EP0960275A1 - High pressure pump for supplying fuel in fuel injection systems of internal combustion engines - Google Patents

High pressure pump for supplying fuel in fuel injection systems of internal combustion engines

Info

Publication number
EP0960275A1
EP0960275A1 EP98966148A EP98966148A EP0960275A1 EP 0960275 A1 EP0960275 A1 EP 0960275A1 EP 98966148 A EP98966148 A EP 98966148A EP 98966148 A EP98966148 A EP 98966148A EP 0960275 A1 EP0960275 A1 EP 0960275A1
Authority
EP
European Patent Office
Prior art keywords
pressure pump
fuel
high pressure
valve
common
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.)
Granted
Application number
EP98966148A
Other languages
German (de)
French (fr)
Other versions
EP0960275B1 (en
Inventor
Josef Güntert
Jürgen HAMMER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0960275A1 publication Critical patent/EP0960275A1/en
Application granted granted Critical
Publication of EP0960275B1 publication Critical patent/EP0960275B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • 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
    • 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
    • F02M59/20—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
    • F02M59/366—Valves being actuated electrically
    • 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
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion

Definitions

  • the invention relates to a high-pressure pump for supplying fuel to fuel injection systems of internal combustion engines, in particular in a common rail injection system, the fuel injection system comprising a low-pressure part which contains a fuel tank and a pre-feed pump, and a high-pressure part which contains the high-pressure pump and a common distributor bar , into which a fuel flow is conveyed by the high pressure pump through a common channel.
  • a constant fuel flow is normally conveyed through the prefeed pump into individual elements of the high-pressure pump, regardless of the need.
  • the individual elements of the high-pressure pump can be, for example, a plurality of cylinders, in each of which a piston can be moved back and forth in order to draw in the fuel and apply high pressure to it. If regardless of need constant speed-dependent fuel flow is pumped from the high pressure pump into the common manifold, this means that the power consumption of the high pressure pump is constant even when the demand drops. This has an unfavorable effect on the overall efficiency of the internal combustion engine. Furthermore, the excess, high-pressure compressed amount of fuel must be controlled again from the high-pressure pump, which leads to temperature increases in the fuel.
  • the invention is therefore based on the problem of a To provide high pressure pump, which overcomes the disadvantages mentioned above.
  • damage to the individual elements of the high-pressure pump should be avoided during operation.
  • a simply constructed high-pressure pump is to be created which meets high safety requirements and which can nevertheless be manufactured inexpensively.
  • a high pressure pump for supplying fuel to fuel injection systems of internal combustion engines, in particular with a common rail injection system, the fuel injection system comprising a low pressure part which contains a fuel tank and a pre-feed pump and a high pressure part which contains the high pressure pump and a common distributor bar, into which a fuel flow is conveyed by the high-pressure pump through a common channel, in that a demand quantity control for the fuel flow conveyed by the high-pressure pump is integrated.
  • a special embodiment of the invention is characterized in that the demand quantity control comprises a directional control valve which delivers the fuel flow conveyed by the high pressure pump, as required, either to the common distributor rail or to the low pressure part of the fuel injection system.
  • the high pressure pump serves as an actuator in the pressure control loop.
  • the demand quantity control of the fuel flow conveyed by the high pressure pump is advantageously carried out with only one directional valve. This saves costs in the manufacture of the high pressure pump.
  • the installation space of the high-pressure pump is advantageously limited.
  • a further special embodiment of the invention is characterized in that the directional valve is a 3/2-way valve which is mounted in the common channel and the common channel in a first valve position with the common manifold and in a second Valve position connects with the low pressure part of the fuel injection system.
  • the fuel flow In the second valve position, the fuel flow returns to the low-pressure part of the fuel injection system without pressure, without being subjected to high pressure.
  • the fuel flow can either be returned to the fuel tank or to the connecting line between the prefeed pump and the high pressure pump. Because the entire fuel flow is conveyed by the high-pressure pump, a division into a delivery flow and a lubrication flow in the low-pressure part can be omitted.
  • a further special embodiment of the invention is characterized in that a check valve is arranged between the directional valve and the common distributor bar. In the first valve position, the common channel is connected to the common manifold.
  • the check valve arranged between the directional control valve and the common distributor strip ensures that the fuel is compressed by the individual elements of the high-pressure pump until a desired pressure is reached. When the desired pressure is reached, the check valve opens and the fuel flows into the common rail. The fuel is therefore only subjected to high pressure in the high pressure pump when the directional control valve is in the first valve position.
  • Another special embodiment of the invention is characterized in that the directional valve can be actuated magnetically. Short switching times can be achieved by the magnetic actuation of the directional valve.
  • a further special embodiment of the invention is characterized in that the high-pressure pump is a radial piston pump, which comprises a drive shaft mounted in a pump housing, which is eccentric or has cam-like elevations in the circumferential direction, and preferably comprises a plurality of pistons arranged radially with respect to the drive shaft in a respective cylinder space which can be moved back and forth in the respective cylinder space in the radial direction by rotating the drive shaft.
  • Radial piston pumps of this type are particularly suitable for common rail injection systems. When the pistons are moved back and forth, caffeine is sucked in first and then compressed.
  • the present invention generally has the advantage that it can be implemented simply and inexpensively.
  • the basic idea of the present invention can also be applied to conventional high-pressure pumps in a simple manner, because known components from conventional high-pressure pumps can be used. This increases the development effort and the cost risk kept low.
  • Figure 1 shows a schematic representation of a fuel injection system with a high pressure pump and a directional control valve in a first valve position
  • Figure 2 shows a schematic representation of the
  • Figure 3 shows an embodiment of a high pressure pump according to the invention.
  • FIG. 1 shows a schematic representation of a fuel injection system with an inventive High pressure pump, which is denoted overall by 1.
  • a prefeed pump 2 supplies fuel 4 from a tank 3 through a fuel line 5 to the high-pressure pump 1.
  • the high-pressure pump 1 comprises three elements 6, 7, 8.
  • the elements 6, 7, 8 are each formed by a cylinder in which a piston is located can move back and forth. When the pistons shown in FIG. 1 move downward, fuel is drawn in through the fuel line 5. When the pistons move upwards, the fuel contained in the cylinders is compressed and fed into a common channel 10.
  • a magnetically controlled 3/2-way valve 12 is installed in the common channel 10. In the position of the directional control valve 12 shown in FIG. 1, the fuel reaches the fuel line 5 from the common channel 10 via a return 15.
  • FIG. 2 shows the same fuel injection system as shown in FIG. 1. The only difference is that the valve is in a different position. In the position of the directional control valve 12 shown in FIG. 2, the fuel passes from the common channel 10 into a channel 11 in which a check valve 13 is attached. During operation of the high-pressure pump 1, fuel is conveyed from the elements 6, 7, 8 into the channel 11 until the pressure is so great that the check valve 13 opens. Then the high-pressure fuel passes through a line 14 into a common manifold, not shown.
  • the high-pressure pump shown in FIG. 3 is a radial piston pump for supplying high-pressure fuel in fuel injection systems of internal combustion engines.
  • the radial piston pump comprises a drive shaft 21 mounted in a pump housing 20 with an eccentrically designed shaft section 22.
  • a ring 23 is provided on the eccentric shaft section 22, with respect to which the shaft section 22 can be rotated.
  • the ring 23 comprises a plurality of mutually offset flats against which a piston 24 is supported.
  • the pistons 24 are each accommodated in a cylinder space 25 such that they can move back and forth in the radial direction relative to the drive shaft 21.
  • the foot of the piston 24 is designed as a plate 26, which on the ring
  • the plate 26 is fastened to the piston 24 by a cage 27 and is pressed against the ring 23 by a spring 28.
  • Fuel is drawn into the cylinder chamber 25 from a fuel line 5. If the piston 24 of the Moved away drive shaft 21, the fuel located in the cylinder chamber 25 is conveyed via channels 30, 31, 32 into a common channel 10. In the common channel 10, the fuel is pumped from all cylinder rooms. In the sectional view shown in FIG. 3, only one cylinder space 25 can be seen, but generally a plurality of cylinder spaces 25 are arranged radially to the drive shaft 21.
  • a check valve 35 ensures that the fuel is not delivered from the cylinder chamber 25 into the fuel line 5. Accordingly, a check valve 36 ensures during the intake stroke that the fuel is not drawn from the common channel 10 into the cylinder chamber 25.
  • a 3/2-way valve 12 is attached in the common channel 10.
  • the directional control valve 12 has a cylindrical body 41 with a trumpet-shaped closure element 44. Openings 42, 43 are provided in the cylindrical body 41. In the position of the directional control valve 12 shown in FIG. 3, the fuel can pass from the common channel 10 through the openings 42, 43 in the valve body 41 into a channel 11.
  • a check valve 13 is fitted in the channel 11.
  • the check valve 13 opens and the high-pressure fuel passes through a channel 50 via a high-pressure line to a common rail, which is referred to as a common rail and is not shown in FIG.
  • a common rail which is referred to as a common rail and is not shown in FIG.
  • fuel which is subjected to high pressure is thus delivered into the common distributor rail.
  • the 3/2 way valve switches to its second position.
  • the cylindrical valve body 41 In the second position (not shown) of the 3/2-way valve, the cylindrical valve body 41 is displaced upwards in such a way that it closes the channel 11. At the same time, the trumpet-shaped closure element 44 lifts off its seat, so that the fuel flows out of the channel 10 into a space 51, which is connected to a return, not shown. In the second valve position, the fuel that is not required is therefore not subjected to high pressure.

Abstract

The invention relates to a high pressure pump for supplying fuel in fuel injection systems of internal combustion engines. The fuel injection system comprises a low pressure part, containing a fuel tank (3) and a presupply pump(2), and a high pressure part, comprising the high pressure pump (1) and a common distributor strip. The high pressure pump (1) pumps a flow of fuel into said distributor strip through a common channel (10). This helps to improve the overall degree of efficiency of the engine since the power consumption of the high pressure pump (1) is reduced as a result.

Description

Hochdruckpumpe zur KraftstoffVersorgung beiHigh pressure pump for fuel supply at
Kraf stoffeinspritzsyste en von Brennkraf maschinenFuel injection systems of internal combustion engines
Stand der TechnikState of the art
Die Erfindung betrifft eine Hochdruckpumpe zur Kraftstoffversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen, insbesondere bei einem Common-Rail- Einspritzsystem, wobei das Kraf stoffeinspritzsystem einen Niederdruckteil, der einen Kraf stofftank und eine Vorförderpumpe enthält, und eine Hochdruckteil umfaßt, der die Hochdruckpumpe und eine gemeinsame Verteilerleiste enthält, in die von der Hochdruckpumpe durch einen gemeinsamen Kanal ein Kraftstoffström gefördert wird.The invention relates to a high-pressure pump for supplying fuel to fuel injection systems of internal combustion engines, in particular in a common rail injection system, the fuel injection system comprising a low-pressure part which contains a fuel tank and a pre-feed pump, and a high-pressure part which contains the high-pressure pump and a common distributor bar , into which a fuel flow is conveyed by the high pressure pump through a common channel.
Bei herkömmlichen Kraftstoffeinspritzsystemen der vorab geschilderten Art wird normalerweise unabhängig vom Bedarf ein konstanter Kraftstoffström durch die Vorförderpumpe in einzelne Elemente der Hochdruckpumpe gefördert. Die einzelnen Elemente der Hochdruckpumpe können beispielsweise mehrere Zylinder sein, in denen jeweils ein Kolben hin- und herbewegbar ist, um den Kraftstoff anzusaugen und mit Hochdruck zu beaufschlagen. Wenn unabhängig vom Bedarf ein konstanter drehzahlabhängiger Kraftstoffström von der Hochdruckpumpe in die gemeinsame Verteilerleiste gefördert wird, bedeutet das, daß die Leistungsaufnahme der Hochdruckpumpe auch bei sinkendem Bedarf konstant ist. Das wirkt sich ungünstig auf den Gesamtwirkungsgrad der Brennkraftmaschine aus. Des weiteren muß die überschüssige, auf Hochdruck verdichtete Kraf stoffmenge wieder aus der Hochdruckpumpe abgesteuert werden, was zu Temperaturerhöhungen des Kraftstoffs führt .In conventional fuel injection systems of the type described above, a constant fuel flow is normally conveyed through the prefeed pump into individual elements of the high-pressure pump, regardless of the need. The individual elements of the high-pressure pump can be, for example, a plurality of cylinders, in each of which a piston can be moved back and forth in order to draw in the fuel and apply high pressure to it. If regardless of need constant speed-dependent fuel flow is pumped from the high pressure pump into the common manifold, this means that the power consumption of the high pressure pump is constant even when the demand drops. This has an unfavorable effect on the overall efficiency of the internal combustion engine. Furthermore, the excess, high-pressure compressed amount of fuel must be controlled again from the high-pressure pump, which leads to temperature increases in the fuel.
Zur Verbesserung des Gesamtwirkungsgrads der Brennkraftmaschine ist vorgeschlagen worden, eine geregelte, elektrische Niederdruckförderpumpe zu verwenden, um den Kraf stoffström zu den einzelnen Elementen der Hochdruckpumpe zu steuern. Diese Lösung hat unter anderem jedoch den Nachteil, daß es beim Ansaughub der Hochdruckpumpe zu Beschädigungen infolge von Kavitation kommen kann.To improve the overall efficiency of the internal combustion engine, it has been proposed to use a regulated, electrical low-pressure feed pump to control the fuel flow to the individual elements of the high-pressure pump. However, this solution has the disadvantage, among other things, that damage can occur as a result of cavitation during the suction stroke of the high-pressure pump.
Außerdem ist in dem Europäischen Patent 0 481 964 vorgeschlagen worden, die Befüllung der einzelnen Elemente der Hochdruckpumpe jeweils durch ein Magnetventil zu steuern. Diese Lösung ist jedoch sehr aufwendig und mit hohen Kosten verbunden, da für jedes Element der Hochdruckpumpe ein Magnetventil benötigt wird.In addition, it has been proposed in European Patent 0 481 964 to control the filling of the individual elements of the high pressure pump in each case by means of a solenoid valve. However, this solution is very complex and associated with high costs, since a solenoid valve is required for each element of the high-pressure pump.
Der Erfindung liegt daher das Problem zugrunde, eine Hochdruckpumpe bereitzustellen, welche die vorstehend genannten Nachteile überwindet. Insbesondere sollen Beschädigungen der einzelenen Elemente der Hochdruckpumpe im Betrieb vermieden werden. Darüber hinaus soll eine einfach aufgebaute Hochdruckpumpe geschaffen werden, die hohe Sicherheitsanforderungen erfüllt und trotzdem kostengünstig hergestellt werden kann.The invention is therefore based on the problem of a To provide high pressure pump, which overcomes the disadvantages mentioned above. In particular, damage to the individual elements of the high-pressure pump should be avoided during operation. In addition, a simply constructed high-pressure pump is to be created which meets high safety requirements and which can nevertheless be manufactured inexpensively.
Das Problem wird durch die in dem unabhängigen Patentanspruch offenbarte Hochdruckpumpe gelöst. Besondere Ausführungsarten der Erfindung sind in den Unteransprüchen offenbart .The problem is solved by the high pressure pump disclosed in the independent claim. Particular embodiments of the invention are disclosed in the subclaims.
Das Problem ist bei einer Hochdruckpumpe zur Kraftstoffversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen, insbesondere bei einem Common-Rail- Einspritzsystem, wobei das Kraftstoffeinspritzsystem einen Niederdruckteil, der einen Kraftstofftank und eine Vorförderpumpe enthält, und eine Hochdruckteil umfaßt, der die Hochdruckpumpe und eine gemeinsame Verteilerleiste enthält, in die von der Hochdruckpumpe durch einen gemeinsamen Kanal ein Kraftstoffstrom gefördert wird, dadurch gelöst, daß eine Bedarfsmengensteuerung für den von der Hochdruckpumpe geförderten Kraftstoffstrom integriert ist. Die in die Hochdruckpumpe integrierteThe problem is with a high pressure pump for supplying fuel to fuel injection systems of internal combustion engines, in particular with a common rail injection system, the fuel injection system comprising a low pressure part which contains a fuel tank and a pre-feed pump and a high pressure part which contains the high pressure pump and a common distributor bar, into which a fuel flow is conveyed by the high-pressure pump through a common channel, in that a demand quantity control for the fuel flow conveyed by the high-pressure pump is integrated. The integrated in the high pressure pump
Bedarfsmengensteuerung trägt zur Verbesserung des Motorgesamtwirkungsgrads bei, weil die Leistungsaufnahme der Hochdruckpunmpe dadurch sinkt. Die Bedarfsmengensteuerung des von der Hochdruckpumpe geförderten KraftstoffStroms liefert den Vorteil, daß eine Teilbefüllung der einzelnen Elemente der Hochdruckpumpe vermieden wird. Dadurch wird die Kavitationsgef hr verringert.Demand control helps improve overall engine efficiency because of power consumption this causes the high-pressure pump to drop. The requirement quantity control of the fuel flow conveyed by the high-pressure pump provides the advantage that partial filling of the individual elements of the high-pressure pump is avoided. This reduces the risk of cavitation.
Eine besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Bedarfsmengensteuerung ein Wegeventil umfaßt, das den von der Hochdruckpumpe geförderten Kraftstoffström, je nach Bedarf, entweder zu der gemeinsamen Verteilerleiste oder zu dem Niederdruckteil des Kraftstoffeinspritzsystems liefert. Damit ist es möglich, durch eine geeignete Regelstrategie des Drucks auf einen erwünschten Sollwert zu regeln. Die Hochdruckpumpe dient dabei als Steller im Druckregelkreis. Die Bedarfsmengensteuerung des von der Hochdruckpumpe geförderten KraftstoffStroms erfolgt vorteilhaft mit nur einem Wegeventil. Dadurch werden Kosten bei der Herstellung der Hochdruckpumpe eingespart. Zudem wird der Bauraum der Hochdruckpumpe in vorteilhafter Weise begrenzt.A special embodiment of the invention is characterized in that the demand quantity control comprises a directional control valve which delivers the fuel flow conveyed by the high pressure pump, as required, either to the common distributor rail or to the low pressure part of the fuel injection system. This makes it possible to regulate the pressure to a desired setpoint by means of a suitable control strategy. The high pressure pump serves as an actuator in the pressure control loop. The demand quantity control of the fuel flow conveyed by the high pressure pump is advantageously carried out with only one directional valve. This saves costs in the manufacture of the high pressure pump. In addition, the installation space of the high-pressure pump is advantageously limited.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß das Wegeventil ein 3/2- Wegeventil ist, das in dem gemeinsamen Kanal angebracht ist und den gemeinsamen Kanal in einer ersten Ventilstellung mit der gemeinsamen Verteilerleiste und in einer zweiten Ventilstellung mit dem Niederdruckteil des Kraftstoffeinspritzsystems verbindet. In der zweiten Ventilstellung gelangt der Kraftstoffstrom wieder drucklos in den Niederdruckteil des Kraftstoffeinspritzsystems, ohne mit Hochdruck beaufschlagt zu werden. Der Kraftstoffström kann entweder in den Kraftstofftank oder in die Verbindungsleitung zwischen der Vorförderpumpe und der Hochdruckpumpe zurückgeführt werden. Dadurch, daß der gesamte Kraftstoffström durch die Hochdruckpumpe gefördert wird, kann eine Aufteilung in einen Förderstrom und einen Schmierstrom im Niederdruckteil entfallen.A further special embodiment of the invention is characterized in that the directional valve is a 3/2-way valve which is mounted in the common channel and the common channel in a first valve position with the common manifold and in a second Valve position connects with the low pressure part of the fuel injection system. In the second valve position, the fuel flow returns to the low-pressure part of the fuel injection system without pressure, without being subjected to high pressure. The fuel flow can either be returned to the fuel tank or to the connecting line between the prefeed pump and the high pressure pump. Because the entire fuel flow is conveyed by the high-pressure pump, a division into a delivery flow and a lubrication flow in the low-pressure part can be omitted.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß zwischen dem Wegeventil und der gemeinsamen Verteilerleiste ein Rückschlagventil angeordnet ist. In der ersten Ventilstellung ist der gemeinsame Kanal mit der gemeinsamen Verteilerleiste verbunden. Durch das zwischen dem Wegeventil und der gemeinsamen Verteilerleiste angeordnete Rückschlagventil wird erreicht, daß der Kraftstoff durch die einzelnen Elemente der Hochdruckpumpe solange verdichtet wird, bis ein gewünschter Druck erreicht ist. Wenn der gewünschte Druck erreicht ist, öffnet das Rückschlagventil und der Kraftstoff strömt in die gemeinsame Verteilerleiste. Der KrafStoff wird also nur dann in der Hochdruckpumpe mit Hochdruck beaufschlagt, wenn sich das Wegeventil in der ersten Ventilstellung befindet. Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß das Wegeventil magnetisch betätigbar ist. Durch die magnetische Betätigung des Wegeventils können kurze Schaltzeiten realisiert werden.A further special embodiment of the invention is characterized in that a check valve is arranged between the directional valve and the common distributor bar. In the first valve position, the common channel is connected to the common manifold. The check valve arranged between the directional control valve and the common distributor strip ensures that the fuel is compressed by the individual elements of the high-pressure pump until a desired pressure is reached. When the desired pressure is reached, the check valve opens and the fuel flows into the common rail. The fuel is therefore only subjected to high pressure in the high pressure pump when the directional control valve is in the first valve position. Another special embodiment of the invention is characterized in that the directional valve can be actuated magnetically. Short switching times can be achieved by the magnetic actuation of the directional valve.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Hochdruckpumpe eine Radialkolbenpumpe ist, die eine in einem Pumpengehäuse gelagerte Antriebswelle, die exzentrisch ausgebildet ist oder in Umfangsrichtung nockenartige Erhebungen aufweist, und vorzugsweise mehrere bezüglich der Antriebswelle radial in einem jeweiligen Zylinderraum angeordnete Kolben umfaßt, die durch Drehen der Antriebswelle in dem jeweiligen Zylinderraum in radialer Richtung hin und her bewegbar sind. Derartige Radialkolbenpumpen sind insbesondere für Common-Rail-Einspritzsysteme geeignet. Beim Hin- und Herbewegen der Kolben wird zuerst Kaftstoff angesaugt und dann verdichtet .A further special embodiment of the invention is characterized in that the high-pressure pump is a radial piston pump, which comprises a drive shaft mounted in a pump housing, which is eccentric or has cam-like elevations in the circumferential direction, and preferably comprises a plurality of pistons arranged radially with respect to the drive shaft in a respective cylinder space which can be moved back and forth in the respective cylinder space in the radial direction by rotating the drive shaft. Radial piston pumps of this type are particularly suitable for common rail injection systems. When the pistons are moved back and forth, caffeine is sucked in first and then compressed.
Die vorliegende Erfindung hat allgemein den Vorteil, daß sie einfach und kostengünstig realisiert werden kann. Der Grundgedanke der vorliegenden Erfindung kann zudem in einfacher Art und Weise auf herkömmliche Hochdruckpumpen angewendet werden, weil bekannte Komponenten aus herkömmlichen Hochdruckpumpen verwendet werden können. Dadurch wird der Entwicklungsaufwand und das Kostenrisiko gering gehalten.The present invention generally has the advantage that it can be implemented simply and inexpensively. The basic idea of the present invention can also be applied to conventional high-pressure pumps in a simple manner, because known components from conventional high-pressure pumps can be used. This increases the development effort and the cost risk kept low.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus den Unteransprüchen sowie der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnungen ein Ausführungsbeispiel im Einzelnen beschrieben ist. Dabei können die in den Ansprüchen und in der Beschreibung erwähnten Merkmale jeweils einzeln für sich oder in beliebiger Kombination erfindungswesentlich sein. Ein Weg zum Ausführen der beanspruchten Erfindung ist nachfolgend anhand der Zeichnungen im Einzelnen erläutert.Further advantages, features and details of the invention emerge from the subclaims and the following description, in which an exemplary embodiment is described in detail with reference to the drawings. The features mentioned in the claims and in the description can each be essential to the invention individually or in any combination. One way of carrying out the claimed invention is explained in detail below with reference to the drawings.
Figur 1 zeigt eine schematische Darstellung eines Kraftstoffeinspritzsystems mit einer Hochdruckpumpe und einem Wegeventil in einer ersten Ventilstellung;Figure 1 shows a schematic representation of a fuel injection system with a high pressure pump and a directional control valve in a first valve position;
Figur 2 zeigt eine schematische Darstellung desFigure 2 shows a schematic representation of the
Kraftstoffeinspritzsystems aus Figur 1 mit dem Wegeventil in einer zweiten Ventilstellung; undFuel injection system from Figure 1 with the directional control valve in a second valve position; and
Figur 3 zeigt eine Ausführungsform einer erfindungsgemäßen Hochdruckpumpe .Figure 3 shows an embodiment of a high pressure pump according to the invention.
Figur 1 zeigt eine schematische Darstellung eines Kraftstoffeinspritzsystems mit einer erfindungsgemäßen Hochdruckpumpe, die insgesamt mit 1 bezeichnet ist. Eine Vorförderpumpe 2 liefert aus einem Tank 3 Kraftstoff 4 durch eine Kraftstoffleitung 5 zu der Hochdruckpumpe 1. Die Hochdruckpumpe 1 umfaßt drei Elemente 6, 7, 8. Die Elemente 6, 7, 8 werden jeweils von einem Zylinder gebildet, in dem sich ein Kolben hin- und herbewegen kann. Wenn sich die in Figur 1 dargestellten Kolben nach unten bewegen, wird Kraftstoff durch die Kraftstoffleitung 5 angesaugt. Wenn sich die Kolben nach oben bewegen, wird der in den Zylindern enthaltene Kraftstoff komprimiert und in einen gemeinsamen Kanal 10 gefördert.Figure 1 shows a schematic representation of a fuel injection system with an inventive High pressure pump, which is denoted overall by 1. A prefeed pump 2 supplies fuel 4 from a tank 3 through a fuel line 5 to the high-pressure pump 1. The high-pressure pump 1 comprises three elements 6, 7, 8. The elements 6, 7, 8 are each formed by a cylinder in which a piston is located can move back and forth. When the pistons shown in FIG. 1 move downward, fuel is drawn in through the fuel line 5. When the pistons move upwards, the fuel contained in the cylinders is compressed and fed into a common channel 10.
In den gemeinsamen Kanal 10 ist ein magnetgesteuertes 3/2- Wegeventil 12 eingebaut. In der in Figur 1 gezeigten Stellung des Wegeventils 12, gelangt der Kraftstoff aus dem gemeinsamen Kanal 10 über einen Rücklauf 15 wieder in die Kraftstoffleitung 5.A magnetically controlled 3/2-way valve 12 is installed in the common channel 10. In the position of the directional control valve 12 shown in FIG. 1, the fuel reaches the fuel line 5 from the common channel 10 via a return 15.
In Figur 2 ist das gleiche Kraftstoffeinspritzsystem wie in Figur 1 gezeigt. Der einzige Unterschied besteht darin, daß sich das Ventil in einer anderen Stellung befindet. In der in Figur 2 gezeigten Stellung des Wegeventils 12 gelangt der Kraftstoff aus dem gemeinsamen Kanal 10 in einen Kanal 11, in dem ein Rückschlagventil 13 angebracht ist. Im Betrieb der Hochdruckpumpe 1 wird solange Kraftstoff aus den Elementen 6, 7, 8 in den Kanal 11 gefördert, bis der Druck so groß ist, daß das Rückschlagventil 13 öffnet. Dann gelangt der mit Hochdruck beaufschlagte Krafstoff über eine Leitung 14 in eine nicht dargestellte gemeinsame Verteilerleiste .FIG. 2 shows the same fuel injection system as shown in FIG. 1. The only difference is that the valve is in a different position. In the position of the directional control valve 12 shown in FIG. 2, the fuel passes from the common channel 10 into a channel 11 in which a check valve 13 is attached. During operation of the high-pressure pump 1, fuel is conveyed from the elements 6, 7, 8 into the channel 11 until the pressure is so great that the check valve 13 opens. Then the high-pressure fuel passes through a line 14 into a common manifold, not shown.
Bei der in Figur 3 gezeigten Hochdruckpumpe handelt es sich um eine Radialkolbenpumpe zur Kraftstoffhochdruckversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen. Die Radialkolbenpumpe umfaßt eine in einem Pumpengehäuse 20 gelagerte Antriebswelle 21 mit einem exzentrisch ausgebildeten Wellenabschnitt 22. Auf dem exzentrischen Wellenabschnitt 22 ist ein Ring 23 vorgesehen, gegenüber dem der Wellenabschnitt 22 drehbar ist. Der Ring 23 umfaßt mehrere zueinander versetzte Abflachungen gegen die sich jeweils ein Kolben 24 abstützt. Die Kolben 24 sind jeweils in einem Zylinderraum 25 zur Antriebswelle 21 in radialer Richtung hin- und herbewegbar aufgenommen. Der Fuß des Kolbens 24 ist als Platte 26 ausgebildet, die an dem RingThe high-pressure pump shown in FIG. 3 is a radial piston pump for supplying high-pressure fuel in fuel injection systems of internal combustion engines. The radial piston pump comprises a drive shaft 21 mounted in a pump housing 20 with an eccentrically designed shaft section 22. A ring 23 is provided on the eccentric shaft section 22, with respect to which the shaft section 22 can be rotated. The ring 23 comprises a plurality of mutually offset flats against which a piston 24 is supported. The pistons 24 are each accommodated in a cylinder space 25 such that they can move back and forth in the radial direction relative to the drive shaft 21. The foot of the piston 24 is designed as a plate 26, which on the ring
23 anliegt. Die Platte 26 ist jeweils durch einen Käfig 27 an dem Kolben 24 befestigt und wird durch eine Feder 28 gegen den Ring 23 gedrückt.23 is present. The plate 26 is fastened to the piston 24 by a cage 27 and is pressed against the ring 23 by a spring 28.
Wenn die Antriebswelle 21 in Drehung versetzt wird, bewirkt die Exzentrizität des Wellenabschnitts 22, daß die KolbenWhen the drive shaft 21 is rotated, the eccentricity of the shaft portion 22 causes the pistons
24 in den Zylinderräumen 25 hin- und herbewegt werden. Wenn sich der Kolben 24 zu der Antriebswelle 21 hin bewegt, wird24 be moved back and forth in the cylinder rooms 25. When the piston 24 moves toward the drive shaft 21,
Kraftstoff aus einer Kraftstoffleitung 5 in den Zylinderraum 25 angesaugt. Wenn sich der Kolben 24 von der Antriebswelle 21 wegbewegt, wird der in dem Zylinderraum 25 befindliche Kraftstoff über Kanäle 30, 31, 32 in einen gemeinsamen Kanal 10 gefördert. In den gemeinsamen Kanal 10 wird der Kraftstoff aus sämtlichen Zylinderräumen gefördert. In der in Figur 3 dargestellten Schnittansicht ist nur ein Zylinderraum 25 zu sehen, aber in der Regel sind mehrere Zylinderräume 25 radial zu der Antriebswelle 21 angeordnet.Fuel is drawn into the cylinder chamber 25 from a fuel line 5. If the piston 24 of the Moved away drive shaft 21, the fuel located in the cylinder chamber 25 is conveyed via channels 30, 31, 32 into a common channel 10. In the common channel 10, the fuel is pumped from all cylinder rooms. In the sectional view shown in FIG. 3, only one cylinder space 25 can be seen, but generally a plurality of cylinder spaces 25 are arranged radially to the drive shaft 21.
Während des Förderhubs sorgt ein Rückschlagventil 35 dafür, daß der Kraftstoff nicht aus dem Zylinderraum 25 in die Kraftstoffleitung 5 gefördert wird. Dementsprechend sorgt ein Rückschlagventil 36 während des Saughubs dafür, daß der Kraftstoff nicht aus dem gemeinsamen .Kanal 10 in den Zylinderraum 25 angesaugt wird.During the delivery stroke, a check valve 35 ensures that the fuel is not delivered from the cylinder chamber 25 into the fuel line 5. Accordingly, a check valve 36 ensures during the intake stroke that the fuel is not drawn from the common channel 10 into the cylinder chamber 25.
In dem gemeinsamen Kanal 10 ist ein 3/2-Wegeventil 12 angebracht. Das Wegeventil 12 hat einen zylinderförmigen Körper 41 mit einem trompetenförmigen Verschlußelement 44. In dem zylinderförmigen Körper 41 sind Öffnungen 42, 43 vorgesehen. In der in Figur 3 gezeigten Stellung des Wegeventils 12 kann der Kraftstoff aus dem gemeinsamen Kanal 10 durch die Öffnungen 42, 43 in dem Ventilkörper 41 in einen Kanal 11 gelangen. In dem Kanal 11 ist ein Rückschlagventil 13 angebracht.In the common channel 10, a 3/2-way valve 12 is attached. The directional control valve 12 has a cylindrical body 41 with a trumpet-shaped closure element 44. Openings 42, 43 are provided in the cylindrical body 41. In the position of the directional control valve 12 shown in FIG. 3, the fuel can pass from the common channel 10 through the openings 42, 43 in the valve body 41 into a channel 11. A check valve 13 is fitted in the channel 11.
Wenn der Druck in dem Kanal 11 den sogenannten Raildruck erreicht, öffnet das Rückschlagventil 13 und der mit Hochdruck beaufschlagte Kraftstoff gelangt durch einen Kanal 50 über eine Hochdruckleitung zu einer gemeinsamen Verteilerleiste, die als common rail bezeichnet wird und in Figur 3 nicht dargestellt ist. In der in Figur 3 gezeigten Stellung des 3/2 -Wegeventils 12 wird also mit Hochdruck beaufschlagter Kraftstoff in die gemeinsame Verteilerleiste gefördert. Wenn kein Kraftstoff mehr benötigt wird, schaltet das 3/2 -Wegeventil in seine zweite Stellung um.If the pressure in the channel 11 is the so-called rail pressure reached, the check valve 13 opens and the high-pressure fuel passes through a channel 50 via a high-pressure line to a common rail, which is referred to as a common rail and is not shown in FIG. In the position of the 3/2-way valve 12 shown in FIG. 3, fuel which is subjected to high pressure is thus delivered into the common distributor rail. When fuel is no longer required, the 3/2 way valve switches to its second position.
In der nicht dargestellten zweiten Stellung des 3/2- Wegeventils ist der zylinderförmige Ventilkörper 41 so nach oben verschoben, daß er den Kanal 11 verschließt. Gleichzeitig hebt das trompetenförmige Verschlußelement 44 von seinem Sitz ab, so daß der Kraftstoff aus dem Kanal 10 in einen Raum 51 gelanngt, der mit einem nicht dargestellten Rücklauf verbunden ist. In der zweiten Ventilstellung wird der nicht benötigte Kraftstoff also nicht mit Hochdruck beaufschlagt . In the second position (not shown) of the 3/2-way valve, the cylindrical valve body 41 is displaced upwards in such a way that it closes the channel 11. At the same time, the trumpet-shaped closure element 44 lifts off its seat, so that the fuel flows out of the channel 10 into a space 51, which is connected to a return, not shown. In the second valve position, the fuel that is not required is therefore not subjected to high pressure.

Claims

Ansprüche Expectations
1. Hochdruckpumpe zur Kraftstoffversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen, insbesondere bei einem Common-Rail -Einspritzsystem, wobei das Kraftstoffeinspritzsystem einen Niederdruckteil, der einen Kraftstofftank (3) und eine Vorförderpumpe (2) enthält, und eine Hochdruckteil umfaßt, der die Hochdruckpumpe (1) und eine gemeinsame1. High-pressure pump for fuel supply in fuel injection systems of internal combustion engines, in particular in a common rail injection system, the fuel injection system comprising a low-pressure part, which contains a fuel tank (3) and a pre-feed pump (2), and a high-pressure part, which contains the high-pressure pump (1) and a common one
Verteilerleiste enthält, in die von der Hochdruckpumpe (1) durch einen gemeinsamen Kanal (10) ein Kraftstoffström gefördert wird, dadurch gekennzeichnet, daß eine Bedarfsmengensteuerung (12) für den von derContains manifold into which a fuel flow is conveyed by the high pressure pump (1) through a common channel (10), characterized in that a demand quantity control (12) for the
Hochdruckpumpe (1) geförderten Kraftstoffström integriert ist.High pressure pump (1) delivered fuel flow is integrated.
2. Hochdruckpumpe nach Anspruch 1 , dadurch gekennzeichnet, daß die Bedarfsmengensteuerung ein2. High pressure pump according to claim 1, characterized in that the demand control
Wegeventil (12) umfaßt, das den von der Hochdruckpumpe (1) geförderten Kraftstoffström, je nach Bedarf, entweder zu der gemeinsamen Verteilerleiste oder zu dem Niederdruckteil des Kraftstoffeinspritzsystems liefert .Directional control valve (12), which the fuel flow delivered by the high pressure pump (1), as required either to the common rail or to the low pressure part of the fuel injection system.
3. Hochdruckpumpe nach Anspruch 2 , dadurch gekennzeichnet, daß das Wegeventil ein 3/2 -Wegeventil3. High pressure pump according to claim 2, characterized in that the directional valve is a 3/2 way valve
(12) ist, das in dem gemeinsamen Kanal (10) angebracht ist und den gemeinsamen Kanal (10) in einer ersten Ventilstellung mit der gemeinsamen Verteilerleiste und in einer zweiten Ventilstellung mit dem(12), which is mounted in the common channel (10) and the common channel (10) in a first valve position with the common manifold and in a second valve position with the
Niederdruckteil des Kraftstoffeinspritzsystems verbindet .Low pressure part of the fuel injection system connects.
4. Hochdruckpumpe nach Anspruch 2 oder 3 , dadurch gekennzeichnet, daß zwischen dem Wegeventil (12) und der gemeinsamen Verteilerleiste ein Rückschlagventil4. High-pressure pump according to claim 2 or 3, characterized in that a check valve between the directional valve (12) and the common manifold
(13) angeordnet ist.(13) is arranged.
5. Hochdruckpumpe nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, daß das Wegeventil (12) magnetisch betätigbar ist.5. High-pressure pump according to one of claims 2 to 4, characterized in that the directional valve (12) can be actuated magnetically.
6. Hochdruckpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Hochdruckpumpe eine Radialkolbenpumpe ist, die eine in einem Pumpengehäuse (20) gelagerte Antriebswelle (21) , die exzentrisch ausgebildet ist oder in Umfangsrichtung nockenartige Erhebungen aufweist, und vorzugsweise mehrere bezüglich der Antriebswelle (21) radial in einem jeweiligen Zylinderraum (25) angeordnete Kolben (24) umfaßt, die durch Drehen der Antriebswelle (21) in dem jeweiligen Zylinderraum (25) in radialer Richtung hin und her bewegbar sind. 6. High-pressure pump according to one of the preceding claims, characterized in that the high-pressure pump is a radial piston pump which has a drive shaft (21) which is mounted in a pump housing (20) and is eccentric or in Has circumferential cam-like elevations, and preferably comprises a plurality of pistons (24) arranged radially with respect to the drive shaft (21) in a respective cylinder space (25), which by rotating the drive shaft (21) in the respective cylinder space (25) back and forth in the radial direction are movable.
EP98966148A 1997-12-17 1998-11-17 High pressure pump for supplying fuel in fuel injection systems of internal combustion engines Expired - Lifetime EP0960275B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19756087 1997-12-17
DE19756087A DE19756087A1 (en) 1997-12-17 1997-12-17 High pressure pump for fuel supply in fuel injection systems of internal combustion engines
PCT/DE1998/003379 WO1999031383A1 (en) 1997-12-17 1998-11-17 High pressure pump for supplying fuel in fuel injection systems of internal combustion engines

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EP0960275A1 true EP0960275A1 (en) 1999-12-01
EP0960275B1 EP0960275B1 (en) 2004-08-11

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EP (1) EP0960275B1 (en)
JP (1) JP2001511869A (en)
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WO (1) WO1999031383A1 (en)

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JP2001511869A (en) 2001-08-14
WO1999031383A1 (en) 1999-06-24
EP0960275B1 (en) 2004-08-11
US6186120B1 (en) 2001-02-13
DE59811797D1 (en) 2004-09-16
DE19756087A1 (en) 1999-06-24

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