EP2732164B1 - Gear ring pump - Google Patents
Gear ring pump Download PDFInfo
- Publication number
- EP2732164B1 EP2732164B1 EP12746262.0A EP12746262A EP2732164B1 EP 2732164 B1 EP2732164 B1 EP 2732164B1 EP 12746262 A EP12746262 A EP 12746262A EP 2732164 B1 EP2732164 B1 EP 2732164B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- pump housing
- portal support
- suction
- pressure
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C15/0023—Axial sealings for working fluid
- F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2230/00—Manufacture
- F04C2230/60—Assembly methods
- F04C2230/602—Gap; Clearance
Definitions
- the invention relates to a gerotor pump, in particular for use in small pump units, which are preferably produced by electric motor operated as a modular pump and used in vehicle and engine.
- Toothed ring pumps for example in the design of gerotor pumps are used in automotive and engine construction, inter alia, in internal combustion engines as fuel pumps or oil pumps.
- the wheelset used in gerotor pumps consists of an externally toothed inner rotor and an internally toothed outer rotor, wherein the inner rotor is rotatably connected to the drive shaft and having fewer teeth than the outer rotor, and the outer rotor is rotatably mounted in a cylindrical chamber of the pump housing so that the teeth of the eccentric to the outer rotor mounted inner rotor partially mesh with the teeth of the outer rotor.
- pressure and suction area of the wheelset kidney-shaped pump chambers are arranged in the pump housing, which are connected via connection channels directly to the pump housing arranged pressure and suction connection lines and ensure that the liquid to be pumped from the suction line via the Wheelset is pressed into pressure connection line.
- kidney-shaped passage openings are arranged in this bearing plate, in the region of the pump chambers of the gerotor motor, so that the bearing plate at the same time takes over the task of a guide body and in connection with the bearing plate adjacent assemblies, according to the US 7,614,227 B2 presented solution, a regulation of the traction drive of the lawn tractor, ie a regulation of its speed and its direction of travel, can be ensured.
- gerotor pumps used as oil pumps in the internal combustion engines are used there for engine lubrication, which is known e.g. in motor vehicles over a temperature range of minus 40 ° C to the range of hot idling operation of about 160 ° C must be guaranteed.
- the pump housings are often die-cast aluminum and the gear sets are made of sintered steel, varying over the wide operating range / temperature range of minus 40 ° C to about 160 ° C, due to the different thermal expansion coefficients of aluminum and steel inevitably also the axial play between the gear set and the pump housing as a function of the current operating temperature. In this case occur at low operating temperatures, due to narrow gaps, usually friction losses and high operating temperatures due to large gaps, losses in volumetric efficiency, which can be up to 50% to 60% of the best for each gerotor pump assembly volumetric efficiency.
- the volumetric efficiency decreases approximately linearly with increasing temperatures.
- An outer diameter smaller constructive design of a gerotor pump is from the DE 10 2008 054 758 A1 known.
- Elastomer seals are arranged to compensate for tolerances between the adjacent components.
- the invention is therefore based on the object to develop a gerotor pump, which eliminates the aforementioned disadvantages of the prior art, and in particular at small, ie also in the outer diameter of the Housing small pumping units, which are preferably operated by electric motor and manufactured as a modular pump that largely the same Ge Reifenohwel be used in geometry, can be used, wherein the to be developed ring gear pump also according to the customer's request in the timing of the pump manufacturing technology should be easily modifiable , so that always a fluidically optimal behavior of the pump according to the invention is ensured, it should be very inexpensive to produce the ring gear pump to be developed even in very small pump sizes, and also with the use of very cost-effective components, such as pump housings made of aluminum and pump steel, even under extreme operating conditions, such as an oil pump in conjunction with an internal combustion engine, ie over the temperature working range of such oil pump, from about - 40 ° C to about + 160 ° C away, always e ensure optimum axial gap (and thereby minimal losses),
- FIGS. 1 to 5 illustrated, according to the invention ring gear pump with a pump housing 1, one arranged in the pump housing 1 Working space 2 with arranged in the end wall 3 of the working space 2 in the pump housing 1 inlet and Ausström Schemeen, arranged on the pump housing 1, sealed by a seal 4 housing cover 5, arranged with a rotatably mounted in the pump housing 1, mounted in a pump bearing 6 drive shaft 7 at which a wheelset 8 is arranged, which consists of a rotatably connected to the drive shaft 7 externally toothed inner rotor 9 and an internally toothed outer rotor 10 which is rotatably mounted in a rotor bearing 11 in the cylindrical working space 2 of the pump housing 1 such that the teeth of the eccentric to the outer rotor 10 mounted inner rotor 9 in regions with the teeth of the outer rotor 10 mesh with one or both sides in the suction region of the wheelset 8 arranged / arranged Saugniere / n 12 and one or both sides in the pressure range of the wheelse
- slidably mounted port carrier 18 is arranged, in which both a suction kidney 12 and a pressure kidney 13 is arranged and both each separated from one another, the port carrier 18 over the entire thickness of the port carrier 18, this in the form of an inlet chamber 19 connected to the suction kidney 12, as well as on the other hand connected to the pressure kidney 13 Ausströmströmhunt 20th penetrate, wherein the thickness of the port carrier 18 corresponds approximately to the thickness of the wheelset 8 and this can also exceed by up to 20%, and the coefficient of thermal expansion of the port carrier 18 is about 70% to 120% higher than the thermal expansion coefficient of the pump housing 1, and that the drive shaft 7, which is non-rotatably connected to the inner rotor 9, by no means protrudes into (or is supported in) the port carrier 18.
- the port carrier 18 is wear-resistant on the end face adjacent to the wheelset 8 or is wear-resistant coated, or that a sliding plate 25 rotatably connected to the port carrier 18 is arranged between the wheelset 8 and the port carrier 18, whereby between the wheelset 8 and the port carrier 18 in addition to the friction losses and the wear is minimized, so that by means of the solution according to the invention a long service life can be ensured with high efficiency.
- FIG. 1 is shown as one of the possible designs of this feature, arranged between the wheelset 8 and the port carrier 18 sliding plate 25, wherein on the sliding plate 25, a latching nose 26 is arranged, which positively engages with a arranged on the port carrier 18 locking groove 27 in operative connection, and thereby the Sliding plate 25 rotatably connected to the port carrier 18.
- the sliding plate 25 is reduced in its flexural rigidity, thereby better applying and adapting to the wheelset 8 and the port support 18 is possible. simultaneously can be achieved with the shaft guide bore 28, a slight projection of the drive shaft 7.
- the housing cover 5 via arranged in the pump housing 1 positioning pins 21 and the housing cover 5 associated Positionierkerben 22 against rotation on the pump housing 1, and the port carrier 18 by means of eccentrically arranged in the port carrier 18 pin guide bore 24 and one in the end wall 3 of the working space 2 of Pin guide bore 24 associated arranged guide pin 23 is axially displaceably mounted in the pump housing 1.
- This arrangement of the invention allows in connection with the inventive arrangement of the port support 18 in the axial direction next to the wheelset 8 of the ring gear pump according to the invention, since the port carrier 18 the inflow and outflow of the pump in its functional geometry maps that in conjunction with the invention, outer cylindrical geometry of the port carrier 18 this easily rotated within certain limits in the pump housing 1, and exactly, eg by guide pins 23 in the pump housing 1, can be positioned securely.
- the timing of the pump to the particular application of the pump can be optimized fluidically.
- the port carrier 18 according to the invention also serves to simultaneously ensure optimization of the axial gap.
- the port carrier 18 whose coefficient of thermal expansion preferably has twice the value of the thermal expansion coefficient of the housing material.
- the thickness of the port carrier 18 corresponds approximately to the thickness of the wheelset. 8
- the thickness of the port carrier 18 can be increased to approximately 120% of the thickness of the wheelset 8, for example.
- thermoset materials which are e.g. by targeted admixture of friction reducing substances significantly improve the running behavior of the adjacent arranged wheelset.
- the port carrier 18 is made of sintered and resin-bound sodium chlorides.
- a given axial thermal expansion of an aluminum pump housing having an aluminum thermal expansion coefficient of about 23x10 -6 K -1 can be achieved through a sintered and resin bonded sodium chloride port support having a thermal expansion coefficient of sodium chloride of about 40 ... 44 x 10 -6 K -1 , effectively, ie, compensated for with a relatively small thickness of a port carrier 18 made of sintered and resin-bound sodium chloride.
- the axial gaps depending on the respective operating temperature are always optimized in the entire temperature working range of the pump, i. it is cost effective to ensure optimal dynamic axial gap compensation.
- the axial gaps are larger at low temperatures and at higher temperatures by significantly greater length expansion of the port carrier 18 to reduce the axial play.
- Another advantage of the solution according to the invention consists in the fact that in the Axialspaltkompensation invention presented here, the wheelset 8 remains free of axial loads, so that the resulting friction moments are avoided, which inevitably always lead to efficiency losses.
- the inventively desired temperature-compensating effect of the inventively placed in the axial direction next to the wheelset 8 invention port carrier 18 causes temperature increase and consequent axial growth of the working space 2 in the pump housing 1, in which the wheelset 8 and the port support 18 are housed, that by a clear higher thermal expansion of the port support 18 according to the invention, the axial growth of the working space 2 is balanced with simultaneous attention to the growth of the wheelset 8.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Description
Die Erfindung betrifft eine Zahnringpumpe, insbesondere für den Einsatz in kleinen Pumpenaggregaten, die vorzugsweise elektromotorisch betrieben als Baukastenpumpen hergestellt und im Fahrzeug- und Motorenbau eingesetzt werden.The invention relates to a gerotor pump, in particular for use in small pump units, which are preferably produced by electric motor operated as a modular pump and used in vehicle and engine.
Zahnringpumpen, beispielsweise in der Bauform von Gerotorpumpen werden im Fahrzeug- und Motorenbau unter anderem bei Verbrennungsmotoren als Kraftstoffpumpen oder als Ölpumpen eingesetzt.
Der in Gerotorpumpen eingesetzte Laufradsatz, besteht aus einem außenverzahnten Innenrotor und einem innenverzahnten Außenrotor, wobei der Innenrotor drehfest mit der Antriebswelle verbunden ist und weniger Zähne als der Außenrotor aufweist, und der Außenrotor drehbar in einer zylindrischen Kammer des Pumpengehäuses so gelagert ist, dass die Zähne des exzentrisch zum Außenrotor gelagerten Innenrotors bereichsweise mit den Zähnen des Außenrotors kämmen.Toothed ring pumps, for example in the design of gerotor pumps are used in automotive and engine construction, inter alia, in internal combustion engines as fuel pumps or oil pumps.
The wheelset used in gerotor pumps, consists of an externally toothed inner rotor and an internally toothed outer rotor, wherein the inner rotor is rotatably connected to the drive shaft and having fewer teeth than the outer rotor, and the outer rotor is rotatably mounted in a cylindrical chamber of the pump housing so that the teeth of the eccentric to the outer rotor mounted inner rotor partially mesh with the teeth of the outer rotor.
Im Druck- und Saugbereich des Laufradsatzes sind im Pumpengehäuse nierenförmige Pumpenkammern (Druck- und Saugniere/n) angeordnet, welche über Anschlusskanäle direkt mit am Pumpengehäuse angeordneten Druck- und Sauganschlussleitungen in Verbindung stehen und gewährleisten, dass die zu pumpende Flüssigkeit von der Sauganschlussleitung über den Laufradsatz in Druckanschlussleitung gepresst wird.In the pressure and suction area of the wheelset kidney-shaped pump chambers (pressure and Saugniere / n) are arranged in the pump housing, which are connected via connection channels directly to the pump housing arranged pressure and suction connection lines and ensure that the liquid to be pumped from the suction line via the Wheelset is pressed into pressure connection line.
In der
Die in den Verbrennungsmotoren als Ölpumpen eingesetzten Gerotorpumpen dienen dort der Motorschmierung, welche z.B. bei Kraftfahrzeugen über einen Temperaturbereich von minus 40°C bis in den Bereich des Heißleerlaufbetriebs von ca. 160°C gewährleistet sein muss.The gerotor pumps used as oil pumps in the internal combustion engines are used there for engine lubrication, which is known e.g. in motor vehicles over a temperature range of minus 40 ° C to the range of hot idling operation of about 160 ° C must be guaranteed.
Da fast alle Pumpengehäuse aus Gründen der Kosten- und Gewichtsersparnis aus anderen Materialien gefertigt werden, wie die im jeweiligen Pumpengehäuse angeordnete Zahnradsätze, beispielsweise werden die Pumpengehäuse oftmals aus Aluminium-Druckguss und die Zahnradsätze aus Sinterstahl hergestellt, verändert sich über den großen Arbeitsbereich/Temperaturbereich von minus 40°C bis ca. 160°C, aufgrund der unterschiedlichen Wärmeausdehnungskoeffizienten von Aluminium und Stahl zwangsläufig auch das Axialspiel zwischen dem Zahnradsatz und dem Pumpengehäuse in Abhängigkeit von der jeweils aktuellen Betriebstemperatur. Dabei treten bei niedrigen Betriebstemperaturen, infolge enger Spaltmaße, zumeist Reibungsverluste und bei hohen Betriebstemperaturen, infolge zu großer Spaltmaße, Verluste im volumetrischen Wirkungsgrad auf, die bis zu 50% bis 60 % des für die jeweilige Zahnringpumpenanordnung günstigsten volumetrischen Wirkungsgrades betragen können.Since almost all pump housings are made of other materials for cost and weight savings, such as the gear sets located in the respective pump housing, for example, the pump housings are often die-cast aluminum and the gear sets are made of sintered steel, varying over the wide operating range / temperature range of minus 40 ° C to about 160 ° C, due to the different thermal expansion coefficients of aluminum and steel inevitably also the axial play between the gear set and the pump housing as a function of the current operating temperature. In this case occur at low operating temperatures, due to narrow gaps, usually friction losses and high operating temperatures due to large gaps, losses in volumetric efficiency, which can be up to 50% to 60% of the best for each gerotor pump assembly volumetric efficiency.
Dabei sinkt der volumetrische Wirkungsgrad mit steigenden Temperaturen etwa linear ab.The volumetric efficiency decreases approximately linearly with increasing temperatures.
Im Stand der Technik wurden daher die unterschiedlichsten Lösungen zur Optimierung des Axialspaltes/Axialspieles vorgeschlagen.In the prior art, therefore, a variety of solutions for optimizing the axial gap / axial clearance have been proposed.
So ist aus der
Durch den Einbau derartiger Distanzelemente, beispielsweise aus Nickelstahl, verkleinert sich das Axialspiel bei hohen Temperaturen und vergrößert sich bei niedrigen Temperaturen.By installing such spacers, such as nickel steel, reduces the axial clearance at high temperatures and increases at low temperatures.
Der Einbau derartiger Distanzelemente führt zu einer Erhöhung des volumetrischen Wirkungsgrades gegenüber herkömmlichen Pumpen aus Aluminium-Druckguss mit Zahnradsätzen aus Stahl von bis zu 40 bis 50%, hat dabei jedoch den Nachteil, da die Distanzelemente zwangsläufig außerhalb des Pumpenrotor-Durchmessers und innerhalb des Pumpengehäuses angeordnet werden müssen, dass diese Lösung eine wesentliche radiale Vergrößerung des Bauraumes der jeweiligen Pumpe erfordert.The incorporation of such spacers leads to an increase in the volumetric efficiency over conventional pumps made of die-cast aluminum with steel gear sets of up to 40 to 50%, but it has the disadvantage that the spacers necessarily located outside of the pump rotor diameter and within the pump housing must be that this solution requires a substantial radial increase in the space of the respective pump.
Eine im Außendurchmesser kleiner bauende Bauform einer Zahnringpumpe ist aus der
Diese Lösung hat jedoch den Nachteil, dass aufgrund der unter Federvorspannung am Rotor anliegenden Bauteile zwangsläufig stirnseitig am Rotor Reibmomente auftreten, die hohe Wirkungsgradverluste zur Folge haben.However, this solution has the disadvantage that due to the applied spring preload on the rotor components inevitably occur on the front side of the rotor friction moments that have high efficiency losses result.
Gleichzeitig erhöht sich aufgrund der in den Pumpengehäuse integrierten Bauund Funktionselemente, wie den Lagerstellen für die Antriebswelle, den im Pumpengehäuse anzuordnenden Saug- und Drucknieren und den zugehörigen Anschlusskanälen zwangsläufig mit kleiner werdender Baugröße der Fertigungs- und Montageaufwand.At the same time increases due to integrated in the pump housing Bauund functional elements, such as the bearing points for the drive shaft, to be arranged in the pump housing suction and pressure kidneys and the associated connection channels inevitably with smaller size of the manufacturing and assembly costs.
Zudem beeinträchtigen mit kleiner werdender Baugröße die Spaltgeometrien überproportional den Wirkungsgrad.In addition, the gap geometries disproportionately affect the efficiency with a smaller size.
Um nun, insbesondere mit kleiner werdender Baugröße, die Fertigungsgenauigkeit und damit den Fertigungsaufwand zu reduzieren, wurde im Stand der Technik vorgeschlagen diese Gehäuse insbesondere von kleinen Zahnringpumpen modular aufzubauen, d.h. aus mehreren Bauteilen zusammenzufügen.In order to reduce the manufacturing accuracy and thus the production cost, in particular with smaller size, it has been proposed in the prior art to modularly construct these housings, in particular of small gerotor pumps, i. from several components.
Bei diesen Bauformen werden zwischen den benachbarten Bauteilen Elastdomerdichtungen zum Toleranzausgleich angeordnet.In these designs Elastomer seals are arranged to compensate for tolerances between the adjacent components.
Bei diesen Lösungen mit elastischem Toleranzausgleich treten beim Verspannen der benachbarten Bauteile zwangsläufig "Restspannungen" auf, welche an den Stirnseiten des Laufradsatzes wiederum zu Reibmomenten führen.In these solutions with elastic tolerance compensation inevitably occur during clamping of the adjacent components "residual stresses", which in turn lead to friction moments on the faces of the wheelset.
Werden die benachbarten Bauteilen jedoch "gerade" so verspannt, dass zwischen Ihnen noch toleranzbedingte Spalte verbleiben, dann treten mit zunehmender Betriebstemperatur am Laufradsatz stirnseitig Leckageverluste auf, die, wie bereits erläutert, den Wirkungsgrad bei den sehr klein bauenden Zahnringpumpen überproportional stark beeinträchtigen.However, if the adjacent components are "strained" so that between them still tolerance-related gaps remain, then occur with increasing operating temperature on the wheelset frontal leakage losses, which, as already explained, affect the efficiency of the very small-built gerotor pumps disproportionately strong.
Um nun diese, entweder aus Leckageverlusten resultierenden, oder aus der "Verspannung" der Elastdomerdichtungen gegen den Laufradsatz resultierenden Wirkungsgradverluste zu reduzieren, muss zur Axialspaltkompensation, insbesondere bei sehr klein bauenden Zahnringpumpen, zwangsläufig die Fertigungsgenauigkeit und damit der Herstellungsaufwand überproportional erhöht werden.Now these, either from leakage losses resulting, or from the "strain" of Elastdomerdichtungen against the wheelset To reduce the resulting efficiency losses, the production accuracy and thus the production cost must be increased disproportionately for Axialspaltkompensation, especially in very small-built gerotor pumps.
Zur Axialspaltkompensation werden im Stand der Technik auch beidseitig dem Pumpenlaufradsatz benachbarte, axial verschiebbare Dichtplatten eingesetzt, auf deren dem Pumpenlaufradsatz abgewanden Seite von Elastdomerdichtungen umschlossene Hohlräume angeordnet sind, die dann im Betriebszustand der Pumpe druckbeaufschlagt werden.For Axialspaltkompensation be used on both sides of the Pumpenlaufradsatz adjacent, axially displaceable sealing plates in the art on which the Pumpenlaufradsatz abgewanden side of Elastdomerdichtungen cavities are arranged, which are then pressurized in the operating state of the pump.
Doch bei klein bauenden Zahnringpumpen ist gerade diese Lösung mit beidseitig des Pumpenlaufradsatzes benachbart angeordneten, axial verschiebbaren Dichtplatten nicht geeignet, um mit vertretbaren Fertigungskosten einen optimalen Wirkungsgrad zu erzielen.However, in the case of small-diameter gerotor pumps, this solution with adjoining the pump impeller set on both sides, axially displaceable sealing plates are not suitable for achieving optimum efficiency with justifiable manufacturing costs.
Der Einsatz dieser axial verschiebbaren Dichtplatten mit Druckbeaufschlagung eines von Elastdomerdichtungen umschlossenen, zwischen den benachbarten Bauteilen angeordneten Hohlraumes bewirkt jedoch auch gleichzeitig, dass zudem der Hohlrauminnendruck auch randseitig auf die Elastdomerdichtung einwirkt, so dass mit kleiner werdender Pumpenbaugröße der axiale Toleranzausgleich mit druckbeaufschlagten Elastdomerdichtungen bewirkt, dass das Verhältnis der "Elastdomerdichtungskraft" zur hydraulisch generierten Kraft immer ungünstiger wird, und dass mit kleiner werdender Baugröße der Zahnringpumpen (z.B. bei Gerotorpumpen mit einem Fördervolumenstrom von ca. 8 l/min und Außenabmessungen von ca. 40 mm x 40 mm x 40 mm) die nicht kalkulierbaren "Störkräfte" überwiegen und dann den Gesamtwirkungsgrad Pumpe dominierend beeinflussen.However, the use of these axially displaceable sealing plates with pressurization of a Elastomers sealed enclosing, arranged between the adjacent components cavity also causes the same time that the cavity internal pressure also acts on the edge edge of the Elastdomerdichtung, so that causes with decreasing pump size of the axial tolerance compensation with pressurized Elastdomerdichtungen that the ratio of the "Elastdomerdichtungskraft" to the hydraulically generated force is always unfavorable, and that with smaller size of the gerotor pumps (eg in gerotor pumps with a flow rate of about 8 l / min and external dimensions of about 40 mm x 40 mm x 40 mm) outweigh the incalculable "disturbing forces" and then dominate the overall efficiency of the pump.
Der Erfindung liegt daher die Aufgabe zugrunde, eine Zahnringpumpe zu entwickeln, die die vorgenannten Nachteile des Standes der Technik beseitigt, und die insbesondere bei kleinen, d.h. auch bei im Außendurchmesser des Gehäuses klein bauenden Pumpenaggregaten, welche vorzugsweise elektromotorisch betrieben und als Baukastenpumpen derart gefertigt werden, dass weitestgehend in der Geometrie gleiche Gehäuserohteile verwendet werden, eingesetzt werden kann, wobei die zu entwickelnde Zahnringpumpe zudem entsprechend des jeweiligen Kundenwunsches in den Steuerzeiten der Pumpe fertigungstechnisch einfach modifizierbar sei soll, so dass stets ein strömungstechnisch optimales Verhalten der erfindungsgemäßen Pumpe gewährleistet ist, dabei soll die zu entwickelnde Zahnringpumpe auch in sehr kleinen Pumpenbaugrößen sehr kostengünstig herstellbar sein, und zudem auch bei Verwendung von sehr kostengünstigen Baugruppen, wie Pumpengehäusen aus Aluminium und Pumpenrädern aus Stahl, selbst unter extremen Einsatzbedingungen, wie beispielsweise als Ölpumpe in Verbindung mit einem Verbrennungsmotor, d.h. über den Temperaturarbeitsbereich derartiger Ölpumpe, von ca. - 40 °C bis ca. + 160 °C hinweg, stets einen optimalen Axialspalt (und dadurch minimale Verluste) gewährleisten, so dass über den gesamten Drehzahl- und Temperaturbereich derartiger Pumpe hinweg stets ein hoher Gesamtwirkungsgrad gewährleistet ist, wobei die zu entwickelnde Zahnringpumpe selbstverständlich im gesamten Drehzahl- und Temperaturbereich stets zuverlässig, robust und störunanfällig arbeiten soll.The invention is therefore based on the object to develop a gerotor pump, which eliminates the aforementioned disadvantages of the prior art, and in particular at small, ie also in the outer diameter of the Housing small pumping units, which are preferably operated by electric motor and manufactured as a modular pump that largely the same Gehäuserohteile be used in geometry, can be used, wherein the to be developed ring gear pump also according to the customer's request in the timing of the pump manufacturing technology should be easily modifiable , so that always a fluidically optimal behavior of the pump according to the invention is ensured, it should be very inexpensive to produce the ring gear pump to be developed even in very small pump sizes, and also with the use of very cost-effective components, such as pump housings made of aluminum and pump steel, even under extreme operating conditions, such as an oil pump in conjunction with an internal combustion engine, ie over the temperature working range of such oil pump, from about - 40 ° C to about + 160 ° C away, always e ensure optimum axial gap (and thereby minimal losses), so over the entire speed and temperature range of such pump away always a high overall efficiency is guaranteed, the developing ring gear pump is of course always reliable throughout the speed and temperature range, robust and susceptible to interference ,
Erfindungsgemäß wird diese Aufgabe durch eine Zahnringpumpe mit den Merkmalen des Hauptanspruches der Erfindung gelöst.According to the invention this object is achieved by a gerotor pump with the features of the main claim of the invention.
Vorteilhafte Ausführungen, Einzelheiten wie auch weitere Merkmale der Erfindung ergeben sich aus den Unteransprüchen sowie der nachfolgenden Beschreibung des erfindungsgemäßen Ausführungsbeispieles in Verbindung mit den Zeichnungen zur erfindungsgemäßen Lösung.Advantageous embodiments, details and other features of the invention will become apparent from the dependent claims and the following description of the embodiment of the invention in conjunction with the drawings for the solution according to the invention.
Nachfolgend soll nun die Erfindung an Hand eines Ausführungsbeispieles in Verbindung mit fünf Darstellungen näher erläutert werden.Below, the invention will now be explained in more detail with reference to an embodiment in conjunction with five representations.
Es zeigen dabei die
- Figur 1 :
- eine Explosivdarstellung einer erfindungsgemäßen Zahnringpumpe in der Bauform einer Gerotorpumpe in einer perspektivischen Ansicht von oben, in Längsrichtung der
Antriebswelle 7 aus der Richtung desGehäusedeckels 5; - Figur 2 :
- eine Explosivdarstellung der erfindungsgemäßen Zahnringpumpe in der Bauform einer Gerotorpumpe in einer perspektivischen Ansicht von oben und aus der Richtung des
Pumpengehäuses 1; - Figur 3 :
- eine Explosivdarstellung der erfindungsgemäßen Zahnringpumpe in der Bauform einer Gerotorpumpe in einer perspektivischen Ansicht von vorn, aus Richtung der
Antriebswelle 7 und desGehäusedeckels 5; - Figur 4 :
- eine Zusammenstellungszeichnung der erfindungsgemäßen Zahnringpumpe in der Bauform einer Gerotorpumpe in der Vorderansicht (mit Blick auf den Deckel) mit der Darstellung der Schnittführung für
;Figur 5 - Figur 5:
- eine Zusammenstellungszeichnung der erfindungsgemäßen Zahnringpumpe in der Bauform einer Gerotorpumpe, in der Seitenansicht, im Teilschnitt mit der Schnittführung gemäß
.Figur 4
- FIG. 1:
- an exploded view of a gerotor pump according to the invention in the form of a gerotor pump in a perspective view from above, in the longitudinal direction of the
drive shaft 7 from the direction of thehousing cover 5; - FIG. 2:
- an exploded view of the ring gear pump according to the invention in the design of a gerotor pump in a perspective view from above and from the direction of the
pump housing 1; - FIG. 3:
- an exploded view of the ring gear pump according to the invention in the design of a gerotor pump in a perspective view from the front, from the direction of the
drive shaft 7 and thehousing cover 5; - FIG. 4:
- an assembly drawing of the gerotor pump according to the invention in the design of a gerotor pump in the front view (with a view of the lid) with the representation of the cutting guide for
FIG. 5 ; - FIG. 5:
- an assembly drawing of the ring gear pump according to the invention in the design of a gerotor pump, in the side view, in partial section with the cutting guide according to
FIG. 4 ,
Die in den
Erfindungswesentlich ist in diesem Zusammenhang, dass im Pumpengehäuse 1 zwischen dem Laufradsatz 8 und der Stirnwand 3 des Arbeitsraumes 2 verdrehsicher ein in Richtung der Antriebswelle 7 verschiebbar gelagerter Portträger 18 angeordnet ist, in dem sowohl eine Saugniere 12 wie auch eine Druckniere 13 angeordnet ist und beide jeweils voneinander getrennt den Portträger 18 über die gesamte Dicke des Portträgers 18, diesen in Form einer mit der Saugniere 12 verbundenen Einströmkammer 19, wie auch andererseits einer mit der Druckniere 13 verbundenen Ausströmströmkammer 20 durchdringen, wobei die Dicke des Portträgers 18 in etwa der Dicke des Laufradsatzes 8 entspricht und diese aber auch um bis zu 20% überragen kann, und der Wärmeausdehnungskoeffizient des Portträgers 18 etwa um 70% bis 120% über dem Wärmeausdehnungskoeffizienten des Pumpengehäuses 1 liegt, und dass die drehfest mit dem Innenrotor 9 verbundene Antriebswelle 7 keinesfalls in den Portträger 18 hineinragt, (bzw. in diesem gelagert ist). Kennzeichnend ist weiterhin, dass der Portträger 18 an der dem Laufradsatz 8 benachbarten Stirnseite verschleißfest ausgebildet, bzw. verschleißfest beschichtet ist, oder dass zwischen dem Laufradsatz 8 und dem Portträger 18 ein drehfest mit dem Portträger 18 verbundenes Gleitblech 25 angeordnet ist, wodurch zwischen dem Laufradsatz 8 und dem Portträger 18 neben den Reibungsverlusten auch der Verschleiß minimiert wird, so dass mittels der erfindungsgemäßen Lösung eine lange Lebensdauer bei hohem Wirkungsgrad gewährleistet werden kann.Essential to the invention is in this context that in the
In der
Wesentlich ist dabei auch, dass im Gleitblech 25 ebenfalls eine der Saugniere 12 des Portträger 18 zugeordnete Saugniere 12 und auch eine der Druckniere 13 des Portträger 18 zugeordnete Druckniere 13 angeordnet sind, so dass ein ungehinderter Durchtritt des Fördermediums "durch das Gleitblech hindurch" gegeben ist.It is also essential that in the
Vorteilhaft ist in diesem Zusammenhang auch, wenn im Gleitblech 25 eine Wellenführungsbohrung 28 angeordnet ist.It is also advantageous in this context if a shaft guide bore 28 is arranged in the
Durch die Einbringung der Wellenführungsbohrung 28 wird das Gleitblech 25 in seiner Biegesteifigkeit reduziert, dadurch ist ein besseres Anlegen und Anpassen an den Laufradsatz 8 und den Portträger 18 möglich. Gleichzeitig kann mit der Wellenführungsbohrung 28 ein geringfügiger Überstand der Antriebswelle 7 erreicht werden.By introducing the shaft guide bore 28, the
Erfindungsgemäß ist auch, dass der Gehäusedeckel 5 über im Pumpengehäuse 1 angeordnete Positionierstifte 21 und am Gehäusedeckel 5 zugeordnete Positionierkerben 22 verdrehsicher am Pumpengehäuse 1, und der Portträger 18 mittels einer exzentrisch im Portträger 18 angeordneten Stiftführungsbohrung 24 und einem in der Stirnwand 3 des Arbeitsraumes 2 der Stiftführungsbohrung 24 zugeordnet angeordneten Führungsstift 23 axial verschiebbar im Pumpengehäuse 1 gelagert ist.According to the invention is that the
Diese erfindungsgemäße Anordnung ermöglicht in Verbindung mit der erfindungsgemäßen Anordnung des erfindungsgemäßen Portträgers 18 in axialer Richtung neben dem Laufradsatz 8 der erfindungsgemäßen Zahnringpumpe, da der Portträger 18 den Zu- und Abströmbereich der Pumpe in seiner funktionellen Geometrie abbildet, dass in Verbindung mit der erfindungsgemäßen, äußeren zylindrischen Geometrie des Portträgers 18 dieser in gewissen Grenzen problemlos im Pumpengehäuse 1 verdreht, und exakt, z.B. durch Führungsstifte 23 im Pumpengehäuse 1, lagesicher positioniert werden kann.This arrangement of the invention allows in connection with the inventive arrangement of the
Somit können mittels des erfindungsgemäßen Einsatzes des erfindungsgemäßen Portträgers 18, durch die oben beschriebene drehwinkelbedingte Anpassung erstmals problemlos, einfach und zudem sehr kostengünstig die Steuerzeiten der Pumpe auf den jeweiligen Einsatzfall der Pumpe strömungstechnisch optimiert werden.Thus, by means of the inventive use of the port support 18 according to the invention by the rotation angle-related adaptation described above for the first time easily, easily and also very cost-effective, the timing of the pump to the particular application of the pump can be optimized fluidically.
Zudem dient der erfindungsgemäße Portträger 18 aber auch dazu gleichzeitig eine Optimierung des Axialspaltes zu gewährleisten.In addition, the
Hierzu werden für den Portträger 18 erfindungsgemäß Werkstoffe eingesetzt, deren Wärmeausdehnungskoeffizient möglichst den doppelten Wert des Wärmeausdehnungskoeffizienten des Gehäusewerkstoffes aufweist.For this purpose, materials are used according to the invention for the
Die Dicke des Portträgers 18 entspricht dabei in etwa der Dicke des Laufradsatzes 8.The thickness of the
Um jedoch bei entsprechend gewünschtem axialem Grundspiel zwischen dem Laufradsatz 8 und dem Portträger 18 eine Überkompensation des Axialspaltes zu bewirken, kann die Dicke des Portträgers 18 beispielsweise auch auf ca. 120 % der Dicke des Laufradsatzes 8 erhöht werden.However, in order to effect an overcompensation of the axial gap with correspondingly desired axial basic play between the
Im vorliegenden Ausführungsbeispiel, mit einem Pumpengehäuse 1 aus Aluminium, wurden als Werkstoffe für den Portträger 18 modifizierte Duroplaste eingesetzt, wobei die Dicke des Portträgers selbstverständlich in Abhängigkeit von dem jeweils für den Portträger 18 eingesetzten Grundmaterial variiert.In the present embodiment, with a
Für den Portträger 18 können aber auch speziell modifizierte Duroplastwerkstoffe eingesetzt werden, die z.B. durch gezielte Beimengung von reibungsreduzierenden Stoffen das Laufverhalten des benachbart angeordneten Laufradsatzes deutlich verbessern.For the
Erfindungsgemäß ist es auch, wenn der Portträger 18 aus gesinterten und harzgebundenen Natriumchloriden gefertigt wird.It is also according to the invention if the
Durch die Verwendung von gesinterten und harzgebundenen Natriumchloriden zur Herstellung der Portträger 18 kann eine vorgegebene axiale Wärmeausdehnung eines Aluminiumpumpengehäuses mit einem Wärmeausdehnungskoeffizienten für Aluminium von etwa 23 x 10-6 K-1 durch einen Portträgers aus gesinterten und harzgebundenen Natriumchloriden, bei einem Wärmeausdehnungskoeffizienten für Natriumchlorid von etwa 40 ... 44 x 10-6 K-1, effektiv, d.h. mit relativ geringer Dickenabmessung eines aus gesinterten und harzgebundenen Natriumchloriden gefertigten Portträgers 18 kompensiert werden.By using sintered and resin bound sodium chlorides to form the port supports 18, a given axial thermal expansion of an aluminum pump housing having an aluminum thermal expansion coefficient of about 23x10 -6 K -1 can be achieved through a sintered and resin bonded sodium chloride port support having a thermal expansion coefficient of sodium chloride of about 40 ... 44 x 10 -6 K -1 , effectively, ie, compensated for with a relatively small thickness of a
Mittels der erfindungsgemäßen Lösung werden somit bei Einsatz unterschiedlicher Werkstoffe für Gehäuse und Rotor stets die von der jeweiligen Betriebstemperatur abhängenden Axialspalte im gesamten Temperaturarbeitsbereich der Pumpe optimiert, d.h. es wird kostengünstig eine optimale, dynamische Axialspaltkompensation gewährleistet.By means of the solution according to the invention, therefore, when using different materials for housing and rotor, the axial gaps depending on the respective operating temperature are always optimized in the entire temperature working range of the pump, i. it is cost effective to ensure optimal dynamic axial gap compensation.
In Abhängigkeit von der Wahl des Werkstoffes für den Portträger 18 in Verbindung mit der Dimensionierung der Dicke des Portträger 18 wird es auch möglich, die Axialspalte bei niedrigen Temperaturen größer zu gestalten und bei höheren Temperaturen durch deutlich größere Längenausdehnung des Portträgers 18 das Axialspiel zu verkleinern.Depending on the choice of material for the
Eine derartige Tendenz "unterstützt" das natürliche Viskositätsverhalten von diversen Ölsorten und führt somit zu einer insgesamt wesentlich effizienter arbeitenden Pumpe.Such a tendency "supports" the natural viscosity behavior of various types of oil and thus leads to an overall much more efficient working pump.
Ein weiterer Vorteil der erfindungsgemäßen Lösung besteht auch darin, dass bei der hier vorgestellten erfindungsgemäßen Axialspaltkompensation der Laufradsatz 8 frei von axialen Belastungen bleibt, so dass die dadurch auftretenden Reibmomente vermieden werden, die zwangsläufig stets zu Wirkungsgradverlusten führen.Another advantage of the solution according to the invention consists in the fact that in the Axialspaltkompensation invention presented here, the
Der erfindungsgemäß gewollte temperaturkompensierende Effekt des erfindungsgemäß in axialer Richtung neben dem Laufradsatz 8 platzierten erfindungsgemäßen Portträgers 18 bewirkt bei Temperaturerhöhung und einem daraus resultierenden axialen Wachstum des Arbeitsraumes 2 im Pumpengehäuse 1, in dem der Laufradsatz 8 und der Portträgers 18 untergebracht sind, dass durch eine deutlich höhere Wärmeausdehnung des erfindungsgemäßen Portträgers 18, das axiale Wachstum des Arbeitsraumes 2 unter gleichzeitiger Beachtung des Wachstums des Laufradsatzes 8 ausgeglichen wird.The inventively desired temperature-compensating effect of the inventively placed in the axial direction next to the
Bei überkompensiertem Längenausgleich besteht erfindungsgemäß die Möglichkeit, das axiale Grundspiel bei tiefen Temperaturen relativ hoch zu legen, und dadurch dem Viskositätsverhalten des zu fördernden Mediums entgegenzukommen, um so die Antriebsleistung im niedrigen Temperaturbereich der erfindungsgemäßen Zahnringpumpe zu reduzieren, und so den Wirkungsgrad auch in diesem Betriebspunkt deutlich zu erhöhen. Dabei ermöglicht die erfindungsgemäße Lösung infolge der erfindungsgemäßen Anordnung des erfindungsgemäßen Portträgers 18 in Verbindung mit all den bereits beschriebenen Wirkungen zudem gleichzeitig auch die Herstellung von im Außendurchmesser des Gehäuses klein bauenden Pumpenaggregaten.In the case of overcompensated length compensation, it is possible according to the invention to set the axial basic play relatively low at low temperatures, and thereby to accommodate the viscosity behavior of the medium to be conveyed, in order to reduce the drive power in the low temperature range of the ring gear pump according to the invention, and thus also the efficiency in this operating point to increase significantly. At the same time, the solution according to the invention, as a result of the arrangement according to the invention of the
- 11
- Pumpengehäusepump housing
- 22
- Arbeitsraumworking space
- 33
- Stirnwandbulkhead
- 44
- Dichtungpoetry
- 55
- Gehäusedeckelhousing cover
- 66
- Pumpenlagerpump bearings
- 77
- Antriebswelledrive shaft
- 88th
- Laufradsatzwheelset
- 99
- Innenrotorinner rotor
- 1010
- Außenrotorouter rotor
- 1111
- Rotorlagerungrotor bearing
- 1212
- Saugnieresuction kidney
- 1313
- Drucknierepressure kidney
- 1414
- Saugkanalsuction
- 1515
- Sauganschlusssuction
- 1616
- Druckkanalpressure channel
- 1717
- Druckanschlusspressure connection
- 1818
- Portträgerport carrier
- 1919
- Einströmkammerinflow
- 2020
- Ausströmkammeroutflow
- 2121
- Positionierstiftpositioning
- 2222
- Positionierkerbepositioning groove
- 2323
- Führungsstiftguide pin
- 2424
- StiftführungsbohrungPin guide bore
- 2525
- Gleitblechsliding
- 2626
- Rastnaselocking lug
- 2727
- Rastnutlocking groove
- 2828
- WellenführungsbohrungWave guide bore
Claims (7)
- Gear ring pump with a pump housing (1), with a working space (2) in the pump housing (1) with intake and / or outlet areas located in the front wall (3) of the working space (2) in the pump housing (1) a sealed housing cover (5) located at the pump housing (1) by using a seal (4), with a rotatable drive shaft (7) mounted on a pump bearing (6) in the pump housing (1) where an impeller mechanism (8) is located, consisting of an interior rotor (9) with external gear teeth connected rotatably with the drive shaft (7) and an exterior rotor (10) with internal gear teeth, which is mounted rotatably in a rotor bearing (11) in the cylindrical working space (2) of the pump housing (1) in such a way that the teeth of the interior rotator (9) located off-centre to the exterior rotor (10) mesh in certain areas with the teeth of the exterior rotor (10), with suction manifold(s) (12) located on one or both sides in the suction area of the impeller mechanism (8) and with pressure manifold(s) (13) located on one or both sides in the pressure area of the impeller mechanism (8), whereby the suction manifold(s) (12) is / are connected via one suction duct (14) / suction ducts (14) located in the pump housing (1) with at least one suction connection (15) located at the pump housing (1) and that the pressure manifold(s) (13) is / are connected via one pressure duct (16) / pressure ducts (16) located in the pump housing (1) with at least one pressure connection (17) located at the pump housing (1) and that the liquid to be pumped from the suction connection (15) through the impeller mechanism (8) located in the pump housing (1) is forced into the pressure connection (17), characterized by the fact,- that the pump bearing (6) is located in the housing cover (5) and- that a mounted portal support (18) is located in the pump housing (1) between the impeller mechanism (8) and the front wall (3) of the working space (2) so that it is twist-free and can be slid in the direction of the drive shaft (7) where both a suction manifold (12) and also a pressure manifold (13) are located and where both penetrate the portal support (18) completely separate from each other over the entire thickness of the portal support (18) in the form of an inflow chamber (19) connected with the suction manifold(s) (12) and an outflow chamber (20) connected with the pressure manifold (13), whereby the thickness of the portal support (18) either corresponds to the thickness of the impeller mechanism (8), or extends beyond the thickness of the impeller mechanism (8) by up to 20%, whereby the coefficient of thermal expansion of the portal support (18) is 70% to 120% more than the coefficient of thermal expansion of the pump housing (1) and- that the drive shaft (7) connected twist-free with the interior rotor (9) does not project in any way at all into the portal support (18) and- that the portal support (18), designed to be wear resistant or coated on the front side adjacent to the impeller mechanism (8) and / or that a twist-free sliding plate (25), connected with portal support is located between the impeller mechanism (8) and the portal support (18).
- Gear ring pump according to claim 1, characterized by the fact that the housing cover (5) is mounted by a positioning pin (21) located in the pump housing (1) and associated positioning notches (22) at the housing cover (5) on the pump housing (1) so that it is twist-free and that the portal support (18) is mounted at the pump housing (1) by using a pin guide hole (24) located eccentrically in the portal support (18) and a guide pin (23) associated with the pin guide hole (24) in the front wall (3) of the working space (2) so that it can be moved axially.
- Gear ring pump according to claim 1, characterized by the fact that the portal support (18) is made out of modified Duroplast.
- Gear ring pump according to claim 1, characterized by the fact that the portal support (18) is made out of sintered and resin-coated sodium chloride.
- Gear ring pump according to claim 1 with a sliding plate (25) located between the impeller mechanism (8) and the portal support (18), characterized by the fact that a suction manifold (12) associated with the suction manifold (12) of the portal support (18) and also a pressure manifold (13) associated with the pressure manifold (13) of the portal support (18) are also arranged in the sliding plate (25).
- Gear ring pump according to claim 5, characterized by the fact that a locking catch (26) is located in the sliding plate (25) to form a positive, locking operative connection with a locking slot (27) located at the portal support (18).
- Gear ring pump according to claim 5, characterized by the fact that a shaft guide hole (28) is located in the sliding plate (25).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102011107157A DE102011107157B4 (en) | 2011-07-14 | 2011-07-14 | Annular gear pump |
PCT/DE2012/000650 WO2013007233A1 (en) | 2011-07-14 | 2012-06-27 | Gear ring pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2732164A1 EP2732164A1 (en) | 2014-05-21 |
EP2732164B1 true EP2732164B1 (en) | 2015-09-09 |
Family
ID=46651294
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12746262.0A Not-in-force EP2732164B1 (en) | 2011-07-14 | 2012-06-27 | Gear ring pump |
Country Status (5)
Country | Link |
---|---|
US (1) | US9309885B2 (en) |
EP (1) | EP2732164B1 (en) |
DE (1) | DE102011107157B4 (en) |
ES (1) | ES2553790T3 (en) |
WO (1) | WO2013007233A1 (en) |
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Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107636310A (en) * | 2015-05-20 | 2018-01-26 | 凯斯帕公司 | Gear pump and its implementation |
ITUB20159726A1 (en) * | 2015-12-22 | 2017-06-22 | Bosch Gmbh Robert | PUMPING GROUP FOR FUEL SUPPLEMENTATION, PREFERABLY GASOIL, TO AN INTERNAL COMBUSTION ENGINE |
CN109969259B (en) * | 2017-12-28 | 2021-06-18 | 比亚迪股份有限公司 | Electric oil pump assembly and vehicle with same |
CN111183287B (en) | 2018-02-14 | 2022-04-01 | 斯泰克波尔国际工程产品有限公司 | Cycloid pump with mandrel |
DE102018210415A1 (en) * | 2018-05-08 | 2019-11-14 | Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg | Electric fluid pump and motor vehicle transmission |
USD923060S1 (en) * | 2018-08-09 | 2021-06-22 | Psg Germany Gmbh | Pump |
US10247295B1 (en) * | 2018-10-22 | 2019-04-02 | GM Global Technology Operations LLC | Transfer case oil pump assembly |
USD966342S1 (en) * | 2020-02-07 | 2022-10-11 | Pedrollo S.P.A. | Electric pump |
USD960203S1 (en) * | 2020-09-28 | 2022-08-09 | Hugo Vogelsang Maschinenbau Gmbh | Pump for liquids |
US11661938B2 (en) * | 2021-08-31 | 2023-05-30 | GM Global Technology Operations LLC | Pump system and method for optimized torque requirements and volumetric efficiencies |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
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US3128707A (en) * | 1960-03-11 | 1964-04-14 | Robert W Brundage | Multiple discharge hydraulic pump |
GB943624A (en) | 1960-10-05 | 1963-12-04 | Doulton & Co Ltd | Permeable plastic materials |
US3805526A (en) * | 1972-11-03 | 1974-04-23 | Aplitec Ltd | Variable displacement rotary hydraulic machines |
JPH07208348A (en) | 1994-01-27 | 1995-08-08 | Brother Ind Ltd | Pump |
DE19720286A1 (en) | 1997-05-15 | 1998-11-19 | Winter Gmbh | Plastic water pump casing for vehicle engine comprising two injection moulded, tempered, duroplastic halves |
US6769889B1 (en) * | 2003-04-02 | 2004-08-03 | Delphi Technologies, Inc. | Balanced pressure gerotor fuel pump |
DE10331979A1 (en) | 2003-07-14 | 2005-02-17 | Gkn Sinter Metals Gmbh | Pump with optimized axial clearance |
US7614227B2 (en) * | 2006-08-04 | 2009-11-10 | Briggs And Stratton Corporation | Rotary control valve for a hydrostatic transmission |
DE102008054758A1 (en) | 2008-12-16 | 2010-06-17 | Robert Bosch Gmbh | delivery unit |
-
2011
- 2011-07-14 DE DE102011107157A patent/DE102011107157B4/en not_active Expired - Fee Related
-
2012
- 2012-06-27 ES ES12746262.0T patent/ES2553790T3/en active Active
- 2012-06-27 EP EP12746262.0A patent/EP2732164B1/en not_active Not-in-force
- 2012-06-27 WO PCT/DE2012/000650 patent/WO2013007233A1/en active Application Filing
- 2012-06-27 US US14/232,007 patent/US9309885B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
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EP2732164A1 (en) | 2014-05-21 |
DE102011107157A1 (en) | 2013-01-17 |
US9309885B2 (en) | 2016-04-12 |
DE102011107157B4 (en) | 2013-02-28 |
US20140154125A1 (en) | 2014-06-05 |
WO2013007233A1 (en) | 2013-01-17 |
WO2013007233A4 (en) | 2013-03-07 |
ES2553790T3 (en) | 2015-12-11 |
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