EP1930595A2 - Conveying unit - Google Patents
Conveying unit Download PDFInfo
- Publication number
- EP1930595A2 EP1930595A2 EP07117869A EP07117869A EP1930595A2 EP 1930595 A2 EP1930595 A2 EP 1930595A2 EP 07117869 A EP07117869 A EP 07117869A EP 07117869 A EP07117869 A EP 07117869A EP 1930595 A2 EP1930595 A2 EP 1930595A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- gear
- internal gear
- external gear
- pair
- internal
- 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
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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
- 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
-
- 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
- F04C2/084—Toothed wheels
Definitions
- oil pumps which are used for example in the context of ESP control systems that are used for vehicle dynamics control, come as oil pumps an internally toothed precharge, which is designed according to the gerotor principle used.
- the pair of gears used in this internally toothed precharge pump includes a pinion and a ring gear enclosing it. Both the pinion and the ring gear represent sintered components which are subjected to a curing process after sintering. Due to the manufacturing process sintering, however, a different degree of scattering radial clearance arises between the tooth heads or tooth flanks due to the prevailing sinter tolerances. This has an influence on the efficiency and the achievable delivery rate of this pre-charging pump used on ESP systems, for example, which is designed as an internal gear pump. If the sintering tolerances fluctuate very much, the delivery rate of the internally toothed precharge pump inevitably fluctuates very strongly, which represents a rather unsatisfactory overall situation.
- the pinion and the surrounding ring gear of a delivery unit such as a precharge pump for ESP systems or an oil pump for internal combustion engines are sintered or alternatively manufactured by way of metal powder injection molding. Both the pinion and the ring gear are then subjected to a hardening process.
- the toothing between the sintered and hardened pinion and this surrounding also sintered and hardened ring gear is tapered. This means that the lying on the end faces of the tooth tips or the tooth flanks are on different pitch circles with respect to the pinion and the ring gear.
- the gear pairs i. the combination of ring gear and pinion, if necessary, the pinion can be processed simultaneously on suitable grinding machines at the same time, as the parts produced by means of the sintering process or by means of metal injection molding technology usually represent tool-falling parts.
- FIG. 1 is a plan view of a pair of gears, an internal gear and an external gear comprising, refer to.
- a gear pair 10 as shown in FIG. 1 which can be used for example within an oil pump, comprises an internal gear 12 and an external gear 14.
- the internal gear 12 has a driving teeth 18 which meshes with a counter-toothing 20 of the shaft 16.
- the shaft 16 and the internal gear 12 are in an eccentricity e, see.
- Reference numeral 22 is mounted with respect to an axis 44 of the external gear 14.
- FIG. 1 is a plan view of a first plan side 24 of the interconnected gear pair 10, ie, the internal gear 12 and the external gear 14 is shown.
- the internal gear 12 is free of play in the ring gear representing external gear 14 joined.
- the internal gear 12 has a number of teeth 28, each having tooth heads 30.
- a radial play which is established between the tooth heads 30 and corresponding tooth heads on the inner circumference of the external gearwheel 14 is indicated by reference numeral 32.
- a first plan side 24 of the gear pair 10 is formed by the first planar side 34 of the internal gear 12 and the first planar side 36 of the external gear 14.
- FIG. 2 Shown according to FIG. 2 is a cut through the in FIG. 1 in the assembled state shown gear pair 10 along the cutting path II - II.
- FIG. 2 shows that the internal gear 12 is inserted into the external gear 14 of the gear pair 10. From the sectional view according to FIG. 2 that the in FIG. 1 represented sectional course II - II, it can further be seen that the first plane side 24 of the gear pair 10, the first planar side 34 of the internal gear 12 and the first planar side 36 of the external gear 14 includes. Thus, the first plan side 24 of the gear pair disintegrates into two plan sides of two separate components. From the illustration according to FIG. 2 also shows that the first planar side 34 of the internal gear 12 projects beyond a projection c over the first planar side 36 of the external gear 14.
- the second plan side 26 of the joined gear pair 10 represented by a second plan side 38, the internal gear 12 and by a second plan side 40, which by the external gear 14 of the gear pair 10 for an oil pump in in FIG. 1 formed, joined state formed.
- the internal gear 12 is arranged with an undersize d with respect to its second plane side 38.
- the second plan side 38 of the internal gear 12 is about the undersize d under the second plan side 40 of the external gear 14 of the gear pair 10 in the assembled state.
- FIG. 2 shown, joined state with the above-described supernatant c or the undersize d represents the state in which an assembled gear pair 10, the internal gear 12 and the external gear 14 comprising frontally ground flat. Before the surface grinding process of the plan sides 24, 26 of the gear pair 10, the components internal gear 12 and external gear 14 are hardened.
- a flat grinding of the first plane side 24 of the gear pair 10 in the non-backlash state of the internal gear 12 and external gear 14 is carried out.
- the first plan page 24 is removed by the grinding amount a, so that in in FIG. 2 State shown a ground flat, common first plan side 24 on the gear pair 10, that is, both the internal gear 12 and the external gear 14 is obtained.
- a flat grinding the second plan page 26 is generated, ie the undersize d as shown in FIG FIG.
- the common axial dimension corresponds to the axial dimension H 1 , which is formed by the removal of material on the joined gear pair 10 by the grinding a or the grinding b, can after the separation of the components 12, 14 after the surface grinding a further grinding of the internal gear 12 done.
- an axial play of the order of a few microns, preferably within the range between 3 .mu.m and 6 .mu.m can be achieved on the internal gear 12, so that the possibly this further grinding operation to be subjected to internal gear 12 has a also called Ritzel Adjustnexcellent axial dimension H 2 , which of the after the grinding process of the plan sides 24, 26 obtained common axial dimension H 1 of the two components joined together inner gear 12 and outer gear 14 deviates by the few microns mentioned.
- first pitch circle diameter 48 lying on the first plan side 24 of the joined gear pair 10 exceeds the second pitch circle diameter 50 which is formed on the rear side, ie the second plane side 26 of the joined gear pair 10.
- the diameter difference between the Pitch diameters 48, 50 results depending on the selected cone angle of the conical toothing 46 according to the sectional view in FIG. 2 ,
- the back grinding of the inside arranged internal gear 12 by the said measure preferably lying in the range between 3 .mu.m and 6 .mu.m, also omitted.
- the dimension H 2 corresponds to the common axial dimension H 1 of the joined components internal gear 12 and external gear 14.
- the substantially reduced radial clearance 32 on the mutually contacting tooth heads 30 of the internal gear 12 and the external gear 14 is required because between the tooth tips 30 line contact occurs and therefore no gap coverage occurs.
- a gap overlap adjusts itself to the axially sealing surfaces of the gearwheel pair 10, ie its end faces 12 and 14 and the inner sides of the pump housing which are respectively opposite thereto. The longer the gap overlap between the face sides 24, 26, equivalent to the first face side 34 of the internal gear 12, the first face 36 of the external gear 14, which represent the first face side 24 and the second face 38 of the internal gear 12, which together with the second face side 40 of the external gear 14 represent the second plan side 26 of the gear pair 10 and the opposite surfaces of the pump housing, a greater sealing effect can be achieved.
- the solution proposed by the invention provides a gear pair 10 available, which, for example, for an oil pump or for a feed pump for a Hydraulic fluid for a manual transmission, to use application examples, can be used.
Abstract
Description
Aus der Publikation "Ölpumpen für Verbrennungsmotoren" Pierburg AG, Alfred Pierburg Straße 1, 41460 Neuss, vgl. Seite 2 ist eine innenverzahnte Zahnradpumpe in Normalbauweise sowie in extrem flachbauender Bauweise bekannt. Innenverzahnte Zahnradpumpen werden als Ölpumpen für Verbrennungskraftmaschinen eingesetzt. Die Ölpumpe kann als außenverzahnte Pumpe und als innenverzahnte Pumpe von der Kurbelwelle der Verbrennungskraftmaschine direkt angetrieben werden oder mittels eines Nebenantriebs, so zum Beispiel elektrisch angetrieben werden. Verbrennungskraftmaschinen benötigen im unteren Drehzahlspektrum durch ölhydraulische Aufgaben, so zum Beispiel hydraulischen Ventilspielausgleich, Kolbenkühlung, Nockenwellenverstellung usw. sowie auf Grund von Drehzahlabsenkungen im Leerlauf größere Ölvolumenströme. Diese werden bei ungeregelten Pumpen im hohen Drehzahlbereich zu erheblichen Verlustleistungen führen, sodass bei heute eingesetzten Ölpumpen diese in der Regel geregelt ausgelegt sind.From the publication "Oil pumps for internal combustion engines" Pierburg AG, Alfred Pierburg road 1, 41460 Neuss, cf. Page 2 is an internally toothed gear pump in normal construction and in extremely flat construction known. Internal toothed gear pumps are used as oil pumps for internal combustion engines. The oil pump can be directly driven by the crankshaft of the internal combustion engine as externally toothed pump and as internally toothed pump or by means of a power take-off, so for example electrically driven. Internal combustion engines require in the lower speed range by oil hydraulic tasks, such as hydraulic valve clearance compensation, piston cooling, camshaft adjustment, etc., and due to speed drops at idle larger oil flow rates. These will result in uncontrolled pumps in the high speed range to considerable power losses, so that oil pumps used today are designed to be regulated in the rule.
Bei aus dem Stand der Technik bekannten Ölpumpen, die zum Beispiel im Rahmen von ESP-Regelsystemen, die zur Fahrdynamikregelung dienen, eingesetzt werden, kommen als Ölpumpen eine innenverzahnte Vorladepumpe, die nach dem Gerotorprinzip ausgelegt ist, zum Einsatz.In known from the prior art oil pumps, which are used for example in the context of ESP control systems that are used for vehicle dynamics control, come as oil pumps an internally toothed precharge, which is designed according to the gerotor principle used.
Das bei dieser Vorladepumpe mit Innenverzahnung eingesetzte Zahnradpaar umfasst ein Ritzel sowie ein dieses umschließendes Hohlrad. Sowohl das Ritzel als auch das Hohlrad stellen gesinterte Bauteile dar, die nach dem Sintern einem Härtungsvorgang unterzogen werden. Aufgrund des Fertigungsvorgangs Sintern stellt sich jedoch zwischen den Zahnköpfen bzw. Zahnflanken aufgrund der herrschenden Sintertoleranzen ein unterschiedlich stark streuendes Radialspiel ein. Dieses hat Einfluss auf den Wirkungsgrad und die erzielbare Förderleistung dieser an ESP-Systemen zum Beispiel eingesetzten Vorladepumpe, die als Innenzahnradpumpe ausgelegt ist. Schwanken die Sintertoleranzen sehr stark, so schwankt zwangsläufig auch die Förderleistung der innenverzahnten Vorladepumpe sehr stark, was insgesamt gesehen einen recht unbefriedigenden Zustand darstellt.The pair of gears used in this internally toothed precharge pump includes a pinion and a ring gear enclosing it. Both the pinion and the ring gear represent sintered components which are subjected to a curing process after sintering. Due to the manufacturing process sintering, however, a different degree of scattering radial clearance arises between the tooth heads or tooth flanks due to the prevailing sinter tolerances. This has an influence on the efficiency and the achievable delivery rate of this pre-charging pump used on ESP systems, for example, which is designed as an internal gear pump. If the sintering tolerances fluctuate very much, the delivery rate of the internally toothed precharge pump inevitably fluctuates very strongly, which represents a rather unsatisfactory overall situation.
Der erfindungsgemäß vorgeschlagenen Lösung folgend werden das Ritzel und das dieses umgebende Hohlrad eines Förderaggregates, wie zum Beispiel einer Vorladepumpe für ESP-Systeme oder einer Ölpumpe für Verbrennungskraftmaschinen gesintert oder alternativ dazu im Wege des Metallpulverspritzgusses gefertigt. Sowohl das Ritzel als auch das Hohlrad werden anschließend einem Härtungsprozess unterzogen. Die Verzahnung zwischen dem gesinterten und gehärteten Ritzel und dem dieses umschließenden ebenfalls gesinterten und gehärteten Hohlrad verläuft konisch. Dies bedeutet, dass die an den Stirnseiten liegenden Enden der Zahnköpfe bzw. der Zahnflanken auf unterschiedlichen Teilkreisen in Bezug auf das Ritzel und das Hohlrad liegen.Following the proposed solution according to the invention, the pinion and the surrounding ring gear of a delivery unit, such as a precharge pump for ESP systems or an oil pump for internal combustion engines are sintered or alternatively manufactured by way of metal powder injection molding. Both the pinion and the ring gear are then subjected to a hardening process. The toothing between the sintered and hardened pinion and this surrounding also sintered and hardened ring gear is tapered. This means that the lying on the end faces of the tooth tips or the tooth flanks are on different pitch circles with respect to the pinion and the ring gear.
Zum Schleifen des Ritzels und des Hohlrades an den Stirnflächen wird das Ritzel spielfrei in das Hohlrad hineingesteckt und danach eine Schleifoperation an beiden Stirnseiten der beiden Werkstücke durchgeführt. Dabei wird ein erstes Maß H1 erhalten. Anschließend kann das innenliegend angeordnete Ritzel (Innenzahnrad) um ein geringes Spiel in der Größenordnung zwischen 3 und 6 µm auf ein geringeres Maß H2, welches in Bezug auf das Maß H1 geringer ist, geschliffen wurden. Dadurch entsteht ein Axialspiel zwischen Ritzel und Hohlrad. Durch die konisch ausgebildete Verzahnung an Ritzel und Hohlrad entsteht ein geringes Radialspiel in der Größenordnung weniger µm. Mit dieser Maßnahme lässt sich ein sehr guter hydraulischer Wirkungsgrad einer derart gefertigten innenverzahnten Pumpe erreichen, der auch bei höheren Drücken in der Größenordnung von 50 bar aufrechterhalten werden kann. Auf das Zurückschleifen des Ritzels, d.h. der Ausbildung des Untermaßes H2 am Ritzel in Bezug auf das Maß H1 des Verbundes aus Ritzel und Hohlrad kann dann verzichtet werden, wenn ein Radialspiel zwischen den sich drehenden Zahnrädern, d.h. dem relativ zum Hohlrad rotierenden Ritzel sowie dem Pumpengehäuse in axialer Richtung und ausreichend Radialspiel an den Zahnköpfen gewährleistet ist und ein Klemmen der miteinander kämmenden Zähnräder ausgeschlossen ist.For grinding the pinion and the ring gear on the end faces of the pinion is inserted into the ring gear backlash and then carried out a grinding operation on both end faces of the two workpieces. In this case, a first measure H 1 is obtained. Subsequently, the internally arranged pinion (internal gear) by a small clearance on the order of 3 to 6 microns to a lesser degree H 2 , which is lower in relation to the dimension H 1 , were ground. This creates an axial play between pinion and ring gear. Due to the conical toothing of pinion and ring gear creates a small radial clearance in the order of a few microns. With this measure, a very good hydraulic efficiency of a thus manufactured internal gear pump can be achieved, which can be maintained even at higher pressures in the order of 50 bar. On the back grinding of the pinion, ie the Training the undersize H 2 on the pinion with respect to the dimension H 1 of the composite of pinion and ring gear can then be dispensed with, if a radial play between the rotating gears, ie the relative to the ring gear rotating pinion and the pump housing in the axial direction and sufficient radial play is ensured at the tooth tips and a clamping of the meshing toothed wheels is excluded.
Die Zahnradpaare, d.h. die Kombination aus Hohlrad und Ritzel, im Bedarfsfall auch die Ritzel, können zusammen auf geeigneten Schleifmaschinen gleichzeitig bearbeitet werden, da die im Wege des Sinterverfahrens oder im Wege der Metallpulverspritzgusstechnik hergestellten Teile in der Regel werkzeugfallende Teile darstellen. Eine weitere Möglichkeit, mit welcher der hydraulische Wirkungsgrad hin zu höheren Drücken in die Grö-ßenordnung von 50 bar und mehr verschoben werden kann, stellt das Einlaufen der miteinander kämmenden Zahnräder, d.h. des gesinterten und gehärteten Ritzels und des gesinterten und gehärteten Hohlrades mit einem Verschleißmittel so zum Beispiel einer Läppaste dar.The gear pairs, i. the combination of ring gear and pinion, if necessary, the pinion can be processed simultaneously on suitable grinding machines at the same time, as the parts produced by means of the sintering process or by means of metal injection molding technology usually represent tool-falling parts. Another way in which the hydraulic efficiency can be shifted to higher pressures of the order of 50 bars and more, is the running-in of the intermeshing gears, i. the sintered and hardened pinion and the sintered and hardened ring gear with a wear agent such as a lapping.
Anhand der Zeichnung wird die Erfindung nachstehend eingehender beschrieben. Es zeigt:
- Figur 1
- eine Draufsicht auf die konisch verzahnten Bauteile Ritzel und Hohlrad mit Schnittverlauf A - B und
- Figur 2
- den Schnittverlauf A - B entsprechend
Figur 1 in gesonderter Darstellung.
- FIG. 1
- a plan view of the conically toothed components pinion and ring gear with cutting profile A - B and
- FIG. 2
- the cutting course A - B accordingly
FIG. 1 in separate presentation.
Ein Zahnradpaar 10 gemäß der Darstellung in
Analog verhält es sich mit einer in
Aus der Darstellung gemäß
Dargestellt gemäß
Aus der Darstellung gemäß
In analoger Weise wird die zweite Planseite 26 des gefügten Zahnradpaares 10 gemäß der Schnittdarstellung in
Der in
Zunächst erfolgt ein Planschleifen der ersten Planseite 24 des Zahnradpaares 10 im aus Innenzahnrad 12 und Außenzahnrad 14 gefügten, spielfreien Zustand. Die erste Planseite 24 wird um das Schleifmaß a abgetragen, so dass im in
Während vor dem Trennen der Bauteile 12 und 14 das gemeinsame Axialmaß dem Axialmaß H1 entspricht, welches durch den Materialabtrag am gefügten Zahnradpaar 10 durch das Schleifmaß a bzw. das Schleifmaß b entsteht, kann nach dem Trennen der Bauteile 12, 14 nach dem Planschleifen eine weitere Schleifbearbeitung des Innenzahnrades 12 erfolgen. Dabei kann am Innenzahnrad 12 ein Axialspiel in der Größenordnung von wenigen µm, bevorzugt innerhalb des Bereiches zwischen 3 µm und 6 µm erreicht werden, so dass das ggf. diesem weiteren Schleifvorgang zu unterziehende Innenzahnrad 12 ein auch als Ritzelhöhenmaß bezeichnetes Axialmaß H2 aufweist, welches vom nach dem Schleifvorgang der Planseiten 24, 26 erhaltenen gemeinsamen Axialmaß H1 der beiden miteinander gefügten Bauteile Innenzahnrad 12 und Außenzahnrad 14 um die genannten wenigen µm abweicht.While before the separation of the
Aus dem Axialspiel des Innenzahnrads 12 ergibt sich unter Berücksichtigung des Konuswinkels der konischen Verzahnung 46 ein wesentlich kleineres Radialspiel 32 (vgl. Darstellung gemäß
Für den Fall, dass das Axialspiel zwischen den bewegten Zahnräder, d.h. dem Innenzahnrad 12 und dem Außenzahnrad 14 und dem das Zahnradpaar 10 umgebenden Pumpengehäuse für ein Freilaufen des Innenzahnrades 12 und des Außenzahnrades 14, d.h. deren Nichtklemmen, ausreichend ist, kann das Zurückschleifen des innenliegend angeordneten Innenzahnrades 12 um das genannte Maß, bevorzugt im Bereich zwischen 3 µm und 6 µm liegend, auch unterbleiben. Dies bedeutet, dass bei ausreichendem Axialspiel zwischen dem bewegten Innenzahnrad 12 und dem stationären Außenzahnrad 14 des Zahnradpaares 10 das Maß H2 dem gemeinsamem Axialmaß H1 der gefügten Bauteilen Innenzahnrad 12 und Außenzahnrad 14 entspricht.In the event that the axial clearance between the moving gears, ie, the
Das wesentlich verringerte Radialspiel 32 an den einander berührenden Zahnköpfen 30 des Innenzahnrades 12 und des Außenzahnrades 14 ist erforderlich, da zwischen den Zahnköpfen 30 eine Linienberührung auftritt und demzufolge keine Spaltüberdeckung eintritt. Eine Spaltüberdeckung stellt sich hingegen an den axialdichtenden Flächen des Zahnradpaares 10, d.h. dessen Stirnseiten 12 und 14 und den diesen jeweils gegenüberliegenden Innenseiten des Pumpengehäuses ein. Je länger die Spaltüberdeckung zwischen den Planseiten 24, 26, gleichbedeutend mit der ersten Planseite 34 des Innenzahnrades 12, der ersten Planseite 36 des Außenzahnrades 14, welche die erste Planseite 24 darstellen und der zweiten Planseite 38 des Innenzahnrades 12, die zusammen mit der zweiten Planseite 40 des Außenzahnrades 14 die zweite Planseite 26 des Zahnradpaares 10 darstellen und den gegenüberliegenden Flächen des Pumpengehäuses ist, eine umso größere Abdichtwirkung ist erzielbar. Da diese Spaltüberdeckung den miteinander kämmenden Zahnrädern 12 und 14 im Bereich der Förderräume, d.h. im Bereich der miteinander kämmenden Verzahnung fehlt, wird eine Verbesserung des hydraulischen Wirkungsgrads etahydr durch das minimale Radialspiel 32 im Bereich der Innenverzahnung aufgrund der oben stehend skizzierten Maßnahmen erzielt.The substantially reduced
Damit stellt die erfindungsgemäß vorgeschlagene Lösung ein Zahnradpaar 10 zur Verfügung, welches zum Beispiel für eine Ölpumpe oder für eine Förderpumpe für ein Hydraulikfluid für ein Schaltgetriebe, um Anwendungsbeispiele zu nennen, eingesetzt werden kann.Thus, the solution proposed by the invention provides a
Claims (10)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200610056845 DE102006056845A1 (en) | 2006-12-01 | 2006-12-01 | Delivery unit e.g. citation pump of electrical submersible pump systems and an oil pump for internal combustion engine, has gear train, internal gear wheel and external gear wheel |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1930595A2 true EP1930595A2 (en) | 2008-06-11 |
EP1930595A3 EP1930595A3 (en) | 2015-03-18 |
EP1930595B1 EP1930595B1 (en) | 2016-12-14 |
Family
ID=39198189
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07117869.3A Expired - Fee Related EP1930595B1 (en) | 2006-12-01 | 2007-10-04 | Conveying unit |
Country Status (2)
Country | Link |
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EP (1) | EP1930595B1 (en) |
DE (1) | DE102006056845A1 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012193769A (en) * | 2011-03-15 | 2012-10-11 | Asmo Co Ltd | Inscribed planetary reduction gear and gear pump |
WO2011128218A3 (en) * | 2010-04-16 | 2013-03-07 | Robert Bosch Gmbh | Gear pump |
WO2013013883A3 (en) * | 2011-07-28 | 2013-08-22 | Zf Friedrichshafen Ag | Gearbox pump |
JP2013199849A (en) * | 2012-03-23 | 2013-10-03 | Hitachi Automotive Systems Ltd | Internal gear pump |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008054767A1 (en) | 2008-12-16 | 2010-06-17 | Robert Bosch Gmbh | Conveying device, particularly gear wheel pump, has housing, with two housing units, where conveyor elements are formed as gear wheels and are inserted between two housing units |
DE102008054755A1 (en) | 2008-12-16 | 2010-06-17 | Robert Bosch Gmbh | Conveying device, particularly gear wheel pump, has housing, where surfaces of housing units have mounting surfaces for mounting conveyor elements |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DK165462C (en) * | 1982-04-07 | 1993-04-19 | Sumitomo Heavy Industries | HYDRAULIC ENGINE |
DE9405502U1 (en) * | 1994-03-26 | 1994-07-28 | Witeg Wissenschaftlich Tech Ge | Precision liquid pump made from molded parts with a wide tolerance range |
JP2000027769A (en) * | 1998-07-08 | 2000-01-25 | Unisia Jecs Corp | Internal gear pump or motor, and manufacture thereof |
-
2006
- 2006-12-01 DE DE200610056845 patent/DE102006056845A1/en not_active Ceased
-
2007
- 2007-10-04 EP EP07117869.3A patent/EP1930595B1/en not_active Expired - Fee Related
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2011128218A3 (en) * | 2010-04-16 | 2013-03-07 | Robert Bosch Gmbh | Gear pump |
JP2012193769A (en) * | 2011-03-15 | 2012-10-11 | Asmo Co Ltd | Inscribed planetary reduction gear and gear pump |
WO2013013883A3 (en) * | 2011-07-28 | 2013-08-22 | Zf Friedrichshafen Ag | Gearbox pump |
CN103717900A (en) * | 2011-07-28 | 2014-04-09 | Zf腓德烈斯哈芬股份公司 | Gearbox pump |
JP2013199849A (en) * | 2012-03-23 | 2013-10-03 | Hitachi Automotive Systems Ltd | Internal gear pump |
Also Published As
Publication number | Publication date |
---|---|
DE102006056845A1 (en) | 2008-06-05 |
EP1930595B1 (en) | 2016-12-14 |
EP1930595A3 (en) | 2015-03-18 |
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