EP0906511B1 - Pump, especially high pressure pump for use in a fuel injector of an internal combustion engine - Google Patents

Pump, especially high pressure pump for use in a fuel injector of an internal combustion engine Download PDF

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Publication number
EP0906511B1
EP0906511B1 EP97953670A EP97953670A EP0906511B1 EP 0906511 B1 EP0906511 B1 EP 0906511B1 EP 97953670 A EP97953670 A EP 97953670A EP 97953670 A EP97953670 A EP 97953670A EP 0906511 B1 EP0906511 B1 EP 0906511B1
Authority
EP
European Patent Office
Prior art keywords
pump
shaft
housing
pump shaft
internal combustion
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
Application number
EP97953670A
Other languages
German (de)
French (fr)
Other versions
EP0906511A1 (en
Inventor
Hans-Peter Stiefel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0906511A1 publication Critical patent/EP0906511A1/en
Application granted granted Critical
Publication of EP0906511B1 publication Critical patent/EP0906511B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0448—Sealing means, e.g. for shafts or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S464/00—Rotary shafts, gudgeons, housings, and flexible couplings for rotary shafts
    • Y10S464/901—Rapid attachment or release

Definitions

  • the invention relates to a pump, in particular a high-pressure pump for a fuel injection device of an internal combustion engine, according to the preamble of claim 1.
  • DE 44 19 927 A1 describes a piston pump High pressure pump for fuel known in its pump housing a piston-cylinder unit comprising a working space is arranged and a pump shaft for driving the piston-cylinder unit is stored.
  • the pump shaft is in hers Center mounted and carries on its output side, flying end mounted an eccentric, over which the piston-cylinder unit is applied.
  • To drive the pump shaft is a drive gear on its end protruding from the pump housing attached.
  • This well-known pump which is used as a lubricant pump, has a relatively short overall length, but it can be not produce independently of the internal combustion engine. Besides, can the function of this known pump and its individual pump elements only after installation in the cylinder head wall of the engine being checked.
  • the pump with the characterizing features of claim 1 has that compared to the advantage that the non-rotatable mounting of Pump shaft on a shaft of the drive motor no bearings for the pump shaft in the pump housing required be, so that there is a shortened length of the pump. In addition, there is no pump shaft bearing increased service life in the pump housing.
  • the pump according to the invention can be used as a separate one Manufacture assembly and independent of the internal combustion engine check for functionality.
  • a transport bracket for the pump shaft is provided, preferably two from each other has spaced holding means.
  • the invention provided that the implementation of the pump shaft from the pump housing using an axial shaft seal is sealed, in which two flat surfaces close together be pressed. It can also be used for an eccentric Movement of the sealing surfaces against each other a flawless Ensure sealing.
  • a particularly unproblematic installation of the pump results itself if the pump shaft has a drive-side bearing journal has, which in a corresponding axial bore in the Shaft of the internal combustion engine is insertable.
  • This training also enables the particularly simple connection of a Auxiliary drive used for test operation of the pump for test purposes is required.
  • a pump according to the invention comprises a Pump housing 10 with one or more receiving areas 11 for one pump element 12 and one receiving area 13, in which a pump shaft 14 with its output end is arranged.
  • the receiving area 13 for the output side The end of the pump shaft 14 forms together with it facing sections of the receiving area or areas 11 a Inlet area 15 for a relatively low pressure standing medium to be conveyed, especially for under pressure standing fuel.
  • the inlet area 15 is over a Not shown feed line with a not shown Low pressure inlet connection is connected to the pump housing 10.
  • the pump element 12 comprises a piston as the working element 16, which is guided displaceably in a piston guide 17.
  • the piston guide 17 is inserted into a holding part 18 which the pump element 12 in the receiving area 11 of the pump housing 10 holds.
  • On the outer circumference of the holding part 18 is in the area of its inner end provided a seal 19 which the inlet area 15 seals against a conveyor area 20 in the the medium to be pumped with relatively high pressure, in particular is pumped at high pressure and the holding part 18 in the area surrounded by outlet bores 21 provided therein.
  • the Conveying area 20 is connected via a line, not shown a high-pressure outlet connection, not shown, on the pump housing 10 connected.
  • the conveying area becomes 20 on the outside through a seal 22 between the holding part 18 and the Receiving area 11 for the housing inner wall surrounding the pump element 12 sealed.
  • the piston 16 has an axial inlet channel 23, which on arranged in the piston guide 17 end of the piston 16 opens and the via a transverse inlet bore 24 in end of the piston 16 protruding from the piston guide 17 is connected to the inlet area 15.
  • the piston 16 carries an inlet valve 25 and thus delimits a working space in the piston guide 17 26 by an exhaust valve 27 against a high pressure exhaust area 28 is closable.
  • the high pressure outlet area 28 stands over the outlet bores 21 with the delivery area 20 in connection.
  • the inlet valve 25 is designed so that it during of the suction stroke of the piston 16, that is, if this comes from the Piston guide 17 moved out, opens so that during the Suction strokes to be conveyed medium from the inlet area 15 through the inlet bore 24, the inlet channel 23 and the open inlet valve 25 can flow into the work space 26.
  • the Delivery strokes i.e. when the piston 16 is in the piston guide 17 moves in, closes the inlet valve 25, so that the Working space 26 enclosed medium under pressure becomes.
  • a slide shoe 29 is attached, with which the piston 16 via one on a serving as a crank element Eccentric 31 of the pump shaft 14 rotatably mounted cam ring 30 supports so that the piston 16 can be driven by the pump shaft 14 is.
  • a spring 32 is provided which is at one end on the slide shoe 29 and with its other end on the holding part 18th supports.
  • driver lugs 36 are provided, which are diametrically opposed to each other with respect to the pump shaft axis A. opposite.
  • a circumferential retaining web 37 is provided, whose outer circumference is larger than that of the sealing collar 33.
  • an auxiliary pin 38 is attached, which is aligned coaxially with the journal 34 is.
  • the pump shaft 14 is in the pump housing 10 used that their auxiliary pin 38 with radial Play in an auxiliary bore provided in the pump housing 10 39 runs while the sealing collar 33 in the region of a passage opening 40 of the pump housing 10 is located in one of With respect to the pump shaft axis A axially extending centering collar 41 is surrounded.
  • the centering collar 41 and the auxiliary bore 39 are coaxially aligned with each other.
  • a radial shaft seal 43 is in the passage opening 40 tightly inserted, the inner diameter of which is larger than that Outer diameter of the sealing collar 33.
  • On the inner diameter of the A support surface 42 is provided for the radial shaft seal 43.
  • the Inner diameter is smaller than the outer diameter of the Sealing collar 33. Sealing lip 44 thus becomes sealing collar 33 deforms and lies sealingly against it.
  • Sealing lip 44 can also be, for example, a grooved ring or the like be used.
  • the inside diameter is expedient the sealing lip 44 chosen so that the sealing lip 44, too if in the manner described during transportation and storage is deformed, the inside of the pump against dust and Seals dirt.
  • the radial shaft seal 43 is shaped in this way and the sealing lip 44 is installed so that the pump shaft 14 comes to rest on the support surface 42 before the sealing lip 44 could be damaged by crushing.
  • the sealing collar 33 and the support surface 42 of the radial shaft seal 43 form together with the auxiliary pin 38 and Auxiliary hole 39 a transport bracket for the pump shaft 14 in the pump housing 10, which the pump shaft 14 at Motor housing 45 'attached pump essentially in its later operating position in the pump housing 10 holds.
  • the forming a first holding means Support surface 42 and that forming a second holding means Auxiliary bore 39 are axially spaced apart, so that the pump shaft 14 in the pump housing 10 cannot tilt. This can in particular prevent that the or Piston 16 too far from the associated piston guides 17 can be pulled out, what to assemble the pump Problems, especially damage to the piston 16 when Reinsert.
  • a second holding means can be used also an auxiliary pin or the like on the inner wall of the Pump housing 10 are provided. In this case it would be a corresponding auxiliary hole or the like in or on Eccentric 31 to be arranged.
  • the holding web 37 is used on the pump shaft 14 during transport and storage together with the radial shaft seal 43 as fallout protection for the pump shaft 14.
  • the bearing journal is first 34 of the pump shaft 14 in one, in particular as a fitting bore trained, axial bearing bore 47 in the shaft 46 and subsequently the centering collar 41 in a to the shaft 46 of the Internal combustion engine inserted coaxial mounting hole 48.
  • the pump shaft 14 is thus through the joining of the journal 34 of the pump shaft 14 into the bearing bore 47 of the shaft 46 radially and by meshing the Driving nose 36 with the groove 49 rotatably in the shaft 46 of the Internal combustion engine stored.
  • the radial mounting of the pump shaft 14 on the shaft 46 of the Internal combustion engine can also be reversed a journal on the shaft 46 and a bearing bore in realize the pump shaft 14. It is also possible to both the shaft 46 of the internal combustion engine as well as the pump shaft 14 to be provided with a bearing bore, and Bearing of the pump shaft 14 on the shaft 46 of the internal combustion engine to use a journal that fits into both bearing bores is used. In particular, this allows both on the not yet installed pump and on the internal combustion engine far beyond the pump housing 10 or the motor housing 45 'Avoid protruding parts, in particular can easily be damaged during transport.
  • the axial bearing of the pump shaft 14 can be in almost everyone done in any way, since only very low bearing forces are to be included.
  • the axial Bearing of the pump shaft 14 for example by support the driver lugs 36 on the shaft 46 of the internal combustion engine or by supporting the retaining web 37 on the support ring 44.
  • the receiving bore 48 there is a leakage space for from the inlet area 15 leaking through the radial shaft seal 43, medium to be conveyed, in particular fuel, is formed, the one in the outer peripheral surface of the centering collar 41 used sealing ring 52 against the external environment and by a lip seal 51 against the shaft 46 and thus against Lubricating oil from their shaft bearings is sealed.
  • This Leakage space is, for example, via a bore 48 'in the pump housing 10 disposed of when the medium to be pumped fuel is, in a manner not shown with an intake pipe of the internal combustion engine can be connected.
  • the bore 48 'in the pump housing 10 can also, as in FIG. 5 shown a bore 48 "provided in the motor housing 45 ' his.
  • the lip seal 51 which is designed to seal against lubricating oil is against harmful effects of the medium to be pumped, especially fuel, protected. This allows the Extend the life of the lip seal 51.
  • the pump shaft 14 runs during operation, that is if it is from Internal combustion engine via shaft 46, preferably the camshaft, is driven without its own radial bearing in the pump housing 10 free in this without grazing anywhere.
  • the on the wall 45 of the motor housing 45 'of the internal combustion engine attached assembly from pump housing 10, pump element 12, pump shaft 14 and radial shaft seal 43 can for example by means of screws 53, only one of which is shown is attached to the wall 45 of the internal combustion engine.
  • a pump shaft 14 ' can also be used in the journal 34 adjacent to the sealing collar 33, a transverse bore 54, in which, as in Fig. 5 in connection with shown a second embodiment of the invention, a driver pin 55 is used, which is on the outer circumference of the journal 34 protrudes so far that it is in engagement with the grooves 49 on the shaft 46 of the internal combustion engine is feasible.
  • the second embodiment includes the Pump according to the invention, a pump housing 10 in which one or a plurality of pump elements 12 and a pump shaft 14 'are arranged are.
  • the structure and arrangement of the pump element 12 corresponds the structure described with reference to FIG. 1.
  • radial shaft seal 43 instead of at 1 is provided radial shaft seal 43 however, in the pump shown in Fig. 5, an axial shaft seal 56 provided to the inlet area 15 against the Seal the receiving bore 48 in the wall 45 of the internal combustion engine.
  • the axial shaft seal 56 includes one on the sealing collar 33 pressed driver 57, in the, adjacent to the holding web 37 a spring 58 and a pressure ring 59 on the from the holding bridge 37 opposite side of the spring 58 is used. It is a sealing ring between the pressure ring 59 and the sealing collar 33 60 arranged, the pressure ring 59 for tolerance compensation in seals axially against the sealing collar 33.
  • a Slide ring 62 used, the one on its outer circumference Seal ring 63 carries.
  • a washer 64 attached to the extension 61 of the centering collar 41 z. B. attached by crimping is, the slide ring 62 together with the sealing ring 63 in Receiving area of the extension 61 of the centering collar 41.
  • the axial shaft seal 56 acts here as the first holding means the transport bracket, while the disc 64, which the Slide ring 62 in the extension 61 of the centering collar 41 holds, as fall-out protection during transport and storage serves the pump.
  • the auxiliary pin 38 is supported in the axial direction and preferably from one Low-friction material, in particular from a plain bearing material is made.
  • the use of the axial shaft seal 56 described the pump according to the invention has the advantage that a possible Radial play of the shaft 46 of the internal combustion engine, that too an eccentric rotation of the pump shaft axis A and thus leads to an eccentric circulation of the pressure ring 59, none Influence on the sealing of the pump, because the superimposed Sealing surfaces are flat and perpendicular to the nominal course the pump shaft axis A.
  • One due to radial play tilting of the shaft 46 of the internal combustion engine of the pressure ring 59 relative to the sealing collar 33 compensated by the spring 58 and the sealing ring 60.
  • the pump according to the invention for example using radial piston pumps with one pump element 12 or more, preferably with three pump elements arranged in a star shape 12 has been described, can also be used as an axial piston pump form.
  • the invention Pump in which the pump shaft 14, 14 'without self-storage in the pump housing 10 used tightly in this and in one Drive shaft is radially and non-rotatably supported, also as Gear pump or the like to perform.
  • the invention can be used with all types of pumps, in which one or more work elements via an eccentric a pump shaft are to be driven.
  • the pump according to the invention has the particular advantage that it as an independent assembly independent of other parts manufactured and as a fully pre-assembled, already sealed Assembly are checked directly at the manufacturer can.
  • the pump operation both the functionality of the individual pump elements 12, as well as their interaction with the pump shaft 14, 14 'and check the tightness completely.
  • Another The advantage is that later assembly on the final Location, i.e. on an internal combustion engine, none Dirt can get into the pump. Furthermore extends the elimination of the bearing of the pump shaft 14, 14 ' in the pump housing 10 the life of the pump.
  • the transport bracket provided in the pump according to the invention significantly simplifies the later assembly of the pump on Motor housing 45 'because the pump shaft 14, 14' and thus also the bearing pin 34 essentially in the intended operating position being held.
  • the spring 58 ensures a dimensional tolerance and wear largely independent, uniform and constant surface pressure between each other sliding surfaces of the pressure ring 59 and the sliding ring 62, that is, between the end face 65 and the sliding surface 66.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)

Description

Die Erfindung betrifft eine Pumpe, insbesondere eine Hochdruckpumpe für eine Kraftstoffeinspritzvorrichtung eines Verbrennungsmotors, nach dem Oberbegriff des Anspruchs 1.The invention relates to a pump, in particular a high-pressure pump for a fuel injection device of an internal combustion engine, according to the preamble of claim 1.

STAND DER TECHNIKSTATE OF THE ART

Aus der DE 44 19 927 A1 ist eine als Kolbenpumpe ausgebildete Hochdruckpumpe für Kraftstoff bekannt, in deren Pumpengehäuse eine einen Arbeitsraum umfaßende Kolben-Zylinder-Einheit angeordnet und eine Pumpenwelle zum Antrieb der Kolben-Zylinder-Einheit gelagert ist. Die Pumpenwelle ist in ihrer Mitte gelagert und trägt an ihrem abtriebsseitigen, fliegend gelagerten Ende einen Exzenter, über den die Kolben-Zylinder-Einheit beaufschlagt wird. Zum Antrieb der Pumpenwelle ist auf ihrem aus dem Pumpengehäuse herausragenden Ende ein Antriebszahnrad befestigt. DE 44 19 927 A1 describes a piston pump High pressure pump for fuel known in its pump housing a piston-cylinder unit comprising a working space is arranged and a pump shaft for driving the piston-cylinder unit is stored. The pump shaft is in hers Center mounted and carries on its output side, flying end mounted an eccentric, over which the piston-cylinder unit is applied. To drive the pump shaft is a drive gear on its end protruding from the pump housing attached.

Aufgrund der Lagerung der Pumpenwelle im Pumpengehäuse ergibt sich eine relativ große Baulänge der Pumpe, die somit einen relativ großen Platzbedarf aufweist. Außerdem ist eine relativ aufwendige Antriebsverbindung von einer Motorwelle zum Antriebszahnrad erforderlich, die ebenfalls einen gewissen Einbauraum im Motorraum benötigt. Darüber hinaus ergeben sich große Lagerbelastungen, die zu einem erhöhten Verschleiß und einer verringerten Lebensdauer führen, da die wirksame Lagerlänge verglichen mit der Länge des vom Lager hervorstehenden abtriebsseitigen Endes der Pumpenwelle relativ klein ist.Due to the bearing of the pump shaft in the pump housing, this results a relatively large overall length of the pump, which is therefore a relative has a large space requirement. It is also a relatively complex one Drive connection from a motor shaft to the drive gear required, which also has a certain installation space in the engine compartment needed. In addition, there are large bearing loads that too lead to increased wear and a reduced service life, as the effective bearing length compared to the length of the bearing protruding output-side end of the pump shaft is relatively small is.

Die Veröffentlichung EP 0 290 855 A zeigt eine Kolbenpumpe mit einer in einem Pumpengehäuse gelagerten Pumpenwelle. Die in radialer Richtung wirkenden Kräfte der Pumpenwelle werden von dem an ein Motorgehäuse anflanschbaren Pumpengehäuse getragen. Weil die in radialer Richtung wirkenden Kräfte erheblich sind, muß das Pumpengehäuse entsprechend ausreichend groß dimensioniert sein. Dadurch weist diese Pumpe ein erhebliches Gewicht auf und benötigt ziemlich viel Bauraum.The publication EP 0 290 855 A shows a piston pump with a pump shaft mounted in a pump housing. The one in radial From this point on, the forces acting on the pump shaft become one Motor housing flanged pump housing worn. Because the in radial forces are considerable, the pump housing be dimensioned sufficiently large accordingly. Thereby this pump has a considerable weight and needs quite a bit lots of installation space.

Aus der DE 42 17 910 A1 ist eine von einem Verbrennungsmotor angetriebene Hydraulikpumpe bekannt, die in einem Hohlraum einer Zylinderkopfwand angeordnet ist. In diesen Hohlraum erstreckt sich durch eine Öffnung in der Zylinderkopfwand ein Ende einer Nockenwelle, auf dem ein Exzenter drehfest angeordnet ist, der einen Kolben eines Pumpenelements antreibt. Nach dem Einsetzen des Pumpenelements und dem Anbringen des Exzenters auf dem Nockenwellenende wird der Hohlraum in der Zylinderkopfwand mittels eines Deckels verschlossen. DE 42 17 910 A1 describes one driven by an internal combustion engine Hydraulic pump known in a cavity Cylinder head wall is arranged. Extends into this cavity through an opening in the cylinder head wall one end of a camshaft, on which an eccentric is rotatably arranged, one Drives piston of a pump element. After inserting the pump element and attaching the eccentric to the camshaft end the cavity in the cylinder head wall by means of a cover locked.

Diese bekannte Pumpe, die als Schmiermittelpumpe eingesetzt wird, weist zwar eine relativ kurze Baulänge auf, jedoch läßt sie sich nicht unabhängig von dem Verbrennungsmotor herstellen. Außerdem kann die Funktion dieser bekannten Pumpe und ihrer einzelnen Pumpenelemente erst nach dem Einbau in die Zylinderkopfwand des Motors geprüft werden.This well-known pump, which is used as a lubricant pump, has a relatively short overall length, but it can be not produce independently of the internal combustion engine. Besides, can the function of this known pump and its individual pump elements only after installation in the cylinder head wall of the engine being checked.

Vorteile der ErfindungAdvantages of the invention

Die Pumpe mit den kennzeichnenden Merkmalen des Anspruchs 1 hat dem gegenüber den Vorteil, daß sich durch die drehfeste Lagerung der Pumpenwelle an einer Welle des Antriebsmotors keine Lager für die Pumpenwelle im Pumpengehäuse benötigt werden, so daß sich eine verkürzte Baulänge der Pumpe ergibt. Außerdem ergibt sich durch den Wegfall der Lagerung der Pumpenwelle im Pumpengehäuse eine erhöhte Lebensdauer.The pump with the characterizing features of claim 1 has that compared to the advantage that the non-rotatable mounting of Pump shaft on a shaft of the drive motor no bearings for the pump shaft in the pump housing required be, so that there is a shortened length of the pump. In addition, there is no pump shaft bearing increased service life in the pump housing.

Darüber hinaus läßt sich die erfindungsgemäße Pumpe als separate Baugruppe herstellen und unabhängig vom Verbrennungsmotor auf ihre Funktionsfähigkeit prüfen. Um beim Transport und der Lagerung unkontrollierte Bewegungen der beweglichen Pumpenelemente und damit Probleme bei der späteren Montage und Beschädigungen zu vermeiden, ist bei einem bevorzugten Ausführungsbeispiel der Erfindung eine Transporthalterung für die Pumpenwelle vorgesehen, die vorzugsweise zwei voneinander beabstandete Haltemittel aufweist.In addition, the pump according to the invention can be used as a separate one Manufacture assembly and independent of the internal combustion engine check for functionality. To transport and the storage of uncontrolled movements of the moving pump elements and thus problems with the later assembly and Avoiding damage is a preferred embodiment the invention a transport bracket for the pump shaft is provided, preferably two from each other has spaced holding means.

Besonders vorteilhaft ist es, wenn die Durchführung der Pumpenwelle aus dem Pumpengehäuse abgedichtet ist, da das Pumpeninnere hierdurch vor Verunreinigungen während der Lagerung, dem Transport und der Montage geschützt ist.It is particularly advantageous if the pump shaft is passed through is sealed from the pump housing, since the pump interior this prevents contamination during storage, is protected during transport and assembly.

Um ein Radialspiel in der Lagerung der Welle des Verbrennungsmotors ohne Einfluß auf die Dichtigkeit der Pumpe ausgleichen zu können, ist bei einer vorteilhaften Ausgestaltung der Erfindung vorgesehen, daß die Durchführung der Pumpenwelle aus dem Pumpengehäuse mittels einer Axialwellendichtung abgedichtet ist, bei der zwei ebene Flächen dicht aufeinander gepreßt werden. Damit läßt sich auch bei einer exzenterförmigen Bewegung der Dichtflächen gegeneinander eine einwandfreie Abdichtung sicherstellen.To radial play in the bearing of the shaft of the internal combustion engine compensate without affecting the tightness of the pump To be able to, is in an advantageous embodiment the invention provided that the implementation of the pump shaft from the pump housing using an axial shaft seal is sealed, in which two flat surfaces close together be pressed. It can also be used for an eccentric Movement of the sealing surfaces against each other a flawless Ensure sealing.

Eine besonders unproblematische Montage der Pumpe ergibt sich, wenn die Pumpenwelle einen antriebsseitigen Lagerzapfen aufweist, der in eine entsprechende axiale Bohrung in der Welle des Verbrennungsmotors einsteckbar ist. Diese Ausbildung ermöglicht auch den besonders einfachen Anschluß eines Hilfsantriebs, der für einen Testbetrieb der Pumpe zu Prüfzwecken erforderlich ist.A particularly unproblematic installation of the pump results itself if the pump shaft has a drive-side bearing journal has, which in a corresponding axial bore in the Shaft of the internal combustion engine is insertable. This training also enables the particularly simple connection of a Auxiliary drive used for test operation of the pump for test purposes is required.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Hauptanspruch angegebenen Kolbenpumpe möglich.By the measures listed in the subclaims advantageous developments and improvements in Piston pump specified in the main claim possible.

ZEICHNUNGDRAWING

Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
einen Schnitt durch eine Pumpe nach einem ersten Ausführungsbeispiel der Erfindung,
Fig. 2a
einen Schnitt durch das abtriebsseitige Ende einer Welle eines Verbrennungsmotors für die Verwendung mit einer Pumpe nach der Erfindung,
Fig. 2b
eine um 90° gedrehte Seitenansicht des Endes der Welle nach Fig. 2a,
Fig. 3
eine Seitenansicht einer Pumpenwelle für die Pumpe nach Fig. 1,
Fig. 4
eine Seitenansicht einer Pumpenwelle für eine Pumpe nach einem zweiten Ausführungsbeispiel der Erfindung und
Fig. 5
einen Schnitt durch eine Pumpe nach dem zweiten Ausführungsbeispiel der Erfindung.
Embodiments of the invention are shown in simplified form in the drawing and explained in more detail in the following description. Show it:
Fig. 1
2 shows a section through a pump according to a first exemplary embodiment of the invention,
Fig. 2a
3 shows a section through the output-side end of a shaft of an internal combustion engine for use with a pump according to the invention,
Fig. 2b
a side view of the end of the shaft according to FIG. 2a rotated by 90 °,
Fig. 3
2 shows a side view of a pump shaft for the pump according to FIG. 1,
Fig. 4
a side view of a pump shaft for a pump according to a second embodiment of the invention and
Fig. 5
a section through a pump according to the second embodiment of the invention.

In den verschiedenen Figuren der Zeichnung sind einander entsprechende Teile mit gleichen Bezugszeichen versehen.In the different figures of the drawing are corresponding to each other Provide parts with the same reference numerals.

BESCHREIBUNG DER AUSFÜHRUNGSBEISPIELEDESCRIPTION OF THE EMBODIMENTS

Wie in Fig. 1 gezeigt, umfaßt eine erfindungsgemäße Pumpe ein Pumpengehäuse 10 mit einem oder mehreren Aufnahmebereichen 11 für jeweils ein Pumpenelement 12 und einen Aufnahmebereich 13, in dem eine Pumpenwelle 14 mit ihrem abtriebsseitigen Ende angeordnet ist. Der Aufnahmebereich 13 für das abtriebsseitige Ende der Pumpenwelle 14 bildet zusammen mit ihm zugewandten Abschnitten des bzw. der Aufnahmebereiche 11 einen Zulaufbereich 15 für ein unter relativ niedrigem Druck stehendes zu förderndes Medium, insbesondere für unter Vordruck stehenden Kraftstoff. Der Zulaufbereich 15 ist über eine nicht dargestellte Zulaufleitung mit einem nicht gezeigtem Niederdruck-Zulaufanschluß am Pumpengehäuse 10 verbunden ist.As shown in Fig. 1, a pump according to the invention comprises a Pump housing 10 with one or more receiving areas 11 for one pump element 12 and one receiving area 13, in which a pump shaft 14 with its output end is arranged. The receiving area 13 for the output side The end of the pump shaft 14 forms together with it facing sections of the receiving area or areas 11 a Inlet area 15 for a relatively low pressure standing medium to be conveyed, especially for under pressure standing fuel. The inlet area 15 is over a Not shown feed line with a not shown Low pressure inlet connection is connected to the pump housing 10.

Das Pumpenelement 12 umfaßt als Arbeitselement einen Kolben 16, der in einer Kolbenführung 17 verschiebbar geführt ist. Die Kolbenführung 17 ist in ein Halteteil 18 eingesetzt, das das Pumpenelement 12 im Aufnahmebereich 11 des Pumpengehäuses 10 hält. Am Außenumfang des Halteteils 18 ist im Bereich seines inneren Endes eine Dichtung 19 vorgesehen, die den Zulaufbereich 15 gegen einen Förderbereich 20 abdichtet, in den das zu fördernde Medium mit relativ hohem Druck, insbesondere mit Hochdruck gepumpt wird und der das Halteteil 18 im Bereich von darin vorgesehenen Auslaßbohrungen 21 umgibt. Der Förderbereich 20 ist über eine nicht dargestellte Leitung mit einem nicht gezeigten Hochdruck-Auslaßanschluß am Pumpengehäuse 10 verbunden. Nach außen wird der Förderbereich 20 durch eine Dichtung 22 zwischen dem Halteteil 18 und der den Aufnahmebereich 11 für das Pumpenelement 12 umgebenden Gehäuseinnenwand abgedichtet. The pump element 12 comprises a piston as the working element 16, which is guided displaceably in a piston guide 17. The piston guide 17 is inserted into a holding part 18 which the pump element 12 in the receiving area 11 of the pump housing 10 holds. On the outer circumference of the holding part 18 is in the area of its inner end provided a seal 19 which the inlet area 15 seals against a conveyor area 20 in the the medium to be pumped with relatively high pressure, in particular is pumped at high pressure and the holding part 18 in the area surrounded by outlet bores 21 provided therein. The Conveying area 20 is connected via a line, not shown a high-pressure outlet connection, not shown, on the pump housing 10 connected. The conveying area becomes 20 on the outside through a seal 22 between the holding part 18 and the Receiving area 11 for the housing inner wall surrounding the pump element 12 sealed.

Der Kolben 16 weist einen axialen Zulaufkanal 23 auf, der am in der Kolbenführung 17 angeordneten Ende des Kolbens 16 mündet und der über eine quer verlaufende Zulaufbohrung 24 im aus der Kolbenführung 17 hervorstehenden Ende des Kolbens 16 mit dem Zulaufbereich 15 verbunden ist. An der Mündung des axialen Zulaufkanals 23 trägt der Kolben 16 ein Zulaufventil 25 und begrenzt damit in der Kolbenführung 17 einen Arbeitsraum 26, der von einem Auslaßventil 27 gegen einen Hochdruck-Auslaßbereich 28 verschließbar ist. Der Hochdruck-Auslaßbereich 28 steht über die Auslaßbohrungen 21 mit dem Förderbereich 20 in Verbindung.The piston 16 has an axial inlet channel 23, which on arranged in the piston guide 17 end of the piston 16 opens and the via a transverse inlet bore 24 in end of the piston 16 protruding from the piston guide 17 is connected to the inlet area 15. At the mouth of the axial inlet channel 23, the piston 16 carries an inlet valve 25 and thus delimits a working space in the piston guide 17 26 by an exhaust valve 27 against a high pressure exhaust area 28 is closable. The high pressure outlet area 28 stands over the outlet bores 21 with the delivery area 20 in connection.

Das Zulaufventil 25 ist dabei so ausgebildet, daß es während des Saughubs des Kolbens 16, also wenn sich dieser aus der Kolbenführung 17 herausbewegt, öffnet, so daß während des Saughubs zu förderndes Medium aus dem Zulaufbereich 15 durch die Zulaufbohrung 24, den Zulaufkanal 23 und das offene Zulaufventil 25 in den Arbeitsraum 26 strömen kann. Während des Förderhubs, also wenn sich der Kolben 16 in die Kolbenführung 17 hineinbewegt, schließt das Zulaufventil 25, so daß das im Arbeitsraum 26 eingeschlossene Medium unter Druck gesetzt wird. Sobald der Druck im Arbeitsraum 26 einen vom Auslaßventil 27 vorgegebenen Hochdruck erreicht, öffnet dieses und das unter Hochdruck stehende zu fördernde Medium kann durch das offene Auslaßventil 27, den Hochdruck-Auslaßbereich 28, die Auslaßbohrungen 21 in den Förderbereich 20 gepumpt werden, von wo aus es durch die nicht gezeigte Leitung zum Hochdruck-Auslaßanschluß am Pumpengehäuse 10 strömt.The inlet valve 25 is designed so that it during of the suction stroke of the piston 16, that is, if this comes from the Piston guide 17 moved out, opens so that during the Suction strokes to be conveyed medium from the inlet area 15 through the inlet bore 24, the inlet channel 23 and the open inlet valve 25 can flow into the work space 26. During the Delivery strokes, i.e. when the piston 16 is in the piston guide 17 moves in, closes the inlet valve 25, so that the Working space 26 enclosed medium under pressure becomes. As soon as the pressure in the working space 26 is from the exhaust valve 27 predetermined high pressure reached, this and that opens medium to be pumped under high pressure can be open outlet valve 27, the high pressure outlet region 28, the Outlet bores 21 are pumped into the delivery area 20, from where it goes through the line, not shown, to the high pressure outlet connection flows on the pump housing 10.

Am freien aus der Kolbenführung 17 hervorstehenden Ende Ende des Kolbens 16 ist ein Gleitschuh 29 angebracht, mit dem sich der Kolben 16 über einen auf einem als Kurbelelement dienenden Exzenter 31 der Pumpenwelle 14 drehbar gelagerten Hubring 30 abstützt, so daß der Kolben 16 von der Pumpenwelle 14 antreibbar ist. Um den Kolben 16 während seines Saughubs über den Gleitschuh 29 mit dem Hubring 30 in Eingriff zu halten, ist eine Feder 32 vorgesehen, die sich mit ihrem einen Ende am Gleitschuh 29 und mit ihrem anderen Ende am Halteteil 18 abstützt.At the free end protruding from the piston guide 17 of the piston 16, a slide shoe 29 is attached, with which the piston 16 via one on a serving as a crank element Eccentric 31 of the pump shaft 14 rotatably mounted cam ring 30 supports so that the piston 16 can be driven by the pump shaft 14 is. To over the piston 16 during its suction stroke to hold the slide shoe 29 in engagement with the lifting ring 30, a spring 32 is provided which is at one end on the slide shoe 29 and with its other end on the holding part 18th supports.

Wie besonders gut in Fig. 3 zu erkennen ist, weist die Pumpenwelle 14 einen Dichtbund 33 auf, an den sich auf der vom Exzenter 31 abgewandten Seite ein Lagerzapfen 34 anschließt, der gegenüber dem Dichtbund 33 einen verringerten Durchmesser aufweist. An der zwischen dem Lagerzapfen 34 und dem Dichtbund 33 gebildeten Schulter 35 sind Mitnehmernasen 36 vorgesehen, die einander in Bezug auf die Pumpenwellenachse A diametral gegenüberliegen. Zwischen dem Dichtbund 33 und dem Exzenter 31 ist ein umfangsmäßig umlaufender Haltesteg 37 vorgesehen, dessen Außenumfang größer ist als der des Dichtbunds 33. An der freien Stirnseite des Exzenters 31 ist ein Hilfszapfen 38 angebracht, der koaxial mit dem Lagerzapfen 34 ausgerichtet ist.As can be seen particularly well in FIG. 3, the pump shaft 14 on a sealing collar 33 to which on the Eccentric 31 facing away from a bearing pin 34 connects the reduced diameter compared to the sealing collar 33 having. On the between the journal 34 and the sealing collar 33 formed shoulder 35 driver lugs 36 are provided, which are diametrically opposed to each other with respect to the pump shaft axis A. opposite. Between the sealing collar 33 and the eccentric 31, a circumferential retaining web 37 is provided, whose outer circumference is larger than that of the sealing collar 33. On the free end face of the eccentric 31 is an auxiliary pin 38 attached, which is aligned coaxially with the journal 34 is.

Wie Fig. 1 zeigt, ist die Pumpenwelle 14 so in das Pumpengehäuse 10 eingesetzt, daß ihr Hilfszapfen 38 mit radialem Spiel in einer im Pumpengehäuse 10 vorgesehenen Hilfsbohrung 39 läuft, während der Dichtbund 33 im Bereich einer Durchlaßöffnung 40 des Pumpengehäuses 10 liegt, die von einem sich in Bezug auf die Pumpenwellenachse A axial erstreckenden Zentrierbund 41 umgeben ist. Der Zentrierbund 41 und die Hilfsbohrung 39 sind dabei miteinander koaxial ausgerichtet.As shown in Fig. 1, the pump shaft 14 is in the pump housing 10 used that their auxiliary pin 38 with radial Play in an auxiliary bore provided in the pump housing 10 39 runs while the sealing collar 33 in the region of a passage opening 40 of the pump housing 10 is located in one of With respect to the pump shaft axis A axially extending centering collar 41 is surrounded. The centering collar 41 and the auxiliary bore 39 are coaxially aligned with each other.

In die Durchlaßöffnung 40 ist eine Radialwellendichtung 43 dicht eingesetzt, deren Innendurchmesser größer ist als der Außendurchmesser des Dichtbundes 33. Am Innendurchmesser der Radialwellendichtung 43 ist eine Stützfläche 42 vorgesehen. Zur Abdichtung des Zulaufsbereichs 15 bzw. des Aufnahmebereichs 13 für den Exzenter 31 der Pumpenwelle 14 ist in der Radialwellendichtung 43 eine Dichtlippe 44 gehalten, deren Innendurchmesser kleiner ist als der Außendurchmesser des Dichtbundes 33. Somit wird die Dichtlippe 44 vom Dichtbund 33 verformt und liegt abdichtend an diesem an. Anstatt der Dichtlippe 44 kann auch beispielsweise ein Nutring oder dergleichen verwendet werden.A radial shaft seal 43 is in the passage opening 40 tightly inserted, the inner diameter of which is larger than that Outer diameter of the sealing collar 33. On the inner diameter of the A support surface 42 is provided for the radial shaft seal 43. For sealing the inlet area 15 or the receiving area 13 for the eccentric 31 of the pump shaft 14 is in the Radial shaft seal 43 held a sealing lip 44, the Inner diameter is smaller than the outer diameter of the Sealing collar 33. Sealing lip 44 thus becomes sealing collar 33 deforms and lies sealingly against it. Instead of Sealing lip 44 can also be, for example, a grooved ring or the like be used.

Bei der Lagerung und beim Transport der Pumpe, also der selbstständigen, aus Pumpengehäuse 10, Pumpenelement 12, Pumpenwelle 14 und Radialwellendichtung 43 bestehenden Baugruppe, wird die Pumpenwelle 14 von der bzw. den Federn 32 mit ihrem Dichtbund 33 gegen die an der Radialwellendichtung 43 vorgesehene Stützfläche 42 und mit dem Hilfszapfen 38 gegen die Innenwand der Hilfsbohrung 39 gedrückt und festgehalten. Dabei kann die Dichtlippe 44 der Radialwellendichtung 43 nur um die halbe Durchmesserdifferenz zwischen dem Innendurchmesser der Stützfläche 42 und dem Außendurchmesser des Dichtbundes 33 verformt werden. Diese Durchmesserdifferenz ist dabei so ausgelegt, daß eine bleibende Verformung der Dichtlippe 44 vermieden wird. Zweckmäßigerweise ist der Innendurchmesser der Dichtlippe 44 so gewählt, daß die Dichtlippe 44, auch wenn sie in der beschriebenen Weise während Transport und Lagerung verformt ist, das Innere der Pumpe gegen Staub und Schmutz abdichtet. Die Radialwellendichtung 43 ist so geformt und die Dichtlippe 44 ist so eingebaut, daß die Pumpenwelle 14 an der Stützfläche 42 zur Anlage kommt, bevor die Dichtlippe 44 durch Quetschung beschädigt werden könnte.When storing and transporting the pump, i.e. the independent, from pump housing 10, pump element 12, pump shaft 14 and radial shaft seal 43 existing assembly, is the pump shaft 14 by the spring or springs 32 with its sealing collar 33 against that on the radial shaft seal 43 provided support surface 42 and with the auxiliary pin 38 against pressed and held the inner wall of the auxiliary bore 39. The sealing lip 44 of the radial shaft seal 43 can only by half the diameter difference between the inner diameter the support surface 42 and the outer diameter of the sealing collar 33 are deformed. This difference in diameter is included designed so that a permanent deformation of the sealing lip 44th is avoided. The inside diameter is expedient the sealing lip 44 chosen so that the sealing lip 44, too if in the manner described during transportation and storage is deformed, the inside of the pump against dust and Seals dirt. The radial shaft seal 43 is shaped in this way and the sealing lip 44 is installed so that the pump shaft 14 comes to rest on the support surface 42 before the sealing lip 44 could be damaged by crushing.

Der Dichtbund 33 und die Stützfläche 42 der Radialwellendichtung 43 bilden dabei zusammen mit dem Hilfszapfen 38 und der Hilfsbohrung 39 eine Transporthalterung für die Pumpenwelle 14 im Pumpengehäuse 10, die die Pumpenwelle 14 bei nicht am Motorgehäuse 45' befestigter Pumpe im wesentlichen in ihrer späteren Betriebslage im Pumpengehäuse 10 hält. Hierbei ist es von Vorteil, daß die ein erstes Haltemittel bildende Stützfläche 42 und die ein zweites Haltemittel bildende Hilfsbohrung 39 axial voneinander beabstandet sind, so daß die Pumpenwelle 14 im Pumpengehäuse 10 nicht verkippen kann. Damit läßt sich insbesondere verhindern, daß der oder die Kolben 16 zu weit aus der bzw. den zugeordneten Kolbenführungen 17 herausgezogen werden, was bei der Montage der Pumpe zu Problemen, insbesondere zu Beschädigungen der Kolben 16 beim Wiedereinschieben führen kann.The sealing collar 33 and the support surface 42 of the radial shaft seal 43 form together with the auxiliary pin 38 and Auxiliary hole 39 a transport bracket for the pump shaft 14 in the pump housing 10, which the pump shaft 14 at Motor housing 45 'attached pump essentially in its later operating position in the pump housing 10 holds. Here is it is advantageous that the forming a first holding means Support surface 42 and that forming a second holding means Auxiliary bore 39 are axially spaced apart, so that the pump shaft 14 in the pump housing 10 cannot tilt. This can in particular prevent that the or Piston 16 too far from the associated piston guides 17 can be pulled out, what to assemble the pump Problems, especially damage to the piston 16 when Reinsert.

Anstelle der Hilfsbohrung 39 kann als zweites Haltemittel auch ein Hilfszapfen oder dergleichen an der Innenwand des Pumpengehäuses 10 vorgesehen werden. In diesem Fall wäre dann eine entsprechende Hilfsbohrung oder dergleichen im bzw. am Exzenter 31 anzuordnen.Instead of the auxiliary bore 39, a second holding means can be used also an auxiliary pin or the like on the inner wall of the Pump housing 10 are provided. In this case it would be a corresponding auxiliary hole or the like in or on Eccentric 31 to be arranged.

Zusätzlich dient der Haltesteg 37 an der Pumpenwelle 14 während des Transports und der Lagerung zusammen mit der Radialwellendichtung 43 als Herausfallsicherung für die Pumpenwelle 14.In addition, the holding web 37 is used on the pump shaft 14 during transport and storage together with the radial shaft seal 43 as fallout protection for the pump shaft 14.

Um die Pumpe, also die aus Pumpengehäuse 10, Pumpenelement 12, Pumpenwelle 14 und Radialwellendichtung 43 bestehende selbständige Baugruppe an einer Wand 45 eines Verbrennungsmotors zu montieren und dabei die Pumpenwelle 14 mit einer angetriebenen Welle 46 des Verbrennungsmotors, z. B. mit einer Nockenwelle in Eingriff zu bringen, wird zunächst der Lagerzapfen 34 der Pumpenwelle 14 in eine, insbesondere als Paßbohrung ausgebildete, axiale Lagerbohrung 47 in der Welle 46 und nachfolgend der Zentrierbund 41 in eine zur Welle 46 des Verbrennungsmotors koaxiale Aufnahmebohrung 48 eingeschoben. Dabei treten die Mitnehmernasen 36 an der Schulter 35 der Pumpenwelle 14 in eine als Mitnehmerausnehmung dienende Nut 49 am stirnseitigen Ende der Welle 46 ein, die wie insbesondere in den Fig. 2a und 2b gezeigt, in einem stirnseitigen Bund 50 vorgesehen ist. Die Pumpenwelle 14 ist somit durch das Fügen des Lagerzapfens 34 der Pumpenwelle 14 in die Lagerbohrung 47 der Welle 46 radial und durch des Verzahnen der Mitnehmernase 36 mit der Nut 49 drehfest in der Welle 46 des Verbrennungsmotors gelagert.Around the pump, i.e. the pump element 10, pump element 12, pump shaft 14 and radial shaft seal 43 existing independent assembly on a wall 45 of an internal combustion engine to assemble and the pump shaft 14 with a driven Shaft 46 of the internal combustion engine, e.g. B. with a To engage camshaft, the bearing journal is first 34 of the pump shaft 14 in one, in particular as a fitting bore trained, axial bearing bore 47 in the shaft 46 and subsequently the centering collar 41 in a to the shaft 46 of the Internal combustion engine inserted coaxial mounting hole 48. The driver lugs 36 on the shoulder 35 of the Pump shaft 14 in a groove serving as a driver recess 49 at the front end of the shaft 46, which as in particular 2a and 2b, in an end face Bund 50 is provided. The pump shaft 14 is thus through the joining of the journal 34 of the pump shaft 14 into the bearing bore 47 of the shaft 46 radially and by meshing the Driving nose 36 with the groove 49 rotatably in the shaft 46 of the Internal combustion engine stored.

Die radiale Lagerung der Pumpenwelle 14 an der Welle 46 des Verbrennungsmotors läßt sich auch in umgekehrter Weise mit einem Lagerzapfen an der Welle 46 und einer Lagerbohrung in der Pumpenwelle 14 verwirklichen. Ferner ist es möglich, sowohl die Welle 46 des Verbrennungsmotors als auch die Pumpenwelle 14 jeweils mit einer Lagerbohrung zu versehen, und zur Lagerung der Pumpenwelle 14 an der Welle 46 des Verbrennungsmotors einen Lagerzapfen zu verwenden, der in beide Lagerbohrungen eingesetzt wird. Insbesondere lassen sich hierdurch sowohl an der noch nicht montierten Pumpe als auch am Verbrennungsmotor weit über das Pumpengehäuse 10 bzw. das Motorgehäuse 45' vorstehende Teile vermeiden, die insbesondere beim Transport leicht beschädigt werden können.The radial mounting of the pump shaft 14 on the shaft 46 of the Internal combustion engine can also be reversed a journal on the shaft 46 and a bearing bore in realize the pump shaft 14. It is also possible to both the shaft 46 of the internal combustion engine as well as the pump shaft 14 to be provided with a bearing bore, and Bearing of the pump shaft 14 on the shaft 46 of the internal combustion engine to use a journal that fits into both bearing bores is used. In particular, this allows both on the not yet installed pump and on the internal combustion engine far beyond the pump housing 10 or the motor housing 45 'Avoid protruding parts, in particular can easily be damaged during transport.

Die axiale Lagerung der Pumpenwelle 14 kann in nahezu jeder beliebigen Weise erfolgen, da hier nur sehr geringe Lagerkräfte aufzunehmen sind. Z. B. kann sich die Pumpenwelle 14 mit dem Hilfszapfen 38 am Boden der Hilfsbohrung 39 oder mit der Strinfläche des Exzenters 31 direkt oder über den Hubring 30 an einer gegenüberliegenden Innenwand des Pumpengehäuses 10 abstützen. In der anderen axialen Richtung kann die axiale Lagerung der Pumpenwelle 14 beispielsweise durch Abstützung der Mitnehmernasen 36 an der Welle 46 des Verbrennungsmotors oder durch Abstützung des Haltestegs 37 am Stützring 44 erfolgen.The axial bearing of the pump shaft 14 can be in almost everyone done in any way, since only very low bearing forces are to be included. For example, the pump shaft 14 with the auxiliary pin 38 at the bottom of the auxiliary bore 39 or with the line surface of the eccentric 31 directly or via the cam ring 30 on an opposite inner wall of the pump housing Support 10. In the other axial direction, the axial Bearing of the pump shaft 14 for example by support the driver lugs 36 on the shaft 46 of the internal combustion engine or by supporting the retaining web 37 on the support ring 44.

In der Aufnahmebohrung 48 ist ein Leckraum für aus dem Zulaufbereich 15 durch die Radialwellendichtung 43 ausleckendes, zu förderndes Medium, insbesondere Kraftstoff, gebildet, der durch einen in die Außenumfangsfläche des Zentrierbundes 41 eingesetzten Dichtring 52 gegen die äußere Umgebung und durch eine Lippendichtung 51 gegen die Welle 46 und damit gegen Schmieröl aus deren Wellenlager abgedichtet ist. Dieser Leckraum wird beispielsweise über eine Bohrung 48' im Pumpengehäuse 10 entsorgt, die, wenn das zu fördernde Medium Kraftstoff ist, in nicht näher dargestellter Weise mit einem Ansaugrohr des Verbrennungsmotors verbunden sein kann. Anstelle der Bohrung 48' im Pumpengehäuse 10 kann auch, wie in Figur 5 dargestellt eine Bohrung 48" im Motorgehäuse 45' vorgesehen sein.In the receiving bore 48 there is a leakage space for from the inlet area 15 leaking through the radial shaft seal 43, medium to be conveyed, in particular fuel, is formed, the one in the outer peripheral surface of the centering collar 41 used sealing ring 52 against the external environment and by a lip seal 51 against the shaft 46 and thus against Lubricating oil from their shaft bearings is sealed. This Leakage space is, for example, via a bore 48 'in the pump housing 10 disposed of when the medium to be pumped fuel is, in a manner not shown with an intake pipe of the internal combustion engine can be connected. Instead of the bore 48 'in the pump housing 10 can also, as in FIG. 5 shown a bore 48 "provided in the motor housing 45 ' his.

Durch eine ständige Entsorgung des Leckraums wird die Lippendichtung 51, die zur Abdichtung gegen Schmieröl ausgelegt ist, gegen schädliche Einwirkungen des zu fördernden Mediums, insbesondere Kraftstoff, geschützt. Hierdurch läßt sich die Lebensdauer der Lippendichtung 51 verlängern.Through permanent disposal of the leakage space, the lip seal 51, which is designed to seal against lubricating oil is against harmful effects of the medium to be pumped, especially fuel, protected. This allows the Extend the life of the lip seal 51.

Da die Aufnahmebohrung 48 in der Wand 45 des Verbrennungsmotors mit der angebtriebenen Welle 46 koaxial ausgerichtet ist und da der Zentrierbund 41 mit der Hilfsbohrung 39 ebenfalls koaxial bzw. konzentrisch ausgerichtet ist, ist die Pumpenwelle 14, die mit ihrem Lagerzapfen 34 in der als Paßbohrung ausgebildeten Lagerbohrung 47 der Welle 46 gelagert ist, auch mit ihrem Hilfszapfen 38 zur Hilfsbohrung 39 und mit ihrem Stützbund 33 zur Radialwellendichtung 43 koaxial ausgerichtet. Da ferner der Außendurchmesser des Hilfszapfens 38 kleiner ist als der Innendurchmesser der Hilfsbohrung 39 und da der Außendurchmesser des Dichtbundes 33 kleiner ist, als der Durchmesser der Stützfläche 42 an der Radialwellendichtung 43, läuft die Pumpenwelle 14 beim Betrieb, also wenn sie vom Verbrennungsmotor über die Welle 46, vorzugsweise die Nockenwelle, angetrieben wird, ohne eigene radiale Lagerung im Pumpengehäuse 10 in diesem frei ohne irgendwo zu streifen. Since the receiving bore 48 in the wall 45 of the internal combustion engine is coaxially aligned with the driven shaft 46 and since the centering collar 41 with the auxiliary bore 39 also is aligned coaxially or concentrically, the pump shaft 14, with its journal 34 in the as a fitting bore trained bearing bore 47 of the shaft 46 is mounted, too with their auxiliary pin 38 to the auxiliary bore 39 and with their Support collar 33 coaxially aligned with the radial shaft seal 43. Furthermore, since the outer diameter of the auxiliary pin 38 is smaller is as the inner diameter of the auxiliary bore 39 and there the outer diameter of the sealing collar 33 is smaller than that Diameter of the support surface 42 on the radial shaft seal 43, the pump shaft 14 runs during operation, that is if it is from Internal combustion engine via shaft 46, preferably the camshaft, is driven without its own radial bearing in the pump housing 10 free in this without grazing anywhere.

Die an die Wand 45 des Motorgehäuses 45' des Verbrennungsmotors angesetzte Baugruppe aus Pumpengehäuse 10, Pumpenelement 12, Pumpenwelle 14 und Radialwellendichtung 43 kann beispielsweise mittels Schrauben 53, von denen nur eine gezeigt ist, an der Wand 45 des Verbrennungsmotors befestigt werden.The on the wall 45 of the motor housing 45 'of the internal combustion engine attached assembly from pump housing 10, pump element 12, pump shaft 14 and radial shaft seal 43 can for example by means of screws 53, only one of which is shown is attached to the wall 45 of the internal combustion engine.

Anstelle der beschriebenen Pumpenwelle 14 mit den Mitnehmernasen 36 kann auch eine Pumpenwelle 14' verwendet werden, die im Lagerzapfen 34 benachbart zum Dichtbund 33 eine Querbohrung 54 aufweist, in die, wie in Fig. 5 im Zusammenhang mit einem zweiten Ausführungsbeispiel der Erfindung dargestellt, ein Mitnehmerstift 55 eingesetzt ist, der über den Außenumfang des Lagerzapfens 34 so weit vorsteht, daß er in Mitnahmeeingriff mit den Nuten 49 an der Welle 46 des Verbrennungsmotors bringbar ist.Instead of the described pump shaft 14 with the driver lugs 36, a pump shaft 14 'can also be used in the journal 34 adjacent to the sealing collar 33, a transverse bore 54, in which, as in Fig. 5 in connection with shown a second embodiment of the invention, a driver pin 55 is used, which is on the outer circumference of the journal 34 protrudes so far that it is in engagement with the grooves 49 on the shaft 46 of the internal combustion engine is feasible.

Wie Fig. 5 zeigt, umfaßt das zweite Ausführungsbeispiel der erfindungsgemäßen Pumpe ein Pumpengehäuse 10, in dem ein oder mehrere Pumpenelemente 12 und eine Pumpenwelle 14' angeordnet sind. Der Aufbau und die Anordnung des Pumpenelements 12 entspricht dem anhand von Fig. 1 beschriebenen Aufbau. Die Pumpenwelle 14' unterscheidet sich von der anhand von Fig. 1 und 3 beschriebenen Pumpenwelle nur durch die unterschiedliche Ausbildung der Mitnahmemittel für die drehfeste Lagerung an der Welle 46 des Verbrennungsmotors. Anstelle der bei der Pumpe nach Fig. 1 vorgesehenen Radialwellendichtung 43 ist jedoch bei der in Fig. 5 gezeigten Pumpe eine Axialwellendichtung 56 vorgesehen, um den Zulaufbereich 15 gegen die Aufnahmebohrung 48 in der Wand 45 des Verbrennungsmotors abzudichten.5 shows, the second embodiment includes the Pump according to the invention, a pump housing 10 in which one or a plurality of pump elements 12 and a pump shaft 14 'are arranged are. The structure and arrangement of the pump element 12 corresponds the structure described with reference to FIG. 1. The pump shaft 14 'differs from that with reference to FIGS. 1 and 3 described pump shaft only by the different Training of the means of transport for the non-rotatable storage the shaft 46 of the internal combustion engine. Instead of at 1 is provided radial shaft seal 43 however, in the pump shown in Fig. 5, an axial shaft seal 56 provided to the inlet area 15 against the Seal the receiving bore 48 in the wall 45 of the internal combustion engine.

Die Axialwellendichtung 56 umfaßt einen auf den Dichtbund 33 aufgepreßten Mitnehmer 57, in den, benachbart zum Haltesteg 37 eine Feder 58 und ein Druckring 59 auf der vom Haltesteg 37 abgewandten Seite der Feder 58 eingesetzt ist. Dabei ist zwischen dem Druckring 59 und dem Dichtbund 33 ein Dichtring 60 angeordnet, der den Druckring 59 zum Toleranzausgleich in axialer Richtung verschiebbar gegen den Dichtbund 33 abdichtet.The axial shaft seal 56 includes one on the sealing collar 33 pressed driver 57, in the, adjacent to the holding web 37 a spring 58 and a pressure ring 59 on the from the holding bridge 37 opposite side of the spring 58 is used. It is a sealing ring between the pressure ring 59 and the sealing collar 33 60 arranged, the pressure ring 59 for tolerance compensation in seals axially against the sealing collar 33.

In eine axiale Verlängerung 61 des Zentrierbundes 41 ist ein Gleitring 62 eingesetzt, der auf seinem Außenumfang einen Dichtring 63 trägt. Eine Scheibe 64, die an der Verlängerung 61 des Zentrierbundes 41 z. B. durch Verbördeln befestigt ist, hält den Gleitring 62 zusammen mit dem Dichtring 63 im Aufnahmebereich der Verlängerung 61 des Zentrierbundes 41.In an axial extension 61 of the centering collar 41 is a Slide ring 62 used, the one on its outer circumference Seal ring 63 carries. A washer 64 attached to the extension 61 of the centering collar 41 z. B. attached by crimping is, the slide ring 62 together with the sealing ring 63 in Receiving area of the extension 61 of the centering collar 41.

Beim Zusammenbau der Pumpe nach Fig. 5 werden zunächst der Mitnehmer 57, die Feder 58, der Dichtring 60 und der Druckring 59 in dieser Reihenfolge auf dem Dichtbund 33 der Pumpenwelle 14' montiert. Anschließend wird der Mitnehmerstift 55 in die Querbohrung 54 eingesetzt. Da die Länge des Mitnehmerstifts 55 größer ist als der Außendurchmesser des Dichtbundes 33 bzw. größer als der Innendurchmesser des Druckrings 59 hält der Mitnehmerstift 55 die auf der Pumpenwelle 14' angeordneten Teile der Axialwellendichtung 56 auf dem Dichtbund 33 und dient somit als Herausfallsicherung insbesondere für den Druckring 59 so lange dieser noch nicht am Gleitring 62 anliegt.When assembling the pump of FIG. 5, the Driver 57, the spring 58, the sealing ring 60 and the pressure ring 59 in this order on the sealing collar 33 of the pump shaft 14 'mounted. Then the driver pin 55 inserted into the transverse bore 54. Because the length of the driving pin 55 is larger than the outer diameter of the sealing collar 33 or larger than the inner diameter of the pressure ring 59 the driver pin 55 holds those arranged on the pump shaft 14 ' Parts of the axial shaft seal 56 on the sealing collar 33 and thus serves as protection against falling out, in particular for the pressure ring 59 as long as it is not on the slide ring 62 is present.

Sobald die Pumpenwelle 14' in das Pumpengehäuse 10 eingesetzt und auch die in der axialen Verlängerung 61 des Zentrierbundes 41 gehaltenen Teile der Axialwellendichtung 56 montiert sind, wird der Druckring 59 von der Feder 58 mit seiner von der Feder 58 abgewandten Stirnfläche 65, die eine radiale, quer zur Pumpenwellenachse A liegende Dichtfläche bildet, axial gegen eine Stirnfläche am Gleitring 62 gepreßt, die eine als Dichtfläche dienende Gleitfläche 66 darstellt. Die Kraft der Feder 58, die zwischen dem Druckring 59 und dem Haltesteg 37 angeordnet ist, wird über den Haltesteg 37, den Exzenter 31 und den Hilfszapfen 38 am Pumpengehäuse 10 abgestützt.As soon as the pump shaft 14 'is inserted into the pump housing 10 and also in the axial extension 61 of the centering collar 41 held parts of the axial shaft seal 56 mounted are, the pressure ring 59 of the spring 58 with its of End face 65 facing away from spring 58, which has a radial forms a sealing surface lying transversely to the pump shaft axis A, axially pressed against an end face on the slide ring 62, the one represents as a sealing surface sliding surface 66. The Force of the spring 58 which between the pressure ring 59 and the Holding web 37 is arranged, the holding web 37, the Eccentric 31 and the auxiliary pin 38 supported on the pump housing 10.

Die Axialwellendichtung 56 wirkt hierbei als erstes Haltemittel der Transporthalterung, während die Scheibe 64, die den Gleitring 62 in der Verlängerung 61 des Zentrierbundes 41 hält, als Herausfallsicherung beim Transport und bei der Lagerung der Pumpe dient.The axial shaft seal 56 acts here as the first holding means the transport bracket, while the disc 64, which the Slide ring 62 in the extension 61 of the centering collar 41 holds, as fall-out protection during transport and storage serves the pump.

Um während des Betriebs der Pumpe für die Pumpenwelle 14' ein reibungsarmes axiales Gleitlager bereitzustellen, ist in der Hilfsbohrung 39 eine Scheibe 67 eingesetzt, die den Hilfszapfen 38 in axialer Richtung abstützt und vorzugsweise aus einem reibungsarmen Werkstoff, insbesondere aus einem Gleitlagerwerkstoff hergestellt ist.To one during the operation of the pump for the pump shaft 14 ' Providing low-friction axial plain bearings is in the Auxiliary hole 39 inserted a washer 67, the auxiliary pin 38 is supported in the axial direction and preferably from one Low-friction material, in particular from a plain bearing material is made.

Die Verwendung der beschriebenen Axialwellendichtung 56 bei der erfindungsgemäßen Pumpe hat den Vorteil, daß ein mögliches Radialspiel der Welle 46 des Verbrennungsmotors, das zu einem exzentrischen Umlauf der Pumpenwellenachse A und damit zu einem exzentrischen Umlauf des Druckrings 59 führt, keinen Einfluß auf die Abdichtung der Pumpe hat, da die aufeinanderliegenden Dichtflächen eben sind und senkrecht zum Sollverlauf der Pumpenwellenachse A liegen. Eine infolge des Radialspiels der Welle 46 des Verbrennungsmotors auftretende Verkippung des Druckrings 59 gegenüber dem Dichtbund 33 wird hierbei durch die Feder 58 und den Dichtring 60 ausgeglichen.The use of the axial shaft seal 56 described the pump according to the invention has the advantage that a possible Radial play of the shaft 46 of the internal combustion engine, that too an eccentric rotation of the pump shaft axis A and thus leads to an eccentric circulation of the pressure ring 59, none Influence on the sealing of the pump, because the superimposed Sealing surfaces are flat and perpendicular to the nominal course the pump shaft axis A. One due to radial play tilting of the shaft 46 of the internal combustion engine of the pressure ring 59 relative to the sealing collar 33 compensated by the spring 58 and the sealing ring 60.

Die erfindungsgemäße Pumpe, die beispielsweise anhand von Radialkolbenpumpen mit einem Pumpenelement 12 oder mehreren, vorzugsweise mit drei sternförmig angeordneten Pumpenelementen 12 beschrieben wurde, läßt sich auch als Axialkolbenpumpe ausbilden. Darüber hinaus ist es möglich, die erfindungsgemäße Pumpe, bei der die Pumpenwelle 14, 14' ohne Eigenlagerung im Pumpengehäuse 10 dicht in diesem eingesetzt und in einer Antriebswelle radial und drehfest lagerbar ist, auch als Zahnradpumpe oder dergleichen auszuführen. Besonders vorteilhaft läßt sich die Erfindung bei allen Pumpenarten einsetzen, bei denen ein oder mehrere Arbeitselemente über einen Exzenter einer Pumpenwelle anzutreiben sind.The pump according to the invention, for example using radial piston pumps with one pump element 12 or more, preferably with three pump elements arranged in a star shape 12 has been described, can also be used as an axial piston pump form. In addition, it is possible to use the invention Pump in which the pump shaft 14, 14 'without self-storage in the pump housing 10 used tightly in this and in one Drive shaft is radially and non-rotatably supported, also as Gear pump or the like to perform. Particularly advantageous the invention can be used with all types of pumps, in which one or more work elements via an eccentric a pump shaft are to be driven.

Die erfindungsgemäße Pumpe hat insbesondere den Vorteil, daß sie als selbständige Baugruppe unabhängig von anderen Teilen hergestellt und als vollständig vormontierte, bereits abgedichtete Baugruppe direkt beim Hersteller geprüft werden kann. Dabei läßt sich insbesondere auch der Pumpenbetrieb, also sowohl die Funktionsfähigkeit der einzelnen Pumpenelemente 12, als auch deren Zusammenwirken mit der Pumpenwelle 14, 14' und die Dichtheit vollständig prüfen. Ein weiterer Vorteil besteht darin, daß bei der späteren Montage am endgültigen Einsatzort, also an einem Verbrennungsmotor, kein Montageschmutz in die Pumpe eindringen kann. Darüber hinaus verlängert der Wegfall der Lagerung der Pumpenwelle 14, 14' im Pumpengehäuse 10 die Lebensdauer der Pumpe.The pump according to the invention has the particular advantage that it as an independent assembly independent of other parts manufactured and as a fully pre-assembled, already sealed Assembly are checked directly at the manufacturer can. In particular, the pump operation, both the functionality of the individual pump elements 12, as well as their interaction with the pump shaft 14, 14 'and check the tightness completely. Another The advantage is that later assembly on the final Location, i.e. on an internal combustion engine, none Dirt can get into the pump. Furthermore extends the elimination of the bearing of the pump shaft 14, 14 ' in the pump housing 10 the life of the pump.

Die bei der erfindungsgemäßen Pumpe vorgesehene Transporthalterung erleichert wesentlich die spätere Montage der Pumpe am Motorgehäuse 45', da die Pumpenwelle 14, 14' und damit auch der Lagerzapfen 34 im wesentlichen in der vorgesehenen Betriebsstellung gehalten werden.The transport bracket provided in the pump according to the invention significantly simplifies the later assembly of the pump on Motor housing 45 'because the pump shaft 14, 14' and thus also the bearing pin 34 essentially in the intended operating position being held.

Die Verwendung einer Axialwellendichtung ermöglich darüber hinaus auf besonders zuverlässige Weise eine Abdichtung der Pumpe unabhängig von Toleranzen der Welle 46 des Verbrennungsmotors insbesondere unabhängig von deren Radialspiel.The use of an axial shaft seal enables this also sealing in a particularly reliable manner Pump regardless of tolerances of the shaft 46 of the internal combustion engine especially regardless of their radial play.

Als Werkstoff für den Druckring 59 und den Gleitring 62 können formstabile, reibungsmäßig und verschleißmäßig bestens aufeinander abgestimmte, kraftstoffbeständige Werkstoffe verwendet werden. Die Feder 58 sorgt für eine, von Maßtoleranzen und Verschleiß weitgehend unabhängige, gleichmäßige und gleichbleibende Flächenpressung zwischen den aufeinander gleitenden Flächen des Druckrings 59 und des Gleitrings 62, also zwischen der Stirnfläche 65 und der Gleitfläche 66.As a material for the pressure ring 59 and the sliding ring 62 can dimensionally stable, frictionally and wear-resistant coordinated, fuel-resistant materials are used become. The spring 58 ensures a dimensional tolerance and wear largely independent, uniform and constant surface pressure between each other sliding surfaces of the pressure ring 59 and the sliding ring 62, that is, between the end face 65 and the sliding surface 66.

Bei dem in Figur 1 dargestellten Ausführungsbeispiel ist die Stützfläche 42 über die Radialwellendichtung 43 indirekt am Pumpengehäuse 10 vorgesehen. Es ist aber auch möglich, z. B. den Außendurchmesser des Haltesteges 37 so auf den Durchmesser der Durchlaßöffnung 40 abzustimmen, daß vor dem Anbau des Pumpengehäuses 10 an das Motorgehäuse 45' sich die Pumpenwelle 14 bzw. 14' über den umlaufenden Haltesteg 37 an der Durchlaßöffung 40 abstützen kann. Bei dieser Variante dient die Durchlaßöffnung 40 als direkt am Pumpengehäuse 10 vorgesehene Stützfläche 42' (Fig. 5). Die Stützfläche 42 bzw. 42' ist also jeweils mindestens indirekt mit dem Pumpengehäuse 10 verbunden.In the embodiment shown in Figure 1 is the Support surface 42 indirectly via the radial shaft seal 43 Pump housing 10 provided. But it is also possible, for. B. the outer diameter of the holding web 37 to the diameter the passage opening 40 to vote that before the installation of the Pump housing 10 to the motor housing 45 'the pump shaft 14 or 14 'on the circumferential retaining web 37 on the Passage opening 40 can support. This variant serves the passage opening 40 as provided directly on the pump housing 10 Support surface 42 '(Fig. 5). The support surface 42 or 42 ' is therefore at least indirectly with the pump housing 10 connected.

Zwischen der Stützfläche 42 bzw. 42' und dem Bereich der Pumpenwelle 14 bzw. 14', der vor dem Anbau des Pumpengehäuses 10 an das Motorgehäuse 45' an der Stützfläche 42, 42' anliegt, gibt es eine Durchmesserdifferenz, also einen radialen Abstand, wobei der Abstand so bemessen ist, daß die Pumpenwelle 14, 14', sobald die Pumpe an das Motorgehäuse 45' angebaut ist, unabhängig von eventuell auftretendem Radialschlag der Welle 46, die Stützfläche 42 bzw. 42' nicht berühren kann.Between the support surface 42 or 42 'and the area of the pump shaft 14 and 14 ', respectively, before the pump housing 10 abuts the motor housing 45 'on the support surface 42, 42', there is a difference in diameter, i.e. a radial distance, the distance being such that the pump shaft 14, 14 'as soon as the pump is attached to the motor housing 45' is independent of any radial runout that may occur Shaft 46, the support surface 42 or 42 'can not touch.

Claims (21)

  1. Pump, in particular high-pressure pump for a fuel injector of an internal combustion engine, having a pump housing, having at least one working chamber which is located in the pump housing in functional terms between an inflow region and a delivery region and in which a working element is arranged in a moveable manner, and having a pump shaft which is provided in the pump housing and by means of which the working element can be driven, characterized in that the pump housing (10) can be fastened on a wall (45) of a housing (45') of an internal combustion engine, it being possible for the pump shaft (14, 14') to be mounted radially on an internal-combustion-engine shaft (46) mounted in the engine housing (45').
  2. Pump according to Claim 1, characterized in that a transporting mount (33, 42, 42', 38, 39; 33, 56, 38, 39) for the pump shaft (14; 14') is provided, said mount retaining the pump shaft (14; 14') essentially in its operating position as long as the pump housing (10) is not fastened on the engine housing (45').
  3. Pump according to Claim 2, characterized in that the transporting mount comprises first and second retaining means (42, 42'; 56 and 39), which are spaced apart from one another in the direction of the longitudinal axis of the pump shaft (14, 14').
  4. Pump according to Claim 3, characterized in that the first retaining means (42, 42'; 56) support the pump shaft (14; 14') in the region of a through-passage opening (40) provided in the pump housing (10), while the second retaining means (39) act on the inner housing end of the pump shaft (14, 14').
  5. Pump according to one of Claims 1 to 4, characterized in that the pump shaft (14, 14') is guided, by way of its drive end, with sealing action through a through-passage opening (40) provided in the pump housing (10).
  6. Pump according to Claim 5, characterized in that the pump shaft (14; 14') has a sealing collar (33) which interacts with a seal (43; 56), which grips around the pump shaft (14; 14'), in order to seal the pump housing (10) in the through-passage region for the pump shaft (14; 14').
  7. Pump according to Claim 6, characterized in that provided at least indirectly in the pump housing (10) is a supporting surface (42, 42') which grips around the pump shaft (14, 14') and of which the diameter is larger than the corresponding diameter of the pump shaft (14, 14').
  8. Pump according to Claim 6 or 7, characterized in that the seal (43), which grips around the pump shaft (14; 14'), has a radially inner sealing lip (44) which has its inner circumference resting on the sealing collar (33) and of which the internal diameter is smaller than the external diameter of the sealing collar (33).
  9. Pump according to Claim 6, characterized in that arranged with sealing action on the sealing collar (33) of the pump shaft (14') is an axially displaceable pressure-exerting ring (59) which is pressed, by way of an end surface (65), against a radially positioned sliding surface (66) which is provided on a sliding ring (62) which is inserted with sealing action into the through-passage opening (40) for the pump shaft (14') and is fixed axially at least in one direction.
  10. Pump according to one of Claims 6 to 9, characterized in that, on that side of the sealing collar (33) which is assigned to the pump housing (10), the pump shaft (14, 14') bears a retaining crosspiece (37) which projects radially outwards beyond the sealing collar (33).
  11. Pump according to one of Claims 6 to 10 and 3 or 4, characterized in that the seal (43; 56), which grips around the pump shaft (14; 14'), comprises or forms the first retaining means (42; 56).
  12. Pump according to one of the preceding claims, characterized in that, at its drive end, the pump shaft (14, 14') has a bearing journal (34) which projects out of the pump housing (10) and can be plugged into a corresponding axial bearing bore (47) in the shaft (46) of the internal combustion engine.
  13. Pump according to one of the preceding claims, characterized in that provided on the pump shaft (14; 14') is a driving means (36; 55) which, with the pump installed in the internal combustion engine, engages in at least one carry-along element (49) provided at the drive end of the shaft (46) of the internal combustion engine.
  14. Pump according to Claim 13, characterized in that the driving means provided is a driving pin (55) which extends transversely to the pump shaft (14') and projects outwards beyond the outer circumference of the bearing journal (34).
  15. Pump according to Claim 14, characterized in that the driving pin (55) extends, transversely to the pump shaft (14'), through a corresponding transverse bore (54) and projects outwards beyond the sealing collar (33) on at least one side.
  16. Pump according to one of the preceding claims, characterized in that, in order to align the pump shaft (14, 14') in the pump housing (10), there is provided on the latter a centring means (41) which is assigned to the through-passage opening (40) for the pump shaft (14, 14') and interacts with a corresponding centring means (48) which is assigned to the shaft (46) of the internal combustion engine and is located on the wall (45) of the engine housing (45').
  17. Pump according to Claim 16, characterized in that provided on the pump housing (10), as centring means, is a centring collar (41) which encloses the through-passage opening (40) for the pump shaft (14, 14') and can be inserted into an accommodating bore (48) which serves as the centring means, is coaxial with the shaft (46) of the internal combustion engine and is located in the wall (45) of the engine housing (45').
  18. Pump according to Claims 16 or 17 and 3 or 4, characterized in that, at its inner housing end, the pump shaft (14, 14') has a supporting means (38) which interacts with the second retaining means (39), arranged on the pump housing (10), the second retaining means (39) being aligned coaxially with the centring means (41).
  19. Pump according to Claim 18, characterized in that the pump shaft (14, 14') has, as supporting means, an auxiliary journal (38) which is coaxial with the bearing journal (34) and engages with radial play in an auxiliary bore (39) which is coaxial with the centring means (41) and serves as second retaining means.
  20. Pump according to Claim 19, characterized in that the auxiliary journal (38) is supported axially in the auxiliary bore (39).
  21. Pump according to Claim 19 or 20, characterized in that inserted into the auxiliary bore (39) is a disc (67) which serves as an axial bearing and preferably consists of a low-friction material, in particular of a plain-bearing material.
EP97953670A 1997-03-27 1997-12-24 Pump, especially high pressure pump for use in a fuel injector of an internal combustion engine Expired - Lifetime EP0906511B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19712872A DE19712872A1 (en) 1997-03-27 1997-03-27 Pump, in particular high-pressure pump for a fuel injection device of an internal combustion engine
DE19712872 1997-03-27
PCT/DE1997/003011 WO1998044258A1 (en) 1997-03-27 1997-12-24 Pump, especially high pressure pump for use in a fuel injector of an internal combustion engine

Publications (2)

Publication Number Publication Date
EP0906511A1 EP0906511A1 (en) 1999-04-07
EP0906511B1 true EP0906511B1 (en) 2001-11-14

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EP97953670A Expired - Lifetime EP0906511B1 (en) 1997-03-27 1997-12-24 Pump, especially high pressure pump for use in a fuel injector of an internal combustion engine

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US (1) US6210129B1 (en)
EP (1) EP0906511B1 (en)
JP (1) JP2000514902A (en)
DE (2) DE19712872A1 (en)
ES (1) ES2168687T3 (en)
WO (1) WO1998044258A1 (en)

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Also Published As

Publication number Publication date
ES2168687T3 (en) 2002-06-16
DE59705396D1 (en) 2001-12-20
EP0906511A1 (en) 1999-04-07
DE19712872A1 (en) 1998-10-01
WO1998044258A1 (en) 1998-10-08
JP2000514902A (en) 2000-11-07
US6210129B1 (en) 2001-04-03

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