EP2596232B1 - Fuel delivery device - Google Patents

Fuel delivery device Download PDF

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Publication number
EP2596232B1
EP2596232B1 EP11726103.2A EP11726103A EP2596232B1 EP 2596232 B1 EP2596232 B1 EP 2596232B1 EP 11726103 A EP11726103 A EP 11726103A EP 2596232 B1 EP2596232 B1 EP 2596232B1
Authority
EP
European Patent Office
Prior art keywords
pressure
fuel
pump
delivery device
fuel delivery
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP11726103.2A
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German (de)
French (fr)
Other versions
EP2596232A1 (en
Inventor
Jost Krauss
Guenter Veit
Andreas Sommerer
Steffen Meyer-Salfeld
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP2596232A1 publication Critical patent/EP2596232A1/en
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Publication of EP2596232B1 publication Critical patent/EP2596232B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/02—Pumps peculiar thereto
    • 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
    • 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
    • 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
    • F02M59/22—Varying quantity or timing by adjusting cylinder-head space
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/023—Means for varying pressure in common rails
    • F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
    • F02M63/025—Means for varying pressure in common rails by bleeding fuel pressure from the common rail
    • 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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/46—Details, component parts or accessories not provided for in, or of interest apart from, the apparatus covered by groups F02M69/02 - F02M69/44
    • F02M69/54—Arrangement of fuel pressure regulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members

Definitions

  • the feed pump 10 can be arranged on the high-pressure pump 16, integrated into it or arranged remotely from the high-pressure pump 16, for example in the reservoir 12 or in a hydraulic line between the reservoir 12 and the high-pressure pump 16.
  • the high-pressure pump 16 has at least one pump element, which in turn has a pump piston which is driven in a lifting movement.
  • the high pressure pump 16 may have its own drive shaft through which the lifting movement of the pump piston is effected via a cam or eccentric.
  • the drive shaft of the high pressure pump 16 is mechanically driven, for example via a transmission or a belt drive from the internal combustion engine, so that the speed of the high-pressure pump 16 is proportional to the speed of the internal combustion engine.
  • the feed pump 10 can be arranged remotely from the at least one high-pressure pump 16, for example also in the storage container 12.
  • the feed pump 10 is connected via a hydraulic line 6 to the suction side of the at least one high-pressure pump 16.
  • a fuel filter 38 can be arranged in the hydraulic line in order to prevent dirt particles from entering the high-pressure pump 16 and the high-pressure region 18.
  • a pressure regulating valve 22 can be provided, by which the pressure prevailing in the high-pressure region 18 is controlled. If an excessively high pressure is present in the high-pressure region 18, excess fuel can reach the reservoir 12 via the hydraulic line 2 in the return line 8 via the pressure regulating valve 22. Thus, in the high-pressure region 18, a required pressure can be set depending on operating parameters of the internal combustion engine.
  • FIG. 2 is exemplified a pump with adjustable displacement volume in a schematic sectional view of a fuel delivery device. It has a housing 40 in which a rotor 42 with at least one or more vanes 44 is located. The rotor 42 rotates about an axis that passes perpendicular to the blade through a center M1.
  • a circular stator ring 46 is clamped by a first actuating piston 48 and a second actuating piston 50.
  • the two adjusting pistons are arranged opposite each other. There may be another bearing point of the stator ring 46 by a height adjustment screw, not shown.
  • the axis of the circular stator ring 46 passes through a center M2.
  • the back of the first actuating piston 48 is acted upon via a hydraulic line 26 with a control pressure.
  • the control pressure is in the described embodiment by a Krafftstoff Kunststoff horr within the fuel delivery to the Provided.
  • the second actuating piston 50 counteracts the first actuating piston 48 and is held by a spring 52 in a certain position. Due to the control pressure and the spring force, two forces act in opposite directions on the stator ring 46.
  • stator 46 is displaced in the housing. If both forces are equal, the stator ring is in the middle position and the two center points M1 and M2 lie on one another. In this case, the flow rate of the fuel is returned to a zero flow rate, i. the flow rate is zero.
  • the feed pump 10 can be operated at the same speed or variable speed via a mechanical or electric drive.
  • the speed of the feed pump 10 influences the amount of fuel delivered.
  • the control pressure can be promoted a variable amount of fuel at the same speed.
  • a delivery pump 10 with adjustable delivery volume is the "adjustable vane pump, type PV7" from Bosch Rexroth, which is similar in construction to the described delivery pump 10, but would have to be adapted to the dimensions and requirements of a fuel delivery device.
  • an external gear pump or a roller-cell pump or an internal gear pump or a pendulum slide pump can also be used as the delivery pump 10 with adjustable delivery volume.
  • An example of a volume-adjustable pendulum slide pump is in the published patent application DE 101 02 531 A1 shown.
  • control pressure acts on the first actuating piston 48 and thus influences the displacement volume of the feed pump 10.
  • a pressure-side fuel filter 38 is provided, alternatively the pressure on the Suction side of the high pressure pump 16 between the fuel filter 38 and high pressure pump 16 serve as a control pressure.
  • the fuel in the return line 8 to the reservoir 12 are controlled by the pressure control valve 22 in the high pressure region 18.
  • the pressure control valve 22 may be located directly on the high pressure accumulator 18 or on the high pressure pump 16 or between the high pressure pump 16 and high pressure accumulator 18.
  • the pressure control valve 22 is regulated by an electrical control unit. If there is a higher pressure than required in the high-pressure region 18, excess fuel is deactivated with the aid of the pressure regulating valve 22.
  • the pressure in the return 8 increases depending on the amount of fuel being removed. The increased fuel return increases the pressure in the Return 8 upstream of the throttle 24 and the control pressure on the first actuating piston 48 increases. The displacement volume of the feed pump 10 is reduced and thus reduces the flow rate of the fuel. If only little fuel is diverted from the pressure control valve 22 into the return 8, the control pressure drops and the delivery pump 10 increases the delivery rate of the fuel.
  • FIG. 4 shows a further embodiment of the invention.
  • the pressure in the high pressure region 18 acts directly on the first control piston 48 of the feed pump 10 and thus affects the displacement of the feed pump 10 prevails in the high-pressure accumulator 18 too high a pressure, the Fuel delivery of the feed pump 10 is reduced, the pressure in the high pressure accumulator 18 is too low, the fuel delivery of the feed pump 10 is increased, otherwise it remains constant.
  • the rear side of the second actuating piston 50 can be subjected to a control pressure for the controlled influencing of the displacement volume.
  • a force which is composed of the force of the spring 52 and the control pressure acts on the second actuating piston 50.
  • the control pressure acting on the second actuating piston 50 comes from any point of the fuel delivery device and should be lower than the control pressure, which acts on the back of the first actuating piston 48.
  • FIG. 5 shows a further embodiment of the invention.
  • the control pressure is controlled by a pressure control valve 15 which is connected to an electronic control device 19.
  • the electrical control device 19 is connected to a pressure sensor 17 in the high-pressure region 18, which supplies information about the pressure in the high-pressure region 18 to the electronic control device 19.
  • the electrical control device 19 controls the pressure control valve 15 and thus influenced by the control pressure, the delivery rate of the feed pump 10.
  • Unnecessary fuel is via a hydraulic line in the reservoir 12 deactivated.
  • the pressure control valve 15 is a continuous adjustment of the force on the second actuating piston 50 of the feed pump 10 is possible.
  • the delivery characteristic of the feed pump 10 changes and there are different displacement volumes of the feed pump 10 at the same control pressure.

Landscapes

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

Description

Die Erfindung betrifft eine Kraftstofffördereinrichtung für eine Kraftstoffeinspritzung einer Brennkraftmaschine nach dem Oberbegriff des unabhängigen Anspruches.The invention relates to a fuel delivery device for a fuel injection of an internal combustion engine according to the preamble of the independent claim.

Stand der TechnikState of the art

Eine solche Kraftstofffördereinrichtung und ihre Funktionsweise ist bereits durch die Schriftreihe Diesel-Speichereinspritzsystem Common-Rail (ISBN-978-3-86522-010-3) der Robert Bosch GmbH oder EP 1195 514 A2 bekannt. Diese Kraftstofffördereinrichtung weist eine elektrisch angetriebene Förderpumpe auf, durch die Kraftstoff zur Saugseite einer Hochdruckpumpe gefördert wird. Durch die Hochdruckpumpe wird Kraftstoff in einen Hochdruckbereich gefördert, aus dem zumindest mittelbar wenigstens ein Injektor der Kraftstoffeinspritzeinrichtung mit Kraftstoff versorgt wird. Es ist eine elektrische Steuereinrichtung vorgesehen, die über eine Sensoreinrichtung ein Signal für den im Hochdruckbereich herrschenden Druck erhält. Durch die elektrische Steuereinrichtung wird der elektrische Antrieb der Förderpumpe variabel angesteuert, so dass die Kraftstofffördermenge der Förderpumpe durch Variation der Drehzahl verändert werden kann. Dadurch ist eine an die Betriebsbedingungen angepasste Kraftstofffördermenge der Förderpumpe möglich, die jedoch einen hohen Antriebsleistungsbedarf hat und elektrische Steuer- und Sensoreinrichtungen benötigt.Such a fuel delivery device and its operation is already by the Series Diesel common rail injection system (ISBN-978-3-86522-010-3) of the Robert Bosch GmbH or EP 1195 514 A2 known. This fuel delivery device has an electrically driven delivery pump through which fuel is conveyed to the suction side of a high-pressure pump. The high-pressure pump delivers fuel into a high-pressure region, from which at least indirectly at least one injector of the fuel injection device is supplied with fuel. An electrical control device is provided which receives a signal for the pressure prevailing in the high-pressure region via a sensor device. By the electrical control device, the electric drive of the feed pump is variably controlled, so that the fuel delivery amount of the feed pump can be changed by varying the speed. As a result, adapted to the operating conditions fuel delivery of the feed pump is possible, however, has a high drive power demand and electrical control and sensor devices needed.

DE 196 18 932 A1 offenbart eine mit verstellbarem Verdrängungsvolumen Niederdruckkraftstofffördereinrichtung, die Sensoreinrichtungen benötigt. DE 196 18 932 A1 discloses an adjustable displacement low pressure fuel delivery system that requires sensor devices.

Offenbarung der ErfindungDisclosure of the invention

Die erfindungsgemäße Kraftstofffördereinrichtung mit den kennzeichnenden Merkmalen des Anspruchs 1 hat den Vorteil, dass die Förderpumpe ein verstellbares Verdrängungsvolumen hat, wodurch eine variable Kraftstoffmenge bei gleicher Drehzahl der Förderpumpe gefördert werden kann. Durch die Möglichkeit die Kraftstofffördermenge bei gleicher Drehzahl zu variieren, kann die Regelung der Kraftstofffördermenge über den elektrischen Antrieb und die Steuer- und Sensoreinrichtungen entfallen, wodurch Kosten eingespart werden können. Die Förderpumpe kann entweder mechanisch oder elektrisch angetrieben werden und ihre Kraftstofffördermenge bei gleicher Drehzahl variieren.The fuel delivery device according to the invention with the characterizing features of claim 1 has the advantage that the feed pump has an adjustable displacement volume, whereby a variable amount of fuel at the same speed of the feed pump can be promoted. The ability to vary the fuel delivery at the same speed, the regulation of the fuel flow rate via the electric drive and the control and sensor devices can be omitted, which costs can be saved. The feed pump can be driven either mechanically or electrically and vary their fuel delivery at the same speed.

Mit den Maßnahmen der Unteransprüche sind vorteilhafte Weiterbildungen und Verbesserungen der Erfindung möglich.With the measures of the dependent claims advantageous refinements and improvements of the invention are possible.

In einer ersten vorteilhaften Ausführungsform der Kraftstofffördereinrichtung fördert die Förderpumpe eine variable Kraftstoffmenge, die zwischen einer Nullfördermenge und einer maximalen Menge variiert. Die maximale Menge wird durch das maximale Verdrängungsvolumen der Förderpumpe bestimmt. Durch den weiten Bereich, in dem die Kraftstofffördermenge variieren kann, ist eine optimale Anpassung der Kraftstofffördermenge an den Kraftstoffbedarf im Hochdruckbereich möglich. Es entfallen zusätzliche Bauteile, wie z.B. der elektrische Antrieb der Förderpumpe, eine elektrische Steuereinrichtung zur Regelung des elektrischen Antriebs oder eine Zumesseinheit (ZME), die die Kraftstofffördermenge an den Bedarf der Hochdruckpumpe anpasst.In a first advantageous embodiment of the fuel delivery device, the delivery pump delivers a variable amount of fuel that varies between a zero delivery amount and a maximum amount. The maximum amount is determined by the maximum displacement of the feed pump. Due to the wide range in which the fuel delivery rate can vary, an optimal adjustment of the fuel delivery to the fuel demand in the high pressure range is possible. It eliminates additional components, such. the electric drive of the feed pump, an electrical control device for controlling the electric drive or a metering unit (ZME), which adapts the fuel delivery to the needs of the high pressure pump.

Erfindungsgemäß wird das verstellbare Verdrängungsvolumen über einen Steuerdruck, welcher über eine hydraulische Leitung auf einen Stellkolben der Förderpumpe wirkt, geregelt. Es müssen keine weiteren externen Steuereinrichtungen hinzugezogen werden, um die Kraftstofffördermenge der Förderpumpe an den Bedarf im Hochdruckbereich anzupassen. Des Weiteren entfallen Sensoreinheiten zur Druckerfassung, da der Druck nicht bestimmt werden muss, sondern direkt die Fördermenge beeinflusst. Dies reduziert den Kostenaufwand und vereinfacht den Aufbau des Niederdruckkreislaufes.According to the invention, the adjustable displacement volume is controlled via a control pressure, which acts on a control piston of the feed pump via a hydraulic line. There are no additional external control devices are required to adjust the fuel delivery of the feed pump to the needs in the high pressure area. Furthermore, there is no need for sensor units for pressure detection, since the pressure does not have to be determined, but directly affects the flow rate. This reduces the cost and simplifies the construction of the low pressure circuit.

In einer weiteren vorteilhaften Weiterbildung ist der Steuerdruck der Kraftstoffdruck auf der Druckseite der Förderpumpe. In diesem Fall passt sich die Förderpumpe optimal an den Kraftstoffbedarf im Hochdruckbereich an. Es müssen keine weiteren Bauteile, wie Überströmventil und Zumesseinheit eingesetzt werden. Da von der Förderpumpe immer die von der Hochdruckpumpe benötigte Kraftstoffmenge gefördert wird und zuviel geförderter Kraftstoff nicht abgesteuert werden muss, verringert sich der Kraftstoffverbrauch.In a further advantageous development, the control pressure is the fuel pressure on the pressure side of the feed pump. In this case, the delivery pump adapts optimally to the fuel demand in the high-pressure range. There are no other components, such as overflow valve and metering unit can be used. Since of the feed pump always required by the high pressure pump fuel is promoted and too much subsidized fuel does not have to be diverted, the fuel consumption is reduced.

Ein besonderer Vorteil ergibt sich, wenn der Steuerdruck der Kraftstoffdruck zwischen einem druckseitig verbauten Kraftstofffilter und der Saugseite der Hochdruckpumpe ist. Die Förderpumpe stellt unabhängig vom Druckverlust des Kraftstofffilters den Druck auf der Saugseite der Hochdruckpumpe ein. Einflussgrößen wie der Beladungszustand des Kraftstofffilters oder temperaturbedingte Versulzung des Kraftstofffilters werden kompensiert.A particular advantage is obtained when the control pressure is the fuel pressure between a fuel filter installed on the pressure side and the suction side of the high-pressure pump. The feed pump adjusts the pressure on the suction side of the high-pressure pump, regardless of the pressure loss of the fuel filter. Influencing factors such as the load condition of the fuel filter or temperature-related volatilization of the fuel filter are compensated.

Ein weiterer Vorteil ergibt sich, wenn der Steuerdruck der Kraftstoffdruck im Rücklauf zum Vorratsbehälter ist. Auch bei dieser Lösung reduziert sich der Einsatz weiterer Bauteile, da auf die Zumesseinheit verzichtet werden kann. Es dient der zuviel geförderte Kraftstoff als Steuerdruck, so dass eine andere Auslegung der Stellglieder der Förderpumpe möglich ist.Another advantage arises when the control pressure is the fuel pressure in the return to the reservoir. Also in this solution, the use of other components, since it can be dispensed with the metering unit. It serves too much subsidized fuel as a control pressure, so that a different interpretation of the actuators of the feed pump is possible.

Je nach Auslegung wird der Kraftstoff in den Rücklauf zum Vorratsbehälter von einem Überströmventil auf der Saugseite der Hochdruckpumpe abgesteuert oder der Kraftstoff in den Rücklauf zum Vorratsbehälter wird von einem Druckregelventil im Hochdruckbereich abgesteuert.Depending on the design of the fuel in the return to the reservoir is controlled by an overflow valve on the suction side of the high pressure pump or the fuel in the return to the reservoir is controlled by a pressure control valve in the high pressure area.

Ein besonderer Vorteil ergibt sich, wenn der Steuerdruck der Kraftstoffdruck im Hochdruckspeicher ist. Dadurch ergibt sich ein Regelkreis, der den Druck im Hochdruckspeicher ohne elektrische Istwerterfassung, elektrische Signalverarbeitung und elektrische Steller einregelt. Des Weiteren ist der Entfall des Druckregelventils am Hochdruckspeicher möglich.A particular advantage arises when the control pressure is the fuel pressure in the high-pressure accumulator. This results in a control loop that regulates the pressure in the high-pressure accumulator without electrical actual value detection, electrical signal processing and electrical adjuster. Furthermore, the elimination of the pressure control valve on the high-pressure accumulator is possible.

Ein weiterer Vorteil ergibt sich, wenn das verstellbare Verdrängungsvolumen über einen Regeldruck geregelt wird. Der Regeldruck wird über eine elektrische Steuereinrichtung und ein Druckregelventil verändert. Damit eröffnet sich die Möglichkeit die Fördercharakteristik zu verändern und damit die Kraftstofffördermenge der Förderpumpe kontrolliert zu beeinflussen. Je nach Motorbetriebspunkt oder abhängig vom Druck im Hochdruckspeicher kann die Einstellung des Regeldruckes zum Verändern des Verdrängungsvolumens verändert werden. Vorteilhaft ist der Einsatz einer Flügelzellenpumpe oder eine Außenzahnradpumpe oder eine Rollenzellenpumpe oder eine Innenzahnradpumpe oder eine Pendelschieberpumpe als Förderpumpe mit verstellbaren Fördervolumen, da auf bekannte Pumpenbauarten zurückgegriffen werden kann und sich der Entwicklungsaufwand reduziert.Another advantage arises when the adjustable displacement volume is regulated via a control pressure. The control pressure is changed via an electrical control device and a pressure control valve. This opens up the possibility to change the delivery characteristics and thus to control the fuel delivery of the pump controlled. Depending on the engine operating point or depending on the pressure in the high-pressure accumulator, the setting of the control pressure for changing the displacement volume can be changed. Advantageously, the use of a vane pump or an external gear pump or a roller-cell pump or an internal gear pump or a pendulum slide pump as a pump with adjustable displacement, as can be used on known pump types and reduces the development effort.

Ausführungsbeispieleembodiments

Bevorzugte Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.Preferred embodiments of the invention are illustrated in the drawing and explained in more detail in the following description.

Es zeigen:

  • Figur 1 eine Kraftstofffördereinrichtung in einer schematischen Darstellung entsprechend einem ersten Ausführungsbeispiel der Erfindung;
  • Figur 2 eine Pumpe mit verstellbaren Verdrängungsvolumen in einer schematischen Schnittdarstellung für eine Kraftstofffördereinrichtung;
  • Figur 3 eine Kraftstofffördereinrichtung in einer schematischen Darstellung entsprechend einem zweiten Ausführungsbeispiel der Erfindung;
  • Figur 4 eine Kraftstofffördereinrichtung in einer schematischen Darstellung entsprechend einem dritten Ausführungsbeispiel der Erfindung;
  • Figur 5 eine Kraftstofffördereinrichtung in einer schematischen Darstellung entsprechend einem vierten Ausführungsbeispiel der Erfindung.
Show it:
  • FIG. 1 a fuel delivery device in a schematic representation according to a first embodiment of the invention;
  • FIG. 2 a pump with adjustable displacement volume in a schematic sectional view of a fuel delivery device;
  • FIG. 3 a fuel delivery device in a schematic representation according to a second embodiment of the invention;
  • FIG. 4 a fuel delivery device in a schematic representation according to a third embodiment of the invention;
  • FIG. 5 a fuel delivery device in a schematic representation according to a fourth embodiment of the invention.

Figur 1 zeigt eine Kraftstofffördereinrichtung in einer schematischen Darstellung entsprechend einem ersten Ausführungsbeispiel der Erfindung. Die Kraftstofffördereinrichtung weist eine Förderpumpe 10 auf, die Kraftstoff aus einem Vorratsbehälter 12 ansaugt. Durch die Förderpumpe 10 wird Kraftstoff zur Saugseite wenigstens einer Hochdruckpumpe 16 gefördert, die ebenfalls Bestandteil der Kraftstofffördereinrichtung ist. Der Antrieb der Förderpumpe 10 kann mechanisch über Kupplung, Zahnrad oder Zahnriemen durch den Motor oder die Hochdruckpumpe erfolgen. Alternativ kann die Förderpumpe 10 einen elektrischen Antrieb aufweisen, der mit veränderlicher Leistung und damit variabler Drehzahl oder konstanter Leistung und Drehzahl betrieben werden kann. FIG. 1 shows a fuel delivery device in a schematic representation according to a first embodiment of the invention. The fuel delivery device has a feed pump 10, which draws fuel from a reservoir 12. By the feed pump 10, fuel is conveyed to the suction side of at least one high pressure pump 16, which is also part of the fuel delivery device. The drive of the feed pump 10 can be mechanical via the clutch, toothed belt or toothed belt by the motor or the high-pressure pump. Alternatively, the feed pump 10 may have an electric drive, which can be operated with variable power and thus variable speed or constant power and speed.

Durch die wenigstens eine Hochdruckpumpe 16 wird Kraftstoff in einen Hochdruckbereich 18 der Kraftstofffördereinrichtung gefördert, der beispielsweise einen Hochdruckspeicher 18 umfasst. Aus dem Hochdruckbereich 18 werden ein oder mehrere Injektoren 20 mit Kraftstoff versorgt, wobei jedem Zylinder der Brennkraftmaschine ein Injektor 20 zugeordnet ist.By means of the at least one high-pressure pump 16, fuel is conveyed into a high-pressure region 18 of the fuel delivery device, which comprises, for example, a high-pressure accumulator 18. One or more injectors 20 are supplied with fuel from the high-pressure region 18, wherein an injector 20 is assigned to each cylinder of the internal combustion engine.

Die Förderpumpe 10 kann an der Hochdruckpumpe 16 angeordnet, in diese integriert sein oder entfernt von der Hochdruckpumpe 16 angeordnet sein, beispielsweise im Vorratsbehälter 12 oder in einer hydraulischen Leitung zwischen dem Vorratsbehälter 12 und der Hochdruckpumpe 16. Die Hochdruckpumpe 16 weist wenigstens ein Pumpenelement auf, das wiederum einen Pumpenkolben aufweist, der in einer Hubbewegung angetrieben wird. Die Hochdruckpumpe 16 kann eine eigene Antriebswelle aufweisen, durch die über einen Nocken oder Exzenter die Hubbewegung des Pumpenkolbens bewirkt wird. Die Antriebswelle der Hochdruckpumpe 16 wird mechanisch, beispielsweise über ein Getriebe oder einen Riementrieb von der Brennkraftmaschine angetrieben, so dass die Drehzahl der Hochdruckpumpe 16 proportional zur Drehzahl der Brennkraftmaschine ist. Alternativ kann auch vorgesehen sein, dass die Hochdruckpumpe 16 keine eigene Antriebswelle aufweist und die Hubbewegung des Pumpenkolbens durch einen Exzenter oder Nocken einer Welle der Brennkraftmaschine bewirkt wird. Dabei können auch mehrere Hochdruckpumpen 16 vorgesehen sein. Alternativ kann auch eine hydraulische Betätigung vorgesehen sein.The feed pump 10 can be arranged on the high-pressure pump 16, integrated into it or arranged remotely from the high-pressure pump 16, for example in the reservoir 12 or in a hydraulic line between the reservoir 12 and the high-pressure pump 16. The high-pressure pump 16 has at least one pump element, which in turn has a pump piston which is driven in a lifting movement. The high pressure pump 16 may have its own drive shaft through which the lifting movement of the pump piston is effected via a cam or eccentric. The drive shaft of the high pressure pump 16 is mechanically driven, for example via a transmission or a belt drive from the internal combustion engine, so that the speed of the high-pressure pump 16 is proportional to the speed of the internal combustion engine. Alternatively, it can also be provided that the high-pressure pump 16 does not have its own drive shaft and the lifting movement of the pump piston is effected by an eccentric or cam of a shaft of the internal combustion engine. In this case, several high-pressure pumps 16 may be provided. Alternatively, a hydraulic actuation may be provided.

Die Förderpumpe 10 kann entfernt von der wenigstens einen Hochdruckpumpe 16 angeordnet sein, beispielsweise auch im Vorratsbehälter 12. Die Förderpumpe 10 ist dabei über eine hydraulische Leitung 6 mit der Saugseite der wenigstens einen Hochdruckpumpe 16 verbunden. In der hydraulischen Leitung kann ein Kraftstofffilter 38 angeordnet sein, um zu verhindern, dass Schmutzpartikel in die Hochdruckpumpe 16 und in den Hochdruckbereich 18 gelangen.The feed pump 10 can be arranged remotely from the at least one high-pressure pump 16, for example also in the storage container 12. The feed pump 10 is connected via a hydraulic line 6 to the suction side of the at least one high-pressure pump 16. A fuel filter 38 can be arranged in the hydraulic line in order to prevent dirt particles from entering the high-pressure pump 16 and the high-pressure region 18.

Im Hochdruckbereich 18 kann ein Druckregelventil 22 vorgesehen sein, durch das der im Hochdruckbereich 18 herrschende Druck kontrolliert wird. Ist im Hochdruckbereich 18 ein zu hoher Druck vorhanden, so kann über das Druckregelventil 22 überschüssiger Kraftstoff über die hydraulische Leitung 2 in den Rücklauf 8 zum Vorratsbehälter 12 gelangen. Somit kann im Hochdruckbereich 18 ein erforderlicher Druck abhängig von Betriebsparametern der Brennkraftmaschine eingestellt werden.In the high-pressure region 18, a pressure regulating valve 22 can be provided, by which the pressure prevailing in the high-pressure region 18 is controlled. If an excessively high pressure is present in the high-pressure region 18, excess fuel can reach the reservoir 12 via the hydraulic line 2 in the return line 8 via the pressure regulating valve 22. Thus, in the high-pressure region 18, a required pressure can be set depending on operating parameters of the internal combustion engine.

Überschüssiger Kraftstoff aus dem Antriebsbereich der Hochdruckpumpe 16 kann über die hydraulische Leitung 28 zum Rücklauf 8 und damit zum Vorratsbehälter 12 geleitet werden. Wird mehr Kraftstoff als benötigt von der Förderpumpe 10 zur Saugseite der Hochdruckpumpe 16 gefördert, so kann überschüssiger Kraftstoff durch ein Überströmventil 34 an der Hochdruckpumpe 16 über die hydraulische Leitung 28 zum Rücklauf 8 und damit zum Vorratsbehälter 12 geleitet werden.Excess fuel from the drive range of the high-pressure pump 16 can be passed via the hydraulic line 28 to the return 8 and thus to the reservoir 12. If more fuel than required is conveyed from the feed pump 10 to the suction side of the high-pressure pump 16, excess fuel can be passed through an overflow valve 34 on the high-pressure pump 16 via the hydraulic line 28 to the return 8 and thus to the storage container 12.

Des Weiteren kann ein Kraftstoffrücklauf der Injektoren 20 über die hydraulische Leitung 4 zum Rücklauf 8 und damit zum Vorratsbehälter 12 geleitet werden.Furthermore, a fuel return of the injectors 20 via the hydraulic line 4 to the return 8 and thus to the reservoir 12 are passed.

In Figur 2 ist beispielhaft eine Pumpe mit verstellbarem Verdrängungsvolumen in einer schematischen Schnittdarstellung für eine Kraftstofffördereinrichtung dargestellt. Sie weist ein Gehäuse 40 auf, in dem sich ein Rotor 42 mit wenigstens einem oder mehreren Flügeln 44 befindet. Der Rotor 42 rotiert um eine Achse, die senkrecht zum Blatt durch einen Mittelpunkt M1 geht.In FIG. 2 is exemplified a pump with adjustable displacement volume in a schematic sectional view of a fuel delivery device. It has a housing 40 in which a rotor 42 with at least one or more vanes 44 is located. The rotor 42 rotates about an axis that passes perpendicular to the blade through a center M1.

Ein kreisförmiger Statorring 46 wird von einem ersten Stellkolben 48 und einem zweiten Stellkolben 50 eingespannt. Die beiden Stellkolben sind gegenüber voneinander angeordnet. Es kann noch ein weiterer Auflagepunkt des Statorringes 46 durch eine nicht dargestellte Höhenstellschraube existieren. Die Achse des kreisförmigen Statorringes 46 verläuft durch einen Mittelpunkt M2. Die Rückseite des ersten Stellkolbens 48 wird über eine hydraulische Leitung 26 mit einem Steuerdruck beaufschlagt. Der Steuerdruck wird im beschriebenen Ausführungsbeispiel durch einen Krafftstoffdruck innerhalb der Kraftstofffördereinrichtung zur Verfügung gestellt. Der zweite Stellkolben 50 wirkt dem ersten Stellkolben 48 entgegen und wird von einer Feder 52 in einer bestimmten Stellung gehalten. Durch den Steuerdruck und die Federkraft wirken zwei Kräfte in gegensätzlicher Richtung auf den Statorring 46.A circular stator ring 46 is clamped by a first actuating piston 48 and a second actuating piston 50. The two adjusting pistons are arranged opposite each other. There may be another bearing point of the stator ring 46 by a height adjustment screw, not shown. The axis of the circular stator ring 46 passes through a center M2. The back of the first actuating piston 48 is acted upon via a hydraulic line 26 with a control pressure. The control pressure is in the described embodiment by a Krafftstoffdruck within the fuel delivery to the Provided. The second actuating piston 50 counteracts the first actuating piston 48 and is held by a spring 52 in a certain position. Due to the control pressure and the spring force, two forces act in opposite directions on the stator ring 46.

Innerhalb des Statorringes 46 dreht sich der elektrisch oder mechanisch angetriebene Rotor 42 und die im Rotor geführten Flügel 44 werden durch Fliehkräfte gegen den Statorring 46 gedrückt. Die für den Transport des Kraftstoffes erforderlichen Zellen 54 werden durch die Drehung des Rotors 42 zunehmend größer und füllen sich dabei mit Kraftstoff über einen Saugkanal 56 der Kraftstoff aus dem Vorratsbehälter 12 ansaugt. Mit Erreichen des größten Zellenvolumens werden die Zellen 54 von der Saugseite getrennt und erhalten bei einer weiteren Drehung Verbindung zur Druckseite. Bei einer weiteren Drehung werden die Zellen 54 verengt und drücken Flüssigkeit über den Druckkanal 58 in eine hydraulische Leitung, die zur Saugseite der Hochdruckpumpe 16 führt.Within the stator ring 46, the electrically or mechanically driven rotor 42 rotates and the blades 44 guided in the rotor are pressed against the stator ring 46 by centrifugal forces. The necessary for the transport of the fuel cells 54 are increasingly larger by the rotation of the rotor 42 and thereby fill with fuel via a suction channel 56 of the fuel from the reservoir 12 sucks. Upon reaching the largest cell volume, the cells 54 are separated from the suction side and get in a further rotation connection to the pressure side. In a further rotation, the cells 54 are narrowed and press liquid via the pressure channel 58 in a hydraulic line leading to the suction side of the high-pressure pump 16.

Abhängig von der Kraft, die sich aus dem Kraftstoffdruck auf den ersten Stellkolben 48 ergibt und der Kraft die die Feder 52 auf den zweiten Stellkolben 50 ausübt, wird der Statorring 46 im Gehäuse verschoben. Sind beide Kräfte gleich groß, so befindet sich der Statorring in Mittelstellung und die beiden Mittelpunkte M1 und M2 liegen aufeinander. In diesem Fall geht die Fördermenge des Kraftstoffes auf eine Nullfördermenge zurück, d.h. die Fördermenge ist Null.Depending on the force resulting from the fuel pressure on the first actuating piston 48 and the force exerted by the spring 52 on the second actuating piston 50, the stator 46 is displaced in the housing. If both forces are equal, the stator ring is in the middle position and the two center points M1 and M2 lie on one another. In this case, the flow rate of the fuel is returned to a zero flow rate, i. the flow rate is zero.

Fällt der Kraftstoffdruck, so dass die Kraft durch die Feder 52 größer ist als die Kraft, die sich aus dem Kraftstoffdruck auf den ersten Stellkolben 48 ergibt, so verschiebt die Feder 52 den Statorring 46 in eine exzentrische Lage bei der die Mittelpunkte M1 und M2 nicht mehr aufeinander liegen. Da die Saug- und die Druckseite von einander getrennt werden, verdrängt die Förderpumpe 10 wieder Kraftstoff. Mit zunehmendem Abstand der Mittelpunkte M1 und M2 wird das Verdrängungsvolumen der Pumpe größer.If the fuel pressure drops, so that the force through the spring 52 is greater than the force resulting from the fuel pressure on the first control piston 48, the spring 52 shifts the stator ring 46 in an eccentric position at the midpoints M1 and M2 not more on each other. Since the suction and the pressure side are separated from each other, the feed pump 10 displaces fuel again. With increasing distance of the centers M1 and M2, the displacement volume of the pump becomes larger.

Die Förderpumpe 10 kann mit gleicher Drehzahl oder variabler Drehzahl über einen mechanischen oder elektrischen Antrieb betrieben werden. Die Drehzahl der Förderpumpe 10 beeinflusst die geförderte Kraftstoffmenge. Durch die Regelung des Steuerdruckes kann eine variable Kraftstoffmenge bei gleicher Drehzahl gefördert werden.The feed pump 10 can be operated at the same speed or variable speed via a mechanical or electric drive. The speed of the feed pump 10 influences the amount of fuel delivered. By the scheme the control pressure can be promoted a variable amount of fuel at the same speed.

Ein Beispiel einer Förderpumpe 10 mit verstellbaren Fördervolumen ist die "Verstellbare Flügelzellenpumpe, Typ PV7" von Bosch Rexroth, die in ihrem Aufbau der beschriebenen Förderpumpe 10 gleicht, aber auf die Dimensionen und Anforderungen einer Kraftstofffördereinrichtung angepasst werden müsste.An example of a delivery pump 10 with adjustable delivery volume is the "adjustable vane pump, type PV7" from Bosch Rexroth, which is similar in construction to the described delivery pump 10, but would have to be adapted to the dimensions and requirements of a fuel delivery device.

Alternativ lässt sich als Förderpumpe 10 mit verstellbaren Fördervolumen auch eine Außenzahnradpumpe oder eine Rollenzellenpumpe oder eine Innenzahnradpumpe oder eine Pendelschieberpumpe einsetzen. Ein Beispiel einer mengenregulierbaren Pendelschieberpumpe ist in der Offenlegungsschrift DE 101 02 531 A1 gezeigt.Alternatively, an external gear pump or a roller-cell pump or an internal gear pump or a pendulum slide pump can also be used as the delivery pump 10 with adjustable delivery volume. An example of a volume-adjustable pendulum slide pump is in the published patent application DE 101 02 531 A1 shown.

Im Ausführungsbeispiel nach Figur 1 ist der Steuerdruck der Kraftstoffdruck auf der Druckseite 6 der Förderpumpe 10. Über eine hydraulische Leitung 26 wirkt der Steuerdruck auf den ersten Stellkolben 48 und beeinflusst damit das Verdrängungsvolumen der Förderpumpe 10. Falls ein druckseitiger Kraftstofffilter 38 vorgesehen ist, kann alternativ der der Druck auf der Saugseite der Hochdruckpumpe 16 zwischen Kraftstofffilter 38 und Hochdruckpumpe 16 als Steuerdruck dienen.In the embodiment according to FIG. 1 via a hydraulic line 26, the control pressure acts on the first actuating piston 48 and thus influences the displacement volume of the feed pump 10. If a pressure-side fuel filter 38 is provided, alternatively the pressure on the Suction side of the high pressure pump 16 between the fuel filter 38 and high pressure pump 16 serve as a control pressure.

Wird durch eine Veränderung der Betriebsbedingungen kurzeitig mehr Kraftstoff als benötigt von der Förderpumpe 10 zur Hochdruckpumpe 16 gefördert, so baut sich in der hydraulischen Leitung 6 ein erhöhter Druck auf. Der Druck in der hydraulischen Leitung 6 steigt abhängig von der Menge des zuviel geförderten Kraftstoffes. Durch den Druckanstieg steigt der Steuerdruck auf den ersten Stellkolben 48, das Verdrängungsvolumen der Förderpumpe 10 wird verringert und damit die Fördermenge des Kraftstoffes reduziert. Die Kraftstoffmenge der Förderpumpe 10 wird an den Bedarf der Hochdruckpumpe 16 angepasst. Wenn der Kraftstoffdruck in der hydraulischen Leitung 6 sinkt, weil die Hochdruckpumpe 16 einen erhöhten Kraftstoffbedarf hat, sinkt auch der Steuerdruck und die Förderpumpe 10 erhöht die Fördermenge des Kraftstoffes. Die Kraftstofffördermenge der Förderpumpe 10 wird an den Bedarf der Hochdruckpumpe 16 angepasst. Zur Vereinfachung des Niederdruckkreises aber mit dem gleichen Effekt kann eine Regelung der Förderpumpe 10 auf den eigenen Förderdruck vorgenommen werden.If, due to a change in the operating conditions, more fuel than required is conveyed from the feed pump 10 to the high-pressure pump 16 for a short time, an increased pressure builds up in the hydraulic line 6. The pressure in the hydraulic line 6 increases depending on the amount of fuel delivered too much. Due to the increase in pressure, the control pressure on the first control piston 48 increases, the displacement volume of the feed pump 10 is reduced and thus reduces the flow rate of the fuel. The fuel quantity of the feed pump 10 is adapted to the needs of the high-pressure pump 16. When the fuel pressure in the hydraulic line 6 decreases because the high-pressure pump 16 has an increased fuel demand, the control pressure also decreases, and the delivery pump 10 increases the delivery rate of the fuel. The fuel delivery rate of the feed pump 10 is adapted to the needs of the high-pressure pump 16. To simplify the low pressure circuit but with the same effect, a regulation of the feed pump 10 can be made to the own discharge pressure.

Figur 3 zeigt eine weitere Ausführungsform der Erfindung. Hierbei ist der Steuerdruck der Kraftstoffdruck in einem Rücklauf 8 zum Vorratsbehälter 12. Durch eine Drossel 24 baut sich im Rücklauf 8 zum Vorratsbehälter 12 ein Kraftstoffdruck auf, der über die hydraulische Leitung 26 oder direkt mit dem ersten Stellkolben 48 der Förderpumpe 10 verbunden ist. Auf die Drossel 24 im Rücklauf 8 zum Vorratsbehälter 12 kann verzichtet werden, wenn ein Gegendruck durch eine nicht dargestellte Strahlpumpe im Rücklauf 8 zum Vorratsbehälter 12 entsteht. FIG. 3 shows a further embodiment of the invention. In this case, the control pressure of the fuel pressure in a return line 8 to the reservoir 12. Through a throttle 24 builds up in the return line 8 to the reservoir 12, a fuel pressure which is connected via the hydraulic line 26 or directly to the first control piston 48 of the feed pump 10. On the throttle 24 in the return 8 to the reservoir 12 may be omitted if a back pressure created by a jet pump, not shown in the return line 8 to the reservoir 12.

Wird durch eine Veränderung der Betriebsbedingungen kurzeitig mehr Kraftstoff als benötigt von der Förderpumpe 10 zur Hochdruckpumpe 16 gefördert, so wird mit Hilfe eines Überströmventils 34 der überschüssige Kraftstoff über die hydraulische Leitung 28 zum Rücklauf 8 abgesteuert. Der Druck im Rücklauf 8 steigt abhängig von der Menge des zuviel geförderten Kraftstoffes. Durch den Druckanstieg im Rücklauf 8 steigt der Steuerdruck auf den ersten Stellkolben 48, das Verdrängungsvolumen der Förderpumpe 10 wird verringert und damit die Fördermenge des Kraftstoffes reduziert. Wird nur wenig Kraftstoff von Überströmventil 34 in den Rücklauf 8 abgesteuert, so sinkt der Steuerdruck und die Förderpumpe 10 erhöht die Fördermenge des Kraftstoffes. Die Kraftstofffördermenge der Förderpumpe 10 wird an den Kraftstoffbedarf der Hochdruckpumpe 16 angepasst.If, due to a change in the operating conditions, more fuel than required is conveyed from the feed pump 10 to the high-pressure pump 16, the excess fuel is diverted via the hydraulic line 28 to the return 8 with the aid of an overflow valve 34. The pressure in the return 8 increases depending on the amount of fuel delivered too much. Due to the increase in pressure in the return line 8, the control pressure increases to the first control piston 48, the displacement volume of the feed pump 10 is reduced and thus reduces the flow rate of the fuel. If only a little fuel is diverted from the overflow valve 34 into the return 8, the control pressure drops and the delivery pump 10 increases the delivery rate of the fuel. The fuel delivery rate of the feed pump 10 is adapted to the fuel demand of the high-pressure pump 16.

Alternativ kann der Kraftstoff in den Rücklauf 8 zum Vorratsbehälter 12 vom Druckregelventil 22 im Hochdruckbereich 18 abgesteuert werden. Das Druckregelventil 22 kann sich hierbei direkt am Hochdruckspeicher 18 oder an der Hochdruckpumpe 16 oder zwischen Hochdruckpumpe 16 und Hochdruckspeicher 18 befinden. Das Druckregelventil 22 wird dabei von einer elektrischen Steuereinheit geregelt. Befindet sich ein höherer Druck als benötigt im Hochdruckbereich 18, so wird überschüssiger Kraftstoff mit Hilfe des Druckregelventils 22 abgesteuert. Der Druck im Rücklauf 8 steigt abhängig von der Menge des abgesteuerten Kraftstoffes. Durch den erhöhten Kraftstoffrücklauf erhöht sich der Druck im Rücklauf 8 vor der Drossel 24 und der Steuerdruck auf den ersten Stellkolben 48 steigt an. Das Verdrängungsvolumen der Förderpumpe 10 wird verringert und damit die Fördermenge des Kraftstoffes reduziert. Wird nur wenig Kraftstoff von Druckregelventil 22 in den Rücklauf 8 abgesteuert, so sinkt der Steuerdruck und die Förderpumpe 10 erhöht die Fördermenge des Kraftstoffes.Alternatively, the fuel in the return line 8 to the reservoir 12 are controlled by the pressure control valve 22 in the high pressure region 18. The pressure control valve 22 may be located directly on the high pressure accumulator 18 or on the high pressure pump 16 or between the high pressure pump 16 and high pressure accumulator 18. The pressure control valve 22 is regulated by an electrical control unit. If there is a higher pressure than required in the high-pressure region 18, excess fuel is deactivated with the aid of the pressure regulating valve 22. The pressure in the return 8 increases depending on the amount of fuel being removed. The increased fuel return increases the pressure in the Return 8 upstream of the throttle 24 and the control pressure on the first actuating piston 48 increases. The displacement volume of the feed pump 10 is reduced and thus reduces the flow rate of the fuel. If only little fuel is diverted from the pressure control valve 22 into the return 8, the control pressure drops and the delivery pump 10 increases the delivery rate of the fuel.

Figur 4 zeigt eine weitere Ausführungsform der Erfindung. Hierbei ist der Steuerdruck der Kraftstoffdruck im Hochdruckspeicher 18. Durch die hydraulische Leitung 26 wirkt der Druck im Hochdruckbereich 18 direkt auf den ersten Stellkolben 48 der Förderpumpe 10 und beeinflusst somit das Verdrängungsvolumen der Förderpumpe 10. Herrscht im Hochdruckspeicher 18 ein zu hoher Druck, wird die Kraftstofffördermenge der Förderpumpe 10 reduziert, ist der Druck im Hochdruckspeicher 18 zu niedrig, wird die Kraftstofffördermenge der Förderpumpe 10 erhöht, ansonsten bleibt sie konstant. FIG. 4 shows a further embodiment of the invention. By the hydraulic line 26, the pressure in the high pressure region 18 acts directly on the first control piston 48 of the feed pump 10 and thus affects the displacement of the feed pump 10 prevails in the high-pressure accumulator 18 too high a pressure, the Fuel delivery of the feed pump 10 is reduced, the pressure in the high pressure accumulator 18 is too low, the fuel delivery of the feed pump 10 is increased, otherwise it remains constant.

Bei allen gezeigten Ausführungsformen der Erfindung kann zur kontrollierten Beeinflussung des Verdrängungsvolumens die Rückseite des zweiten Stellkolbens 50 mit einem Regeldruck beaufschlagt werden. Damit wirkt eine Kraft, die sich aus der Kraft der Feder 52 und dem Regeldruck zusammensetzt, auf den zweiten Stellkolben 50. Der Regeldruck, der auf den zweiten Stellkolben 50 wirkt, stammt aus einer beliebigen Stelle der Kraftstofffördereinrichtung und sollte niedriger sein als der Steuerdruck, der auf die Rückseite des ersten Stellkolbens 48 wirkt.In all embodiments of the invention shown, the rear side of the second actuating piston 50 can be subjected to a control pressure for the controlled influencing of the displacement volume. Thus, a force, which is composed of the force of the spring 52 and the control pressure acts on the second actuating piston 50. The control pressure acting on the second actuating piston 50 comes from any point of the fuel delivery device and should be lower than the control pressure, which acts on the back of the first actuating piston 48.

Figur 5 zeigt eine weitere Ausführungsform der Erfindung. Hierbei ist der Regeldruck der Kraftstoffdruck auf der Druckseite der Förderpumpe 10. Der Regeldruck wird über ein Druckregelventil 15, welches mit einer elektronischen Steuereinrichtung 19 verbunden ist, kontrolliert. Die elektrische Steuereinrichtung 19 ist mit einem Drucksensor 17 im Hochdruckbereich 18 verbunden, welcher Informationen über den Druck im Hochdruckbereich 18 an die elektronische Steuereinrichtung 19 liefert. Abhängig vom Druck im Hochdruckbereich 18 regelt die elektrische Steuereinrichtung 19 das Druckregelventil 15 und beeinflusst somit über den Regeldruck kontrolliert die Fördermenge der Förderpumpe 10. Nicht benötigter Kraftstoff wird über eine hydraulische Leitung in den Vorratsbehälter 12 abgesteuert. Durch das Druckregelventil 15 ist eine stufenlose Verstellung der Kraft auf den zweiten Stellkolben 50 der Förderpumpe 10 möglich. Durch die Veränderung des Regeldruckes verändert sich die Fördercharakteristik der Förderpumpe 10 und es ergeben sich unterschiedliche Verdrängungsvolumina der Förderpumpe 10 bei gleichem Steuerdruck. FIG. 5 shows a further embodiment of the invention. Here, the control pressure of the fuel pressure on the pressure side of the feed pump 10. The control pressure is controlled by a pressure control valve 15 which is connected to an electronic control device 19. The electrical control device 19 is connected to a pressure sensor 17 in the high-pressure region 18, which supplies information about the pressure in the high-pressure region 18 to the electronic control device 19. Depending on the pressure in the high-pressure region 18, the electrical control device 19 controls the pressure control valve 15 and thus influenced by the control pressure, the delivery rate of the feed pump 10. Unnecessary fuel is via a hydraulic line in the reservoir 12 deactivated. By the pressure control valve 15 is a continuous adjustment of the force on the second actuating piston 50 of the feed pump 10 is possible. By changing the control pressure, the delivery characteristic of the feed pump 10 changes and there are different displacement volumes of the feed pump 10 at the same control pressure.

Claims (12)

  1. Fuel delivery device for a fuel injection device of an internal combustion engine, having a supply pump (10) and at least one high-pressure pump (16), wherein the supply pump (10) delivers fuel from a fuel tank (12) to the suction side of the high-pressure pump (16) and the high-pressure pump (16) delivers fuel to a high-pressure region (18), characterized in that the supply pump (10) has a variable displacement, so that a variable quantity of fuel can be delivered at a constant speed of rotation of the supply pump (10), wherein the variable displacement is regulated via a control pressure which acts on a control piston (48) of the supply pump (10) via a hydraulic line (26).
  2. Fuel delivery device according to Claim 1, characterized in that the supply pump (10) delivers a variable quantity of fuel, which varies between a zero delivery quantity and a maximum quantity, the maximum quantity being given by the maximum displacement of the supply pump (10).
  3. Fuel delivery device according to Claim 1, characterized in that the control pressure is the fuel pressure on the delivery side (6) of the supply pump (10).
  4. Fuel delivery device according to Claim 1, characterized in that the control pressure is the fuel pressure between a fuel filter (38) and the suction side of the high-pressure pump (16).
  5. Fuel delivery device according to Claim 1, characterized in that the control pressure is the fuel pressure in a return (8) to the fuel tank (12).
  6. Fuel delivery device according to Claim 1, characterized in that the control pressure is the fuel pressure in the high-pressure accumulator (18).
  7. Fuel delivery device according to Claim 5, characterized in that the fuel is diverted into the return (8) to the fuel tank (12) by an overflow valve (34) on the suction side of the high-pressure pump (16).
  8. Fuel delivery device according to Claim 5, characterized in that fuel is diverted into the return (8) to the fuel tank (12) by a pressure regulator (22) in the high-pressure region (18).
  9. Fuel delivery device according to Claim 1, characterized in that the variable displacement is additionally influenced by a regulating pressure.
  10. Fuel delivery device according to Claim 9, characterized in that the regulating pressure is adjusted by a pressure regulator (15).
  11. Fuel delivery device according to Claim 9 or 10, characterized in that the regulating pressure is adjusted as a function of the engine operating point and/or as a function of the pressure in the high-pressure accumulator (18).
  12. Fuel delivery device according to Claim 1, characterized in that the supply pump (10) is a variable vane cell pump, a variable external gear pump, a variable roller cell pump, a variable internal gear pump or a variable pendulum-slider pump.
EP11726103.2A 2010-07-21 2011-06-09 Fuel delivery device Not-in-force EP2596232B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010031622A DE102010031622A1 (en) 2010-07-21 2010-07-21 Kraftstofffördereinrichung
PCT/EP2011/059556 WO2012010373A1 (en) 2010-07-21 2011-06-09 Fuel delivery device

Publications (2)

Publication Number Publication Date
EP2596232A1 EP2596232A1 (en) 2013-05-29
EP2596232B1 true EP2596232B1 (en) 2016-04-20

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Application Number Title Priority Date Filing Date
EP11726103.2A Not-in-force EP2596232B1 (en) 2010-07-21 2011-06-09 Fuel delivery device

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US (1) US9328710B2 (en)
EP (1) EP2596232B1 (en)
JP (1) JP5693718B2 (en)
KR (1) KR101867632B1 (en)
CN (1) CN103003560B (en)
DE (1) DE102010031622A1 (en)
WO (1) WO2012010373A1 (en)

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Also Published As

Publication number Publication date
JP2013536345A (en) 2013-09-19
CN103003560B (en) 2017-04-05
DE102010031622A1 (en) 2012-01-26
WO2012010373A1 (en) 2012-01-26
JP5693718B2 (en) 2015-04-01
CN103003560A (en) 2013-03-27
KR20130132729A (en) 2013-12-05
US9328710B2 (en) 2016-05-03
US20130112174A1 (en) 2013-05-09
EP2596232A1 (en) 2013-05-29
KR101867632B1 (en) 2018-06-15

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