Gmbh Robert Gearwheel machine for hydrostatic drives has two axially displaceable component parts pressing axially onto side faces of gearwheels with different sized forces
JP2002147368A (en) * 2000-11-09 2002-05-22 Fuji Heavy Ind Ltd Internal rotor type fluid device
AU2003294889A1 (en) * 2002-12-19 2004-07-14 Haldex Hydraulics Gmbh Gear-type machine comprising lateral axial plates
US6902382B2 (en) * 2003-09-11 2005-06-07 Matthew Peter Christensen Gear motor start up control

Also Published As

Publication number Publication date
JP2011506837A (en) 2011-03-03
EP2235375A1 (en) 2010-10-06
JP5583025B2 (en) 2014-09-03
WO2009077248A1 (en) 2009-06-25
CN101896723A (en) 2010-11-24
DE102007060758A1 (en) 2009-06-18
US20100316520A1 (en) 2010-12-16
CN101896723B (en) 2013-05-01

Similar Documents

Publication Publication Date Title
DE2016097A1 (en) Gear pump or motor
EP2160309B1 (en) Gear pump arrangement
DE102007051349A1 (en) Hydraulic gear machine e.g. external gear pump, for e.g. generating hydraulic energy, has actuator device to adjust axis position during machine operation and working against shaft deflection forces, where shafts center distance is changed
EP2235375B1 (en) Liquid pump
DE102011075415A1 (en) Gear pump e.g. outer gear wheel pump, for use in fuel injection system of Otto engine to convey fuel from low pressure region into high pressure region, has axially displaceable sealing plates resiliently prestressed in direction of chamber
DE3921245A1 (en) FUEL PUMP PUMP DESIGNED AS A ROTOR PUMP
DE19924057A1 (en) Gearwheel machine for hydrostatic drives has two axially displaceable component parts pressing axially onto side faces of gearwheels with different sized forces
DE1625115B1 (en) Planetary gear with hydrostatic clutch
EP2222938B1 (en) Bearing unit of a fluid pump
DE102007051352A1 (en) Hydraulic gear wheel machine i.e. external gear wheel machine such as external gear wheel motor, for generating and converting of hydraulic energy, has actuators adjusting opening independent of operating pressure during machine operation
DE2803772C2 (en) Tandem pump
DE102008054753A1 (en) Internal gear pump
DE102007051350A1 (en) Hydraulic gear wheel machine e.g. external gear pump, for producing or transforming hydraulic energy in mobile hydraulics, has changing device with actuator for changing chamber volume or for increasing connection to pressure relief line
EP1074740B1 (en) Hydrostatic rotary piston machine
DE102018212497A1 (en) Fluid delivery device
DE3303856A1 (en) PUMP
DE102014102131A1 (en) Oscillating drivable machine tool
DE102020209407A1 (en) internal gear fluid machine
DE19528631A1 (en) Geared vacuum machine as pump or motor - closes gear housing opening by grooved bearings used to close gear clearance axially under hydrostatic pressure
DE102012208691A1 (en) Hydraulic machine for a motor vehicle
DE19746769C1 (en) Inner geared fluid pump or motor
DE19942297A1 (en) Gear machine
DE102004023149A1 (en) turbomachinery
DE102018002994A1 (en) Fluid pump
DE102004033490A1 (en) Internal geared wheel machine esp. pump has internal geared wheel and eccentric external geared pinion, defining space with two-part filler element supported on contact part, to prevent fluttering

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20100719

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA MK RS

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20130820

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 644757

Country of ref document: AT

Kind code of ref document: T

Effective date: 20140115

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502008011071

Country of ref document: DE

Effective date: 20140130

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20131211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140311

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140411

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140411

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502008011071

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

26N No opposition filed

Effective date: 20140912

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502008011071

Country of ref document: DE

Effective date: 20140912

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141023

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20141023

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141031

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141031

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141023

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141031

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20150630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141023

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 644757

Country of ref document: AT

Kind code of ref document: T

Effective date: 20141023

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141023

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140312

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131211

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20081023

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20211214

Year of fee payment: 14

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502008011071

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230503