EP0831232B1 - Gear pump - Google Patents
Gear pump Download PDFInfo
- Publication number
- EP0831232B1 EP0831232B1 EP97114968A EP97114968A EP0831232B1 EP 0831232 B1 EP0831232 B1 EP 0831232B1 EP 97114968 A EP97114968 A EP 97114968A EP 97114968 A EP97114968 A EP 97114968A EP 0831232 B1 EP0831232 B1 EP 0831232B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- housing
- drive shaft
- feed pump
- gearwheel
- wall
- 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.)
- Expired - Lifetime
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
-
- 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
Definitions
- the invention relates to a feed pump according to the genus of Claim 1.
- Such a feed pump is known from FR-A-1 299 342.
- This Feed pump has a rotatingly driven in a pump chamber Pair of intermeshing gears on which a pumped medium an intake space connected to a storage tank along one between the end face of the gears and the peripheral wall of the Promote pumping chamber formed delivery channel in a pressure chamber.
- the Gears are each in one piece protruding into the housing mounted with the housing trained housing pin.
- a first one Housing pin has an axial through hole into which a drive shaft protrudes.
- the drive shaft protrudes from hers end of the housing out of the housing pin and is by means of a coupling member in the form of a wedge with a first on the first housing pin mounted gear rotatably connected.
- the Drive shaft can be positively connected via the wedge connection be connected to the first gear. Since the first gear on the first housing pin is mounted and by its connection with the drive shaft the torque is transmitted directly to it can have problems with the storage and drive of the first Gear due to manufacturing tolerances.
- the feed pump according to the invention with the features according to claim 1 has the advantage that the transmission of the torque from the drive shaft to the first gear through that as Coupling disc trained coupling member takes one Compensation of manufacturing tolerances enabled.
- the coupling member pressed into the gear preferably has a central recess into which a correspondingly shaped, axially protruding from the drive shaft shaped pin engages.
- the coupling member pressed onto the drive shaft preferably has three radially projecting projections (pegs) on the circumference, which engage in corresponding recesses in the internal gear diameter with little play.
- flats or recesses for example in the form of a round groove, are provided on the housing bearing journal, in which the lubricant (preferably fuel) can collect and then get into the plain bearing more easily, these flattenings preferably on the side of the housing journal remote from the pressure (suction side) are arranged.
- a radial bore in the gear wheel which opens into the inner wall surface from the tooth base between two teeth, also improves the penetration of the lubricant into the slide bearing, since the bore passes through the pressure zone (pressure chamber) with each gear wheel rotation, so that the lubricant is actively pressed into the slide bearing becomes.
- the feed pump according to the invention as a fuel feed pump for delivering fuel from a storage tank to a fuel injection pump of an internal combustion engine is particularly suitable, but can also be used for delivering other liquid media. Further advantages and advantageous embodiments of the subject matter of the invention can be found in the description, the drawing and the claims.
- FIG. 1 shows a view of the closed cover side of the feed pump with the representation of the position of the gears and the inlet and outlet openings
- FIG. 2 shows a sectional view of the first embodiment of the feed pump rotated by 90 ° with respect to FIG. 1, in which the coupling member is pressed onto the drive shaft
- Figure 3 is a partial view of the first gear from Figure 2 in a first view
- Figure 4 shows the gear of Figure 3 in a second sectional view
- Figure 5 is a partial view of the coupling member from Figure 2
- the 6 shows a second embodiment of the feed pump, in which the coupling member is pressed into the inner wall of the gearwheel
- FIG. 1 shows a view of the closed cover side of the feed pump with the representation of the position of the gears and the inlet and outlet openings
- FIG. 2 shows a sectional view of the first embodiment of the feed pump rotated by 90 ° with respect to FIG. 1, in which the coupling member is pressed onto the drive shaft
- Figure 3 is a partial view of
- FIG. 7 shows an individual part of the coupling member from FIG. 6, and FIG. 8 shows an enlarged detail from the gearwheels of FIGS. 2 and 6, showing the radial bore
- FIG. 9 shows a third embodiment in a simplified manner Eighth sectional view in the area of the connection gearwheel / housing bearing journal, in which a bevel is provided on the housing journal
- FIG. 10 shows a fourth exemplary embodiment analogous to the illustration in FIG. 9, in which a round groove is incorporated in the housing journal.
- the feed pump according to the invention shown in FIGS. 1 to 10 in various sections and views is inserted into a feed line (not shown) from a storage tank to a fuel injection pump for internal combustion engines.
- the first exemplary embodiment of the feed pump shown in FIGS. 1 and 2 has a pump chamber 3 in its housing 1, in which a rotatingly driven pair of meshing gears is arranged.
- a first gearwheel 5, which is located in the exemplary embodiment, is rotatably driven by means of an external drive element 7 (not shown in more detail) and transmits this rotary movement via a spur toothing to a second gearwheel 9 meshing with the first gearwheel 5.
- the gearwheels 5, 9 thereby divide the pump chamber 3 their tooth engagement in two sections, of which a first section forms an intake chamber 11 and a second section forms a pressure chamber 13.
- the suction chamber 11 is connected to the pressure chamber 13 via a delivery channel 15 formed between the tooth grooves on the end faces of the first and second gear wheels 5, 9 and the upper and lower peripheral wall of the pump chamber 3.
- the suction chamber 11 and the pressure chamber 13 each have a connection opening in the wall of the pump housing 1, via which the suction chamber 11 is connected to a suction line, not shown, from the storage tank and the pressure chamber 13 to a delivery line, also not shown, to the suction chamber of the fuel injection pump.
- connection opening in the suction chamber 11 forms an inlet opening 17 and the connection opening in the pressure chamber 13 forms an outlet opening 19, which are arranged in a housing cover 21 which closes the pump chamber 3.
- the gear wheels 5, 9 are mounted on housing pins which project into the interior of the pump housing 1 and which are formed in one piece with the pump housing 1.
- a first housing pin 23 located at the bottom forms a bearing pin receiving the first gear wheel 5
- a second housing pin 25 located at the top forms a bearing pin receiving the second gear wheel 9.
- the first housing pin 23 has an axial through bore 27, in which a drive shaft 29 is guided, which is connected in a rotationally locking manner to the drive element 7 at its end facing away from the housing cover 21.
- the drive shaft 29 protrudes from the bore 27 of the first housing pin 23 into a coupling member 31 to the first gear 5, via which the rotary movement of the drive shaft 29 is transmitted to the gear 5.
- 5 in the first exemplary embodiment is designed as a clutch disc 31, which is pressed onto the drive shaft 29 with its radial inner wall and which preferably has three radially projecting projections 33 on its outer circumference. With these formations 33, the clutch disc protrudes into corresponding recesses 35 on the inner wall surface of the first gearwheel 5 shown enlarged in FIGS. 3 and 4 and thus establishes a positive connection between the clutch disc 31 and the first gearwheel 5.
- the clutch disc 231 shown enlarged in FIG. 7, is now pressed with its outer circumferential wall into the inner wall diameter of the first gear 5 at its end on the cover side.
- the clutch disc 231 consists of a metal, preferably steel ring 41, in the interior of which a disk-shaped elastomer part 37 is pressed.
- a preferably square-shaped recess 39 is incorporated, into which a correspondingly shaped pin 43 protrudes axially from the drive shaft 29 and thus establishes a positive connection between the clutch disc 231 and the drive shaft 29.
- a radial bore 51 is provided in both gear wheels 5, 9, which starts from the tooth base 53 extends between two adjacent teeth of the gear wheels 5, 9 to the inner end wall 55 of the gear wheels 5, 9 and thus supplies the slide bearing points 57 with lubricant.
- a flattening 61 is also provided on the housing pin 25 in the third exemplary embodiment shown in a detail in FIG. 9, which is arranged on the side of the housing pin 25 facing away from the pressure chamber 13 of the feed pump and in that can collect the lubricant.
- FIG. 10 shows a fourth exemplary embodiment analogous to FIG. 9, in which, instead of the flat 61, a round-groove-shaped recess 63 is arranged on the side of the housing bearing journal 25 facing away from the pressure chamber, in which the lubricant can collect.
- the first housing pin 23, which is designed as a hollow axis, likewise has a flattened portion 61 or recess 63 on its suction chamber side 11, in a manner not shown, analogous to FIGS. 9 and 10.
- the feed pump according to the invention works in the following way.
- the drive shaft 29 is preferably driven to rotate in proportion to the speed of an internal combustion engine to be supplied.
- the drive shaft 29 transmits the rotary movement via the coupling member 31, (clutch disc 231) to the first gear 5, which in turn drives the second gear 9 meshing with it.
- the delivery medium preferably fuel
- the intake chamber 11 is conveyed from the intake chamber 11 along the delivery channels 15 into the pressure chamber 13. This creates a negative pressure in the intake chamber 11, which is sufficient to draw in additional fuel from the storage tank via the intake line.
- the fuel pressure built up in the pressure chamber 13 causes fuel to be delivered via the outlet opening 19 into the delivery line to the fuel injection pump.
Description
Die Erfindung betrifft eine Förderpumpe nach der Gattung des
Anspruchs 1.The invention relates to a feed pump according to the genus of
Eine solche Förderpumpe ist durch die FR-A-1 299 342 bekannt. Diese Förderpumpe weist ein in einer Pumpkammer rotierend angetriebenes Paar miteinander kämmender Zahnräder auf, die ein Fördermedium aus einem mit einem Vorratstank verbundenen Ansaugraum entlang einem zwischen der Stirnfläche der Zahnräder und der Umfangswand der Pumpkammer gebildeten Förderkanal in einen Druckraum fördern. Die Zahnräder sind jeweils auf einem in das Gehäuse ragenden, einteilig mit dem Gehäuse ausgebildeten Gehäusezapfen gelagert. Ein erster Gehäusezapfen weist dabei eine axiale Durchgangsbohrung auf, in die eine Antriebswelle hineinragt. Die Antriebswelle ragt an ihrem gehäuseinneren Ende aus dem Gehäusezapfen heraus und ist mittels eines Koppelglieds in Form eines Keils mit einem ersten auf dem ersten Gehäusezapfen gelagerten Zahnrad drehschlüssig verbunden. Die Antriebswelle kann dabei formschlüssig über die Keilverbindung mit dem ersten Zahnrad verbunden sein. Da das erste Zahnrad auf dem ersten Gehäusezapfen gelagert ist und durch dessen Verbindung mit der Antriebswelle das Drehmoment direkt auf dieses übertragen wird können sich Probleme mit der Lagerung und dem Antrieb des ersten Zahnrads aufgrund von Fertigungstoleranzen ergeben.Such a feed pump is known from FR-A-1 299 342. This Feed pump has a rotatingly driven in a pump chamber Pair of intermeshing gears on which a pumped medium an intake space connected to a storage tank along one between the end face of the gears and the peripheral wall of the Promote pumping chamber formed delivery channel in a pressure chamber. The Gears are each in one piece protruding into the housing mounted with the housing trained housing pin. A first one Housing pin has an axial through hole into which a drive shaft protrudes. The drive shaft protrudes from hers end of the housing out of the housing pin and is by means of a coupling member in the form of a wedge with a first on the first housing pin mounted gear rotatably connected. The Drive shaft can be positively connected via the wedge connection be connected to the first gear. Since the first gear on the first housing pin is mounted and by its connection with the drive shaft the torque is transmitted directly to it can have problems with the storage and drive of the first Gear due to manufacturing tolerances.
Die erfindungsgemäße Förderpumpe mit den Merkmalen gemäß Anspruch 1
hat demgegenüber den Vorteil, daß die Übertragung des Drehmoments
von der Antriebswelle auf das erste Zahnrad durch das als
Kupplungsscheibe ausgebildete Koppelglied erfolgt, das einen
Ausgleich von Fertigungstoleranzen ermöglicht. The feed pump according to the invention with the features according to
Besonders vorteilhaft ist es zudem das Koppelglied aus
elastischem Material auszubilden und so eine Übertragung von
Schwingungen und Stößen zu vermeiden, sowie eine bestimmte
Flexibilität der Verbindung zu erzielen.
Das in das Zahnrad eingepreßte Koppelglied weist dabei
vorzugsweise eine zentrale Ausnehmung auf, in die ein
entsprechend geformter, axial von der Antriebswelle
vorstehender Formzapfen eingreift.
Das auf die Antriebswelle aufgepreßte Koppelglied weist
vorzugsweise drei radial vorstehende Anformungen (Zapfen) am
Umfang auf, die mit geringem Spiel in entsprechende
Ausnehmungen im Zahnradinnendurchmesser eingreifen.
Ein weiterer Vorteil der Lagerung der Zahnräder auf nach
innen kragenden Gehäusezapfen ist die Möglichkeit einer
verbesserten Lagerschmierung. Dazu sind an den Gehäuse-Lagerzapfen
Anflachungen oder Ausnehmungen, z.B. in Form
einer Rundnut vorgesehen, in denen sich das Schmiermittel
(vorzugsweise Kraftstoff) sammeln kann und dann leichter in
das Gleitlager gelangt, wobei diese Anflachungen
vorzugsweise auf der druckabgewandten Seite (Ansaugseite)
der Gehäusezapfen angeordnet sind. Eine radiale Bohrung im
Zahnrad, die vom Zahnfuß zwischen zwei Zähnen ausgehend in
die Innenwandfläche mündet, verbessert zudem das Eindringen
des Schmiermittels in das Gleitlager, da die Bohrung bei
jeder Zahnradumdrehung die Druckzone (Druckraum) durchfährt,
so daß das Schmiermittel aktiv in das Gleitlager gepreßt
wird.
Dabei ist die Verwendung der erfindungsgemäßen Förderpumpe
als Kraftstoff-Förderpumpe zur Förderung von Kraftstoff aus
einem Vorratstank zu einer Kraftstoffeinspritzpumpe einer
Brennkraftmaschine besonders geeignet, kann aber auch zum
Fördern anderer flüssiger Medien verwendet werden.
Weitere Vorteile und vorteilhafte Ausgestaltungen des
Gegenstandes der Erfindung sind der Beschreibung, der
Zeichnung und den Ansprüchen entnehmbar.It is also particularly advantageous to form the coupling member from elastic material, thus avoiding the transmission of vibrations and shocks, and to achieve a certain flexibility in the connection.
The coupling member pressed into the gear preferably has a central recess into which a correspondingly shaped, axially protruding from the drive shaft shaped pin engages.
The coupling member pressed onto the drive shaft preferably has three radially projecting projections (pegs) on the circumference, which engage in corresponding recesses in the internal gear diameter with little play.
Another advantage of mounting the gears on inwardly projecting housing pins is the possibility of improved bearing lubrication. For this purpose, flats or recesses, for example in the form of a round groove, are provided on the housing bearing journal, in which the lubricant (preferably fuel) can collect and then get into the plain bearing more easily, these flattenings preferably on the side of the housing journal remote from the pressure (suction side) are arranged. A radial bore in the gear wheel, which opens into the inner wall surface from the tooth base between two teeth, also improves the penetration of the lubricant into the slide bearing, since the bore passes through the pressure zone (pressure chamber) with each gear wheel rotation, so that the lubricant is actively pressed into the slide bearing becomes.
The use of the feed pump according to the invention as a fuel feed pump for delivering fuel from a storage tank to a fuel injection pump of an internal combustion engine is particularly suitable, but can also be used for delivering other liquid media.
Further advantages and advantageous embodiments of the subject matter of the invention can be found in the description, the drawing and the claims.
Vier Ausführungsbeispiele der erfindungsgemäßen Förderpumpe
sind in der Zeichnung dargestellt und werden in der
folgenden Beschreibung näher erläutert.
Es zeigen die Figur 1 eine Ansicht auf die geschlossene
Deckelseite der Förderpumpe mit der Darstellung der Lage der
Zahnräder und der Ein- und Auslaßöffnungen, die Figur 2 eine
Schnittdarstellung des ersten Ausführungsbeispiels der
gegenüber der Figur 1 um 90° gedrehten Förderpumpe, bei dem
das Koppelglied auf die Antriebswelle aufgepreßt ist, die
Figur 3 eine Einzelteildarstellung des ersten Zahnrades aus
der Figur 2 in einer ersten Ansicht, die Figur 4 das Zahnrad
der Figur 3 in einer zweiten geschnittenen Darstellung, die
Figur 5 eine Einzelteildarstellung des Koppelgliedes aus der
Figur 2, die Figur 6 ein zweites Ausführungsbeispiel der
Förderpumpe, bei dem das Koppelglied in die Innenwand des
Zahnrades eingepreßt ist, die Figur 7 eine
Einzelteildarstellung des Koppelgliedes aus der Figur 6, die
Figur 8 einen vergrößerten Ausschnitt aus den Zahnrädern der
Figuren 2 und 6 mit Darstellung der Radialbohrung, die Figur
9 ein drittes Ausführungsbeispiel in einer vereinfachten
Ausschnittdarstellung im Bereich der Verbindung
ZahnradZahnrad/Gehäuselagerzapfen, bei dem am Gehäusezapfen ein
Anschliff vorgesehen ist und die Figur 10 ein viertes
Ausführungsbeispiel analog zur Darstellung der Figur 9, bei
dem am Gehäusezapfen eine Rundnut eingearbeitet ist.Four embodiments of the feed pump according to the invention are shown in the drawing and are explained in more detail in the following description.
1 shows a view of the closed cover side of the feed pump with the representation of the position of the gears and the inlet and outlet openings, FIG. 2 shows a sectional view of the first embodiment of the feed pump rotated by 90 ° with respect to FIG. 1, in which the coupling member is pressed onto the drive shaft, Figure 3 is a partial view of the first gear from Figure 2 in a first view, Figure 4 shows the gear of Figure 3 in a second sectional view, Figure 5 is a partial view of the coupling member from Figure 2, the 6 shows a second embodiment of the feed pump, in which the coupling member is pressed into the inner wall of the gearwheel, FIG. 7 shows an individual part of the coupling member from FIG. 6, and FIG. 8 shows an enlarged detail from the gearwheels of FIGS. 2 and 6, showing the radial bore FIG. 9 shows a third embodiment in a simplified manner Eighth sectional view in the area of the connection gearwheel / housing bearing journal, in which a bevel is provided on the housing journal and FIG. 10 shows a fourth exemplary embodiment analogous to the illustration in FIG. 9, in which a round groove is incorporated in the housing journal.
Die in den Figuren 1 bis 10 in verschiedenen Ausschnitten
und Ansichten dargestellte erfindungsgemäße Förderpumpe ist
in eine nicht dargestellte Förderleitung von einem
Vorratstank zu einer Kraftstoffeinspritzpumpe für
Brennkraftmaschinen eingesetzt.
Dabei weist das in den Figuren 1 und 2 dargestellte erste
Ausführungsbeispiel der Förderpumpe in ihrem Gehäuse 1 eine
Pumpkammer 3 auf, in der ein rotierend angetriebenes Paar
miteinander kämmender Zahnräder angeordnet ist.
Ein erstes im Ausführungsbeispiel untenliegendes Zahnrad 5
wird dabei mittels eines nicht genauer dargestellten
externen Antriebselementes 7 rotierend angetrieben und
überträgt diese Drehbewegung über eine Stirnverzahnung auf
ein, mit dem ersten Zahnrad 5 kämmendes zweites Zahnrad 9.
Die Zahnräder 5, 9 teilen dabei die Pumpkammer 3 durch ihren
Zahneingriff in zwei Teilbereiche, von denen ein erster
Teilbereich einen Ansaugraum 11 und ein zweiter Teil einen
Druckraum 13 bilden.
Der Ansaugraum 11 ist dabei über je einen zwischen den
Zahnnuten an den Stirnflächen des ersten und zweiten
Zahnrades 5, 9 und der oberen und unteren Umfangswand der
Pumpkammer 3 gebildeten Förderkanal 15 mit dem Druckraum 13
verbunden. Zudem weisen der Ansaugraum 11 und der Druckraum
13 jeweils eine Anschlußöffnung in der Wand des
Pumpengehäuses 1 auf, über die der Ansaugraum 11 mit einer
nicht dargestellten Ansaugleitung vom Vorratstank und der
Druckraum 13 mit einer ebenfalls nicht dargestellten
Förderleitung zum Saugraum der Kraftstoffeinspritzpumpe
verbunden ist. Dabei bildet die Anschlußöffnung in den
Ansaugraum 11 eine Einlaßöffnung 17 und die Anschlußöffnung
in den Druckraum 13 eine Auslaßöffnung 19, die in einem, die
Pumpkammer 3 verschließenden Gehäusedeckel 21 angeordnet
sind.
Die Zahnräder 5, 9 sind auf in das Innere des Pumpengehäuses
1 ragenden Gehäusezapfen gelagert, die einteilig mit dem
Pumpengehäuse 1 ausgebildet sind. Dabei bildet ein erster
untenliegender Gehäusezapfen 23 einen das erste Zahnrad 5
aufnehmenden Lagerzapfen und ein zweiter obenliegender
Gehäusezapfen 25 einen das zweite Zahnrad 9 aufnehmenden
Lagerzapfen.
Der erste Gehäusezapfen 23 weist eine axiale
Durchgangsbohrung 27 auf, in der eine Antriebswelle 29
geführt ist, die an ihrem dem Gehäusedeckel 21 abgewandten
Ende drehschlüssig mit dem Antriebselement 7 verbunden ist.
An ihrem dem Antriebselement 7 fernen Ende ragt die
Antriebswelle 29 aus der Bohrung 27 des ersten
Gehäusezapfens 23 in ein Koppelglied 31 zum ersten Zahnrad
5, über das die Drehbewegung der Antriebswelle 29 auf das
Zahnrad 5 übertragen wird.
Dabei ist dieses in der Figur 5 näher dargestellte
Koppelglied im ersten Ausführungsbeispiel als
Kupplungsscheibe 31 ausgebildet, die mit ihrer radialen
Innenwand auf die Antriebswelle 29 aufgepreßt ist und die an
ihrem Außenumfang vorzugsweise drei radial vorstehende
Anformungen 33 aufweist. Mit diesen Anformungen 33 ragt die
Kupplungsscheibe in entsprechende Ausnehmungen 35 an der
Innenwandfläche des in den Figuren 3 und 4 vergrößert
dargestellten ersten Zahnrades 5 und stellt so eine
formschlüssige Verbindung zwischen der Kupplungsscheibe 31
und dem ersten Zahnrad 5 her.
Das in den Figuren 6 und 7 dargestellte zweite
Ausführungsbeispiel unterscheidet sich zum ersten
Ausführungsbeispiel in der Art des Kopppelgliedes zwischen
der Antriebswelle 29 und dem ersten Zahnrad 5.
Dabei ist die in der Figur 7 vergrößert dargestellte
Kupplungsscheibe 231 nunmehr mit ihrer Außenumfangswand in
den Innenwanddurchmesser des ersten Zahnrades 5 an dessen
deckelseitigem Ende eingepreßt. Die Kupplungsscheibe 231
besteht dabei aus einem Metall-, vorzugsweise Stahlring 41,
in dessen Inneres ein scheibenförmiges Elastomerteil 37
eingepreßt ist. In diesem Elastomerteil 37 ist eine
vorzugsweise vierkantförmige Ausnehmung 39 eingearbeitet, in
die ein entsprechend geformter, axial von der Antriebswelle
29 vorstehender Zapfen 43 hineinragt und so eine
formschlüssige Verbindung zwischen der Kupplungsscheibe 231
und der Antriebswelle 29 herstellt.
Die Schmierung der Lagerstellen der Zahnräder 5, 9 auf den
Gehäusezapfen 23, 25 erfolgt durch das Fördermedium, wozu,
wie in den Figuren 6 und 8 dargestellt, eine radiale Bohrung
51 in beiden Zahnrädern 5, 9 vorgesehen ist, die sich
ausgehend vom Zahnfuß 53 zwischen zwei benachbarten Zähnen
der Zahnräder 5, 9 bis an die Innendwand 55 der Zahnräder 5,
9 erstreckt und so die Gleitlagerstellen 57 mit Schmierstoff
versorgt.
Um die Schmierung an den Gleitlagerstellen 57 weiter zu
verbessern, ist bei dem in der Figur 9 in einem Ausschnitt
dargestellten dritten Ausführungsbeispiel zudem eine
Anflachung 61 am Gehäusezapfen 25 vorgesehen, die an der dem
Druckraum 13 der Förderpumpe abgewandten Seite des
Gehäusezapfens 25 angeordnet ist und in der sich das
Schmiermittel sammeln kann.
Die Figur 10 zeigt ein viertes Ausführungsbeispiel analog
zur Figur 9, bei dem an Stelle der Anflachung 61 eine
rundnutförmige Ausnehmung 63 an der druckraumabgewandten
Seite des Gehäuselagerzapfens 25 angeordnet ist, in der sich
das Schmiermittel sammel kann.
Der als Hohlachse ausgebildeten ersten Gehäusezapfen 23
weist dabei in nicht näher dargestellter Weise analog zu den
Figuren 9 und 10 ebenfalls eine Anflachung 61 oder
Ausnehmung 63 auf seiner Saugraumseite 11 auf.The feed pump according to the invention shown in FIGS. 1 to 10 in various sections and views is inserted into a feed line (not shown) from a storage tank to a fuel injection pump for internal combustion engines.
The first exemplary embodiment of the feed pump shown in FIGS. 1 and 2 has a
A
The
The
The
5 in the first exemplary embodiment is designed as a
The second exemplary embodiment shown in FIGS. 6 and 7 differs from the first exemplary embodiment in the type of coupling element between the
The
The lubrication of the bearing points of the
In order to further improve the lubrication at the
FIG. 10 shows a fourth exemplary embodiment analogous to FIG. 9, in which, instead of the flat 61, a round-groove-
The
Die erfindungsgemäße Förderpumpe arbeitet in folgender
Weise. Im Betrieb der Förderpumpe wird die Antriebswelle 29
vorzugsweise proportional zur Drehzahl einer zu versorgenden
Brennkraftmaschine rotierend angetrieben. Die Antriebswelle
29 überträgt die Drehbewegung über das Koppelglied 31,
(Kupplungsscheibe 231) auf das erste Zahnrad 5, das
seinerseits das zweite mit ihm kämmende Zahnrad 9 rotierend
antreibt. Durch die Drehbewegungen der miteinander kämmenden
Zahnräder 5, 9 wird das Fördermedium, vorzugsweise
Kraftstoff aus dem Ansaugraum 11 entlang der Förderkanäle 15
in den Druckraum 13 gefördert. Dabei entsteht im Ansaugraum
11 ein Unterdruck, der ausreicht, weiteren Kraftstoff über
die Ansaugleitung aus dem Vorratstank anzusaugen. Der im
Druckraum 13 aufgebaute Kraftstoffdruck bewirkt eine
Kraftstoff-Förderung über die Auslaßöffnung 19 in die
Förderleitung zur Kraftstoffeinspritzpumpe.
Dabei ist es mit der erfindungsgemäßen Lagerausbildung der
Zahnräder 5, 9 möglich, die an den Zahnrädern 5, 9
angreifenden Querkräfte direkt in das Gehäuse 1 der
Förderpumpe einzuleiten, so daß die Antriebswelle 29
lediglich das Antriebsdrehmoment übertragen muß und auf eine
zusätzliche Achse zur Lagerung des zweiten getriebenen
Zahnrades 9 verzichtet werden kann.The feed pump according to the invention works in the following way. In the operation of the feed pump, the
It is possible with the bearing design of the
Claims (7)
- Feed pump with a pair of gearwheels (5, 9), which pair is rotationally driven in a pumping chamber (3), and which gearwheels mesh with one another and feed a pumping medium from an intake space (11) connected to a storage tank, along a feed duct (15) formed between the end face of the gearwheels (5, 9) and the peripheral wall of the pumping chamber (3), into a pressure space (13), the gearwheels (5, 9) in each case being mounted on a housing pin (23, 25) which projects into the housing (1) of the feed pump and is designed in one piece with the housing (1), a first housing pin (23) having an axial through-bore (27) into which a drive shaft (29) projects, the drive shaft (29), at its inner end in the housing, projecting out of the housing pin (23) and being connected, by means of a coupling element, in a rotationally fixed manner to a first gearwheel (5) mounted on the first housing pin (23), the drive shaft (29) being connected positively via the coupling element to the first gearwheel (5), characterized in that the coupling element is designed as a coupling disc (31; 231) which is pressed onto the drive shaft (29) or pressed into the inner wall of the first gearwheel (5) and which is positively connected to the other part, first gearwheel (5) or drive shaft (29).
- Feed pump according to Claim 1, characterized in that the coupling disc (31) is pressed with its inner wall surface onto the drive shaft (29) and has on its outer peripheral surface a plurality of, preferably three, radially outwardly protruding formed-on portions (33) which engage in corresponding cutouts (35) on the inner surface of the first gearwheel (5).
- Feed pump according to Claim 1, characterized in that the coupling disc (231) is pressed with its peripheral wall into the inner wall of the first gearwheel (5) and has a slot-shaped cutout (39) in its end wall (37), in which a shaped pin (43) of corresponding shape protruding axially from the drive shaft (29) engages.
- Feed pump according to Claim 3, characterized in that the end wall disc (37) having the slot-shaped cutout (39) consists of an elastic material which is inserted into a metal ring (41) pressed into the first gearwheel (5).
- Feed pump according to Claim 1, characterized in that the gearwheels (5, 9) have a radial bore (51) which, starting from the tooth foot (53) between two adjacent teeth, ends in the wall (55) of the inside diameter.
- Feed pump according to Claim 1, characterized in that the housing pins (23, 25) have flat portions (61) or cutouts (63) on their peripheral wall.
- Feed pump according to Claim 6, characterized in that the flat portions (61) or cutouts (63) are arranged on that side of the housing pins (23, 25) facing away from the pressure space (13).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19638332 | 1996-09-19 | ||
| DE19638332A DE19638332C2 (en) | 1996-09-19 | 1996-09-19 | Feed pump |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| EP0831232A2 EP0831232A2 (en) | 1998-03-25 |
| EP0831232A3 EP0831232A3 (en) | 1999-03-03 |
| EP0831232B1 true EP0831232B1 (en) | 2003-03-05 |
Family
ID=7806189
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP97114968A Expired - Lifetime EP0831232B1 (en) | 1996-09-19 | 1997-08-29 | Gear pump |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US6071105A (en) |
| EP (1) | EP0831232B1 (en) |
| DE (2) | DE19638332C2 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19940730A1 (en) | 1999-08-27 | 2001-03-01 | Johann Sagawe | External gear pump |
| DE10014548A1 (en) * | 2000-03-23 | 2001-09-27 | Bosch Gmbh Robert | Gear pump for feeding liquid has connection between coupling cavity and compression cavity |
| DE10024884A1 (en) | 2000-05-19 | 2001-11-22 | Bosch Gmbh Robert | Gear pump |
| DE10059423A1 (en) | 2000-11-30 | 2002-06-13 | Bosch Gmbh Robert | Device for conveying liquids, in particular fuel |
| DE10059422A1 (en) * | 2000-11-30 | 2002-06-06 | Bosch Gmbh Robert | Device for conveying liquids, in particular fuel |
| DE10134622B4 (en) | 2001-07-17 | 2018-09-13 | Robert Bosch Gmbh | Gear pump, in particular for conveying fuel from a fuel tank to a high-pressure fuel pump |
| DE102006023380A1 (en) * | 2006-05-17 | 2007-11-22 | Ims Gear Gmbh | Planetary wheel with radial through hole |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE29811438U1 (en) * | 1998-06-26 | 1998-10-01 | Usd Formteiltechnik Gmbh | Rotor for an eccentric screw pump |
| DE19942221A1 (en) * | 1999-09-03 | 2001-03-15 | Luk Fahrzeug Hydraulik | Device for conveying a gaseous or liquid medium |
Family Cites Families (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE589418C (en) * | 1933-12-08 | Johannes Lambeck | Gear pump, especially for pumping cellulose solutions | |
| US2417084A (en) * | 1943-05-27 | 1947-03-11 | Monroe Benjamin Cullen | Steam locomotive |
| CH238205A (en) * | 1943-08-09 | 1945-06-30 | Egersdoerfer Fritz | Double or multiple gear pump. |
| US2672823A (en) * | 1948-01-12 | 1954-03-23 | Waterous Co | Rotary pump |
| US3043497A (en) * | 1959-12-29 | 1962-07-10 | Gabbioneta Roberto | Means for the support of the rotor in liquid ring rotary pumps |
| DE1821554U (en) * | 1960-07-07 | 1960-11-10 | Harry Thalheim | MOTOR DRIVEN GEAR PUMP FOR SMALL PERFORMANCE. |
| FR1299342A (en) * | 1961-09-04 | 1962-07-20 | Coy Mfg Company | Gear pump |
| US3105446A (en) * | 1961-09-05 | 1963-10-01 | Sr Oscar C Blomgren | Gear pump assembly |
| GB1108648A (en) * | 1965-12-01 | 1968-04-03 | Firth Cleveland Fastenings Ltd | Means for connecting a rotatable member to a shaft |
| US4153400A (en) * | 1976-07-16 | 1979-05-08 | Nakamura Kinzoku Kogyosho, Inc. | Rotary pumps circulating pumped fluid to seal |
| DE3033755A1 (en) * | 1980-09-08 | 1982-04-22 | Robert Bosch Gmbh, 7000 Stuttgart | Electric fuel pump unit - has common axis for pump and motor rotors held by pin extending from pump end plate |
| US4392798A (en) * | 1981-04-03 | 1983-07-12 | General Signal Corporation | Gear pump or motor with low pressure bearing lubrication |
| DE8315309U1 (en) * | 1983-05-25 | 1984-10-31 | Robert Bosch Gmbh, 7000 Stuttgart | GEAR PUMP |
| US4902202A (en) * | 1987-07-29 | 1990-02-20 | Hydreco, Inc. | Variable discharge gear pump with energy recovery |
| US5391068A (en) * | 1994-02-15 | 1995-02-21 | Eaton Corporation | Gear pump |
| DE4441505A1 (en) * | 1994-11-22 | 1996-05-23 | Bosch Gmbh Robert | Fuel feed pump for a fuel injection pump for internal combustion engines |
-
1996
- 1996-09-19 DE DE19638332A patent/DE19638332C2/en not_active Expired - Fee Related
-
1997
- 1997-08-29 DE DE59709430T patent/DE59709430D1/en not_active Expired - Fee Related
- 1997-08-29 EP EP97114968A patent/EP0831232B1/en not_active Expired - Lifetime
- 1997-09-19 US US08/934,129 patent/US6071105A/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE29811438U1 (en) * | 1998-06-26 | 1998-10-01 | Usd Formteiltechnik Gmbh | Rotor for an eccentric screw pump |
| DE19942221A1 (en) * | 1999-09-03 | 2001-03-15 | Luk Fahrzeug Hydraulik | Device for conveying a gaseous or liquid medium |
Also Published As
| Publication number | Publication date |
|---|---|
| DE19638332C2 (en) | 2000-07-20 |
| DE19638332A1 (en) | 1998-03-26 |
| EP0831232A2 (en) | 1998-03-25 |
| DE59709430D1 (en) | 2003-04-10 |
| EP0831232A3 (en) | 1999-03-03 |
| US6071105A (en) | 2000-06-06 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| DE69817378T2 (en) | INTERNAL GEAR PUMP | |
| DE102009045222B4 (en) | Parallel-axis differential arrangement with helical toothing | |
| DE10258058A1 (en) | differential assembly | |
| DE19750834C1 (en) | Locking differential for motor vehicle | |
| DE19513380C2 (en) | Sealing, storage and drive of the rotors of a dry-running screw rotor compressor | |
| WO2001004512A1 (en) | Multi-stage spur gear transmission | |
| DE3340748C2 (en) | Gear pumps, in particular for medical purposes | |
| EP0831232B1 (en) | Gear pump | |
| EP3452741B1 (en) | Transmission comprising a pump mechanically driven on a ring gear of the transmission | |
| DE69719937T2 (en) | SPIRAL MACHINE AND BEARING LUBRICATION | |
| DE10058012A1 (en) | Gear pump, in particular for delivering fuel to a high-pressure fuel pump | |
| WO2002077460A1 (en) | Gear feed pump | |
| DE3716083A1 (en) | INNER AXIS ROTARY PISTON | |
| EP0831231B1 (en) | Gear pump | |
| EP0822329A2 (en) | Fuel feed pump for a fuel injection pump for internal combustion engines | |
| DE19714648B4 (en) | Fuel feed pump | |
| DE3542734A1 (en) | Internal-gear pump | |
| DE60304366T2 (en) | COUPLING DEVICE OF A TURNING ELEMENT WITH A CAMSHAFT | |
| DE19647052C2 (en) | Device for conveying working media of an internal combustion engine of a motor vehicle | |
| DE4403649A1 (en) | Screw compressor | |
| EP1373734A1 (en) | Gear feed pump | |
| DE19825376C2 (en) | gear machine | |
| DE1553125A1 (en) | Gear pump | |
| DE102009028449A1 (en) | Toothed wheel pump, particularly fuel pump, has two toothed wheels, which are arranged and combed together in housing, where fuel of suction area is conveyed to pressure area | |
| DE4308975A1 (en) | Shaft-hub connection |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
| AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): DE FR GB IT SE |
|
| AX | Request for extension of the european patent |
Free format text: AL;LT;LV;RO;SI |
|
| PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
| AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AT BE CH DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE |
|
| AX | Request for extension of the european patent |
Free format text: AL;LT;LV;RO;SI |
|
| 17P | Request for examination filed |
Effective date: 19990903 |
|
| AKX | Designation fees paid |
Free format text: DE FR GB IT SE |
|
| 17Q | First examination report despatched |
Effective date: 20011002 |
|
| GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
| GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
| GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
| GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
| GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
| AK | Designated contracting states |
Designated state(s): DE FR GB IT SE |
|
| REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
| REF | Corresponds to: |
Ref document number: 59709430 Country of ref document: DE Date of ref document: 20030410 Kind code of ref document: P |
|
| REG | Reference to a national code |
Ref country code: SE Ref legal event code: TRGR |
|
| GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) | ||
| ET | Fr: translation filed | ||
| PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
| STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
| 26N | No opposition filed |
Effective date: 20031208 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20050819 Year of fee payment: 9 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20051021 Year of fee payment: 9 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20060830 Year of fee payment: 10 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20060831 Year of fee payment: 10 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20070301 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SE Payment date: 20060829 Year of fee payment: 10 |
|
| EUG | Se: european patent has lapsed | ||
| GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20070829 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20070830 |
|
| REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20080430 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20070831 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20070829 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20060831 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20070829 |