EP1911964B1 - High-pressure fuel pump and fuel injection system for a combustion engine - Google Patents

High-pressure fuel pump and fuel injection system for a combustion engine Download PDF

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Publication number
EP1911964B1
EP1911964B1 EP07115205A EP07115205A EP1911964B1 EP 1911964 B1 EP1911964 B1 EP 1911964B1 EP 07115205 A EP07115205 A EP 07115205A EP 07115205 A EP07115205 A EP 07115205A EP 1911964 B1 EP1911964 B1 EP 1911964B1
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EP
European Patent Office
Prior art keywords
pressure
fuel
pump
bearing
return
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.)
Not-in-force
Application number
EP07115205A
Other languages
German (de)
French (fr)
Other versions
EP1911964A1 (en
Inventor
Stefan Kieferle
Achim Koehler
Sascha Ambrock
Walter Fuchs
Andreas Kellner
Christian Langenbach
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP1911964A1 publication Critical patent/EP1911964A1/en
Application granted granted Critical
Publication of EP1911964B1 publication Critical patent/EP1911964B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F02M59/04—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • 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
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow 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
    • 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
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/0265—Pumps feeding common rails
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/023—Means for varying pressure in common rails
    • F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
    • F02M63/024—Means for varying pressure in common rails by bleeding fuel pressure between the low pressure pump and the high pressure pump
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/023—Means for varying pressure in common rails
    • F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
    • F02M63/025—Means for varying pressure in common rails by bleeding fuel pressure from the common rail

Definitions

  • the invention relates to a high-pressure fuel pump for a fuel injection system of an internal combustion engine, with a pump housing in which a drive shaft is supported by a first bearing and a second bearing, with at least one with respect to the drive shaft radially arranged pump element, with a fuel inlet, wherein a prefeed pump fuel in promotes the fuel supply, with a fuel return, with a metering unit for controlling the flow rate of the pump or elements and with a pressure control valve.
  • high-pressure fuel pump serves the pressure control valve to regulate the pressure in the low pressure circuit of the high-pressure fuel pump.
  • the delivery rate of the prefeed pump is usually divided into three partial streams.
  • a first partial flow flows through the metering unit to the suction side of the pump element (s).
  • the second partial flow usually flows through a lubricant throttle through the pump housing and serves there for cooling and lubrication of the pump. From the pump housing this second partial flow enters the fuel return of the fuel injection system.
  • a third partial flow flows through the pressure control valve, which may also be designed as a relief valve and also passes into the fuel return.
  • the invention has for its object to provide a high-pressure fuel pump for a fuel injection system, which is superior in terms of thermal and mechanical load capacity known from the prior art high-pressure fuel pumps.
  • the high-pressure fuel pump according to the invention should be simple in construction and inexpensive to produce.
  • a high-pressure fuel pump for a fuel injection system of an internal combustion engine with a pump housing, with a drive shaft, wherein the drive shaft is mounted in the pump housing by a first bearing and a second bearing, with at least one with respect to the drive shaft radially arranged pump element, with a Fuel supply, via which the fuel high-pressure pump is supplied with pressurized fuel, with a fuel return, with a metering unit for controlling the delivery of the one or more pump elements, and with a pressure control valve, wherein both the metering unit and the pressure control valve are supplied by the fuel return, in that a first check valve is provided downstream of the first bearing, that a second check valve is provided downstream of the second bearing, that the first bearing and the second bearing are under pressure s lubrication and that the first bearing and the second bearing are hydraulically in communication both with the fuel inlet and with a return line.
  • Another advantage of the high-pressure fuel pump according to the invention is that at the same load of the prefeed pump in the interior of the high-pressure fuel pump, a relatively high pressure level is reached because there are no throttle points between the prefeed pump and the interior. Thereby, the Kavitationsne Trent is reduced in the interior of the high-pressure fuel pump and the amount of fuel flowing through the first bearing and the second bearing fuel is increased. As a result, the load capacity of the first and second bearings increases. Since the first bearing and / or the second bearing are usually designed as hydrostatic plain bearings, these bearings benefit particularly from an increased flow rate, since hydrostatic bearings have a higher capacity with increasing flow.
  • an outlet of the pressure control valve opens into the return line. This will ensure that all excess fuel returns from the pressure control valve into the tank where it can cool sufficiently.
  • the output of the pressure control valve on the suction side or the delivery side of the prefeed pump opens into the fuel inlet.
  • a particularly advantageous alternative embodiment of the high-pressure fuel pump according to the invention provides that the pressure regulating valve is formed in two stages with a first output and a second output, that the first output opens into the return line, and that the second output opens into the fuel inlet.
  • FIG. 1 shows a first embodiment of a high-pressure fuel pump 1 according to the invention in a block diagram representation.
  • the high-pressure fuel pump 1 is part of a fuel injection system, which consists essentially of a tank 3, a prefeed pump 5 with an element for flow limitation 52, a filter 7, a rail 9 and a pressure relief valve 11.
  • the injectors, which are connected to the rail 9, are in FIG. 1 not shown.
  • the element for flow rate limitation 52 is formed in the embodiments shown in the figures as a throttle, which is arranged directly at the entrance of the prefeed pump 5.
  • the throttle 52 causes the total compressed in the high-pressure fuel pump 1 amount of fuel is limited.
  • the resulting in an interior 17 of the high-pressure fuel pump 1 pressure is limited according to a characteristic of a pressure control valve 20.
  • the pressure limiting valve 11 opens into a return line 13, in which the leakage quantities of the injectors, not shown, are discharged.
  • the return line 13 opens in this first embodiment in the tank 3 and drives there a jet pump (without reference numerals).
  • the high-pressure fuel pump 1 is hydraulically connected to the tank 3 via a fuel inlet 15, the filter 7 and the prefeed pump 5.
  • the fuel inlet 15 connects a delivery side of the prefeed pump 5 with an interior 17 of the pump housing, so that the entire delivery flow of the prefeed pump 5 enters the interior 17.
  • a fuel return 18 provides a hydraulic connection between the interior 17 of the pump housing on the one hand and a metering unit 19 and the return line 13 on the other hand. Between the fuel return 18 and the return line 13, a pressure regulating valve 20 is arranged.
  • the metering unit 19 serves to control the amount of fuel sucked by pump elements 21 of the high-pressure fuel pump and thus also the delivery rate thereof. These are the Suction sides of the pump elements 21 via a distribution line 23 to the output of the metering unit 19 hydraulically connected.
  • the pump elements 21 consist essentially of suction valves 25, high-pressure side check valves 27 and a piston 29 which oscillates in a cylinder bore (without reference numeral).
  • the pistons 29 of the pump elements 21 are driven by roller tappets 31 of cams 33 of a drive shaft 35.
  • the pump elements 21 convey fuel under high pressure via a high-pressure line 34 into the rail 9.
  • the cams 33 are part of a drive shaft 35, which is rotatably mounted on both sides of the cam 33 in a first bearing and in a second bearing in a pump housing (not shown).
  • the drive shaft 35 is arranged in the interior 17 of the pump housing.
  • the bearings of the drive shaft 35 are in the block diagram according to FIG. 1 shown as throttle point.
  • the first camp has in FIG. 1 the reference numeral 39, while the second bearing has been provided with the reference numeral 41.
  • the pressure control valve 20 downstream of the interior 17 of the high-pressure fuel pump 1 is arranged.
  • the pressure control valve 20 includes a leakage line 57 in the optional throttle 61 may be provided.
  • the pressure control valve 20 downstream of the interior 17 prevails in the interior 17 almost the same pressure as on the pressure side of the prefeed pump 5.
  • the pressure on the pressure side of the prefeed pump 5 and thus the interior 17 is about 3 bar to about 7 bar ,
  • first bearing 39 and the second bearing 41 are usually formed as a sliding bearing, formed by the forced flow through the bearings 39 and 41 in the bearings 39 and / or 41, a hydrostatic lubricating wedge. As a result, the load capacity of the first bearing 39 and the second bearing 41 increases considerably and at the same time the heat dissipation from the first bearing 39 and the second bearing 41 is improved.
  • a first check valve 43 may be arranged downstream of and in series with the first bearing 39.
  • a second check valve 45 may be arranged downstream of and in series with the second bearing 41.
  • the opening pressure of the check valves 43 and 45 is chosen so that they are closed when starting the internal combustion engine and open only when the internal combustion engine is running.
  • the flow resistance of the check valves 43 and 45 ensures that the dispersion of the amount of fuel flowing through the bearings 39 and 41 is reduced.
  • the first check valve 43 and the second check valve 45 open into the return line 13.
  • a throttle or aperture may be provided.
  • the prefeed pump 5 can be designed as a vane pump, as an internal gear pump, in particular as a gerotor pump, or as an external gear pump. These pumps have a gap between the rotating components and the pump housing that causes leakage losses. This gap is shown in Figure 3 by the symbol of a throttle (see reference numeral 49). The leaked through the gap leakage amount is discharged through a leakage line 51.
  • the leakage line 51 opens into the line before the first check valve 43 (not numbered), which supplies the flowing through the first bearing 39 amount of fuel via the first check valve 43 of the return line 13.
  • the high-pressure fuel pump 1 has, inter alia, the following advantages:
  • both the first bearing 39 and the second bearing 41 are forcibly traversed by fuel, which significantly increases their capacity, both in terms of mechanical and thermal stresses.
  • the amount of fuel flowing through the pump housing and bearings 39 and 41 for lubrication and cooling purposes is greatly increased.
  • a lubricating throttle for setting a defined amount of lubricant can be omitted. Due to the large quantities of lubricants, any particles that may be present are quickly washed out of the interior.
  • the delivery head of the prefeed pump can often be reduced, which improves the efficiency of the injection system.
  • FIG. 2 a further embodiment of a fuel injection system according to the invention is also shown as a block diagram. Only the essential differences are explained. The same components are provided with the same reference numerals and it is the case with respect to the previous embodiments said accordingly.
  • the pressure control valve 20 has a first output 53, which opens into the return line 13. Furthermore, the pressure regulating valve 20 has a second outlet 55, which opens into the fuel inlet 15 on the suction side of the prefeed pump 5.
  • the excess amount of fuel discharged from the pressure regulating valve 20 can be divided, so that a part of the excess fuel flows back into the tank 3 via the return line 13, where this fuel can be cooled. Another part of the excess fuel is fed back directly into the fuel inlet 15 in the second output 55 of the pressure regulating valve 20.
  • the full flow rate of the prefeed pump 5 is still used for lubrication of the high-pressure fuel pump, while only a portion of this flow is supplied via the return line 13 to the tank 3 for cooling.
  • the amount of fuel flowing through the return line 13 is about the same as in conventional fuel injection pumps, although the lubrication of the high-pressure fuel pump 1 according to the invention is much more efficient than in conventional high-pressure fuel pumps.
  • throttles 59 and 61 may be provided.
  • first throttle 59 it is possible to limit the part of the excess fuel flowing into the return line 13.
  • second throttle 61 the movements of the valve piston (without reference numerals) of the pressure control valve 20 can be effectively damped.
  • the high pressure delivery and the cooling and lubricating amount are set much more constant.

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

Abstract

The pump (1) has a drive shaft (35) supported in pump housing by bearings (39, 41), and a pump unit (21), which is arranged radially relative to the drive shaft. A conveying pump (5) e.g. external gear pump, conveys fuel to a fuel inlet (15) and a metering unit (19) regulates conveying amount of the pump unit (21). The metering unit and a pressure regulating valve (20) are supplied with the fuel by a fuel return line (18). A non-return valve (43) is provided downstream to the bearing (39) and another non-return valve (45) is provided downstream to the bearing (41).

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem einer Brennkraftmaschine, mit einem Pumpengehäuse in dem eine Antriebswelle durch ein erstes Lager und ein zweites Lager gelagert ist, mit mindestens einem bezüglich der Antriebswelle radial angeordneten Pumpenelement, mit einem Kraftstoffzulauf, wobei eine Vorförderpumpe Kraftstoff in den Kraftstoffzulauf fördert, mit einem Kraftstoffrücklauf, mit einer Zumesseinheit zur Regelung der Fördermenge des oder der Pumpenelemente und mit einem Druckregelventil.The invention relates to a high-pressure fuel pump for a fuel injection system of an internal combustion engine, with a pump housing in which a drive shaft is supported by a first bearing and a second bearing, with at least one with respect to the drive shaft radially arranged pump element, with a fuel inlet, wherein a prefeed pump fuel in promotes the fuel supply, with a fuel return, with a metering unit for controlling the flow rate of the pump or elements and with a pressure control valve.

Bei diesen aus dem Stand der Technik gemäß EP 1389683 A2 bekannten Kraftstoffhochdruckpumpen dient das Druckregelventil dazu, den Druck im Niederdruckkreislauf der Kraftstoffhochdruckpumpe zu regeln. Dabei wird die Fördermenge der Vorförderpumpe üblicherweise in drei Teilströme aufgeteilt. Ein erster Teilstrom fließt durch die Zumesseinheit auf die Saugseite des oder der Pumpenelemente. Der zweite Teilstrom fließt in der Regel über eine Schmierdrossel durch das Pumpengehäuse und dient dort zur Kühlung und Schmierung der Pumpe. Aus dem Pumpengehäuse gelangt dieser zweite Teilstrom in den Kraftstoffrücklauf des Kraftstoffeinspritzsystems.In these from the prior art according to EP 1389683 A2 known high-pressure fuel pump serves the pressure control valve to regulate the pressure in the low pressure circuit of the high-pressure fuel pump. The delivery rate of the prefeed pump is usually divided into three partial streams. A first partial flow flows through the metering unit to the suction side of the pump element (s). The second partial flow usually flows through a lubricant throttle through the pump housing and serves there for cooling and lubrication of the pump. From the pump housing this second partial flow enters the fuel return of the fuel injection system.

Ein dritter Teilstrom fließt durch das Druckregelventil, welches auch als Überströmventil ausgebildet sein kann und gelangt ebenfalls in den Kraftstoffrücklauf.A third partial flow flows through the pressure control valve, which may also be designed as a relief valve and also passes into the fuel return.

Das später veröffentlichte Dokument DE 10 2005 027851 zeigt eine durch Kraftstoff geschmierte Kraftstoffhochedruckpumpe mit einem Rückschlagventil stromabwärts des Pumpeninnenraums in dem zur Schmierung dienenden Teilstrom.The later published document DE 10 2005 027851 shows a fuel lubricated fuel high pressure pump with a check valve downstream of the pump interior in the lubrication substream.

Mit zunehmenden Einspritzdrücken steigen auch die mechanischen und thermischen Belastungen sowohl der Antriebswelle als auch der Lagerung der Antriebswelle im Pumpengehäuse. Diesen steigenden Belastungen sind die herkömmlichen Kraftstoffhochdruckpumpen nicht immer gewachsen.As the injection pressures increase, so too does the mechanical and thermal Loads of both the drive shaft and the bearing of the drive shaft in the pump housing. These increasing loads are not always matched by conventional high-pressure fuel pumps.

Offenbarung der ErfindungDisclosure of the invention

Der Erfindung liegt die Aufgabe zugrunde, eine Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem bereit zu stellen, die bezüglich thermischer und mechanischer Belastbarkeit den aus dem Stand der Technik bekannten Kraftstoffhochdruckpumpen überlegen ist. Außerdem soll die erfindungsgemäße Kraftstoffhochdruckpumpe einfach aufgebaut und kostengünstig herstellbar sein.The invention has for its object to provide a high-pressure fuel pump for a fuel injection system, which is superior in terms of thermal and mechanical load capacity known from the prior art high-pressure fuel pumps. In addition, the high-pressure fuel pump according to the invention should be simple in construction and inexpensive to produce.

Diese Aufgabe wird erfindungsgemäß bei einer Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem einer Brennkraftmaschine, mit einem Pumpengehäuse, mit einer Antriebswelle, wobei die Antriebswelle in dem Pumpengehäuse durch ein erstes Lager und ein zweites Lager gelagert ist, mit mindestens einem bezüglich der Antriebswelle radial angeordneten Pumpenelement, mit einem Kraftstoffzulauf, über den der Kraftstoffhochdruckpumpe unter Druck stehender Kraftstoff zugeführt wird, mit einem Kraftstoffrücklauf, mit einer Zumesseinheit zur Regelung der Fördermenge des oder der Pumpenelemente, und mit einem Druckregelventil, wobei sowohl die Zumesseinheit als auch das Druckregelventil von dem Kraftstoffrücklauf mit Kraftstoff versorgt werden, dadurch gelöst, dass stromabwärts des ersten Lagers ein erstes Rückschlagventil vorgesehen ist, dass stromabwärts des zweiten Lagers ein zweites Rückschlagventil vorgesehen ist, dass das erste Lager und das zweite Lager von unter Druck stehendem Kraftstoff geschmiert werden und dass das erste Lager und das zweite Lager sowohl mit dem Kraftstoffzulauf als auch mit einer Rücklaufleitung hydraulisch in Verbindung steht.This object is achieved with a high-pressure fuel pump for a fuel injection system of an internal combustion engine, with a pump housing, with a drive shaft, wherein the drive shaft is mounted in the pump housing by a first bearing and a second bearing, with at least one with respect to the drive shaft radially arranged pump element, with a Fuel supply, via which the fuel high-pressure pump is supplied with pressurized fuel, with a fuel return, with a metering unit for controlling the delivery of the one or more pump elements, and with a pressure control valve, wherein both the metering unit and the pressure control valve are supplied by the fuel return, in that a first check valve is provided downstream of the first bearing, that a second check valve is provided downstream of the second bearing, that the first bearing and the second bearing are under pressure s lubrication and that the first bearing and the second bearing are hydraulically in communication both with the fuel inlet and with a return line.

Dadurch ist es möglich, dass der gesamte Förderstrom der Vorförderpumpe zur Schmierung und Kühlung der Kraftstoffhochdruckpumpe herangezogen werden kann. Da das erste Rückschlagventil und das zweite Rückschlagventil erst mit Erreichen eines einstellbaren Öffnungsdrucks öffnen, steht in der Startphase der Brennkraftmaschine der gesamte von der Vorförderpumpe geförderte Kraftstoffstrom für den Druckaufbau in den Pumpenelementen zur Verfügung. Dadurch wird zusätzlich der Start der Brennkraftmaschine erleichtert.This makes it possible that the entire flow of the feed pump can be used for lubrication and cooling of the high-pressure fuel pump. Since the first check valve and the second check valve open only when an adjustable opening pressure is reached, in the starting phase of the internal combustion engine, the entire fuel flow delivered by the prefeed pump is available for the pressure build-up in the pump elements. This additionally facilitates the start of the internal combustion engine.

Weitere Vorteile, die während des gesamten Betriebs der Brennkraftmaschine vorhanden sind, sind zunächst die sehr großen Kühl- und Schmiermengen, da die gesamte von der Vorförderpumpe geförderte Kraftstoffmenge zur Kühlung und Schmierung der Kraftstoffhochdruckpumpe eingesetzt werden kann, bevor ein Teil dieser Fördermenge über die Zumesseinheit in die Pumpenelemente der Kraftstoffhochdruckpumpe gelangt.Other advantages that are present throughout the operation of the internal combustion engine, are initially the very large amounts of cooling and lubricating, since the entire funded by the prefeed pump fuel quantity for cooling and lubrication of the High-pressure fuel pump can be used before a part of this flow rate passes through the metering unit in the pump elements of the high-pressure fuel pump.

Der überschüssige Teil des von der Vorförderpumpe geförderten Kraftstoffstroms wird über das Druckregelventil in den Kraftstoffrücklauf zurückgeführt. Dadurch wird eine sehr effektive Kühlung der Kraftstoffhochdruckpumpe ermöglicht, da der über das Druckregelventil abströmende und von der Kraftstoffhochdruckpumpe erwärmte Kraftstoff im Tank des Kraftstoffeinspritzsystems ausreichend gekühlt werden wird, bevor dieser Kraftstoff erneut von der Vorförderpumpe angesaugt und zur Kraftstoffhochdruckpumpe geführt wird.The excess part of the pumped by the feed pump fuel flow is returned via the pressure control valve in the fuel return. As a result, a very effective cooling of the high-pressure fuel pump is made possible because the fuel flowing off via the pressure regulating valve and heated by the high-pressure fuel pump in the fuel injection system tank will be sufficiently cooled before this fuel is sucked in again by the prefeed pump and fed to the high-pressure fuel pump.

Ein weiterer Vorteil der erfindungsgemäßen Kraftstoffhochdruckpumpe besteht darin, dass bei gleicher Belastung der Vorförderpumpe im Innenraum der Kraftstoffhochdruckpumpe ein relativ hohes Druckniveau erreicht wird, da zwischen der Vorförderpumpe und dem Innenraum keine Drosselstellen vorhanden sind. Dadurch wird die Kavitationsneigung im Inneren der Kraftstoffhochdruckpumpe verringert und die Menge des durch das erste Lager und das zweite Lager strömenden Kraftstoffs wird erhöht. Infolgedessen steigt die Belastbarkeit des ersten und des zweiten Lagers. Da das erste Lager und/oder das zweite Lager üblicherweise als hydrostatische Gleitlager ausgebildet sind, profitieren diese Lager ganz besonders von einer erhöhten Durchflussmenge, da hydrostatische Gleitlager mit zunehmender Durchflussmenge eine höhere Tragfähigkeit aufweisen.Another advantage of the high-pressure fuel pump according to the invention is that at the same load of the prefeed pump in the interior of the high-pressure fuel pump, a relatively high pressure level is reached because there are no throttle points between the prefeed pump and the interior. Thereby, the Kavitationsneigung is reduced in the interior of the high-pressure fuel pump and the amount of fuel flowing through the first bearing and the second bearing fuel is increased. As a result, the load capacity of the first and second bearings increases. Since the first bearing and / or the second bearing are usually designed as hydrostatic plain bearings, these bearings benefit particularly from an increased flow rate, since hydrostatic bearings have a higher capacity with increasing flow.

Durch die erhöhte Kühl- und Schmiermenge nicht nur des ersten und des zweiten Lagers, sondern der gesamten Kraftstoffhochdruckpumpe sind höhere Pumpenbelastungen oder, bei gleichen Belastungen, Pumpen mit höherer Lebensdauer möglich.Due to the increased amount of cooling and lubricating not only the first and the second bearing, but the entire high-pressure fuel pump higher pump loads or, for the same loads, pumps with longer life possible.

Bei einer vorteilhaften Ausgestaltung der Erfindung mündet ein Ausgang des Druckregelventils in die Rücklaufleitung. Dadurch wird sichergestellt, dass die gesamte überschüssige Kraftstoffmenge vom Druckregelventil in den Tank zurückgelangt und dort ausreichend abkühlen kann.In an advantageous embodiment of the invention, an outlet of the pressure control valve opens into the return line. This will ensure that all excess fuel returns from the pressure control valve into the tank where it can cool sufficiently.

Alternativ ist es auch möglich, dass der Ausgang des Druckregelventils auf der Saugseite oder der Förderseite der Vorförderpumpe in den Kraftstoffzulauf mündet. Dadurch findet zwar die Kühlung des Kraftstoffs über die Rücklaufleitung und den Tank nicht mehr statt; allerdings bleibt der Vorteil der verbesserten Schmierung aufgrund des höheren Kraftstoffdurchflusses durch den Innenraum und die Lager der Kraftstoffhochdruckpumpe.Alternatively, it is also possible that the output of the pressure control valve on the suction side or the delivery side of the prefeed pump opens into the fuel inlet. As a result, although the cooling of the fuel via the return line and the tank no longer takes place; however, it remains the advantage of the improved lubrication due to the higher fuel flow through the interior and the bearings of the high-pressure fuel pump.

Eine besonders vorteilhafte alternative Ausgestaltung der erfindungsgemäßen Kraftstoffhochdruckpumpe sieht vor, dass das Druckregelventil zweistufig mit einem ersten Ausgang und einem zweiten Ausgang ausgebildet ist, dass der erste Ausgang in die Rücklaufleitung mündet, und dass der zweite Ausgang in den Kraftstoffzulauf mündet.A particularly advantageous alternative embodiment of the high-pressure fuel pump according to the invention provides that the pressure regulating valve is formed in two stages with a first output and a second output, that the first output opens into the return line, and that the second output opens into the fuel inlet.

Dadurch ist es möglich, einerseits die Schmierung der Kraftstoffhochruckpumpe durch den gesamten Förderstrom der Vorförderpumpe zu gewährleisten und gleichzeitig einen Teil des Kraftstoffs in die Kraftstoffzuleitung zurückzuleiten und den verbleibenden Teil über die Rücklaufleitung in den Tank zurückzufördern. So können die erfindungsgemäßen Vorteile nahezu in vollem Umfang erreicht werden, ohne die Fördermenge des Kraftstoffs, die von der Kraftstoffhochdruckpumpe in den Tank zurückgefördert wird, wesentlich zu erhöhen.This makes it possible, on the one hand, to ensure the lubrication of the high-pressure fuel pump through the entire delivery flow of the prefeed pump and at the same time to feed back part of the fuel into the fuel supply line and to feed the remaining part back into the tank via the return line. Thus, the advantages of the invention can be achieved almost fully, without significantly increasing the delivery rate of the fuel, which is fed back from the high-pressure fuel pump in the tank.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Figuren 1 und 2Figures 1 and 2
Ausführungsbeispiele erfindungsgemäßer Kraftstoffhochdruckpumpen und deren Einbindung in ein Kraftstoffeinspritzsystem.Embodiments of high-pressure fuel pumps according to the invention and their integration into a fuel injection system.
Ausführungsformen der ErfindungEmbodiments of the invention

Figur 1 zeigt ein erstes Ausführungsbeispiel einer erfindungsgemäßen Kraftstoffhochdruckpumpe 1 in einer Blockschaltbilddarstellung. FIG. 1 shows a first embodiment of a high-pressure fuel pump 1 according to the invention in a block diagram representation.

Ausführungsformen der ErfindungEmbodiments of the invention

Die Kraftstoffhochdruckpumpe 1 ist Teil eines Kraftstoffeinspritzsystems, das im wesentlichen aus einem Tank 3, einer Vorförderpumpe 5 mit einem Element zur Fördermengenbegrenzung 52, einem Filter 7, einem Rail 9 und einem Druckbegrenzungsventil 11 besteht. Die Injektoren, welche an das Rail 9 angeschlossen sind, sind in Figur 1 nicht dargestellt.The high-pressure fuel pump 1 is part of a fuel injection system, which consists essentially of a tank 3, a prefeed pump 5 with an element for flow limitation 52, a filter 7, a rail 9 and a pressure relief valve 11. The injectors, which are connected to the rail 9, are in FIG. 1 not shown.

Das Element zur Fördermengenbegrenzung 52 ist bei den in den Figuren dargestellten Ausführungsbeispielen als Drossel ausgebildet, die unmittelbar am Eingang der Vorförderpumpe 5 angeordnet ist. Die Drossel 52 bewirkt, dass die insgesamt in der Kraftstoffhochdruckpumpe 1 verdichtete Kraftstoffmenge begrenzt wird. Des Weiteren wird dadurch der sich in einem Innenraum 17 der Kraftstoffhochdruckpumpe 1 ergebende Druck entsprechend einer Kennlinie eines Druckregelventils 20 begrenzt. Diese Effekte wirken sich positiv auf den Wirkungsgrad des Kraftstoffeinspritzsystems und die mechanische Beanspruchung der Kraftstoffhochdruckpumpe 1 aus.The element for flow rate limitation 52 is formed in the embodiments shown in the figures as a throttle, which is arranged directly at the entrance of the prefeed pump 5. The throttle 52 causes the total compressed in the high-pressure fuel pump 1 amount of fuel is limited. Furthermore, the resulting in an interior 17 of the high-pressure fuel pump 1 pressure is limited according to a characteristic of a pressure control valve 20. These effects have a positive effect on the efficiency of the fuel injection system and the mechanical stress of the high-pressure fuel pump 1.

Das Druckbegrenzungsventil 11 mündet in eine Rücklaufleitung 13, in die auch die Leckagemengen der nicht dargestellten Injektoren abgeführt werden. Die Rücklaufleitung 13 mündet bei diesem ersten Ausführungsbeispiel in den Tank 3 und treibt dort eine Strahlpumpe (ohne Bezugszeichen) an.The pressure limiting valve 11 opens into a return line 13, in which the leakage quantities of the injectors, not shown, are discharged. The return line 13 opens in this first embodiment in the tank 3 and drives there a jet pump (without reference numerals).

Im Inneren der Kraftstoffhochdruckpumpe 1 kann optional ein Temperatursensor T angeordnet sein. Die Kraftstoffhochdruckpumpe 1 ist über einen Kraftstoffzulauf 15, den Filter 7 und die Vorförderpumpe 5 hydraulisch mit dem Tank 3 verbunden.Inside the high-pressure fuel pump 1 may optionally be arranged a temperature sensor T. The high-pressure fuel pump 1 is hydraulically connected to the tank 3 via a fuel inlet 15, the filter 7 and the prefeed pump 5.

Der Kraftstoffzulauf 15 verbindet eine Förderseite der Vorförderpumpe 5 mit einem Innenraum 17 des Pumpengehäuses, so dass der gesamte Förderstrom der Vorförderpumpe 5 in den Innenraum 17 gelangt.The fuel inlet 15 connects a delivery side of the prefeed pump 5 with an interior 17 of the pump housing, so that the entire delivery flow of the prefeed pump 5 enters the interior 17.

Ein Kraftstoffrücklauf 18 stellt eine hydraulische Verbindung zwischen dem Innenraum 17 des Pumpengehäuses einerseits sowie einer Zumesseinheit 19 und der Rücklaufleitung 13 andererseits her. Zwischen dem Kraftstoffrücklauf 18 und der Rücklaufleitung 13 ist ein Druckregelventil 20 angeordnet.A fuel return 18 provides a hydraulic connection between the interior 17 of the pump housing on the one hand and a metering unit 19 and the return line 13 on the other hand. Between the fuel return 18 and the return line 13, a pressure regulating valve 20 is arranged.

Die Zumesseinheit 19 dient dazu, die von Pumpenelementen 21 der Kraftstoffhochdruckpumpe angesaugte Kraftstoffmenge und damit auch deren Fördermenge zu steuern. Dazu werden die Saugseiten der Pumpenelemente 21 über eine Verteilleitung 23 mit dem Ausgang der Zumesseinheit 19 hydraulisch verbunden.The metering unit 19 serves to control the amount of fuel sucked by pump elements 21 of the high-pressure fuel pump and thus also the delivery rate thereof. These are the Suction sides of the pump elements 21 via a distribution line 23 to the output of the metering unit 19 hydraulically connected.

Die Pumpenelemente 21 bestehen im wesentlichen aus Saugventilen 25, hochdruckseitigen Rückschlagventilen 27 und einem Kolben 29, der in einer Zylinderbohrung (ohne Bezugszeichen) oszilliert. Die Kolben 29 der Pumpenelemente 21 werden über Rollenstößel 31 von Nocken 33 einer Antriebswelle 35 angetrieben. Die Pumpenelemente 21 fördern unter hohem Druck stehenden Kraftstoff über eine Hochdruckleitung 34 in das Rail 9.The pump elements 21 consist essentially of suction valves 25, high-pressure side check valves 27 and a piston 29 which oscillates in a cylinder bore (without reference numeral). The pistons 29 of the pump elements 21 are driven by roller tappets 31 of cams 33 of a drive shaft 35. The pump elements 21 convey fuel under high pressure via a high-pressure line 34 into the rail 9.

Die Nocken 33 sind Teil einer Antriebswelle 35, die zu beiden Seiten der Nocken 33 in einem ersten Lager und in einem zweiten Lager in einem Pumpengehäuse (nicht dargestellt) drehbar gelagert ist. Die Antriebswelle 35 ist in dem Innenraum 17 des Pumpengehäuses angeordnet. Die Lager der Antriebswelle 35 sind in dem Blockschaltbild gemäß Figur 1 als Drosselstelle dargestellt. Das erste Lager hat in Figur 1 das Bezugszeichen 39, während das zweite Lager mit dem Bezugszeichen 41 versehen wurde.The cams 33 are part of a drive shaft 35, which is rotatably mounted on both sides of the cam 33 in a first bearing and in a second bearing in a pump housing (not shown). The drive shaft 35 is arranged in the interior 17 of the pump housing. The bearings of the drive shaft 35 are in the block diagram according to FIG. 1 shown as throttle point. The first camp has in FIG. 1 the reference numeral 39, while the second bearing has been provided with the reference numeral 41.

Bei dem in Figur 1 dargestellten ersten Ausführungsbeispiel einer erfindungsgemäßen Kraftstoffhochdruckpumpe ist das Druckregelventil 20 stromabwärts des Innenraums 17 der Kraftstoffhochdruckpumpe 1 angeordnet. Das Druckregelventil 20 umfasst eine Leckageleitung 57 in der optional eine Drossel 61 vorgesehen sein kann. Durch die Anordnung des Druckregelventils 20 stromabwärts des Innenraums 17herrscht in dem Innenraum 17 nahezu der gleiche Druck wie auf der Druckseite der Vorförderpumpe 5. In der Regel beträgt der Überdruck auf der Druckseite der Vorförderpumpe 5 und damit des Innenraums 17 etwa 3 bar bis etwa 7 bar.At the in FIG. 1 illustrated first embodiment of a high-pressure fuel pump according to the invention, the pressure control valve 20 downstream of the interior 17 of the high-pressure fuel pump 1 is arranged. The pressure control valve 20 includes a leakage line 57 in the optional throttle 61 may be provided. By the arrangement of the pressure control valve 20 downstream of the interior 17 prevails in the interior 17 almost the same pressure as on the pressure side of the prefeed pump 5. In general, the pressure on the pressure side of the prefeed pump 5 and thus the interior 17 is about 3 bar to about 7 bar ,

Dieser im Innenraum 17 herrschende Druck führt zu einer Verringerung der Kavitationsneigung und damit zur Unterdrückung von Dampfblasen, insbesondere bei hohen Drehzahlen.This prevailing in the interior 17 pressure leads to a reduction in the tendency to cavitation and thus to suppress vapor bubbles, especially at high speeds.

Außerdem führt der erhöhte Innendruck im Innenraum 17 des Pumpengehäuses dazu, dass abhängig von dem im Innenraum 17 herrschenden Druck, der Viskosität des Kraftstoffs und dem Strömungswiderstand des ersten Lagers 39 und des zweiten Lagers 41, eine definierte Kraftstoffmenge durch die Lager 39 und 41 gepresst wird. Dies führt zu einer deutlichen Erhöhung der Belastbarkeit sowohl des ersten Lagers 39, als auch des zweiten Lagers 41.In addition, the increased internal pressure in the interior 17 of the pump housing causes depending on the pressure prevailing in the interior 17, the viscosity of the fuel and the flow resistance of the first bearing 39 and the second bearing 41, a defined amount of fuel through the bearings 39 and 41 is pressed , This leads to a significant increase in the load capacity of both the first bearing 39, and the second bearing 41st

Da das erste Lager 39 und das zweite Lager 41 in der Regel als Gleitlager ausgebildet sind, bildet sich durch die zwangsweise Durchströmung der Lager 39 und 41 in den Lagern 39 und/oder 41 ein hydrostatischer Schmierkeil aus. Dadurch erhöht sich die Belastbarkeit des ersten Lagers 39 und des zweiten Lagers 41 erheblich und gleichzeitig wird auch die Wärmeabfuhr aus dem ersten Lager 39 und dem zweiten Lager 41 verbessert.Since the first bearing 39 and the second bearing 41 are usually formed as a sliding bearing, formed by the forced flow through the bearings 39 and 41 in the bearings 39 and / or 41, a hydrostatic lubricating wedge. As a result, the load capacity of the first bearing 39 and the second bearing 41 increases considerably and at the same time the heat dissipation from the first bearing 39 and the second bearing 41 is improved.

Damit der Druckaufbau innerhalb der Kraftstoffhochdruckpumpe 1 und im Rail 9 beschleunigt wird, kann stromabwärts und in Reihe mit dem ersten Lager 39 ein erstes Rückschlagventil 43 angeordnet sein. Entsprechend kann stromabwärts und in Reihe mit dem zweiten Lager 41 ein zweites Rückschlagventil 45 angeordnet sein. Der Öffnungsdruck der Rückschlagventile 43 und 45 ist so gewählt, dass diese beim Start der Brennkraftmaschine geschlossen sind und erst öffnen, wenn die Brennkraftmaschine läuft. Außerdem sorgt während des Betriebs der Brennkraftmaschine der Strömungswiderstand der Rückschlagventile 43 und 45 dafür, dass die Streuung der Kraftstoffmenge, welche durch die Lager 39 und 41 strömen, verringert wird.,Thus, the pressure build-up within the high-pressure fuel pump 1 and in the rail 9 is accelerated, downstream of and in series with the first bearing 39, a first check valve 43 may be arranged. Accordingly, downstream of and in series with the second bearing 41, a second check valve 45 may be arranged. The opening pressure of the check valves 43 and 45 is chosen so that they are closed when starting the internal combustion engine and open only when the internal combustion engine is running. In addition, during operation of the internal combustion engine, the flow resistance of the check valves 43 and 45 ensures that the dispersion of the amount of fuel flowing through the bearings 39 and 41 is reduced.

Das erste Rückschlagventil 43 und das zweite Rückschlagventil 45 münden in die Rücklaufleitung 13. Alternativ kann anstelle des ersten Rückschlagventils 43 oder anstelle des zweiten Rückschlagventils 45 eine Drossel oder Blende vorgesehen werden.The first check valve 43 and the second check valve 45 open into the return line 13. Alternatively, instead of the first check valve 43 or instead of the second check valve 45, a throttle or aperture may be provided.

Es hat sich bei Versuchen herausgestellt, dass aufgrund der Fertigungstoleranzen beispielsweise am Durchmesser des Lagerzapfens (nicht dargestellt) der Antriebswelle 35 für die Lager 39 und 41 und der zugehörigen Lagerschale (nicht dargestellt) im Pumpengehäuse bei ungünstiger Toleranzlage die Kraftstoffmenge, welche durch die Lager 39 und 41 strömt, innerhalb einer Serie von Kraftstoffhochdruckpumpen 1 erheblich streuen kann. Dieser unerwünschte Effekt wird, falls erforderlich, durch die Rückschlagventile 43 und 45 auf ein unkritisches Maß verringert.It has been found in experiments that due to the manufacturing tolerances, for example, on the diameter of the journal (not shown) of the drive shaft 35 for the bearings 39 and 41 and the associated bearing shell (not shown) in the pump housing at an unfavorable tolerance position, the amount of fuel passing through the bearings 39 and 41 flows within a series of high-pressure fuel pumps 1 can significantly scatter. This undesirable effect is, if necessary, reduced by the check valves 43 and 45 to an uncritical level.

Die Vorförderpumpe 5 kann als Flügelzellenpumpe, als Innenzahnradpumpe, insbesondere als Gerotorpumpe, oder als Außenzahnradpumpe ausgebildet sein. Bei diesen Pumpen ist zwischen den sich drehenden Bauteilen und dem Pumpengehäuse ein Spalt vorhanden, der Leckageverluste verursacht. Dieser Spalt ist in Figur 3 durch das Symbol einer Drossel (siehe Bezugszeichen 49) dargestellt. Die durch den Spalt abfließende Leckagemenge wird durch eine Leckageleitung 51 abgeführt. Die Leckageleitung 51 mündet vor dem ersten Rückschlagventil 43 in die Leitung (ohne Bezugszeichen), welche die durch das erste Lager 39 strömende Kraftstoffmenge über das erste Rückschlagventil 43 der Rücklaufleitung 13 zuführt.The prefeed pump 5 can be designed as a vane pump, as an internal gear pump, in particular as a gerotor pump, or as an external gear pump. These pumps have a gap between the rotating components and the pump housing that causes leakage losses. This gap is shown in Figure 3 by the symbol of a throttle (see reference numeral 49). The leaked through the gap leakage amount is discharged through a leakage line 51. The leakage line 51 opens into the line before the first check valve 43 (not numbered), which supplies the flowing through the first bearing 39 amount of fuel via the first check valve 43 of the return line 13.

Die erfindungsgemäße Kraftstoffhochdruckpumpe 1 hat unter anderem folgende Vorteile:The high-pressure fuel pump 1 according to the invention has, inter alia, the following advantages:

Durch die Anordnung des Druckregelventils 20 im Kraftstoffrücklauf 18 wird das im Innenraum 17 des Pumpengehäuses herrschende Druckniveau angehoben, was die Gefahr von Kavitation und die Gefahr der Dampfblasenbildung verringert.The arrangement of the pressure control valve 20 in the fuel return 18, the pressure prevailing in the interior 17 of the pump housing pressure level is raised, which reduces the risk of cavitation and the risk of vapor bubble formation.

Außerdem werden sowohl das erste Lager 39 als auch das zweite Lager 41 zwangsweise von Kraftstoff durchströmt, was deren Belastbarkeit sowohl bezüglich mechanischer als auch thermischer Beanspruchungen deutlich erhöht.In addition, both the first bearing 39 and the second bearing 41 are forcibly traversed by fuel, which significantly increases their capacity, both in terms of mechanical and thermal stresses.

Eventuell auftretende Schwankungen der Durchflussmenge zwischen verschiedenen Exemplaren in Serie gefertigten erfindungsgemäßen Kraftstoffhochdruckpumpen 1 können durch in Reihe geschaltete Rückschlagventile 43, 45 und/oder Drosseln oder Blenden reduziert werden.Possibly occurring fluctuations in the flow rate between different copies in series produced high-pressure fuel pumps 1 according to the invention can be reduced by series-connected check valves 43, 45 and / or throttles or orifices.

Die zu Schmier- und Kühlzwecken durch das Pumpengehäuse und die Lager 39 und 41 strömende Kraftstoffmenge wird stark erhöht.The amount of fuel flowing through the pump housing and bearings 39 and 41 for lubrication and cooling purposes is greatly increased.

Eine Schmierdrossel zur Einstellung einer definierten Schmiermenge kann entfallen. Durch die großen Schmiermengen werden eventuell vorhandene Partikel schnell aus dem Innenraum geschwemmt.A lubricating throttle for setting a defined amount of lubricant can be omitted. Due to the large quantities of lubricants, any particles that may be present are quickly washed out of the interior.

Die Förderhöhe der Vorförderpumpe kann oftmals reduziert werden, was den Wirkungsgrad des Einspritzsystems verbessert.The delivery head of the prefeed pump can often be reduced, which improves the efficiency of the injection system.

In Figur 2 wird ein weiteres Ausführungsbeispiel eines erfindungsgemäßen Kraftstoffeinspritzsystems ebenfalls als Blockschaltbild dargestellt. Dabei werden nur die wesentliche Unterschiede erläutert. Gleiche Bauteile werden mit gleichen Bezugszeichen versehen und es gilt das bezüglich der vorangegangenen Ausführungsbeispiele Gesagte entsprechend.In FIG. 2 a further embodiment of a fuel injection system according to the invention is also shown as a block diagram. Only the essential differences are explained. The same components are provided with the same reference numerals and it is the case with respect to the previous embodiments said accordingly.

Bei dem Ausführungsbeispiel gemäß Figur 2 hat das Druckregelventil 20 einen ersten Ausgang 53, der in die Rücklaufleitung 13 mündet. Des Weiteren hat das Druckregelventil 20 einen zweiten Ausgang 55, der auf der Saugseite der Vorförderpumpe 5 in den Kraftstoffzulauf 15 mündet. Dadurch kann die überschüssige Kraftstoffmenge, die vom Druckregelventil 20 abgeführt wird, aufgeteilt werden, so dass ein Teil des überschüssigen Kraftstoffs über die Rücklaufleitung 13 in den Tank 3 zurückfließt, wo dieser Kraftstoff gekühlt werden kann. Ein anderer Teil des überschüssigen Kraftstoffs wird im zweiten Ausgang 55 des Druckregelventils 20 direkt in den Kraftstoffzulauf 15 zurückgeführt. Dadurch wird nach wie vor die volle Fördermenge der Vorförderpumpe 5 zur Schmierung der Kraftstoffhochdruckpumpe eingesetzt, während nur ein Teil dieser Fördermenge über die Rücklaufleitung 13 dem Tank 3 zur Kühlung zugeführt wird. Bei diesem Ausführungsbeispiel einer erfindungsgemäßen Kraftstoffhochdruckpumpe ist die durch die Rücklaufleitung 13 strömende Kraftstoffmenge etwa gleich groß wie bei herkömmlichen Kraftstoffeinspritzpumpen, obwohl die Schmierung der erfindungsgemäßen Kraftstoffhochdruckpumpe 1 sehr viel leistungsfähiger ist als bei herkömmlichen Kraftstoffhochdruckpumpen.In the embodiment according to FIG. 2 the pressure control valve 20 has a first output 53, which opens into the return line 13. Furthermore, the pressure regulating valve 20 has a second outlet 55, which opens into the fuel inlet 15 on the suction side of the prefeed pump 5. Thereby, the excess amount of fuel discharged from the pressure regulating valve 20 can be divided, so that a part of the excess fuel flows back into the tank 3 via the return line 13, where this fuel can be cooled. Another part of the excess fuel is fed back directly into the fuel inlet 15 in the second output 55 of the pressure regulating valve 20. As a result, the full flow rate of the prefeed pump 5 is still used for lubrication of the high-pressure fuel pump, while only a portion of this flow is supplied via the return line 13 to the tank 3 for cooling. In this embodiment of a high-pressure fuel pump according to the invention, the amount of fuel flowing through the return line 13 is about the same as in conventional fuel injection pumps, although the lubrication of the high-pressure fuel pump 1 according to the invention is much more efficient than in conventional high-pressure fuel pumps.

Sowohl im ersten Ausgang 53 als auch in der Leckageleitung 57 des Druckregelventils 20 können Drosseln 59 und 61 vorgesehen sein. Mit der ersten Drossel 59 ist es möglich, den Teil des überschüssigen Kraftstoffs, der in die Rücklaufleitung 13 strömt, zu begrenzen. Mit der zweiten Drossel 61 können die Bewegungen des Ventilkolbens (ohne Bezugszeichen) des Druckregelventils 20 wirksam bedämpft werden. Die Hochdruckförderung und die Kühl- und Schmiermenge werden deutlich konstanter eingestellt.Both in the first output 53 and in the leakage line 57 of the pressure control valve 20 throttles 59 and 61 may be provided. With the first throttle 59, it is possible to limit the part of the excess fuel flowing into the return line 13. With the second throttle 61, the movements of the valve piston (without reference numerals) of the pressure control valve 20 can be effectively damped. The high pressure delivery and the cooling and lubricating amount are set much more constant.

Eine alternative Anordnung der Drossel 61 in der Leckageleitung 57 ist gestrichelt dargestellt. Selbstverständlich ist es auch möglich, am zweiten Ausgang 55 des Druckregelventils 20 eine nicht dargestellte Drossel vorzusehen, mit deren Hilfe die direkt in den Kraftstoffzulauf 15 zurückgeförderte Kraftstoffmenge begrenzt wird. Durch eine geeignete Abstimmung der ersten Drossel 59, der zweiten Drossel 61 und gegebenenfalls der dritten Drossel im zweiten Ausgang 55 des Druckregelventils 20 kann die gewünschte Aufteilung der überschüssigen Kraftstoffmenge auf den die Rücklaufleitung 13 und den Kraftstoffzulauf 15 entsprechend den Anforderungen eingestellt werden.An alternative arrangement of the throttle 61 in the leakage line 57 is shown in dashed lines. Of course, it is also possible to provide at the second output 55 of the pressure control valve 20, a throttle, not shown, with the aid of which is directly fed back into the fuel supply 15 fuel quantity limited. By a suitable tuning of the first throttle 59, the second throttle 61 and optionally the third throttle in the second output 55 of the pressure control valve 20, the desired distribution of excess fuel to the return line 13 and the fuel inlet 15 can be adjusted according to the requirements.

Claims (14)

  1. High-pressure fuel pump for a fuel injection system of an internal combustion engine, with a pump casing, with a drive shaft (35), the drive shaft (35) being mounted in the pump casing by means of a first bearing (39) and a second bearing (41), with at least one pump element (21) arranged radially with respect to the drive shaft (35), with a fuel inflow (15), via which the high-pressure fuel pump is supplied with fuel which is under pressure, with a fuel return (18), with a metering unit (19) for regulating the delivery rate of the pump element or pump elements (21), and with a pressure-regulating valve (20), both the metering unit (19) and the pressure-regulating valve (20) being supplied with fuel by the fuel return (18), characterized in that a first non-return valve (43) is provided downstream of the first bearing (39), in that a second non-return valve (45) is provided downstream of the second bearing (41), in that the first bearing (39) and the second bearing (41) are lubricated by fuel which is under pressure, and in that the first bearing (39) and the second bearing (41) are hydraulically connected both to the fuel inflow (15) and to a return line (13).
  2. High-pressure fuel pump according to Claim 1, characterized in that the first bearing (39) and/or the second bearing (41) are/is designed as a plain bearing.
  3. High-pressure fuel pump according to one of the preceding claims, characterized in that the fuel inflow (15) issues into an inner space (17) of the pump casing.
  4. High-pressure fuel pump according to one of the preceding claims, characterized in that an outlet of the pressure-regulating valve (20) issues into the return line (13).
  5. High-pressure fuel pump according to one of Claims 1 to 3, characterized in that the outlet of the pressure-regulating valve (20) issues into the fuel inflow (15).
  6. High-pressure fuel pump according to one of Claims 1 to 3, characterized in that the pressure-regulating valve (20) is of two-stage design, with a first outlet (53) and a second outlet (55), in that the first outlet (53) issues into the return line (13), and in that the second outlet (55) of the pressure-regulating valve (20) issues into the fuel inflow (15).
  7. High-pressure fuel pump according to Claim 6, characterized in that the second outlet (55) of the pressure-regulating valve (20) is opened only when a stipulatable minimum pressure (pmin) prevails at the inlet of the pressure-regulating valve (20).
  8. High-pressure fuel pump according to Claim 6 or 7, characterized in that a first throttle (59) is provided downstream of the first outlet (53), and/or in that a throttle is provided downstream of the second outlet (55).
  9. High-pressure fuel pump according to one of the preceding claims, characterized in that a throttle (61) is provided on a leakage line (57) of the pressure-regulating valve (20).
  10. High-pressure fuel pump according to one of the preceding claims, characterized in that an opening pressure of the first non-return valve (43) and/or an opening pressure of the second non-return valve (45) are/is selected such that the first non-return valve (43) and/or the second non-return valve (45) are/is closed during the starting of the internal combustion engine and open/opens when the idling rotational speed of the internal combustion engine is reached.
  11. Fuel injection system for an internal combustion engine, with a prefeed pump (5), with a tank (3), with a high-pressure fuel pump (1), with a common rail (9) and with an at least one injector, characterized in that the high-pressure fuel pump (1) is a high-pressure fuel pump according to one of the preceding claims.
  12. Fuel injection system according to Claim 11, characterized in that the prefeed pump (5) is driven by the internal combustion engine or by an electric motor.
  13. Fuel injection system according to either one of Claims 11 and 12, characterized in that the prefeed pump (5) is designed as a vane-cell pump, as an internal gear pump or as an external gear pump.
  14. Fuel injection system according to one of Claims 11 to 13, characterized in that the prefeed pump (5) comprises an element for delivery-rate limitation (52), in particular a throttle and/or a diaphragm.
EP07115205A 2006-10-12 2007-08-29 High-pressure fuel pump and fuel injection system for a combustion engine Not-in-force EP1911964B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006048356A DE102006048356A1 (en) 2006-10-12 2006-10-12 High-pressure fuel pump and fuel injection system for an internal combustion engine

Publications (2)

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EP1911964A1 EP1911964A1 (en) 2008-04-16
EP1911964B1 true EP1911964B1 (en) 2010-01-13

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AT (1) ATE455242T1 (en)
DE (2) DE102006048356A1 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMI20080966A1 (en) * 2008-05-23 2009-11-24 Bosch Gmbh Robert METHOD AND PLANT FOR FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE
DE102009001563A1 (en) * 2009-03-16 2010-09-23 Robert Bosch Gmbh high pressure pump
DE102009003098A1 (en) 2009-05-14 2010-11-18 Robert Bosch Gmbh Fuel injection system for internal combustion engine of person vehicle, has high-pressure fuel pump and mechanically operated feed pump, where feed pump is flanged indirectly at flange surface of high pressure fuel pump
DE102009027954A1 (en) 2009-07-23 2011-01-27 Robert Bosch Gmbh Mechanically driven prefeed pump for fuel injection system of internal-combustion engine, has pump arranged between suction-side connection and pressure-lateral connection, where prefeed pump is isolated by two external connections
DE102010031595A1 (en) 2010-07-21 2012-01-26 Robert Bosch Gmbh Fuel pump i.e. gear pump, for conveying fuel in fuel injection system of combustion engine for common-rail system, has relief valve arranged at case, where pressure at maximum overflow rate is small than opening pressure of relief valve
DE102010038895A1 (en) 2010-08-04 2012-02-09 Robert Bosch Gmbh Fuel pump i.e. gear pump, for pumping fuel in common rail injection system of internal combustion engine, has seal provided for sealing housing, where seal is provided at cover and is injected molded to cover
DE102011002750A1 (en) * 2011-01-17 2012-07-19 Robert Bosch Gmbh Method and device for controlling a fuel injection system and fuel injection system
CN103511216B (en) * 2013-09-25 2015-10-21 中国科学技术大学 Syringe pump, injecting systems and injecting method

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19746563A1 (en) * 1997-10-22 1999-04-29 Bosch Gmbh Robert Fuel injection system for IC engine
JP4841772B2 (en) * 2001-09-28 2011-12-21 いすゞ自動車株式会社 Common rail fuel injection control device
DE10215021A1 (en) * 2002-04-05 2003-10-23 Bosch Gmbh Robert Fuel injection device for an internal combustion engine
DE10237592A1 (en) * 2002-08-16 2004-03-11 Robert Bosch Gmbh Fuel injection device for an internal combustion engine
DE102005027851A1 (en) * 2005-06-16 2006-12-21 Robert Bosch Gmbh Fuel injection system for an internal combustion engine

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EP1911964A1 (en) 2008-04-16
DE102006048356A1 (en) 2008-04-17
DE502007002604D1 (en) 2010-03-04
ATE455242T1 (en) 2010-01-15

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