EP2459880A2 - Gear pump - Google Patents

Gear pump

Info

Publication number
EP2459880A2
EP2459880A2 EP10722710A EP10722710A EP2459880A2 EP 2459880 A2 EP2459880 A2 EP 2459880A2 EP 10722710 A EP10722710 A EP 10722710A EP 10722710 A EP10722710 A EP 10722710A EP 2459880 A2 EP2459880 A2 EP 2459880A2
Authority
EP
European Patent Office
Prior art keywords
ring
gear pump
toothed ring
bearing
gear
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.)
Granted
Application number
EP10722710A
Other languages
German (de)
French (fr)
Other versions
EP2459880B1 (en
Inventor
Stanislaw Bodzak
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 EP2459880A2 publication Critical patent/EP2459880A2/en
Application granted granted Critical
Publication of EP2459880B1 publication Critical patent/EP2459880B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/008—Prime movers
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/008—Enclosed motor pump units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • 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
    • F04C2/102—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 the two members rotating simultaneously around their respective axes
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/20—Manufacture essentially without removing material
    • F04C2230/22—Manufacture essentially without removing material by sintering

Definitions

  • the present invention relates to a gear pump according to the preamble of claim 1.
  • Gear pumps include, inter alia, internal gear and gerotor pumps in which a driving gear is eccentric in the internal toothing of a toothed ring.
  • Internal gear pumps which are particularly suitable for providing high pressures, are used to deliver fluids, such as for example, to deliver fuel to an internal combustion engine.
  • the feed pump comprises a first gear and a second gear. Between the two gears, a delivery chamber is formed.
  • the second gear is stored in its center on a thorn.
  • the first gear is an external gear and forms the rotor
  • the second gear is an internal gear, which is entrained in the eccentric center of the first gear.
  • the first gear comprises glued permanent magnets, which are distributed over the circumference.
  • External magnetic field generators generate a rotating, rotating field which causes the direct motoring of the rotor.
  • the problem with such configurations is the bearing of the toothed ring, which must take over the driving torque of the electric motor.
  • EP 1 600 635 A2 describes an internal gear pump which has a pump section with an inner rotor formed on its outer periphery with teeth.
  • An outer rotor has on its inner
  • a gear pump for conveying a fluid with a rotatably mounted on a journal externally toothed gear and an internally toothed ring are provided, which are for generating a conveying effect in meshing engagement, and which are arranged together with an electrically commutatable stator in a housing, wherein the Stator concentrically extends around the toothed ring and cooperates with a magnetic ring for generating an electromotive force, wherein the magnetic ring with the toothed ring for generating the conveying effect a Rotationsbewe- performs, wherein the toothed ring is supported by a sliding bearing.
  • the magnetic ring between the stator and the toothed ring is arranged.
  • the magnetic ring has no Gleitlageraufgabe.
  • the tasks of sliding bearing are advantageously taken over by other components of the réelle leopard- wheel pump and the toothed ring itself.
  • the magnetic ring and the toothed ring are rotatably connected to each other.
  • a driving torque is transmitted from the rotating electromagnetic field to the magnet ring and further to the ring gear of the internal gear pump or gerotor pump.
  • the magnetic ring itself does not take over storage function. This is advantageously taken over by other components, preferably by the toothed ring itself.
  • the toothed ring is made of a non-magnetic material. This achieves a magnetic decoupling between the individual components.
  • the bearing of the toothed ring is provided by a ring-shaped portion, which is formed at least on a surface opposite the toothed ring as a sliding bearing.
  • a second radial gap with a value of 0.1 to 0.5 mm is formed between the stator and the magnetic ring.
  • the ring-shaped section is formed integrally with the housing and protrudes radially inwardly from the latter.
  • the annular-shaped portion is pressed or glued into the housing. - A -
  • the mounting of the toothed ring is provided by a disk-shaped element which has a bearing journal which protrudes from the disk-shaped element and which is received in a corresponding recess provided in the housing.
  • the surface of the journal is designed as a plain bearing.
  • an inner wall of the recess may be formed as a sliding bearing.
  • the fuel connections are to be manufactured in the housing.
  • FIG. 1 shows a section through an internal gear pump according to the prior art
  • Fig. 5 is a plan view of the internal gear pump of Fig. 4;
  • Fig. 1 shows a section through an internal gear pump 1 according to the prior art.
  • the internal gear pump 1 comprises a gear pair, which consists of an internally toothed ring gear 2 and an externally toothed gear wheel 3.
  • the gear 3 is arranged eccentrically to the toothed ring 2 rotatably on a bearing journal 4. If the toothed ring 2 is set in a rotary motion, then meshes with the external teeth of the gear 3 in the internal toothing of the toothed ring 2 and generates a delivery volume flow of the fluid in which the toothing runs.
  • the gear pair of the toothed ring 2 and the gear 3 is arranged in a housing 5, wherein the bearing pin 4 is integrally formed or integrally with the housing 5.
  • the toothed ring 2 is also rotatably connected to a magnetic ring 6, wherein the magnetic ring 6 extends radially around the toothed ring 2.
  • the magnetic ring 6 runs in an inner side of a stator 7, which has an electric winding 8. If the electric winding 8 is commutated electrically by a controller, a circulating magnetic field is generated in the stator 7. Due to the rotating magnetic field of the magnet ring 6 is set in rotation, wherein due to the rotationally fixed connection of the magnet ring 6 with the toothed ring 2, the teeth consisting of the toothed ring 2 and the gear 3 is put into operation.
  • the magnetic ring 6 is slidably mounted on the stator 7.
  • the magnetic ring 6 is provided with a corresponding coating of a suitable sliding material. This design is for the
  • connection cover 9 The open side of the housing 5 of the internal gear pump 1 is closed by means of a connection cover 9, wherein a sealing element 10 is provided for the fluid-tight sealing of the gaps between the connection cover 9 and the housing 5.
  • the sealing element 10 is designed as an O-ring and is arranged in a corresponding circumferential groove (not shown) within the connection cover 9.
  • Fig. 2 shows a section through an internal gear pump 1 according to one embodiment.
  • the internal gear pump 1 according to the embodiment shown here differs essentially from the internal gear pump 1 shown in FIG. 1 in that the magnet ring 6 does not assume the bearing function but the outer ring or the toothed ring 2 is supported by a plain bearing.
  • the magnetic ring 6 and the toothed ring 2 are either positively connected, or the connection is in the embodiment by z. B. bonding the two components together.
  • a drive torque is transmitted from a rotating electromagnetic field to the magnet ring 6 and further to the toothed ring 2 of the internal gear pump 1.
  • the gear 3 is made of non-magnetic Material produced.
  • annular formed portion 1 1 is provided, which is here formed integrally or integrally with the housing 5 and projects radially from an inner wall 14 of the housing 5.
  • the ring-shaped portion 1 1 is formed on a toothed ring 2 opposite the first surface 15 as a sliding bearing 25.
  • a first radial gap 12 is present between a second surface 16 of the annular portion 1 1, which is opposite to the magnetic ring 6, and the magnetic ring 6, a first radial gap 12 is present.
  • Another second radial gap 13 is designed between the magnet ring 6 and the stator 7 to small values with the aim of achieving a good torque transmission and low hydraulic friction.
  • the width of the second radial gap 12, 13 is in a range of 0.1 to 0.5 mm.
  • FIG. 3 shows a section through an internal gear pump 1 according to a further embodiment, which differs from the internal gear pump 1 shown in FIG. 2 in that in this embodiment the annular section 11 is not made integral with the housing 5 but instead is manufactured as a separate component.
  • the ring-shaped portion 1 1 with bearing function is in the housing 5 and in a recess 17, which is provided in the inner wall 14 of the housing 5, pressed or glued.
  • FIG. 4 shows a section through an internal gear pump 1 according to yet another embodiment, wherein the bearing function for the toothed ring 2 assumes a disk-shaped element 18, which has a bearing journal 19 projecting radially from the disk-shaped element 18.
  • the bearing pin 19 of the disk-shaped element 18 is arranged or mounted in a recess 20 formed in the bearing journal 4 of the housing 5, the disk-shaped element 18 abutting against the toothed ring 2 from the outside.
  • the sliding bearing 25 is provided in this case between the bearing pin 19 of the disc-shaped element 18 and the bearing pin 4 of the housing 5.
  • either the surface of the bearing journal 19 or the inner wall 21 of the formed in the bearing journal 4 of the housing 5 recess 20 may be formed as a sliding bearing.
  • Fig. 5 shows a plan view of the internal gear pump 1 of Fig. 4.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

This invention relates to a gear pump (1) for delivering a fluid, comprising an externally toothed gearwheel (3) rotatably mounted on a journal (4), and an internally toothed annular gear (2), said gearwheel and gear meshing so as to produce a delivery action, and arranged together with an electrically commutatable stator (7) inside a housing (5). The stator (7) extends concentrically around the annular gear (2) and cooperates with a magnetic ring (6) in order to generate an electromotive force and the magnetic ring (6) together with the annular gear (2) rotate in order to produce the delivery action. The annular gear (2) is mounted by means of a sliding bearing (25).

Description

Beschreibung  description
Titel title
Zahnradpumpe Die vorliegende Erfindung betrifft eine Zahnradpumpe gemäß dem Oberbegriff des Anspruchs 1. Gear Pump The present invention relates to a gear pump according to the preamble of claim 1.
Stand der Technik State of the art
Zahnradpumpen umfassen unter anderem Innenzahnrad- und Zahnringpumpen, bei denen ein treibendes Zahnrad exzentrisch in der Innenverzahnung eines Zahnringes läuft. Innenzahnradpumpen, die besonders zur Bereitstellung hoher Drücke geeignet sind, werden zur Förderung von Fluiden eingesetzt, wie bei- spielsweise zur Förderung von Kraftstoff zu einer Verbrennungskraftmaschine. Gear pumps include, inter alia, internal gear and gerotor pumps in which a driving gear is eccentric in the internal toothing of a toothed ring. Internal gear pumps, which are particularly suitable for providing high pressures, are used to deliver fluids, such as for example, to deliver fuel to an internal combustion engine.
Im Stand der Technik ist es bekannt, Innenzahnrad- oder Zahnringpumpen in einen elektronisch kommutierten Elektromotor zu integrieren, wobei der Rotor des Elektromotors gleichzeitig als Zahnring der Innenzahnrad- oder Zahnringpumpe ausgebildet ist. In the prior art, it is known to integrate Innenzahnrad- or gerotor pumps in an electronically commutated electric motor, wherein the rotor of the electric motor is simultaneously formed as a toothed ring of Innenzahnrad- or gerotor pump.
In DE 10 2006 007 554 A1 ist eine Förderpumpe beschrieben, welche in einen Elektromotor integriert ist. Die Förderpumpe umfasst ein erstes Zahnrad und ein zweites Zahnrad. Zwischen den beiden Zahnrädern bildet sich ein Förderraum aus. Das zweite Zahnrad lagert in seiner Mitte auf einem Dorn. Das erste Zahnrad ist ein Außenzahnrad und bildet den Rotor, das zweite Zahnrad ist ein Innenzahnrad, welches im außermittigen Zentrum des ersten Zahnrads mitgeschleppt wird. Das erste Zahnrad umfasst eingeklebte Permanentmagnete, die über den Umfang verteilt angeordnet sind. Äußere Magnetfelderzeuger erzeugen ein um- laufendes, sich rotatorisch änderndes Feld, welches das direkte motorische Folgen des Rotors hervorruft. Problematisch bei derartigen Konfigurationen ist jedoch die Lagerung des Zahnrings, welcher das Antriebsdrehmoment des Elektromotors übernehmen muss. Gleichzeitig müssen die hydraulischen Kräfte der Innenzahnradpumpe auf denDE 10 2006 007 554 A1 describes a delivery pump which is integrated in an electric motor. The feed pump comprises a first gear and a second gear. Between the two gears, a delivery chamber is formed. The second gear is stored in its center on a thorn. The first gear is an external gear and forms the rotor, the second gear is an internal gear, which is entrained in the eccentric center of the first gear. The first gear comprises glued permanent magnets, which are distributed over the circumference. External magnetic field generators generate a rotating, rotating field which causes the direct motoring of the rotor. The problem with such configurations, however, is the bearing of the toothed ring, which must take over the driving torque of the electric motor. At the same time, the hydraulic forces of the internal gear pump on the
Stator und weiter an das Pumpengehäuse übertragen werden. Stator and continue to be transferred to the pump housing.
In EP 1 600 635 A2 ist eine Innenzahnradpumpe beschrieben, welche einen Pumpenabschnitt mit einem inneren Rotor aufweist, welcher an seiner äußeren Peripherie mit Zähnen ausgebildet ist. Ein äußerer Rotor weist an seiner innerenEP 1 600 635 A2 describes an internal gear pump which has a pump section with an inner rotor formed on its outer periphery with teeth. An outer rotor has on its inner
Peripherie ausgebildete Zähne auf. Beide Rotoren sind in einem Gehäuse aufgenommen. Die Lagerung des als Zahnring ausgebildeten äußeren Rotors erfolgt hierbei mittels speziell geformter Zusatzbauteile. Die im Stand der Technik bekannten Lösungen zur Lagerung des Zahnrings in einer Innenzahnradpumpe bzw. in einer Zahnringpumpe sind von mechanisch kompliziertem Aufbau und daher konstruktiv aufwändig, komplex und teuer in der Herstellung. Daher ist es erforderlich, eine einfache und kostengünstige Lösung zur Lagerung eines Zahnrings für eine Innenzahnradpumpe oder eine Zahnringpumpe bereitzustellen. Periphery trained teeth on. Both rotors are housed in a housing. The storage of the outer rotor formed as a toothed ring takes place here by means of specially shaped additional components. The known in the prior art solutions for mounting the ring gear in an internal gear pump or in a gerotor pump are mechanically complicated construction and therefore structurally complex, complex and expensive to manufacture. Therefore, it is necessary to provide a simple and inexpensive solution for supporting a ring gear for an internal gear pump or a gerotor pump.
Offenbarung der Erfindung Disclosure of the invention
Vorteile der Erfindung Advantages of the invention
Erfindungsgemäß wird eine Zahnradpumpe zum Fördern eines Fluids mit einem drehbar auf einem Lagerzapfen gelagerten außenverzahnten Zahnrad und einem innenverzahnten Zahnring vorgesehen, welche zur Erzeugung einer Förderwirkung in kämmendem Eingriff stehen, und welche gemeinsam mit einem elektrisch kommutierbaren Stator in einem Gehäuse angeordnet sind, wobei sich der Stator konzentrisch um den Zahnring herum erstreckt und mit einem Magnetring zur Erzeugung einer elektromotorischen Kraft zusammenwirkt, wobei der Magnetring mit dem Zahnring zur Erzeugung der Förderwirkung eine Rotationsbewe- gung ausführt, wobei der Zahnring durch ein Gleitlager gelagert ist. Durch Lagern des Zahnring durch ein Gleitlager wird eine konstruktiv einfache und daher kostengünstige Lösung zur Lagerung vorgesehen. Vorzugsweise ist der Magnetring zwischen dem Stator und dem Zahnring angeordnet. Der Magnetring hat dabei keine Gleitlageraufgabe. Die Aufgaben der Gleitlagerung werden vorteilhafterweise durch andere Bauteile der Innenzahn- radpumpe und den Zahnring selbst übernommen. In noch einer weiteren bevorzugten Ausführungsform sind der Magnetring und der Zahnring drehfest miteinander verbunden. So wird ein Antriebsdrehmoment von dem rotierenden Elektromagnetfeld an den Magnetring und weiter an den Zahnring der Innenzahnradpumpe oder Zahnringpumpe übertragen. Der Magnetring selbst übernimmt keine Lagerfunktion. Diese wird auf vorteilhafte Weise von anderen Bauteilen, vorzugsweise vom Zahnring selbst, übernommen. According to the invention, a gear pump for conveying a fluid with a rotatably mounted on a journal externally toothed gear and an internally toothed ring are provided, which are for generating a conveying effect in meshing engagement, and which are arranged together with an electrically commutatable stator in a housing, wherein the Stator concentrically extends around the toothed ring and cooperates with a magnetic ring for generating an electromotive force, wherein the magnetic ring with the toothed ring for generating the conveying effect a Rotationsbewe- performs, wherein the toothed ring is supported by a sliding bearing. By storing the ring gear through a plain bearing a structurally simple and therefore cost-effective solution for storage is provided. Preferably, the magnetic ring between the stator and the toothed ring is arranged. The magnetic ring has no Gleitlageraufgabe. The tasks of sliding bearing are advantageously taken over by other components of the Innenzahn- wheel pump and the toothed ring itself. In yet another preferred embodiment, the magnetic ring and the toothed ring are rotatably connected to each other. Thus, a driving torque is transmitted from the rotating electromagnetic field to the magnet ring and further to the ring gear of the internal gear pump or gerotor pump. The magnetic ring itself does not take over storage function. This is advantageously taken over by other components, preferably by the toothed ring itself.
Es ist darüber hinaus bevorzugt, wenn der Zahnring aus einem nicht magnetischen Material hergestellt ist. So wird eine magnetische Abkoppelung zwischen den einzelnen Bauteilen erreicht. It is also preferred if the toothed ring is made of a non-magnetic material. This achieves a magnetic decoupling between the individual components.
Gemäß einer weiteren bevorzugten Ausführungsform wird die Lagerung des Zahnrings durch einen ringförmig ausgebildeten Abschnitt vorgesehen, welcher zumindest an einer dem Zahnring gegenüberliegenden Oberfläche als Gleitlager ausgebildet ist. According to a further preferred embodiment, the bearing of the toothed ring is provided by a ring-shaped portion, which is formed at least on a surface opposite the toothed ring as a sliding bearing.
Vorzugsweise ist zwischen dem Stator und dem Magnetring ein zweiter Radialspalt mit einem Wert von 0,1 bis 0,5 mm ausgebildet. Preferably, a second radial gap with a value of 0.1 to 0.5 mm is formed between the stator and the magnetic ring.
Gemäß einer weiteren bevorzugten Ausführungsform ist der ringförmig ausgebil- dete Abschnitt integral mit dem Gehäuse gebildet und ragt von diesem radial nach innen ab. According to a further preferred embodiment, the ring-shaped section is formed integrally with the housing and protrudes radially inwardly from the latter.
Gemäß noch einer weiteren bevorzugten Ausführungsform ist der ringförmig ausgebildete Abschnitt in das Gehäuse eingepresst oder verklebt. - A - According to yet another preferred embodiment, the annular-shaped portion is pressed or glued into the housing. - A -
Es ist auch bevorzugt, wenn die Lagerung des Zahnrings durch ein scheibenförmiges Element vorgesehen wird, welches einen von dem scheibenförmigen Element abragenden Lagerzapfen aufweist, welcher in einer entsprechend in dem Gehäuse vorgesehenen Aussparung aufgenommen ist. Vorzugsweise ist die Oberfläche des Lagerzapfens als Gleitlager ausgebildet. Alternativ kann eine Innenwand der Ausnehmung als Gleitlager ausgebildet sein. Bei dieser Ausführungsform sind die Kraftstoffanschlüsse im Gehäuse zu fertigen. It is also preferred if the mounting of the toothed ring is provided by a disk-shaped element which has a bearing journal which protrudes from the disk-shaped element and which is received in a corresponding recess provided in the housing. Preferably, the surface of the journal is designed as a plain bearing. Alternatively, an inner wall of the recess may be formed as a sliding bearing. In this embodiment, the fuel connections are to be manufactured in the housing.
Kurze Beschreibung der Zeichnungen Brief description of the drawings
Im Nachfolgenden werden Ausführungsbeispiele der Erfindung unter Bezugnahme auf die beigefügten Zeichnungen näher beschrieben. Es zeigt: Fig. 1 einen Schnitt durch eine Innenzahnradpumpe gemäß dem Stand derHereinafter, embodiments of the invention will be described in more detail with reference to the accompanying drawings. 1 shows a section through an internal gear pump according to the prior art
Technik, Technology,
Fig. 2 einen Schnitt durch eine Innenzahnradpumpe gemäß einer Ausführungsform, 2 shows a section through an internal gear pump according to an embodiment,
Fig. 3 einen Schnitt durch eine Innenzahnradpumpe gemäß einer weiteren Ausführungsform, 3 shows a section through an internal gear pump according to a further embodiment,
Fig. 4 einen Schnitt durch eine Innenzahnradpumpe gemäß noch einer weite- ren Ausführungsform, 4 shows a section through an internal gear pump according to yet another embodiment,
Fig. 5 eine Draufsicht auf die Innenzahnradpumpe von Fig. 4; Fig. 5 is a plan view of the internal gear pump of Fig. 4;
Ausführungsformen der Erfindung Embodiments of the invention
In Fig. 1 zeigt einen Schnitt durch eine Innenzahnradpumpe 1 gemäß dem Stand der Technik. Die Innenzahnradpumpe 1 umfasst ein Zahnradpaar, welches aus einen innenverzahnten Zahnring 2 und einem außenverzahnten Zahnrad 3 be- steht. Das Zahnrad 3 ist exzentrisch zum Zahnring 2 drehbar auf einem Lagerzapfen 4 angeordnet. Wird der Zahnring 2 in eine Drehbewegung versetzt, so kämmt die Außenverzahnung des Zahnrads 3 in der Innenverzahnung des Zahnrings 2 und erzeugt einen Fördervolumenstrom des Fluids, in welchem die Verzahnung läuft. Das Zahnradpaar aus dem Zahnring 2 und dem Zahnrad 3 ist in einem Gehäuse 5 angeordnet, wobei der Lagerzapfen 4 einteilig bzw. integral mit dem Gehäuse 5 ausgebildet ist. Der Zahnring 2 ist darüber hinaus drehfest mit einem Magnetring 6 verbunden, wobei sich der Magnetring 6 um den Zahnring 2 radial umlaufend erstreckt. Der Magnetring 6 läuft in einer Innenseite eines Stators 7, welcher eine Elektrowicklung 8 aufweist. Wird die Elektrowicklung 8 durch eine Steuerung elektrisch kommutiert, so wird im Stator 7 ein umlaufendes Mag- netfeld erzeugt. Aufgrund des umlaufenden Magnetfeldes wird der Magnetring 6 in Rotation versetzt, wobei aufgrund der drehfesten Verbindung des Magnetrings 6 mit dem Zahnring 2 auch die Verzahnung bestehend aus dem Zahnring 2 und dem Zahnrad 3 in Betrieb gesetzt wird. Der Magnetring 6 ist an dem Stator 7 gleitend gelagert. Hierbei ist der Magnetring 6 mit einer entsprechenden Beschich- tung aus einem geeigneten Gleitmaterial versehen. Diese Ausführung ist für dieIn Fig. 1 shows a section through an internal gear pump 1 according to the prior art. The internal gear pump 1 comprises a gear pair, which consists of an internally toothed ring gear 2 and an externally toothed gear wheel 3. The gear 3 is arranged eccentrically to the toothed ring 2 rotatably on a bearing journal 4. If the toothed ring 2 is set in a rotary motion, then meshes with the external teeth of the gear 3 in the internal toothing of the toothed ring 2 and generates a delivery volume flow of the fluid in which the toothing runs. The gear pair of the toothed ring 2 and the gear 3 is arranged in a housing 5, wherein the bearing pin 4 is integrally formed or integrally with the housing 5. The toothed ring 2 is also rotatably connected to a magnetic ring 6, wherein the magnetic ring 6 extends radially around the toothed ring 2. The magnetic ring 6 runs in an inner side of a stator 7, which has an electric winding 8. If the electric winding 8 is commutated electrically by a controller, a circulating magnetic field is generated in the stator 7. Due to the rotating magnetic field of the magnet ring 6 is set in rotation, wherein due to the rotationally fixed connection of the magnet ring 6 with the toothed ring 2, the teeth consisting of the toothed ring 2 and the gear 3 is put into operation. The magnetic ring 6 is slidably mounted on the stator 7. Here, the magnetic ring 6 is provided with a corresponding coating of a suitable sliding material. This design is for the
Anwendung hoher Förderdrücke und bei schlecht schmierenden Flüssigkeiten, wie beispielsweise Benzin oder Diesel, nicht geeignet. Application of high discharge pressures and poorly lubricating liquids, such as gasoline or diesel, not suitable.
Die offene Seite des Gehäuses 5 der Innenzahnradpumpe 1 wird mittels eines Anschlussdeckels 9 verschlossen, wobei zur fluiddichten Abdichtung der Spalte zwischen dem Anschlussdeckel 9 und dem Gehäuse 5 ein Dichtelement 10 vorgesehen ist. Das Dichtelement 10 ist als O-Ring ausgeführt und ist in einer entsprechenden umlaufenden Nut (nicht dargestellt) innerhalb des Anschlussdeckels 9 angeordnet. The open side of the housing 5 of the internal gear pump 1 is closed by means of a connection cover 9, wherein a sealing element 10 is provided for the fluid-tight sealing of the gaps between the connection cover 9 and the housing 5. The sealing element 10 is designed as an O-ring and is arranged in a corresponding circumferential groove (not shown) within the connection cover 9.
Fig. 2 zeigt einen Schnitt durch eine Innenzahnradpumpe 1 gemäß einer Ausführungsform. Die hier dargestellte Innenzahnradpumpe 1 gemäß der Ausführungsform unterscheidet sich im Wesentlichen von der in Fig. 1 dargestellten Innenzahnradpumpe 1 dadurch, dass nicht der Magnetring 6 die Lagerfunktion über- nimmt sondern der Außenring bzw. der Zahnring 2 durch ein Gleitlager gelagert wird. Der Magnetring 6 und der Zahnring 2 sind entweder formschlüssig verbunden, oder die Verbindung wird in der Ausführungsform durch z. B. Verkleben der beiden Bauteile miteinander erreicht. Ein Antriebsdrehmoment wird so von einem rotierenden Elektromagnetfeld an den Magnetring 6 und weiter an den Zahnring 2 der Innenzahnradpumpe 1 übertragen. Um eine magnetische Abkopplung zwischen den Bauteilen zu realisieren, ist das Zahnrad 3 aus nicht magnetischem Material hergestellt. Um die Gleitlagerung am Zahnring 2 zu realisieren, ist ein ringförmig ausgebildeter Abschnitt 1 1 vorgesehen, welcher hier einteilig bzw. integral mit dem Gehäuse 5 ausgebildet ist und von einer Innenwand 14 des Gehäuses 5 radial abragt. Der ringförmig ausgebildete Abschnitt 1 1 ist an einer dem Zahnring 2 gegenüberliegenden ersten Oberfläche 15 als Gleitlager 25 ausgebildet. Zwischen einer zweiten Oberfläche 16 des ringförmig ausgebildeten Abschnitts 1 1 , welche dem Magnetring 6 gegenüberliegt, und dem Magnetring 6 ist ein erster Radialspalt 12 vorhanden. Ein weiterer zweiter Radialspalt 13 ist zwischen dem Magnetring 6 und dem Stator 7 auf kleine Werte ausgelegt mit dem Ziel, eine gute Drehmomentübertragung und geringe hydraulische Reibung zu erreichen. Die Breite des zweiten Radialspalts 12, 13 liegt in einem Bereich von 0,1 bis 0,5 mm. Fig. 2 shows a section through an internal gear pump 1 according to one embodiment. The internal gear pump 1 according to the embodiment shown here differs essentially from the internal gear pump 1 shown in FIG. 1 in that the magnet ring 6 does not assume the bearing function but the outer ring or the toothed ring 2 is supported by a plain bearing. The magnetic ring 6 and the toothed ring 2 are either positively connected, or the connection is in the embodiment by z. B. bonding the two components together. A drive torque is transmitted from a rotating electromagnetic field to the magnet ring 6 and further to the toothed ring 2 of the internal gear pump 1. In order to realize a magnetic decoupling between the components, the gear 3 is made of non-magnetic Material produced. In order to realize the sliding bearing on the toothed ring 2, an annular formed portion 1 1 is provided, which is here formed integrally or integrally with the housing 5 and projects radially from an inner wall 14 of the housing 5. The ring-shaped portion 1 1 is formed on a toothed ring 2 opposite the first surface 15 as a sliding bearing 25. Between a second surface 16 of the annular portion 1 1, which is opposite to the magnetic ring 6, and the magnetic ring 6, a first radial gap 12 is present. Another second radial gap 13 is designed between the magnet ring 6 and the stator 7 to small values with the aim of achieving a good torque transmission and low hydraulic friction. The width of the second radial gap 12, 13 is in a range of 0.1 to 0.5 mm.
Fig. 3 zeigt einen Schnitt durch eine Innenzahnradpumpe 1 gemäß einer weite- ren Ausführungsform, welche sich von der in Fig. 2 dargestellten Innenzahnradpumpe 1 dadurch unterscheidet, dass in dieser Ausführungsform der ringförmig ausgebildete Abschnitt 1 1 nicht integral mit dem Gehäuse 5 hergestellt ist sondern als separates Bauteil hergestellt ist. Der ringförmig ausgebildete Abschnitt 1 1 mit Lagerfunktion ist in das Gehäuse 5 bzw. in eine Aussparung 17, welche in der Innenwand 14 des Gehäuses 5 vorgesehen ist, eingepresst oder eingeklebt. 3 shows a section through an internal gear pump 1 according to a further embodiment, which differs from the internal gear pump 1 shown in FIG. 2 in that in this embodiment the annular section 11 is not made integral with the housing 5 but instead is manufactured as a separate component. The ring-shaped portion 1 1 with bearing function is in the housing 5 and in a recess 17, which is provided in the inner wall 14 of the housing 5, pressed or glued.
Fig. 4 zeigt einen Schnitt durch eine Innenzahnradpumpe 1 gemäß noch einer weiteren Ausführungsform, wobei die Lagerfunktion für den Zahnring 2 ein scheibenförmiges Element 18 übernimmt, welches einen radial von dem scheibenför- migen Element 18 abragenden Lagerzapfen 19 aufweist. Der Lagerzapfen 19 des scheibenförmigen Elements 18 ist in einer in dem Lagerzapfen 4 des Gehäuses 5 ausgebildeten Ausnehmung 20 angeordnet bzw. gelagert, wobei das scheibenförmige Element 18 von außen an dem Zahnring 2 anliegt. Das Gleitlager 25 ist in diesem Fall zwischen dem Lagerzapfen 19 des scheibenförmigen Elements 18 und dem Lagerzapfen 4 des Gehäuses 5 vorgesehen. Dabei kann entweder die Oberfläche des Lagerzapfens 19 oder die Innenwand 21 der in dem Lagerzapfen 4 des Gehäuses 5 ausgebildeten Ausnehmung 20 als Gleitlager ausgebildet sein. Bei dieser Ausführungsform sind Kraftstoffanschlüsse 22, 23 in dem Gehäuse 5 vorzusehen. Fig. 5 zeigt eine Draufsicht auf die Innenzahnradpumpe 1 von Fig. 4. Hierbei ist die Position der zwei Kraftstoffanschlüsse 22, 23, welche in dem Gehäuse 5 gefertigt sind, nochmals durch die jeweils doppelt gestrichelten Kreislinien angedeutet. 4 shows a section through an internal gear pump 1 according to yet another embodiment, wherein the bearing function for the toothed ring 2 assumes a disk-shaped element 18, which has a bearing journal 19 projecting radially from the disk-shaped element 18. The bearing pin 19 of the disk-shaped element 18 is arranged or mounted in a recess 20 formed in the bearing journal 4 of the housing 5, the disk-shaped element 18 abutting against the toothed ring 2 from the outside. The sliding bearing 25 is provided in this case between the bearing pin 19 of the disc-shaped element 18 and the bearing pin 4 of the housing 5. In this case, either the surface of the bearing journal 19 or the inner wall 21 of the formed in the bearing journal 4 of the housing 5 recess 20 may be formed as a sliding bearing. In this embodiment, fuel ports 22, 23 are provided in the housing 5. Fig. 5 shows a plan view of the internal gear pump 1 of Fig. 4. Here, the position of the two fuel ports 22, 23, which are made in the housing 5, again indicated by the respective double-dashed circular lines.
Bei der Zahnradpumpe gemäß der Erfindung wird eine konstruktiv einfache und somit kostengünstige Gleitlagerung realisiert. In the gear pump according to the invention, a structurally simple and thus inexpensive slide bearing is realized.

Claims

Ansprüche claims
1. Zahnradpumpe (1 ) zum Fördern eines Fluids mit einem drehbar auf einem Lagerzapfen (4) gelagerten außenverzahnten Zahnrad (3) und ei- nem innenverzahnten Zahnring (2), welche zur Erzeugung einer Förderwirkung in kämmendem Eingriff stehen, und welche gemeinsam mit einem elektrisch kommutierbaren Stator (7) in einem Gehäuse (5) angeordnet sind, wobei sich der Stator (7) konzentrisch um den Zahnring (2) herum erstreckt und mit einem Magnetring (6) zur Erzeugung einer elekt- romotorischen Kraft zusammenwirkt, wobei der Magnetring (6) mit dem1. Gear pump (1) for conveying a fluid with a rotatably mounted on a bearing journal (4) mounted externally toothed gear (3) and an internally toothed ring gear (2), which are in mesh to produce a conveying action, and which together with a electrically commutatable stator (7) are arranged in a housing (5), wherein the stator (7) concentrically around the toothed ring (2) extends around and cooperates with a magnetic ring (6) for generating an electric romotorischen force, wherein the magnetic ring (6) with the
Zahnring (2) zur Erzeugung der Förderwirkung eine Rotationsbewegung ausführt, Toothed ring (2) performs a rotational movement to produce the conveying action,
dadurch gekennzeichnet, dass  characterized in that
der Zahnring (2) durch ein Gleitlager (25) gelagert ist.  the toothed ring (2) is supported by a sliding bearing (25).
2. Zahnradpumpe (1 ) nach Anspruch 1 , 2. gear pump (1) according to claim 1,
dadurch gekennzeichnet, dass  characterized in that
der Magnetring (6) zwischen dem Stator (7) und dem Zahnring (2) angeordnet ist.  the magnetic ring (6) between the stator (7) and the toothed ring (2) is arranged.
3. Zahnradpumpe (1 ) nach Anspruch 1 oder 2, 3. gear pump (1) according to claim 1 or 2,
dadurch gekennzeichnet, dass  characterized in that
der Magnetring (6) und der Zahnring (2) drehfest verbunden sind.  the magnetic ring (6) and the toothed ring (2) are rotatably connected.
4. Zahnradpumpe (1 ) nach einem oder mehreren der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass 4. gear pump (1) according to one or more of claims 1 to 3, characterized in that
der Zahnring (2) aus einem nicht magnetischen Material hergestellt ist.  the toothed ring (2) is made of a non-magnetic material.
5. Zahnradpumpe (1 ) nach einem oder mehreren der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass 5. Gear pump (1) according to one or more of claims 1 to 4, characterized in that
die Lagerung des Zahnrings (2) durch einen ringförmig ausgebildeten Ab- schnitt (1 1 ) vorgesehen wird, welcher zumindest an einer dem Zahnring (2) gegenüberliegenden ersten Oberfläche (15) als Gleitlager (25) ausgebildet ist. the bearing of the toothed ring (2) by a ring-shaped Ab- Section (1 1) is provided which is formed at least on one of the toothed ring (2) opposite the first surface (15) as a sliding bearing (25).
6. Zahnradpumpe (1 ) nach Anspruch 5, 6. gear pump (1) according to claim 5,
dadurch gekennzeichnet, dass  characterized in that
zwischen dem Stator (7) und dem Magnetring (6) ein zweiter Radialspalt (13) mit einem Wert von 0,1 bis 0,5 mm ausgebildet ist.  between the stator (7) and the magnetic ring (6), a second radial gap (13) is formed with a value of 0.1 to 0.5 mm.
7. Zahnradpumpe (1 ) nach Anspruch 5 oder 6, 7. gear pump (1) according to claim 5 or 6,
dadurch gekennzeichnet, dass  characterized in that
der ringförmig ausgebildete Abschnitt (1 1 ) integral mit dem Gehäuse (5) gebildet ist und von diesem radial nach innen abragt.  the ring-shaped portion (1 1) is integrally formed with the housing (5) and protrudes from this radially inwardly.
8. Zahnradpumpe (1 ) nach einem oder mehreren der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass 8. gear pump (1) according to one or more of claims 1 to 6, characterized in that
der ringförmig ausgebildete Abschnitt (1 1 ) in das Gehäuse (5) einge- presst oder eingeklebt ist.  the ring-shaped section (1 1) is pressed or glued into the housing (5).
9. Zahnradpumpe (1 ) nach einem oder mehreren der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass 9. gear pump (1) according to one or more of claims 1 to 4, characterized in that
die Lagerung des Zahnrings (2) durch ein scheibenförmiges Element (18) vorgesehen wird, welches einen von dem scheibenförmigen Element (18) abragenden Lagerzapfen (19) aufweist, welcher in einer entsprechend in dem Gehäuse (5) vorgesehenen Ausnehmung (20) aufgenommen ist.  the bearing of the toothed ring (2) is provided by a disk-shaped element (18) which has a bearing pin (19) projecting from the disk-shaped element (18), which is accommodated in a recess (20) provided correspondingly in the housing (5) ,
10. Zahnradpumpe (1 ) nach Anspruch 9, 10. gear pump (1) according to claim 9,
dadurch gekennzeichnet, dass  characterized in that
die Oberfläche des Lagerzapfens (19) als Gleitlager (25) ausgebildet ist.  the surface of the bearing pin (19) is designed as a sliding bearing (25).
1 1 . Zahnradpumpe (1 ) nach Anspruch 9, 1 1. Gear pump (1) according to claim 9,
dadurch gekennzeichnet, dass  characterized in that
die Innenwand (21 ) der Ausnehmung (20) als Gleitlager (25) ausgebildet ist.  the inner wall (21) of the recess (20) is designed as a slide bearing (25).
EP10722710.0A 2009-07-31 2010-06-08 Gear pump Not-in-force EP2459880B1 (en)

Applications Claiming Priority (2)

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DE200910028154 DE102009028154A1 (en) 2009-07-31 2009-07-31 gear pump
PCT/EP2010/057973 WO2011012364A2 (en) 2009-07-31 2010-06-08 Gear pump

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EP2459880A2 true EP2459880A2 (en) 2012-06-06
EP2459880B1 EP2459880B1 (en) 2017-01-04

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JP (1) JP5536885B2 (en)
CN (1) CN102483058B (en)
DE (1) DE102009028154A1 (en)
IN (1) IN2012DN00753A (en)
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WO (1) WO2011012364A2 (en)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102549834B (en) 2009-10-08 2015-03-11 流体公司 Rechargeable metal-air cell with flow management system
CN202721244U (en) 2010-06-24 2013-02-06 流体股份有限公司 Electrochemical battery provided with step-shaped bracket fuel anode
CN102403525B (en) 2010-09-16 2016-02-03 流体公司 There is progressive electrochemical cell system of analysing oxygen electrode/fuel electrode
JP5908251B2 (en) 2010-11-17 2016-04-26 フルイディック，インク．Ｆｌｕｉｄｉｃ，Ｉｎｃ． Multi-mode charging of hierarchical anode
US8840385B2 (en) 2011-03-03 2014-09-23 Ti Group Automotive Systems, L.L.C. Positive displacement fluid pump
DE112013001156A5 (en) 2012-02-27 2014-12-11 Magna Powertrain Bad Homburg GmbH pump assembly
KR102150609B1 (en) * 2014-02-21 2020-09-01 엘지이노텍 주식회사 Motor
EP3253968A1 (en) * 2015-02-06 2017-12-13 Robert Bosch GmbH Pump unit for feeding fuel, preferably diesel fuel, to an internal combustion engine
DE102015213387A1 (en) * 2015-07-16 2017-01-19 Robert Bosch Gmbh Rotary piston pump
JP6190938B1 (en) * 2016-10-11 2017-08-30 大同機械製造株式会社 Internal gear pump
DE102017223715A1 (en) * 2017-12-22 2019-06-27 Magna Powertrain Bad Homburg GmbH Gerotor pump and method for producing such
CN114320890A (en) * 2022-01-10 2022-04-12 淮安市虎力液压机械有限公司 High-stability hydraulic gear pump
DE102022208141A1 (en) 2022-08-04 2024-02-15 Vitesco Technologies GmbH Pump, especially gear oil pump

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59226647A (en) * 1983-06-02 1984-12-19 Matsushita Electric Ind Co Ltd Dc motor
DE4106060C2 (en) * 1991-02-27 1995-11-30 Fresenius Ag Pump, in particular an encapsulated medical pump
US6270324B1 (en) * 1999-10-26 2001-08-07 Tuthill Corp. Positive displacement pump and thrust bearing assembly
DE10033950C2 (en) * 2000-07-13 2003-02-27 Schwaebische Huettenwerke Gmbh Pump with magnetic coupling
JP2005273648A (en) * 2004-02-23 2005-10-06 Aisin Seiki Co Ltd Electric pump
US7137793B2 (en) 2004-04-05 2006-11-21 Peopleflo Manufacturing, Inc. Magnetically driven gear pump
JP4272112B2 (en) 2004-05-26 2009-06-03 株式会社日立製作所 Motor-integrated internal gear pump and electronic equipment
JP3996919B2 (en) * 2004-08-20 2007-10-24 信越化学工業株式会社 Permanent magnet motor
JP4237731B2 (en) * 2005-05-31 2009-03-11 株式会社日立製作所 Motor-integrated internal gear pump, method for manufacturing the same, and electronic device
DE102006007554A1 (en) 2006-02-16 2007-08-23 Hydraulik-Ring Gmbh Feed pump for a urea solution, to treat heavy vehicle motor exhaust gases, is an electromotor with an integrated gear pump of two meshing cogwheels rotated by a magnetic field
DE102006037177A1 (en) 2006-08-09 2008-02-14 Robert Bosch Gmbh Internal gear pump
CN200989300Y (en) * 2006-08-15 2007-12-12 兰州理工大学 Hydraulic electric machine internal engaging gear pump
US20090167104A1 (en) * 2008-01-02 2009-07-02 Dunn Randy B Stackable brushless DC motor
DE202009000690U1 (en) * 2009-01-16 2009-04-09 Gather Industrie Gmbh Rotary displacement

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2011012364A2 *

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DE102009028154A1 (en) 2011-02-03
US8974207B2 (en) 2015-03-10
JP5536885B2 (en) 2014-07-02
JP2013500430A (en) 2013-01-07
IN2012DN00753A (en) 2015-06-19
WO2011012364A2 (en) 2011-02-03
US20120148426A1 (en) 2012-06-14
CN102483058B (en) 2015-10-07
WO2011012364A3 (en) 2012-02-09
RU2540346C2 (en) 2015-02-10
RU2012107225A (en) 2013-09-10
EP2459880B1 (en) 2017-01-04
CN102483058A (en) 2012-05-30

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