EP0461213B1 - Fuel injection pump for internal combustion engines - Google Patents

Fuel injection pump for internal combustion engines Download PDF

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Publication number
EP0461213B1
EP0461213B1 EP90916706A EP90916706A EP0461213B1 EP 0461213 B1 EP0461213 B1 EP 0461213B1 EP 90916706 A EP90916706 A EP 90916706A EP 90916706 A EP90916706 A EP 90916706A EP 0461213 B1 EP0461213 B1 EP 0461213B1
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EP
European Patent Office
Prior art keywords
lubricating oil
claw
coupling
claws
driving
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
EP90916706A
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German (de)
French (fr)
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EP0461213A1 (en
Inventor
Helmut Laufer
Wolfgang Fehlmann
Ewald Eblen
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0461213A1 publication Critical patent/EP0461213A1/en
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Classifications

    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • 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
    • F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • F02M39/02—Arrangements of fuel-injection apparatus to facilitate the driving of pumps; Arrangements of fuel-injection pumps; Pump drives
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/121—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor with piston arranged axially to driving shaft
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil

Definitions

  • the invention is based on a fuel injection pump for internal combustion engines of the type defined in the preamble of claim 1, as e.g. is known from DE-A-3 605 452.
  • the fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that, due to the engine chamber, which is also only partially filled with lubricant, the limit speed of the cam engine is very high and even in the area of the high drive speed of the drive shaft, which is close to the limit speed, the highly loaded drive surfaces of the drive shaft Claw clutch are adequately lubricated. This drastically increases the service life of the fuel injection pump.
  • the lubricating oil flow forced by the lubricating oil pump from the lubricating oil groove to the lubricating openings in the claw surfaces of the claw coupling is realized in a particularly advantageous manner in that the drive shaft has an axial blind bore which is connected to the lubricating oil groove via a radial bore and is closed on the mouth side is. Oblique bores lead from the blind bore into the drive claws of the drive shaft, which are closed at the end. A distributor bore leads from each oblique bore into those claw surfaces of the drive claws which transmit a torque in the intended direction of rotation of the drive shaft. The mouth openings of the distributor bores in the claw surfaces form the lubricating oil openings.
  • the coupling of the drive claws of the drive shaft to the output claws of the lifting disk connected in a rotationally fixed manner to the distributor piston takes place via a coupling disk designed as a cross disk. So that the claw surfaces of the coupling disk transmitting a drive torque are also sufficiently lubricated, second distributor bores run in the clutch disk, which extend from the claw surfaces of the coupling claws, which bear against the claw surfaces of the drive claws that carry the lubricating oil openings, to the claw surfaces of the same coupling claw that lead in the direction of rotation .
  • first distributor bores lead from all claw surfaces of the drive claws to the oblique bores and form the desired lubricating oil openings with their mouth openings in the claw surfaces.
  • all coupling claws are traversed with second distributor bores, each of which opens into the two claw surfaces delimiting the coupling claw and there in each case a lubricating oil opening realize.
  • all claw surfaces are supplied with lubricating oil, regardless of whether or not they are loaded in the current direction of rotation of the drive shaft. This has the advantage that the fuel injection pump can be used for both directions of rotation of the drive shaft and separate storage for left and right rotation of the drive shaft is avoided.
  • the oil emerging at the claw surfaces is thrown outwards by the centrifugal force and lubricates the rollers of the engine.
  • the lubricating oil circuit is maintained by a feed pump which is driven either by the drive shaft or by a separate electric motor and is generally already present in the oil circuit of the internal combustion engine.
  • the lubricating oil circuit required for the lubrication of the drive shaft and dog clutch can also be used to control the injection adjuster.
  • the control chamber delimited by the injection adjustment piston is connected to the lubricating oil circuit via a throttle and is in turn connected to the engine compartment via an electromagnetically actuated shut-off valve.
  • the electromagnetic check valve is controlled in a clocked manner.
  • the roller ring of the cam engine is installed in such a position that when the injection adjuster is depressurized, the start of delivery, based on the rotational position of the drive shaft, is "early".
  • a pump piston 11 which also serves as a distributor, is set into a reciprocating and simultaneously rotating movement by a drive shaft 12 and with the aid of a cam engine or cam gear 13.
  • a pump working space 14 delimited by the pump piston 11 becomes a Longitudinal distributor groove 15 delivers fuel to one of several pressure channels 16, which are arranged around the pump piston 11 at regular intervals of rotation and each lead to an injection valve assigned to a combustion chamber of the internal combustion engine.
  • the pump work chamber 14 is supplied with fuel by a fuel delivery pump 17, which draws fuel from a fuel tank 18, via a solenoid valve 19.
  • the solenoid valve 19 is open and is switched into its blocking position at the beginning of the delivery or pressure stroke.
  • the drive shaft 12 is mounted in the pump housing 10 by means of two spaced sliding bearings 21, 22 and, like the end of the pump piston 11 remote from the pump working chamber 14, projects into an engine chamber 20 which accommodates the cam gear 13.
  • the cam gear 13 has, in a known manner, a cam or lifting disk 23 which is connected in a rotationally fixed manner to the pump piston 11 and, on its underside facing away from the pump piston 11, carries a number of elevations or cams 24 corresponding to the number of pressure channels 16, which have the same angle of rotation are staggered.
  • a roller ring 25 arranged coaxially to the lifting disk 23 is held in the pump housing 10 so that it can be rotated by a certain angle.
  • rollers 26 are rotatably supported, on which the cam-reinforced underside of the lifting plate 23 is supported under spring force.
  • the roller ring 25 is coupled in a rotationally locking manner to an injection adjusting piston 28 of an injection adjuster 30 via an adjusting bolt 27.
  • the injection adjusting piston 28 delimits a control chamber 29 and is displaced by pressurizing the control chamber 29 against the force of a return spring 31, the roller ring 25 being rotated via the adjusting bolt 27.
  • the cam gear 13 also includes a dog clutch 32, which transmits the rotary movement of the drive shaft 12 to the pump piston 11 irrespective of the axial stroke position of the latter.
  • the claw coupling 32 consists of two drive claws 33, 34 connected to the drive shaft 12 in a rotationally fixed manner, two output claws 35, 36 connected to the lifting disk 23 in a rotationally fixed manner, which in relation to the drive claws 33, 34 in the direction of rotation of the drive shaft 12 are offset by 90 °, and from a cross plate 40 with four segment-like coupling claws 41 - 44, which lie between the drive claws 33, 34 and output claws 35, 36 and produce a rotationally fixed connection between them.
  • the cross disk 40 with the drive claws 33, 34 and output claws 35, 36 engaging in it lies in the interior of the roller ring 25.
  • a lubricating oil circuit has a lubricating oil container 45, from which a lubricating oil pump 46 delivers lubricating oil into a lubricating oil supply line 47.
  • the lubricating oil supply line 47 opens into a lubricating oil groove 48 formed in the pump housing 10 on the drive shaft 12 between the two sliding bearings 21, 22 as an annular groove.
  • a lubricating oil return line 49 connects a drain opening 37 in the engine compartment 20 to the lubricating oil reservoir 45 2/2-way solenoid valve 50 is connected to the lubricating oil supply line 47, to which the control chamber 29 of the hydraulic spray adjuster 30 is also connected via a line section 39.
  • a throttle valve 51 is switched on between the connection point of the power section 39 and the lubricating oil pump 46.
  • a lubricating oil collecting groove 52 is provided, which is sealed on the end face and is connected to the engine compartment 20 via a return bore 53.
  • the lubricating oil supplied by the lubricating oil pump 46 to the lubricating oil groove 48 passes through the two sliding bearings 21, 22 and arrives directly or via the lubricating oil collecting groove 52 and the return bore 53 into the engine compartment 20.
  • Its drain opening 37 is arranged such that the engine compartment 20 is only partially filled with lubricating oil is.
  • the speed limit of the drive shaft 12 is defined as the limit speed at which the lifting disk 23 lifts off the rollers 26 of the roller ring 25 and the exact lifting function of the pump piston 11 is no longer guaranteed.
  • a lubricating oil flow from the lubricating oil groove 48 through the drive shaft 12 is provided directly to the claw clutch 32, which exits via lubricating oil openings in the claw surfaces of the claw clutch 32 and into the engine room 20 flows away. It is sufficient to provide lubricating oil openings in those claw surfaces of the claw clutch 32 that have to transmit the torque in the fixed direction of rotation of the drive shaft 12.
  • an axial blind bore 54 is introduced into the drive shaft 12 from the end face carrying the drive claws 33, 34 to realize this lubricating oil flow, which near the bottom of the bag via a radial bore 55 in the drive shaft 12 with the Lubricating oil groove 48 is connected and is closed on the end face of the drive shaft 12 by a ball 56.
  • an oblique bore 57 or 58 is introduced, which opens into the blind bore 54 and is closed at the end by a ball 59 or 60.
  • a first distributor bore 61 or 62 From each oblique bore 57, 58, a first distributor bore 61 or 62 (FIGS.
  • the distributor bore 61 can be seen extended in the sectional view of the drive claw 34 in FIG. 4, while it is indicated in dashed lines in the sectional view of the cross disk 40 according to FIG. 5.
  • the mouth openings of the first distributor bores 61, 62 form the aforementioned lubricating oil openings 64, 65 in the claw surfaces 33a and 34a.
  • second distributor bores 66, 67 lead to the other claw surfaces 41a, 43a of the coupling claws 41, 43.
  • part of the lubricating oil emerging at the lubricating oil openings 64, 65 flows to the claw surfaces 41 a, 43 a, which transmit a torque to the output claws 35, 36 in the direction of rotation 63 of the drive shaft 12 and flows there through the further lubricating oil openings 68,69 forming mouths of the second distributor bores 66,67 between the contact surfaces of coupling claws 41,42 and output claws 35,36 of the lifting disk 23.
  • This construction ensures that the claw surfaces 33a, 34a, 41a, 43a of the claw coupling transmit a torque 32 are always adequately supplied with lubricating oil.
  • the hydraulic spray adjuster 30 is controlled by means of the lubricating oil circuit to adjust the start of the stroke of the pump piston 11 and thus the start of delivery relative to the rotational position of the drive shaft 12.
  • the solenoid valve 50 is actuated in a clocked manner in such a way that the start of delivery is adjusted to "early" at full load and to "late” at partial load.
  • the roller ring 25 Since there is no engine oil pressure at the start of the internal combustion engine, the roller ring 25 is installed with respect to the rotational position of the drive shaft 12 in such a spatial installation position that when the control chamber 29 of the injection adjuster 30 is depressurized, the roller ring 25 assumes such a position that when the internal combustion engine starts cold, delivery begins Pump piston 11 is at "early”.
  • the spray adjustment piston 28 can thus be adjusted with the engine oil pressure from the idling speed.
  • the required late position is achieved Moving the start of delivery determined by closing the solenoid valve 19 with respect to the rotational position of the pump piston 11 is reached.
  • the invention is not restricted to the exemplary embodiment described above.
  • the lubricating oil supply line 47 can connect the feed pump 46 directly to the lubricating oil groove 48.
  • the throttle valve 51 is then connected upstream of the common connection point from line section 39 to the control chamber 29 of the spray adjuster 30 and from solenoid valve 50 on the lubricating oil supply line 47 to the lubricating oil supply line 47.
  • the lubricating oil container 45 can be omitted if the feed pump 46 is connected directly to the lubricating oil return line 49 on the input side. In this case, the engine room 20 takes over the function of the lubricating oil container 45. The engine room 20 is then incorporated into the engine oil circuit of the internal combustion engine by a separate inlet and a separate outlet. The feed pump 46 is expediently driven by the drive shaft 12. The speed-dependent lubricating oil pressure in the engine compartment 20 can also be controlled by means of a pressure control valve.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Abstract

A fuel injection pump for internal combustion engines has a pump housing (10), an axially and rotatably guided distributor piston (11), a rotating drive shaft (12) fitted in the pump housing (10), a drive system (13) with a dog coupling (32) connecting the drive shaft (12) to the distributor piston (11) and an eccentric (23) rolling on a roller ring (25) with cams (26) and a lubricating oil feed line (47) opening into a lubricating oil groove (48) and a lubricating oil return line (49) leading back from the gear casing (20) partly filled with lubricating oil. To ensure a sufficient supply of lubricating oil to the heavily loaded drive surfaces of the dog coupling (32), lubricating oil flows through the drive shaft (12) from the lubricating oil groove (48) to the dog coupling (32) through apertures (64, 65, 68, 69) in at least those dog surfaces of the dog coupling (32) transmitting rotary force and into the gear casing. (20).

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzpumpe für Brennkraftmaschinen der im Oberbegriff des Anspruchs 1 definierten Gattung, wie sie z.B. aus der DE-A-3 605 452 bekannt ist.The invention is based on a fuel injection pump for internal combustion engines of the type defined in the preamble of claim 1, as e.g. is known from DE-A-3 605 452.

Bei einer bekannten Kraftstoffeinspritzpumpe (DE-PS 1 263 397) ist der Triebwerksraum vollständig mit Schmierflüssigkeit gefüllt, wobei als Schmierflüssigkeit üblicherweise das Motoröl aus dem Ölkreislauf der Brennkraftmaschine verwendet wird. Infolge der relativ hohen Viskosität des Motoröls liegt die Grenzdrehzahl des Nockentriebwerks, d.h. die Drehzahl der Antriebswelle, bei welcher die Hubscheibe "abspringt", und nicht mehr auf den Rollen des Rollenrings abrollt, sehr niedrig. Der Einsatz dieser Kraftstoffeinspritzpumpe ist somit auf langsamlaufende Dieselmotoren beschränkt.In a known fuel injection pump (DE-PS 1 263 397), the engine compartment is completely filled with lubricant, the engine oil from the oil circuit of the internal combustion engine usually being used as the lubricant. As a result of the relatively high viscosity of the engine oil, the limit speed of the cam engine, ie the speed of the drive shaft at which the lifting disk “jumps off” and no longer rolls on the rollers of the roller ring, is very low. The use of this fuel injection pump is therefore limited to slow-running diesel engines.

Bei einer ebenfalls bekannten Kraftstoffeinspritzpumpe (DE 36 05 452 A1) ist der Triebwerksraum infolge einer räumlich entsprechend angeordneten Abflußbohrung in diesem nur teilweise mit Schmierflüssigkeit gefüllt, wodurch sich die Grenzdrehzahl des Nockentriebwerks wesentlich erhöhen läßt. Es hat sich aber gezeigt, daß bei hohen Antriebsdrehzahlen sich die Schmierflüssigkeit im äußeren Bereich der Triebwerksteile ansammelt und die nahe dem Zentrum liegenden Antriebsklauen der Klauenkupplung, welche erhebliche Drehmomente übertragen müssen, nicht geschmiert werden. Die Folge ist ein schneller Verschleiß und eine unangemessen niedrige Lebensdauer der Kraftstoffeinspritzpumpe.In a fuel injection pump (DE 36 05 452 A1), which is also known, the engine compartment is only partially filled with lubricating fluid as a result of a spatially correspondingly arranged drain hole in it, which means that the limit speed of the cam engine can be increased significantly. However, it has been shown that at high drive speeds, the lubricant accumulates in the outer region of the engine parts and the drive claws of the dog clutch, which are located near the center and which have to transmit considerable torques, are not lubricated. The result is rapid wear and an inappropriately short service life of the fuel injection pump.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzpumpe mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß aufgrund des auch hier mit Schmierflüssigkeit nur teilgefüllten Triebwerksraums die Grenzdrehzahl des Nockentriebwerks sehr hoch liegt und selbst im Bereich der hohen, nahe der Grenzdrehzahl liegenden Antriebsdrehzahl der Antriebswelle die hochbelasteten Antriebsflächen der Klauenkupplung ausreichend geschmiert sind. Damit steigt die Lebensdauer der Kraftstoffeinspritzpumpe drastisch an.The fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that, due to the engine chamber, which is also only partially filled with lubricant, the limit speed of the cam engine is very high and even in the area of the high drive speed of the drive shaft, which is close to the limit speed, the highly loaded drive surfaces of the drive shaft Claw clutch are adequately lubricated. This drastically increases the service life of the fuel injection pump.

Durch die in den weiteren Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Anspruch 1 angegebenen Kraftstoffeinspritzpumpe möglich, wobei der Begriff "Schmieröl" als Synonym für alle Arten von Schmierflüssigkeiten verwendet wird und vorzugsweise Motoröl Anwendung findet.The measures listed in the further claims allow advantageous developments and improvements of the fuel injection pump specified in claim 1, the term "lubricating oil" being used as a synonym for all types of lubricating liquids and preferably engine oil being used.

Der von der Schmierölpumpe erzwungene Schmierölfluß von der Schmierölnut zu den Schmieröffnungen in den Klauenflächen der Klauenkupplung wird gemäß einer bevorzugten Ausführungsform der Erfindung in besonders vorteilhafter Weise dadurch realisiert, daß die Antriebswelle eine axiale Sackbohrung aufweist, die über eine Radialbohrung mit der Schmierölnut verbunden und mündungsseitig verschlossen ist. Von der Sackbohrung führen Schrägbohrungen in die Antriebsklauen der Antriebswelle, die stirnseitig verschlossen sind. Von jeder Schrägbohrung führt jeweils eine Verteilerbohrung in diejenigen Klauenflächen der Antriebsklauen, die in der vorgesehenen Drehrichtung der Antriebswelle ein Drehmoment übertragen. Die Mündungsöffnungen der Verteilerbohrungen in den Klauenflächen bilden die Schmierölöffnungen. Die Kopplung der Antriebsklauen der Antriebswelle mit den Abtriebsklauen der mit dem Verteilerkolben drehfest verbundenen Hubscheibe erfolgt über eine als Kreuzscheibe ausgebildete Kopplungsscheibe. Damit auch die ein Antriebsdrehmoment übertragenden Klauenflächen der Kopplungsscheibe ausreichend geschmiert werden, verlaufen in der Kupplungsscheibe zweite Verteilerbohrungen, die sich von den Klauenflächen der Kopplungsklauen, die an den die Schmierölöffnungen tragenden Klauenflächen der Antriebsklauen anliegen, bis zu den in Drehrichtung vorauseilenden Klauenflächen der gleichen Kopplungsklaue erstrecken.According to a preferred embodiment of the invention, the lubricating oil flow forced by the lubricating oil pump from the lubricating oil groove to the lubricating openings in the claw surfaces of the claw coupling is realized in a particularly advantageous manner in that the drive shaft has an axial blind bore which is connected to the lubricating oil groove via a radial bore and is closed on the mouth side is. Oblique bores lead from the blind bore into the drive claws of the drive shaft, which are closed at the end. A distributor bore leads from each oblique bore into those claw surfaces of the drive claws which transmit a torque in the intended direction of rotation of the drive shaft. The mouth openings of the distributor bores in the claw surfaces form the lubricating oil openings. The coupling of the drive claws of the drive shaft to the output claws of the lifting disk connected in a rotationally fixed manner to the distributor piston takes place via a coupling disk designed as a cross disk. So that the claw surfaces of the coupling disk transmitting a drive torque are also sufficiently lubricated, second distributor bores run in the clutch disk, which extend from the claw surfaces of the coupling claws, which bear against the claw surfaces of the drive claws that carry the lubricating oil openings, to the claw surfaces of the same coupling claw that lead in the direction of rotation .

In einer weiteren Ausführungsform der Erfindung führen erste Verteilerbohrungen von allen Klauenflächen der Antriebsklauen zu den Schrägbohrungen und bilden mit ihren Mündungsöffnungen in den Klauenflächen die gewünschten Schmierölöffnungen. In gleicher Weise sind alle Kopplungsklauen mit zweiten Verteilerbohrungen durchzogen, die jeweils in den beiden, die Kopplungsklaue begrenzenden Klauenflächen münden und dort jeweils eine Schmierölöffnung realisieren. Bei dieser Ausführungsform sind alle Klauenflächen mit Schmieröl versorgt, unabhängig davon, ob sie bei der momentanen Drehrichtung der Antriebswelle belastet sind oder nicht. Dies hat den Vorteil, daß die Kraftstoffeinspritzpumpe für beiden Drehrichtungen der Antriebswelle eingesetzt werden kann und eine getrennte Lagerhaltung für Links- und Rechtslauf der Antriebswelle vermieden wird. Das an den Klauenflächen austretende Öl wird durch die Zentrifugalkraft nach außen geschleudert und schmiert die Rollen des Triebwerks. Der Schmierölkreislauf wird durch eine Förderpumpe aufrecht erhalten, die entweder von der Antriebswelle oder von einem separaten elektrischen Motor angetrieben wird und allgemein bereits im Ölkreislauf der Brennkraftmaschine vorhanden ist.In a further embodiment of the invention, first distributor bores lead from all claw surfaces of the drive claws to the oblique bores and form the desired lubricating oil openings with their mouth openings in the claw surfaces. In the same way, all coupling claws are traversed with second distributor bores, each of which opens into the two claw surfaces delimiting the coupling claw and there in each case a lubricating oil opening realize. In this embodiment, all claw surfaces are supplied with lubricating oil, regardless of whether or not they are loaded in the current direction of rotation of the drive shaft. This has the advantage that the fuel injection pump can be used for both directions of rotation of the drive shaft and separate storage for left and right rotation of the drive shaft is avoided. The oil emerging at the claw surfaces is thrown outwards by the centrifugal force and lubricates the rollers of the engine. The lubricating oil circuit is maintained by a feed pump which is driven either by the drive shaft or by a separate electric motor and is generally already present in the oil circuit of the internal combustion engine.

Bei Kraftstoffeinspritzpumpen mit einem hydraulischen Spritzversteller kann der für die Schmierung von Antriebswelle und Klauenkupplung erforderliche Schmierölkreislauf zusätzlich zur Steuerung des Spritzverstellers verwendet werden. Der von dem Spritzverstellkolben begrenzte Steuerraum wird über eine Drossel an dem Schmierölkreislauf angeschlossen und ist seinerseits über ein elektromagnetisch betätigbares Sperrventil mit dem Triebwerksraum verbunden. Zur Erzeugung eines drehzahlabhängig anwachsenden Steuerdrucks im Steuerraum zwecks Verschiebung des Steuerkolbens und damit des Rollenrings zur "Frühverstellung" des Förderbeginns in Bezug auf die Drehlage der Antriebswelle wird das elektromagnetische Sperrventil getaktet angesteuert.In the case of fuel injection pumps with a hydraulic injection adjuster, the lubricating oil circuit required for the lubrication of the drive shaft and dog clutch can also be used to control the injection adjuster. The control chamber delimited by the injection adjustment piston is connected to the lubricating oil circuit via a throttle and is in turn connected to the engine compartment via an electromagnetically actuated shut-off valve. To generate a speed-dependent control pressure in the control room for the purpose of shifting the control piston and thus the roller ring for "early adjustment" of the start of delivery with respect to the rotational position of the drive shaft, the electromagnetic check valve is controlled in a clocked manner.

Da beim Start der Brennkraftmaschine kein Motoröldruck vorhanden ist, wird der Rollenring des Nockentriebwerks in einer solchen Lage eingebaut, daß bei drucklosem Steuerraum des Spritzverstellers der Förderbeginn, bezogen auf die Drehlage der Antriebswelle, auf "früh" steht.Since there is no engine oil pressure at the start of the internal combustion engine, the roller ring of the cam engine is installed in such a position that when the injection adjuster is depressurized, the start of delivery, based on the rotational position of the drive shaft, is "early".

Zeichnungdrawing

Die Erfindung ist anhand von in der Zeichnung dargestellten Ausführungsbeispielen in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
eine schematische Darstellung einer Kraftstoffeinspritzpumpe für eine Brennkraftmaschine,
Fig. 2
eine perspektivische Darstellung einer Klauenkupplung der Kraftstoffeinspritzpumpe in Fig. 1, als Explosionszeichnung,
Fig. 3
eine Seitenansicht einer Antriebswelle der Kraftstoffeinspritzpumpe in Fig. 1, teilweise geschnitten,
Fig. 4
einen Schnitt längs der Linie IV-IV in Fig. 3,
Fig. 5
einen Schnitt einer Kopplungsscheibe der Klauenkupplung in Fig. 2,
Fig. 6
eine gleiche Darstellung wie in Fig. 5 einer Kopplungsscheibe gemäß einem weiteren Ausführungsbeispiel.
The invention is explained in more detail in the following description with reference to exemplary embodiments shown in the drawing. Show it:
Fig. 1
1 shows a schematic illustration of a fuel injection pump for an internal combustion engine,
Fig. 2
2 shows a perspective illustration of a dog clutch of the fuel injection pump in FIG. 1, as an exploded drawing,
Fig. 3
2 shows a side view of a drive shaft of the fuel injection pump in FIG. 1, partly in section,
Fig. 4
a section along the line IV-IV in Fig. 3,
Fig. 5
3 shows a section of a coupling disk of the dog clutch in FIG. 2,
Fig. 6
a same representation as in Fig. 5 of a coupling plate according to another embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Bei der in Fig. 1 schematisch im Schnitt dargestellten Kraftstoffeinspritzpumpe der Verteilerbauart wird ein auch als Verteiler dienender Pumpenkolben 11 durch eine Antriebswelle 12 und mit Hilfe eines Nockentriebwerks oder Nockengetriebes 13 in eine hin- und hergehende und gleichzeitig rotierende Bewegung versetzt. Bei jedem Druckhub des Pumpenkolbens 11 wird dabei aus einem vom Pumpenkolben 11 begrenzten Pumpenarbeitsraum 14 über eine Verteilerlängsnut 15 Kraftstoff zu einem von mehreren Druckkanälen 16 gefördert, die um den Pumpenkolben 11 herum in gleichmäßigen Drehwinkelabständen angeordnet sind und jeweils zu einem einem Brennraum der Brennkraftmaschine zugeordneten Einspritzventil führen. Der Pumpenarbeitsraum 14 wird von einer Kraftstofförderpumpe 17, die Kraftstoff aus einem Kraftstofftank 18 ansaugt, über ein Magnetventil 19 mit Kraftstoff versorgt. Während des Saughubs des Pumpenkolbens 11 ist das Magnetventil 19 geöffnet und wird zu Beginn des Förder- oder Druckhubs in seine Sperrstellung umgeschaltet.In the fuel injection pump of the distributor type, shown schematically in section in FIG. 1, a pump piston 11, which also serves as a distributor, is set into a reciprocating and simultaneously rotating movement by a drive shaft 12 and with the aid of a cam engine or cam gear 13. With each pressure stroke of the pump piston 11, a pump working space 14 delimited by the pump piston 11 becomes a Longitudinal distributor groove 15 delivers fuel to one of several pressure channels 16, which are arranged around the pump piston 11 at regular intervals of rotation and each lead to an injection valve assigned to a combustion chamber of the internal combustion engine. The pump work chamber 14 is supplied with fuel by a fuel delivery pump 17, which draws fuel from a fuel tank 18, via a solenoid valve 19. During the suction stroke of the pump piston 11, the solenoid valve 19 is open and is switched into its blocking position at the beginning of the delivery or pressure stroke.

Die Antriebswelle 12 ist im Pumpengehäuse 10 mittels zweier im Abstand angeordneter Gleitlager 21,22 gelagert und ragt ebenso wie das vom Pumpenarbeitsraum 14 abgekehrte Ende des Pumpenkolbens 11 in einen das Nockengetriebe 13 aufnehmenden Triebwerksraum 20 hinein. Das Nockengetriebe 13 weist in bekannter Weise eine Nocken- oder Hubscheibe 23 auf, die drehfest mit dem Pumpenkolben 11 verbunden ist und an ihrer vom Pumpenkolben 11 abgekehrten Unterseite eine der Zahl der Druckkanäle 16 entsprechende Anzahl von Erhebungen oder Nocken 24 trägt, die um gleiche Drehwinkel versetzt angeordnet sind. Ein koaxial zur Hubscheibe 23 angeordneter Rollenring 25 ist um einen bestimmten Winkel verdrehbar im Pumpengehäuse 10 gehalten. Im Rollenring 25 sind Rollen 26 drehbar gelagert, auf denen sich die nockenbewehrte Unterseite der Hubscheibe 23 unter Federkraft abstützt. Der Rollenring 25 ist über einen Verstellbolzen 27 mit einem Spritzverstellkolben 28 eines Spritzverstellers 30 verdrehschlüssig gekoppelt. Der Spritzverstellkolben 28 begrenzt einen Steuerraum 29 und wird durch Druckbeaufschlagung des Steuerraums 29 gegen die Kraft einer Rückstellfeder 31 verschoben, wobei über den Verstellbolzen 27 der Rollenring 25 gedreht wird. Mit Verdrehen des Rollenrings 25 wird der Hubbeginn des Pumpenkolbens 11 und damit der Förderbeginn des Kraftstoffs in Bezug auf die Drehlage der Antriebswelle 12 nach "früher" verstellt. Rollenring 25 mit Rollen 26 und Spritzversteller 30 sind in Fig. 1 um 90° in die Zeichenebene gedreht dargestellt.The drive shaft 12 is mounted in the pump housing 10 by means of two spaced sliding bearings 21, 22 and, like the end of the pump piston 11 remote from the pump working chamber 14, projects into an engine chamber 20 which accommodates the cam gear 13. The cam gear 13 has, in a known manner, a cam or lifting disk 23 which is connected in a rotationally fixed manner to the pump piston 11 and, on its underside facing away from the pump piston 11, carries a number of elevations or cams 24 corresponding to the number of pressure channels 16, which have the same angle of rotation are staggered. A roller ring 25 arranged coaxially to the lifting disk 23 is held in the pump housing 10 so that it can be rotated by a certain angle. In the roller ring 25 rollers 26 are rotatably supported, on which the cam-reinforced underside of the lifting plate 23 is supported under spring force. The roller ring 25 is coupled in a rotationally locking manner to an injection adjusting piston 28 of an injection adjuster 30 via an adjusting bolt 27. The injection adjusting piston 28 delimits a control chamber 29 and is displaced by pressurizing the control chamber 29 against the force of a return spring 31, the roller ring 25 being rotated via the adjusting bolt 27. With the rotation of the roller ring 25, the start of the stroke of the pump piston 11 and thus the start of delivery of the fuel in relation to the Rotational position of the drive shaft 12 adjusted to "earlier". Roller ring 25 with rollers 26 and spray adjuster 30 are shown rotated by 90 ° in the drawing plane in FIG. 1.

Zum Nockengetriebe 13 gehört noch eine Klauenkupplung 32, welche die Drehbewegung der Antriebswelle 12 unabhängig von der axialen Hublage des Pumpenkolbens 11 auf diesen überträgt. Wie in Fig. 2 perspektivisch dargestellt ist, besteht die Klauenkupplung 32 aus zwei mit der Antriebswelle 12 drehfest verbundenen Antriebsklauen 33,34, zwei mit der Hubscheibe 23 drehfest verbundenen Abtriebsklauen 35,36, die gegenüber den Antriebsklauen 33,34 in Drehrichtung der Antriebswelle 12 um 90° versetzt sind, und aus einer Kreuzscheibe 40 mit vier segmentartigen Kopplungsklauen 41 - 44, welche zwischen den Antriebsklauen 33,34 und Abtriebsklauen 35,36 einliegen und eine drehfeste Verbindung zwischen diesen herstellen. Die Kreuzscheibe 40 mit den in ihr eingreifenden Antriebsklauen 33,34 und Abtriebsklauen 35,36 liegt im Innern des Rollenrings 25.The cam gear 13 also includes a dog clutch 32, which transmits the rotary movement of the drive shaft 12 to the pump piston 11 irrespective of the axial stroke position of the latter. As is shown in perspective in FIG. 2, the claw coupling 32 consists of two drive claws 33, 34 connected to the drive shaft 12 in a rotationally fixed manner, two output claws 35, 36 connected to the lifting disk 23 in a rotationally fixed manner, which in relation to the drive claws 33, 34 in the direction of rotation of the drive shaft 12 are offset by 90 °, and from a cross plate 40 with four segment-like coupling claws 41 - 44, which lie between the drive claws 33, 34 and output claws 35, 36 and produce a rotationally fixed connection between them. The cross disk 40 with the drive claws 33, 34 and output claws 35, 36 engaging in it lies in the interior of the roller ring 25.

Ein Schmierölkreislauf weist einen Schmierölbehälter 45 auf, aus dem eine Schmierölpumpe 46 Schmieröl in eine Schmierölzuführleitung 47 fördert. Die Schmierölzuführleitung 47 mündet in einer im Pumpengehäuse 10 an der Antriebswelle 12 zwischen den beiden Gleitlagern 21,22 als Ringnut ausgebildeten Schmierölnut 48. Eine Schmierölrückführleitung 49 verbindet eine Abflußöffnung 37 im Triebwerksraum 20 mit dem Schmierölbehälter 45. Eine Zuflußöffnung 38 im Triebwerksraum 20 ist über ein 2/2-Wegemagnetventil 50 an die Schmierölzuführleitung 47 angeschlossen, mit welcher auch der Steuerraum 29 des hydraulischen Spritzverstellers 30 über einen Leitungsabschnitt 39 verbunden ist. Zwischen dem Anschlußpunkt des Leistungsabschnittes 39 und der Schmierölpumpe 46 ist ein Drosselventil 51 eingeschaltet. Auf der von der Schmierölnut 48 abgekehrten Seite des äußeren Gleitlagers 21 ist eine Schmierölsammelnut 52 vorgesehen, die stirnseitig abgedichtet ist und über eine Rücklaufbohrung 53 mit dem Triebwerksraum 20 verbunden ist. Das von der Schmierölpumpe 46 der Schmierölnut 48 zugeführte Schmieröl durchsetzt die beiden Gleitlager 21,22 und gelangt unmittelbar bzw. über die Schmierölsammelnut 52 und die Rücklaufbohrung 53 in den Triebwerksraum 20. Dessen Abflußöffnung 37 ist so angeordnet, daß der Triebwerksraum 20 mit Schmieröl nur teilgefüllt ist. Durch diese nur teilweise Füllung des Triebwerksraums 20 weist das Nockengetriebe 13 trotz der hohen Viskosität des als Schmieröl verwendeten Motoröls der Brennkraftmaschine eine hohe Grenzdrehzahl auf. Als Grenzdrehzahl ist diejenige Drehzahl der Antriebswelle 12 definiert, bei welcher die Hubscheibe 23 von den Rollen 26 des Rollenrings 25 abhebt und damit die exakte Hubfunktion des Pumpenkolbens 11 nicht mehr gewährleistet ist.A lubricating oil circuit has a lubricating oil container 45, from which a lubricating oil pump 46 delivers lubricating oil into a lubricating oil supply line 47. The lubricating oil supply line 47 opens into a lubricating oil groove 48 formed in the pump housing 10 on the drive shaft 12 between the two sliding bearings 21, 22 as an annular groove. A lubricating oil return line 49 connects a drain opening 37 in the engine compartment 20 to the lubricating oil reservoir 45 2/2-way solenoid valve 50 is connected to the lubricating oil supply line 47, to which the control chamber 29 of the hydraulic spray adjuster 30 is also connected via a line section 39. A throttle valve 51 is switched on between the connection point of the power section 39 and the lubricating oil pump 46. On the side facing away from the lubricating oil groove 48 outer slide bearing 21, a lubricating oil collecting groove 52 is provided, which is sealed on the end face and is connected to the engine compartment 20 via a return bore 53. The lubricating oil supplied by the lubricating oil pump 46 to the lubricating oil groove 48 passes through the two sliding bearings 21, 22 and arrives directly or via the lubricating oil collecting groove 52 and the return bore 53 into the engine compartment 20. Its drain opening 37 is arranged such that the engine compartment 20 is only partially filled with lubricating oil is. Due to this only partial filling of the engine room 20, the cam gear 13 has a high limit speed despite the high viscosity of the engine oil used as lubricating oil. The speed limit of the drive shaft 12 is defined as the limit speed at which the lifting disk 23 lifts off the rollers 26 of the roller ring 25 and the exact lifting function of the pump piston 11 is no longer guaranteed.

Um bei allen Antriebsdrehzahlen der Antriebswelle 12 eine ausreichende Schmierung der ein relativ hohes Drehmoment übertragenden Klauenkupplung 32 sicherzustellen, ist ein Schmierölfluß von der Schmierölnut 48 durch die Antriebswelle 12 hindurch unmittelbar zur Klauenkupplung 32 vorgesehen, der über Schmierölöffnungen in den Klauenflächen der Klauenkupplung 32 austritt und in den Triebwerksraum 20 abfließt. Dabei ist es ausreichend, Schmierölöffnungen in denjenigen Klauenflächen der Klauenkupplung 32 vorzusehen, die bei der festgelegten Drehrichtung der Antriebswelle 12 das Drehmoment übertragen müssen.In order to ensure sufficient lubrication of the claw clutch 32 transmitting a relatively high torque at all drive speeds of the drive shaft 12, a lubricating oil flow from the lubricating oil groove 48 through the drive shaft 12 is provided directly to the claw clutch 32, which exits via lubricating oil openings in the claw surfaces of the claw clutch 32 and into the engine room 20 flows away. It is sufficient to provide lubricating oil openings in those claw surfaces of the claw clutch 32 that have to transmit the torque in the fixed direction of rotation of the drive shaft 12.

Wie aus Fig. 2 - 5 hervorgeht, ist zur Realisierung dieses Schmierölflusses in die Antriebswelle 12 von der die Antriebsklauen 33,34 tragenden Stirnseite her eine axiale Sackbohrung 54 eingebracht, die nahe des Sackgrundes über eine Radialbohrung 55 in der Antriebswelle 12 mit der Schmierölnut 48 in Verbindung steht und an der Stirnseite der Antriebswelle 12 durch eine Kugel 56 verschlossen ist. Von den beiden Antriebsklauen 33,34 her ist jeweils eine Schrägbohrung 57 bzw. 58 eingebracht, die in der Sackbohrung 54 mündet und stirnseitig durch eine Kugel 59 bzw. 60 verschlossen ist. Von jeder Schrägbohrung 57,58 führt eine erste Verteilerbohrung 61 bzw. 62 (Fig. 4 und 5) zu derjenigen Klauenfläche 33a bzw. 34a der Antriebsklaue 33 bzw. 34, die in Drehrichtung der Antriebswelle 12 (Pfeil 63 in Fig. 5) vorn liegt und das Drehmoment der Antriebswelle 12 auf die Kreuzscheibe 40 überträgt. Die Verteilerbohrung 61 ist in der Schnittdarstellung der Antriebsklaue 34 in Fig. 4 ausgezogen zu sehen, während sie in der Schnittdarstellung der Kreuzscheibe 40 gemäß Fig. 5 strichliniert angedeutet ist. Die Mündungsöffnungen der ersten Verteilerbohrungen 61,62 bilden in den Klauenflächen 33a und 34a die genannten Schmierölöffnungen 64,65. Von den diesen Klauenflächen 33a gegenüberliegenden Klauenflächen 41b,43b der Kopplungsklauen 41,43 führen jeweils zweite Verteilerbohrungen 66,67 zu der anderen Klauenfläche 41a,43a der Kupplungsklauen 41,43. Durch diese zweiten Verteilerbohrungen 66,67 fließt ein Teil des an den Schmierölöffnungen 64,65 austretenden Schmieröls zu den Klauenflächen 41a,43a, die bei der Drehrichtung 63 der Antriebswelle 12 ein Drehmoment auf die Abtriebsklauen 35,36 übertragen und fließt dort durch die weitere Schmierölöffnungen 68,69 bildenden Mündungen der zweiten Verteilerbohrungen 66,67 zwischen die Anlageflächen von Kopplungsklauen 41,42 und Abtriebsklauen 35,36 der Hubscheibe 23. Durch diese konstruktive Gestaltung ist sichergestellt, daß die ein Drehmoment übertragenden Klauenflächen 33a,34a,41a,43a der Klauenkupplung 32 stets ausreichend mit Schmieröl versorgt sind.As can be seen from FIGS. 2 to 5, an axial blind bore 54 is introduced into the drive shaft 12 from the end face carrying the drive claws 33, 34 to realize this lubricating oil flow, which near the bottom of the bag via a radial bore 55 in the drive shaft 12 with the Lubricating oil groove 48 is connected and is closed on the end face of the drive shaft 12 by a ball 56. From each of the two drive claws 33, 34, an oblique bore 57 or 58 is introduced, which opens into the blind bore 54 and is closed at the end by a ball 59 or 60. From each oblique bore 57, 58, a first distributor bore 61 or 62 (FIGS. 4 and 5) leads to that claw surface 33a or 34a of the drive claw 33 or 34 which is at the front in the direction of rotation of the drive shaft 12 (arrow 63 in FIG. 5) lies and transmits the torque of the drive shaft 12 to the cross disk 40. The distributor bore 61 can be seen extended in the sectional view of the drive claw 34 in FIG. 4, while it is indicated in dashed lines in the sectional view of the cross disk 40 according to FIG. 5. The mouth openings of the first distributor bores 61, 62 form the aforementioned lubricating oil openings 64, 65 in the claw surfaces 33a and 34a. From the claw surfaces 41a, 43b of the coupling claws 41, 43 opposite these claw surfaces, second distributor bores 66, 67 lead to the other claw surfaces 41a, 43a of the coupling claws 41, 43. Through these second distributor bores 66, 67, part of the lubricating oil emerging at the lubricating oil openings 64, 65 flows to the claw surfaces 41 a, 43 a, which transmit a torque to the output claws 35, 36 in the direction of rotation 63 of the drive shaft 12 and flows there through the further lubricating oil openings 68,69 forming mouths of the second distributor bores 66,67 between the contact surfaces of coupling claws 41,42 and output claws 35,36 of the lifting disk 23. This construction ensures that the claw surfaces 33a, 34a, 41a, 43a of the claw coupling transmit a torque 32 are always adequately supplied with lubricating oil.

Bei der in Fig. 6 dargestellten Variante der Schmierung der Klauenkupplung 32 sind alle Klauenflächen, unabhängig davon, ob sie bei der jeweils festgelegten Drehrichtung der Antriebswelle 12 ein Drehmoment übertragen oder nicht, mit Schmieröl versorgt. Dadurch ist es möglich, die Kraftstoffeinspritzpumpe unverändert mit beiden Drehrichtungen der Antriebswelle 12 zu betreiben. Hierzu sind zusätzlich in jedem Antriebsnocken 33,34 weitere erste Verteilerbohrungen 70,71 vorgesehen, die wiederum in den Schrägbohrungen 48,49 und in weiteren Schmierölöffnungen in den anderen Klauenflächen der Antriebsklauen 33,34 münden. Die Kreuzscheibe 40 ist mit weiteren zweiten Verteilerbohrungen 72,73 versehen, welche in gleicher Weise, wie die zweiten Verteilerbohrungen 66,67 die Kupplungsklauen 41,43 durchziehen, nunmehr die Kupplungsklauen 42 und 44 durchdringen. Die weitere erste Verteilerbohrung 71 in der Antriebsklaue 34 ist in der Schnittdarstellung in Fig. 4 strichliniert angedeutet.In the variant of the lubrication of the dog clutch 32 shown in FIG. 6, all dog surfaces, regardless of whether or not they transmit a torque in the respectively determined direction of rotation of the drive shaft 12 is supplied with lubricating oil. This makes it possible to operate the fuel injection pump unchanged with both directions of rotation of the drive shaft 12. For this purpose, additional first distributor bores 70, 71 are additionally provided in each drive cam 33, 34, which in turn open in the oblique bores 48, 49 and in further lubricating oil openings in the other claw surfaces of the drive claws 33, 34. The cross disk 40 is provided with further second distributor bores 72, 73, which now penetrate the clutch claws 42 and 44 in the same way as the second distributor bores 66, 67 pass through the clutch claws 41, 43. The further first distributor bore 71 in the drive claw 34 is indicated in dashed lines in the sectional view in FIG. 4.

Mittels des Schmierölkreislaufes wird gleichzeitig der hydraulische Spritzversteller 30 zur Einstellung des Hubbeginns des Pumpenkolbens 11 und damit des Förderbeginns relativ zur Drehlage der Antriebswelle 12 gesteuert. Hierzu wird das Magnetventil 50 getaktet angesteuert, in der Weise, daß bei Vollast der Förderbeginn nach "früh" und bei Teillast nach "spät" verstellt wird.At the same time, the hydraulic spray adjuster 30 is controlled by means of the lubricating oil circuit to adjust the start of the stroke of the pump piston 11 and thus the start of delivery relative to the rotational position of the drive shaft 12. For this purpose, the solenoid valve 50 is actuated in a clocked manner in such a way that the start of delivery is adjusted to "early" at full load and to "late" at partial load.

Da beim Start der Brennkraftmaschine kein Motoröldruck vorliegt, wird der Rollenring 25 bezüglich der Drehlage der Antriebswelle 12 in einer solchen räumlichen Einbaulage eingebaut, daß bei drucklosem Steuerraum 29 des Spritzverstellers 30 der Rollenring 25 eine solche Lage einnimmt, daß bei Kaltstart der Brennkraftmaschine der Förderbeginn des Pumpenkolbens 11 auf "früh" steht. Somit kann der Spritzverstellkolben 28 ab Leerlaufdrehzahl mit dem Motoröldruck verstellt werden. Bei Warmstart der Brennkraftmaschine wird die erforderliche Spätlage durch Verschieben des durch Schließen des Magnetventils 19 festgelegten Förderbeginns bezüglich der Drehlage des Pumpenkolbens 11 erreicht.Since there is no engine oil pressure at the start of the internal combustion engine, the roller ring 25 is installed with respect to the rotational position of the drive shaft 12 in such a spatial installation position that when the control chamber 29 of the injection adjuster 30 is depressurized, the roller ring 25 assumes such a position that when the internal combustion engine starts cold, delivery begins Pump piston 11 is at "early". The spray adjustment piston 28 can thus be adjusted with the engine oil pressure from the idling speed. When the internal combustion engine starts warm, the required late position is achieved Moving the start of delivery determined by closing the solenoid valve 19 with respect to the rotational position of the pump piston 11 is reached.

Die Erfindung ist nicht auf das vorstehend beschriebene Ausführungsbeispiel beschränkt. So kann die Schmierölzuführleitung 47 die Förderpumpe 46 unmittelbar an die Schmierölnut 48 anschließen. Das Drosselventil 51 wird dann dem gemeinsamen Anschlußpunkt von Leitungsabschnitt 39 zum Steuerraum 29 des Spritzverstellers 30 und von Magnetventil 50 an der Schmierölzuführleitung 47 zur Schmierölzuführleitung 47 hin vorgeschaltet.The invention is not restricted to the exemplary embodiment described above. The lubricating oil supply line 47 can connect the feed pump 46 directly to the lubricating oil groove 48. The throttle valve 51 is then connected upstream of the common connection point from line section 39 to the control chamber 29 of the spray adjuster 30 and from solenoid valve 50 on the lubricating oil supply line 47 to the lubricating oil supply line 47.

Der Schmierölbehälter 45 kann entfallen, wenn die Förderpumpe 46 eingangsseitig unmittelbar an die Schmierölrückführleitung 49 angeschlossen wird. In diesem Fall übernimmt der Triebwerksraum 20 die Funktion des Schmierölbehälters 45. Der Triebwerksraum 20 wird dann durch einen separaten Zulauf und einen separaten Ablauf in den Motorölkreislauf der Brennkraftmaschine einbezogen. Die Förderpumpe 46 wird zweckmäßigerweise von der Antriebswelle 12 angetrieben. Mittels eines Drucksteuerventils kann der drehzahlabhängige Schmieröldruck im Triebwerksraum 20 zusätzlich gesteuert werden.The lubricating oil container 45 can be omitted if the feed pump 46 is connected directly to the lubricating oil return line 49 on the input side. In this case, the engine room 20 takes over the function of the lubricating oil container 45. The engine room 20 is then incorporated into the engine oil circuit of the internal combustion engine by a separate inlet and a separate outlet. The feed pump 46 is expediently driven by the drive shaft 12. The speed-dependent lubricating oil pressure in the engine compartment 20 can also be controlled by means of a pressure control valve.

Claims (6)

  1. Fuel injection pump for internal combustion engines, having a pump housing (10), having a distributor piston (11) guided in the pump housing (10) so that it can be rotated and axially displaced, having a rotating driving shaft (12) for at least the distributor piston (11) and supported in the pump housing, having a driving gear (13), which connects the driving shaft to the distributor piston (11), is arranged in a driving gear space (20) and has a claw coupling (32), for generating a rotary motion of the distributor piston, and a roller ring (25) with rollers (26) and a lifting disc (23) connected to the distributor piston, for generating an axial displacement motion of the distributor piston, the end carrying the cams (24) of which lifting disc (23) being supported by spring force on the rollers (26) of the roller ring (25), and having a lubricating oil supply conduit (47), which opens into the driving gear space (20) via a lubricating oil groove (48) surrounding the driving shaft and a hole (54) in the driving shaft (12), and a lubricating oil drain opening (37), which leads away from the driving gear space (20), a lubricating oil flow taking place from the lubricating oil groove (48) to the claw coupling (32) through the hole (54) in the driving shaft (12), characterised in that the lubricating oil flow emerges into the driving gear space (20) via lubricating oil openings (64, 65, 68, 69) in at least those claw surfaces (33a, 34a, 41a, 43a) of driving claws (33, 34) of the claw coupling (32) which are torsionally connected to the driving shaft and transmit a rotational force, and the lubricating oil supply conduit (47) is connected to a lubricating oil pump driven simultaneously with the injection pump in order to generate the lubricating oil flow.
  2. Fuel injection pump according to Claim 1, characterised in that the claw coupling (32) has at least two driving claws (33, 34) torsionally connected to the driving shaft (12), at least two opposite and spatially offset driven claws (35, 36) torsionally connected to the lifting disc (23) and a coupling disc (40) engaging by means of coupling claws (41-44) between the driving claws and the driven claws (33, 34, 35, 36), in that the driving shaft (12) has an axial pocket hole (54) which is in connection with the lubricating oil groove (48) via a radial hole (55) and is closed at the coupling end of the driving shaft (12), in that one oblique hole (57, 58) is introduced from each of the driving claws (33, 34) into the pocket hole (54) and is closed at the end, in that first distributor holes (61, 62) lead from the oblique holes (57, 58) to the claw surfaces (33a, 34a), of the driving claws (33, 34), located in front in the direction of rotation of the driving shaft (12) and there form the lubricating oil openings (64, 65) at the outlet end and in that second distributor holes (66, 67) lead from the claw surfaces (41b, 43b), of the coupling disc (40), in contact with the driving claw surfaces (33a, 34a) carrying the lubricating oil openings (64, 65) to the claw surfaces (41a, 43a), of the coupling disc (40), in contact in the rotational direction with the driven claw surfaces (35, 36) of the lifting disc (23) and there form lubricating oil openings (68, 69) at the outlet end.
  3. Fuel injection pump according to Claim 2, characterised in that further first distributor holes (70, 71) additionally lead from the oblique holes (57, 58) to the other claw surfaces of the driving claws (33, 34) and there form further lubricating oil openings at the outlet end and in that further second distributor holes (72, 73) lead from the claw surfaces, of the coupling disc (40), which face towards these claw surfaces carrying the further lubricating oil openings, to the other claw surfaces of the coupling disc (40) and there open, at the outlet end, into further lubricating oil openings.
  4. Fuel injection pump according to one of Claims 1-3, characterised in that the driving shaft (12) is supported in two sliding bearings (21,22) arranged at a distance apart and in that the lubricating oil groove (48) is arranged between the two sliding bearings (21, 22).
  5. Fuel injection pump according to one of Claims 1-4, characterised in that a hydraulic injection adjuster (30) is provided which has an injection adjustment piston (28), which bounds a control space (29) and has reset springs (31), for adjusting the roller ring (25) in such a way that the beginning of the stroke of the distributor piston (11) is displaced towards "advanced" relative to the rotational position of the driving shaft (12), in that the control space (29) is connected, on the one hand, to the lubricating oil supply conduit (47) via a throttle (51) and is connected, on the other hand, to the driving gear space (20) via a 2/2-way magnetic valve (50) which is activated in a pulsed manner to set a lubricating oil pressure in the control space (29) which depends on rotational speed.
  6. Fuel injection pump according to Claim 5, characterised in that the roller ring (25) is installed in such a position in the pump housing (10) that when the control space (29) of the injection adjuster (30) is unpressurised, the beginning of delivery of the distributor piston (11) in the case of a cold start of the internal combustion engine is at "advanced" relative to the rotational position of the driving shaft (12).
EP90916706A 1989-12-29 1990-11-24 Fuel injection pump for internal combustion engines Expired - Lifetime EP0461213B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3943299A DE3943299A1 (en) 1989-12-29 1989-12-29 FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3943299 1989-12-29

Publications (2)

Publication Number Publication Date
EP0461213A1 EP0461213A1 (en) 1991-12-18
EP0461213B1 true EP0461213B1 (en) 1993-11-03

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP90916706A Expired - Lifetime EP0461213B1 (en) 1989-12-29 1990-11-24 Fuel injection pump for internal combustion engines

Country Status (5)

Country Link
US (1) US5146895A (en)
EP (1) EP0461213B1 (en)
JP (1) JP3051164B2 (en)
DE (2) DE3943299A1 (en)
WO (1) WO1991010063A1 (en)

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DE19739653A1 (en) * 1997-09-10 1999-03-11 Bosch Gmbh Robert Process for producing high-pressure fuel and system for producing high-pressure fuel
DE19801355B4 (en) * 1998-01-16 2004-04-08 Robert Bosch Gmbh High-pressure pump for fuel supply in fuel injection systems of internal combustion engines
DE10155522C1 (en) * 2001-11-12 2003-04-03 Bosch Gmbh Robert Feed device used for supplying the fuel injection system of an auto-ignition internal combustion engine comprises a force-transmission element hinged on the end side of a drive shaft impinged upon by a pre-tensioning element
JP3852753B2 (en) * 2001-12-04 2006-12-06 株式会社デンソー Fuel injection pump
US6668797B2 (en) * 2002-05-13 2003-12-30 Advanced Vehicle Technologies Fuel injection pump system
DE102005033638A1 (en) * 2005-07-19 2007-01-25 Robert Bosch Gmbh Fuel conveyor, in particular for an internal combustion engine
DE102010041429A1 (en) 2010-09-27 2012-03-29 Robert Bosch Gmbh Oldham coupling for use in fuel high pressure pump for fuel injection system of internal combustion engine, has disk with oil supply channel in form of holes and grooves, where grooves extend from surface to another surface of disk
JP6411313B2 (en) * 2015-11-26 2018-10-24 ヤンマー株式会社 Fuel injection pump
CN117738826B (en) * 2024-02-19 2024-05-03 江苏中奕和创智能科技有限公司 Diesel generator with oil control assembly

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US2670684A (en) * 1950-01-21 1954-03-02 Volvo Ab Fuel injection device for internalcombustion engines
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DE3943299A1 (en) 1991-07-04
JP3051164B2 (en) 2000-06-12
EP0461213A1 (en) 1991-12-18
US5146895A (en) 1992-09-15
WO1991010063A1 (en) 1991-07-11
DE59003366D1 (en) 1993-12-09
JPH04504748A (en) 1992-08-20

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