EP0960275B1 - 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 Download PDFInfo
- Publication number
- EP0960275B1 EP0960275B1 EP98966148A EP98966148A EP0960275B1 EP 0960275 B1 EP0960275 B1 EP 0960275B1 EP 98966148 A EP98966148 A EP 98966148A EP 98966148 A EP98966148 A EP 98966148A EP 0960275 B1 EP0960275 B1 EP 0960275B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fuel
- pressure pump
- pump
- high pressure
- valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
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- 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
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- 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
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- 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
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- 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 according to the Preamble of claim 1.
- the advance described type is usually independent of need a constant fuel flow through the pre-feed pump in Individual elements of the high pressure pump are promoted.
- the individual elements of the high pressure pump can, for example be several cylinders, each with a piston back and forth is moved to suck in the fuel and with To apply high pressure. If regardless of need constant speed-dependent fuel flow from the High pressure pump pumped into the common manifold , it means that the power consumption of the High pressure pump is constant even when demand drops. The affects the overall efficiency of the Internal combustion engine. Furthermore, the excess, fuel quantity compressed to high pressure again from the High pressure pump can be shut down, too Temperature increases in the fuel leads.
- From US 5,626,114 is a radial piston high pressure pump where a high pressure side pressure control for everyone Pump elements through a pressure control valve of a valve unit is made.
- This valve unit consists of a 2/2-way valve with an upstream throttle and a pressure control valve arranged in parallel.
- This valve unit is on the high pressure side Distribution rail (common rail) and a bypass line of Distribution board connected.
- the low pressure side is the Valve unit with an unpressurized return line connected.
- the 2/2-way valve is at the start of the engine opened so that the high pressure area of the Fuel injection system with the pressure of the pre-feed pump is applied. As soon as the internal combustion engine is running, the 2/2-way valve is closed. In closed The state of the 2/2-way valve takes over in parallel switched pressure control valve the pressure control of the Rail. This means that the high pressure pump always against the one prevailing in the distribution strip High pressure promotes what the aforementioned disadvantages in terms of overall efficiency and fuel heating Has.
- EP 0 459 429 A1 describes a high-pressure pump with a Pump element known between the high pressure side and Low pressure side of the pump element a flow valve is provided. This flow valve is controlled so that the desired flow rate to the high pressure side is promoted. The excess fuel is over the Low pressure side returned to the fuel tank.
- the disadvantage of this flow rate regulation is that for each pump element requires a flow valve, and that the excess fuel in the pump element first pressurized and then in the flow valve is relaxed. This leads to undesirable warming of the fuel and deteriorates the efficiency of the High pressure pump.
- a high pressure pump is also included in EP 0 481 964 A2 a pump element has been proposed in which the Filling the pump element and thus also its Flow rate is controlled by a 2/2-way solenoid valve.
- the 2/2-way valve can do the hydraulic connection between the low pressure side of the high pressure pump and the Release or close the pump element and thereby the Set the delivery rate of the high pressure pump.
- This Flow control is only possible on high pressure pumps transferable to several pump elements, if for each Pump element a 2/2-way valve is provided. Thereby the costs for the flow rate regulation increase with the Number of pump elements strongly.
- the invention is therefore based on the problem of a Provide high pressure pump which the above overcomes disadvantages mentioned. In particular, should Damage to the individual elements of the high pressure pump in the Operation can be avoided. In addition, one should be simple built high pressure pump can be created, the high Security requirements met and still inexpensive can be manufactured.
- the directional valve arranged according to the invention allows the Flow control of a high pressure pump with several Pump elements through a directional valve. This will cost saved in the manufacture of the high pressure pump. moreover the space of the high pressure pump is advantageous limited.
- the pressure in the common manifold can regulate to a desired setpoint.
- the high pressure pump serves as an actuator in the pressure control loop.
- the delivery rate control according to the invention also bears to improve overall engine efficiency because the The power consumption of the high-pressure pump drops as a result.
- the Demand quantity control according to the invention of the High-pressure pump-supplied fuel flow delivers about it furthermore the advantage that a partial filling of the individual pump elements of the high pressure pump, as in suction control occurs, is avoided. Thereby the risk of cavitation is reduced.
- the invention is characterized in that the directional valve is a 3/2-way valve which is installed in the common channel and the common channel in a first valve position with the common manifold and in a second Valve position with the low pressure part of the Fuel injection system connects.
- the fuel flow is depressurized again in the low pressure part of the fuel injection system without to be pressurized.
- the fuel flow can either be in the fuel tank or in the Connection line between the pre-feed pump and the High pressure pump can be returned. Because the total fuel flow conveyed through the high pressure pump can be divided into a flow and a Lubrication flow in the low pressure part is eliminated.
- a special embodiment of the invention is characterized in that between the directional valve and the common check manifold arranged a check valve is.
- the common channel is in the first valve position connected to the common manifold.
- Another special embodiment of the invention is characterized in that the directional valve is magnetic can be actuated. By the magnetic actuation of the Directional control valve can achieve short switching times.
- a Radial piston pump is one in a pump housing mounted drive shaft, which is eccentric or has cam-like elevations in the circumferential direction, and preferably several radial with respect to the drive shaft comprises pistons arranged in a respective cylinder space, by rotating the drive shaft in each Cylinder space can be moved back and forth in the radial direction are.
- Such radial piston pumps are especially for Suitable for common rail injection systems.
- 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 found in simple way on conventional high pressure pumps be used because known components 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 an inventive High pressure pump, which is denoted overall by 1.
- a Pre-feed pump 2 delivers fuel 4 from a tank 3 through a fuel line 5 to the high pressure pump 1.
- Die 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 can move back and forth. If the in Figure 1 shown moving piston down Fuel drawn through the fuel line 5. If If the pistons move upwards, the Compressed fuel contained in cylinders and into one joint channel 10 promoted.
- a magnetically controlled 3/2-way valve 12 installed in the common channel 10 in the common channel 10 in the common channel 10 in the common channel 10.
- the fuel passes from the common channel 10 via a return 15 in the Fuel line 5.
- Figure 2 is the same fuel injection system as in Figure 1 shown. The only difference is that the valve is in a different position.
- the valve In the Position of the directional valve 12 shown in Figure 2 arrives the fuel from the common channel 10 into a channel 11, in which a check valve 13 is attached.
- the high-pressure pump 1 will continue to run out of fuel promoted the elements 6, 7, 8 in 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 in a common, not shown Rail.
- the high pressure pump shown in FIG. 3 is a radial piston pump for high-pressure fuel supply in fuel injection systems of internal combustion engines.
- the radial piston pump comprises one in a pump housing 20 mounted drive shaft 21 with an eccentric trained shaft section 22. On the eccentric A shaft 23 is provided opposite the shaft section 22 which the shaft section 22 is rotatable.
- the ring 23 includes several staggered flats against each other one piston 24 is supported.
- the pistons 24 are each in a cylinder space 25 to the drive shaft 21 in a radial Direction back and forth recorded.
- the foot of the Piston 24 is designed as a plate 26 on the ring 23 is present.
- the plate 26 is in each case by a cage 27 attached to the piston 24 and is supported by a spring 28 pressed against the ring 23.
- a check valve 35 ensures that that the fuel is not from the cylinder chamber 25 in the Fuel line 5 is promoted. Accordingly ensures a check valve 36 during the suction stroke for the Do not fuel from the common channel 10 in the Cylinder chamber 25 is sucked.
- the directional control valve 12 has a cylindrical shape Body 41 with a trumpet-shaped closure element 44. Openings 42, 43 are provided in the cylindrical body 41 intended. In the position shown in Figure 3 Directional control valve 12 can fuel from the common Channel 10 through openings 42, 43 in valve body 41 get into a channel 11. In channel 11 is a Check valve 13 attached.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Die Erfindung betrifft eine Hochdruckpumpe nach dem
Oberbegriff des Anspruchs 1.The invention relates to a high pressure pump according to the
Preamble of
Bei herkömmlichen Kraftstoffeinspritzsystemen der vorab geschilderten Art wird normalerweise unabhängig vom Bedarf ein konstanter Kraftstoffstrom 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 Kraftstoffstrom 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 Kraftstoffmenge wieder aus der Hochdruckpumpe abgesteuert werden, was zu Temperaturerhöhungen des Kraftstoffs führt.With conventional fuel injection systems, the advance described type is usually independent of need a constant fuel flow through the pre-feed pump in Individual elements of the high pressure pump are promoted. The individual elements of the high pressure pump can, for example be several cylinders, each with a piston back and forth is moved to suck in the fuel and with To apply high pressure. If regardless of need constant speed-dependent fuel flow from the High pressure pump pumped into the common manifold , it means that the power consumption of the High pressure pump is constant even when demand drops. The affects the overall efficiency of the Internal combustion engine. Furthermore, the excess, fuel quantity compressed to high pressure again from the High pressure pump can be shut down, too Temperature increases in the fuel leads.
Zur Verbesserung des Gesamtwirkungsgrads der Brennkraftmaschine ist vorgeschlagen worden, eine geregelte, elektrische Niederdruckförderpumpe zu verwenden, um den Kraftstoffstrom 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 has been proposed to use regulated, electric low pressure feed pump, to the fuel flow to the individual elements of the Control high pressure pump. This solution has among other things however, the disadvantage that the suction stroke of the High pressure pump for damage due to cavitation can come.
Aus der US 5,626,114 ist eine Radialkolben-Hochdruckpumpe bei denen eine hochdruckseitige Druckregelung für alle Pumpenelemente durch ein Druckregelventil einer Ventil-Einheit vorgenommen wird. Diese Ventil-Einheit besteht aus einem 2/2-Wegeventil mit einer vorgeschalteten Drossel und einem parallel dazu angeordneten Druckregelventil. Hochdruckseitig ist diese Ventileinheit an der Verteilerleiste (common-rail) und einer Bypassleitung der Verteilerleiste angeschlossen. Niederdruckseitig ist die Ventil-einheit mit einer drucklosen Rücklaufleitung verbunden.From US 5,626,114 is a radial piston high pressure pump where a high pressure side pressure control for everyone Pump elements through a pressure control valve of a valve unit is made. This valve unit consists of a 2/2-way valve with an upstream throttle and a pressure control valve arranged in parallel. This valve unit is on the high pressure side Distribution rail (common rail) and a bypass line of Distribution board connected. The low pressure side is the Valve unit with an unpressurized return line connected.
Das 2/2-Wegeventil wird beim Start der Brennkraftmaschine geöffnet, damit der Hochdruckbereich des Kraftstoffeinspritzsystems mit dem Druck der Vorförderpumpe beaufschlagt wird. Sobald die Brennkraftmaschine läuft, wird das 2/2-Wegeventil geschlossen. In geschlossenem Zustand des 2/2-Wegeventils übernimmt das parallel geschaltete Druckregelventil die Druckregelung der Verteilerleiste. Dies bedeutet, dass die Hochdruckumpe immer gegen den in der Verteilerleiste herrschenden Hochdruck fördert, was die zuvor genannten Nachteile hinsichtlich Gesamtwirkungsgrad und Kraftstofferhitzung hat.The 2/2-way valve is at the start of the engine opened so that the high pressure area of the Fuel injection system with the pressure of the pre-feed pump is applied. As soon as the internal combustion engine is running, the 2/2-way valve is closed. In closed The state of the 2/2-way valve takes over in parallel switched pressure control valve the pressure control of the Rail. This means that the high pressure pump always against the one prevailing in the distribution strip High pressure promotes what the aforementioned disadvantages in terms of overall efficiency and fuel heating Has.
Aus der EP 0 459 429 A1 ist eine Hochdruckpumpe mit einem Pumpenelement bekannt bei der zwischen Hochdruckseite und Niederdruckseite des Pumpenelements ein Stromventil vorgesehen ist. Dieses Stromventil wird so angesteuert, dass die gewünschte Fördermenge zur Hochdruckseite gefördert wird. Der überschüssige Kraftstoff wird über die Niederdruckseite in den Kraftstofftank zurückgeführt. Nachteilig an dieser Fördermengenregelung ist, dass für jedes Pumpenelement ein Stromventil benötigt wird, und dass der überschüssige Kraftstoff in dem Pumpenelement zuerst unter Druck gesetzt und anschließend in dem Stromventil entspannt wird. Das führt zu einer unerwünschten Erwärmung des Kraftstoffs und verschlechtert den Nutzungsgrad der Hochdruckpumpe.EP 0 459 429 A1 describes a high-pressure pump with a Pump element known between the high pressure side and Low pressure side of the pump element a flow valve is provided. This flow valve is controlled so that the desired flow rate to the high pressure side is promoted. The excess fuel is over the Low pressure side returned to the fuel tank. The disadvantage of this flow rate regulation is that for each pump element requires a flow valve, and that the excess fuel in the pump element first pressurized and then in the flow valve is relaxed. This leads to undesirable warming of the fuel and deteriorates the efficiency of the High pressure pump.
Außerdem ist in der EP 0 481 964 A2 eine Hochdruckpumpe mit einem Pumpenelement vorgeschlagen worden, bei der die Befüllung des Pumpenelements und damit auch dessen Fördermenge durch ein 2/2-Wege-Magnetventil gesteuert wird. Das 2/2-Wegeventil kann die hydraulische Verbindung zwischen der Niederdruckseite der Hochdruckpumpe und dem Pumpenelement freigeben oder verschließen und dadurch die Fördermenge der Hochdruckpumpe einstellen. Diese Fördermengenregelung ist nur auf Hochdruckpumpen mit mehreren Pumpenelementen übertragbar, wenn für jedes Pumpenelement ein 2/2-Wegeventil vorgesehen wird. Dadurch steigen die Kosten für die Fördermengenregelung mit der Zahl der Pumpenelemente stark an.A high pressure pump is also included in EP 0 481 964 A2 a pump element has been proposed in which the Filling the pump element and thus also its Flow rate is controlled by a 2/2-way solenoid valve. The 2/2-way valve can do the hydraulic connection between the low pressure side of the high pressure pump and the Release or close the pump element and thereby the Set the delivery rate of the high pressure pump. This Flow control is only possible on high pressure pumps transferable to several pump elements, if for each Pump element a 2/2-way valve is provided. Thereby the costs for the flow rate regulation increase with the Number of pump elements strongly.
Der Erfindung liegt daher das Problem zugrunde, eine Hochdruckpumpe bereitzustellen, welche die vorstehend genannten Nachteile überwindet. Insbesondere sollen Beschädigungen der einzelnen 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 Provide high pressure pump which the above overcomes disadvantages mentioned. In particular, should Damage to the individual elements of the high pressure pump in the Operation can be avoided. In addition, one should be simple built high pressure pump can be created, the high Security requirements met and still inexpensive can be manufactured.
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 those in the independent Disclosed claim high pressure pump solved. Special Embodiments of the invention are in the subclaims disclosed.
Das erfindungsgemäß angeordnete Wegeventil erlaubt die Fördermengenregelung einer Hochdruckpumpe mit mehreren Pumpenelementen durch ein Wegeventil. Dadurch werden Kosten bei der Herstellung der Hochdruckpumpe eingespart. Zudem wird der Bauraum der Hochdruckpumpe in vorteilhafter Weise begrenzt.The directional valve arranged according to the invention allows the Flow control of a high pressure pump with several Pump elements through a directional valve. This will cost saved in the manufacture of the high pressure pump. moreover the space of the high pressure pump is advantageous limited.
Damit ist es auch möglich, durch eine geeignete Regelstrategie den Druck in der gemeinsamen Verteilerleiste auf einen erwünschten Sollwert zu regeln. Die Hochdruckpumpe dient dabei als Steller im Druckregelkreis.It is also possible with a suitable Control strategy the pressure in the common manifold to regulate to a desired setpoint. The The high pressure pump serves as an actuator in the pressure control loop.
Außerdem trägt die erfindungsgemäße Fördermengenregelung zur Verbesserung des Motorgesamtwirkungsgrads bei, weil die Leistungsaufnahme der Hochdruckpumpe dadurch sinkt. Die erfindungsgemäße Bedarfsmengensteuerung des von der Hochdruckpumpe geförderten Kraftstoffstroms liefert darüber hinaus den Vorteil, daß eine nur teilweise Befüllung der einzelnen Pumpenelemente der Hochdruckpumpe, wie sie bei der Saugmengeregelung auftritt, vermieden wird. Dadurch wird die Kavitationsgefahr verringert. The delivery rate control according to the invention also bears to improve overall engine efficiency because the The power consumption of the high-pressure pump drops as a result. The Demand quantity control according to the invention of the High-pressure pump-supplied fuel flow delivers about it furthermore the advantage that a partial filling of the individual pump elements of the high pressure pump, as in suction control occurs, is avoided. Thereby the risk of cavitation is reduced.
Die 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 Kraftstoffstrom kann entweder in den Kraftstofftank oder in die Verbindungsleitung zwischen der Vorförderpumpe und der Hochdruckpumpe zurückgeführt werden. Dadurch, daß der gesamte Kraftstoffstrom durch die Hochdruckpumpe gefördert wird, kann eine Aufteilung in einen Förderstrom und einen Schmierstrom im Niederdruckteil entfallen.The invention is characterized in that the directional valve is a 3/2-way valve which is installed in the common channel and the common channel in a first valve position with the common manifold and in a second Valve position with the low pressure part of the Fuel injection system connects. In the second Valve position, the fuel flow is depressurized again in the low pressure part of the fuel injection system without to be pressurized. The fuel flow can either be in the fuel tank or in the Connection line between the pre-feed pump and the High pressure pump can be returned. Because the total fuel flow conveyed through the high pressure pump can be divided into a flow and a Lubrication flow in the low pressure part is eliminated.
Eine 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. A special embodiment of the invention is characterized in that between the directional valve and the common check manifold arranged a check valve is. The common channel is in the first valve position connected to the common manifold. By the between the directional valve and the common manifold arranged check valve is achieved that the Fuel from the individual elements of the high pressure pump until the desired pressure is reached is. When the desired pressure is reached, that opens Check valve and the fuel flows into the common manifold. So the fuel will only then pressurized with high pressure in the high pressure pump if the directional control valve is in the first valve position.
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.Another special embodiment of the invention is characterized in that the directional valve is magnetic can be actuated. By the magnetic actuation of the Directional control valve can achieve short switching times.
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.Another special embodiment of the invention is characterized in that the high pressure pump a Radial piston pump is one in a pump housing mounted drive shaft, which is eccentric or has cam-like elevations in the circumferential direction, and preferably several radial with respect to the drive shaft comprises pistons arranged in a respective cylinder space, by rotating the drive shaft in each Cylinder space can be moved back and forth in the radial direction are. Such radial piston pumps are especially for Suitable for common rail injection systems. When going back and forth Moving the pistons first, Kaftstoff is sucked in and then condensed.
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 The basic idea of the present invention can also be found in simple way on conventional high pressure pumps be used because known components 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. Ein Weg zum Ausführen der beanspruchten Erfindung ist nachfolgend anhand der Zeichnungen im Einzelnen erläutert.
Figur 1- zeigt eine schematische Darstellung eines Kraftstoffeinspritzsystems mit einer Hochdruckpumpe und einem Wegeventil in einer ersten Ventilstellung;
Figur 2- zeigt eine schematische Darstellung des
Kraftstoffeinspritzsystems aus
Figur 1 mit dem Wegeventil in einer zweiten Ventilstellung; und Figur 3- zeigt eine Ausführungsform einer erfindungsgemäßen Hochdruckpumpe.
- Figure 1
- shows a schematic representation of a fuel injection system with a high pressure pump and a directional valve in a first valve position;
- Figure 2
- shows a schematic representation of the fuel injection system from Figure 1 with the directional control valve in a second valve position; and
- 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
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.In the
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.In Figure 2 is the same fuel injection system as in
Figure 1 shown. The only difference is that
the valve is in a different position. In the
Position of the
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 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.The high pressure pump shown in FIG. 3 is
a radial piston pump for high-pressure fuel supply
in fuel injection systems of internal combustion engines.
The radial piston pump comprises one in a
Wenn die Antriebswelle 21 in Drehung versetzt wird, bewirkt
die Exzentrizität des Wellenabschnitts 22, daß die Kolben
24 in den Zylinderräumen 25 hin- und herbewegt werden. Wenn
sich der Kolben 24 zu der Antriebswelle 21 hin bewegt, wird
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.When the
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
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
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
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 gelangt, 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 of the 3/2-way valve, not shown
is the
Claims (4)
- High-pressure pump for a fuel injection system of an internal combustion engine, in particular a common-rail fuel injection system, with a high-pressure pump (1) conveying fuel out of a low-pressure part of the fuel injection system, the said low-pressure part containing a fuel tank (3) and a prefeed pump (2), into a common distributor rail of the fuel injection system, an on-demand quantity control (12) for controlling the fuel stream conveyed by the high-pressure pump (1) being integrated into the high-pressure pump (1), the high-pressure pump having a plurality of pump elements (6, 7, 8), the plurality of pump elements (6, 7, 8) conveying fuel into a common duct (10), and the on-demand quantity control comprising a directional valve (12) which delivers the fuel stream conveyed by the high-pressure pump (1), on demand, either to the common distributor rail or to the low-pressure part of the fuel injection system, characterized in that the directional valve is a 3/2-way valve (12) which is mounted in the common duct (10) and which connects the common duct (10) to the common distributor rail in a first valve position and to the low-pressure part of the fuel injection system in a second valve position.
- High-pressure pump according to Claim 1, characterized in that a non-return valve (13) is arranged between the directional valve (12) and the common distributor rail.
- High pressure pump according to one of the preceding claims, characterized in that the directional valve (12) can be actuated magnetically.
- 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) mounted in a pump casing (20), is designed eccentrically or has cam-like elevations in the cirumferential direction, and comprises preferably a plurality of pistons (24) which are arranged in a respective cylinder space (25) radially in relation to the drive shaft (21) and which can be moved back and forth in the radial direction in the respective cylinder space (25) as a result of the rotation of the drive shaft (21).
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 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0960275A1 EP0960275A1 (en) | 1999-12-01 |
EP0960275B1 true EP0960275B1 (en) | 2004-08-11 |
Family
ID=7852239
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98966148A Expired - Lifetime EP0960275B1 (en) | 1997-12-17 | 1998-11-17 | High pressure pump for supplying fuel in fuel injection systems of internal combustion engines |
Country Status (5)
Country | Link |
---|---|
US (1) | US6186120B1 (en) |
EP (1) | EP0960275B1 (en) |
JP (1) | JP2001511869A (en) |
DE (2) | DE19756087A1 (en) |
WO (1) | WO1999031383A1 (en) |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19848040A1 (en) * | 1998-10-17 | 2000-04-20 | Bosch Gmbh Robert | Radial piston pump for high fuel pressure in IC engines with common-rail injection systems has two plates engaging fully on each other, and second back pressure valve between first plate and pump housing |
DE19916376A1 (en) * | 1999-04-12 | 2000-10-19 | Mannesmann Rexroth Ag | Pump housing |
DE19951410A1 (en) * | 1999-10-26 | 2001-05-10 | Bosch Gmbh Robert | Method and device for varying a pre-pressure generated by a low-pressure pump and applied to a high-pressure pump |
DE19959202C2 (en) * | 1999-12-08 | 2002-01-10 | Hans Schuetz | Overpressure shut-off valve for high pressure piston pumps |
JP2001207927A (en) * | 2000-01-26 | 2001-08-03 | Mitsubishi Electric Corp | Fuel supply device |
JP2001221118A (en) * | 2000-02-07 | 2001-08-17 | Bosch Automotive Systems Corp | Fuel injection device |
DE10023033A1 (en) * | 2000-05-11 | 2001-11-22 | Bosch Gmbh Robert | Operation of fuel metering system of direct injection engine, places all high pressure pumps in fuel circuit, with common pressure control system |
DE10144669C1 (en) * | 2001-09-11 | 2003-04-17 | Siemens Ag | Fuel pressure control method for high pressure fuel injection for IC engine supplies fuel quantity corresponding to required fuel pressure to common-rail of fuel injection system |
DE10157375A1 (en) | 2001-11-22 | 2003-06-05 | Daimler Chrysler Ag | high pressure pump |
DE10213626A1 (en) * | 2002-03-27 | 2003-10-23 | Bosch Gmbh Robert | High-pressure fuel pump for a fuel system of an internal combustion engine |
DE10229396A1 (en) * | 2002-06-29 | 2004-01-22 | Robert Bosch Gmbh | Radial piston pump for high-pressure fuel supply in injection systems of internal combustion engines with improved efficiency |
WO2006006495A1 (en) * | 2004-07-12 | 2006-01-19 | Yanmar Co., Ltd. | Accumulator fuel injection device and internal combustion engine with the accumulator fuel injection device |
US20080078362A1 (en) * | 2006-09-29 | 2008-04-03 | Caterpillar Inc. | Variable discharge pump having single control valve |
IT1394070B1 (en) * | 2009-05-13 | 2012-05-25 | Bosch Gmbh Robert | VALVE ASSEMBLY FOR CHECKING THE SUPPLY AND FUEL FLOW OF A COMPRESSION CHAMBER OF A HIGH PRESSURE PISTON PUMP AND HIGH PRESSURE PISTON PUMP INCLUDING SUCH VALVE GROUP |
IT1397725B1 (en) * | 2009-12-22 | 2013-01-24 | Bosch Gmbh Robert | FUEL SUPPLY SYSTEM FROM A TANK TO AN INTERNAL COMBUSTION ENGINE. |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0889233A2 (en) * | 1993-05-06 | 1999-01-07 | Cummins Engine Company, Inc. | Compact high performance fuel system with accumulator |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4838232A (en) * | 1984-08-14 | 1989-06-13 | Ail Corporation | Fuel delivery control system |
US5058553A (en) * | 1988-11-24 | 1991-10-22 | Nippondenso Co., Ltd. | Variable-discharge high pressure pump |
JP2869464B2 (en) * | 1989-05-30 | 1999-03-10 | 富士重工業株式会社 | Fuel injection control device for two-cycle engine |
JP2712760B2 (en) * | 1990-05-29 | 1998-02-16 | トヨタ自動車株式会社 | Fuel injection valve |
JPH08158971A (en) * | 1994-12-07 | 1996-06-18 | Zexel Corp | Fuel pump for high pressure fuel injection device |
IT1281303B1 (en) * | 1995-03-28 | 1998-02-17 | Elasis Sistema Ricerca Fiat | DEVICE FOR REGULATING THE SUPPLY PRESSURE OF A FLUID IN A PRESSURE FLUID ACCUMULATOR, FOR EXAMPLE FOR |
JPH08338335A (en) * | 1995-06-09 | 1996-12-24 | Nippondenso Co Ltd | Fuel feeding device for internal combustion engine |
JP3594144B2 (en) * | 1995-08-30 | 2004-11-24 | 株式会社デンソー | Fuel supply device |
DE19549108A1 (en) * | 1995-12-29 | 1997-07-03 | Bosch Gmbh Robert | High-pressure fuel generation system for a fuel injection system used in internal combustion engines |
JPH09195926A (en) * | 1996-01-17 | 1997-07-29 | Unisia Jecs Corp | Radial plunger pump |
DE19744723A1 (en) * | 1997-10-10 | 1999-04-15 | Bosch Gmbh Robert | Fuel injector |
-
1997
- 1997-12-17 DE DE19756087A patent/DE19756087A1/en not_active Ceased
-
1998
- 1998-11-17 WO PCT/DE1998/003379 patent/WO1999031383A1/en active IP Right Grant
- 1998-11-17 JP JP53187199A patent/JP2001511869A/en not_active Withdrawn
- 1998-11-17 EP EP98966148A patent/EP0960275B1/en not_active Expired - Lifetime
- 1998-11-17 DE DE59811797T patent/DE59811797D1/en not_active Expired - Lifetime
- 1998-11-17 US US09/355,502 patent/US6186120B1/en not_active Expired - Fee Related
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0889233A2 (en) * | 1993-05-06 | 1999-01-07 | Cummins Engine Company, Inc. | Compact high performance fuel system with accumulator |
Also Published As
Publication number | Publication date |
---|---|
JP2001511869A (en) | 2001-08-14 |
US6186120B1 (en) | 2001-02-13 |
WO1999031383A1 (en) | 1999-06-24 |
DE19756087A1 (en) | 1999-06-24 |
DE59811797D1 (en) | 2004-09-16 |
EP0960275A1 (en) | 1999-12-01 |
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