EP2032832B1 - Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine - Google Patents

Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine Download PDF

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Publication number
EP2032832B1
EP2032832B1 EP07728522A EP07728522A EP2032832B1 EP 2032832 B1 EP2032832 B1 EP 2032832B1 EP 07728522 A EP07728522 A EP 07728522A EP 07728522 A EP07728522 A EP 07728522A EP 2032832 B1 EP2032832 B1 EP 2032832B1
Authority
EP
European Patent Office
Prior art keywords
pressure
fuel
pump
low
feed pump
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.)
Active
Application number
EP07728522A
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German (de)
English (en)
French (fr)
Other versions
EP2032832A1 (de
Inventor
Stefan Kieferle
Dorothee Sommer
Oliver Becker
Bjoern Noack
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2032832A1 publication Critical patent/EP2032832A1/de
Application granted granted Critical
Publication of EP2032832B1 publication Critical patent/EP2032832B1/de
Active legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/205—Quantity of fuel admitted to pumping elements being metered by an auxiliary metering device
    • 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
    • F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0023—Valves in the fuel supply and return system
    • 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
    • F02M37/0047—Layout or arrangement of systems for feeding fuel
    • F02M37/0052—Details on the fuel return circuit; Arrangement of pressure regulators

Definitions

  • the invention relates to a fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is characterized by the EP-A-1 195 514 known.
  • This fuel injection device comprises an electric drive having a feed pump, is conveyed by the fuel from a fuel tank in a low pressure region to the suction side of at least one high-pressure pump.
  • the high-pressure pump delivers fuel into a high-pressure region, in which at least one injector is provided, through which fuel is injected at the internal combustion engine.
  • the fuel injection device has an electric control device for controlling the fuel injection. In the low-pressure region, a pressure sensor is arranged, which is connected to the control device.
  • the electric drive of the feed pump for adjusting a variable depending on at least one operating parameter of the internal combustion engine and / or the high-pressure pump flow rate of the feed pump and for generating a predetermined pressure in the low pressure range is controlled. At least part of the fuel delivered by the feed pump into the low-pressure region is passed through a drive region of the high-pressure pump.
  • the electric drive of the feed pump is controlled by the control device for variably setting the quantity of fuel sucked in by the high-pressure pump and conveyed into the high-pressure region. This does not always ensure adequate lubrication and cooling of the drive range of the high-pressure pump.
  • the fuel injection device according to the invention with the features of claim 1 has the advantage that even at high fuel temperatures sufficient lubrication and / or cooling of the drive range of the high-pressure pump is ensured.
  • the embodiment according to claim 2 has the advantage that a possible pressure drop in the flow through the fuel filter has no influence on the pressure detection in the low-pressure region.
  • the embodiment according to claims 4 and 5 has the advantage that the lubrication and / or cooling of the drive region of the high-pressure pump is improved under high load.
  • the embodiment of claim 6 and 7 has the advantage that funded by the pump fuel, which is not sucked by the high-pressure pump, can be removed from the low pressure region.
  • the embodiment according to claim 8 has the advantage that the entire amount of fuel delivered by the delivery pump is available for lubrication and / or cooling of the drive region of the high-pressure pump.
  • FIG. 1 a fuel injection device for an internal combustion engine in a schematic representation
  • FIG. 2 a diagram in which the flow rate of a feed pump and the overflow of an overflow valve is applied over the pressure prevailing in a low pressure region.
  • FIG. 1 schematically a fuel injection device for an internal combustion engine, for example a motor vehicle is shown.
  • the fuel injection device has a feed pump 10 through which fuel is sucked from a fuel storage container 12.
  • the feed pump 10 has an electric drive 14 in the form of an electric motor and the feed pump 10 may be outside or as in FIG. 1 be arranged within the fuel tank 12.
  • a jam or swirl pot 16 may be arranged, from which the feed pump 10 sucks and is ensured by the fact that the pump 10 can suck fuel even at low level in the fuel tank 12.
  • fuel is conveyed for example by at least one jet pump 18.
  • fuel is conveyed to the suction side of a high-pressure pump 20 of the fuel injection device.
  • a fuel filter 22 is provided, through which the pumped by the feed pump 10 fuel is purified before it flows to the high pressure pump 20.
  • the high-pressure pump 20 has one or more pump elements 24, which in turn each have a guided in a cylinder bore 26 pump piston 28.
  • a pump working space 30 is limited in the respective cylinder bore 26.
  • a drive shaft 32 driven in rotation by the internal combustion engine.
  • the drive shaft 32 is rotatably supported, for example, via two bearing points of a housing 34 of the high-pressure pump 14 which are spaced apart from one another in the direction of the axis of rotation of the drive shaft 32.
  • the bearings may be arranged in different parts of the pump housing 34, for example, a first bearing point in a main body of the pump housing 34 and a second bearing point may be arranged in a connected to the main body flange.
  • the drive shaft 32 has at least one cam 36 or an eccentric to its axis of rotation formed portion, wherein the cam 36 may be formed as a multiple cam.
  • the drive shaft 32 of the high-pressure pump 20 is driven by the internal combustion engine, for example, by the crankshaft or camshaft.
  • the coupling of the drive shaft 32 with the internal combustion engine can be done for example via a belt (toothed belt), a chain or gears. Due to the drive of the high-pressure pump 20 by the internal combustion engine, the rotational speed of the drive shaft 32 of the high-pressure pump 20 is proportional to the rotational speed of the internal combustion engine.
  • the respective pump piston 28 can be supported directly or via a plunger 29 on the cam 36 or eccentric of the drive shaft 32.
  • Each pump element 24 has an inlet valve 38 which opens into the pump working chamber 30 and via which the pump working chamber 30 is filled with fuel when the intake stroke of the pump piston 28 is directed radially inward toward the drive shaft 32.
  • Each pumping element 24 also has an outlet valve 40 which opens out of the pump working space 30 and over which the delivery stroke of the pump 12 directed radially outward Pump piston 28 compressed fuel from the pump chamber 30 is displaced.
  • the inlet valve 38 and the outlet valve 40 are each designed as spring-loaded check valves.
  • the drive shaft 32 with the cam 36 or eccentric and the support of the at least one pump piston 28 forms a arranged in the interior of the pump housing 34 drive portion 37 of the high pressure pump 20th
  • the high-pressure pump 14 is conveyed via at least one line fuel in a high-pressure region in which, for example, a memory 42 is arranged.
  • a memory 42 At least one arranged on a cylinder of the internal combustion engine injector 44 is connected, is injected through the fuel into the combustion chamber of the cylinder.
  • the injectors 44 are connected directly or indirectly via hydraulic lines to the high pressure pump 14, wherein the separate memory 42 can be omitted.
  • the injector 44 has a fuel injection valve and, for example, an electrically operated control valve by which the opening and closing function of the fuel injection valve is controlled. It can also be provided that the fuel injection valve is controlled directly by an electric actuator, for example a piezoelectric actuator.
  • the fuel injector also includes an electronic controller 46 that controls fuel injection. By the control device 46, the injector 44 is driven so that a predetermined amount of fuel is injected through this at a given time.
  • a pressure sensor 48 is arranged, by means of which the pressure in the high-pressure region is detected and which is connected to the control device 46. From the memory 42 can discharge a connection to a discharge area, for example a return to the fuel tank 12, which is controlled by a pressure limiting or pressure control valve 43.
  • a fuel metering device 50 is provided between the feed pump 10 and the suction side of the high-pressure pump 20, which is preferably arranged between the fuel filter 22 and the suction side of the high-pressure pump 20.
  • the area between the feed pump 10 and the suction side of the high-pressure pump 20 is referred to below as the low-pressure area.
  • the fuel metering device 50 can be designed such that it continuously or stepwise a different sized flow cross-section in the connection between the feed pump 10 and the suction side of the high pressure pump 20 is adjusted.
  • the fuel metering device 50 may also be formed by a clocked valve which is opened and closed at a certain frequency, this releasing a certain averaged flow area in accordance with its opening duration.
  • the fuel metering device 50 may include an electric actuator 51, which may be, for example, an electromagnet or a piezoelectric actuator, and which is controlled by the control device 46.
  • the fuel metering device 50 may also be hydraulically controlled.
  • the flow cross-section is determined by a piston which is acted upon by a hydraulic pressure movable.
  • the hydraulic pressure can be generated, for example, by the passage of the pressure control valve 43. In this case, with increasing Abêtmenge of the pressure control valve 43, a higher pressure, through which the released by the fuel metering 50 flow cross-section is reduced.
  • the Pressure control valve 43 can be controlled by the control device 46, so that the fuel metering device 50 is controlled indirectly via the Abêtmenge of the pressure control valve 43 by the control device 46.
  • the fuel injection device further has an overflow valve 52 arranged between the feed pump 10 and the fuel metering device 50, by means of which a connection of the low-pressure region to a discharge region is controlled.
  • the discharge area is, for example, a return 53 to the fuel tank 12, wherein in the discharge area a lower pressure prevails than in the low pressure area.
  • the overflow valve 52 is designed as a pressure valve, which opens upon reaching a predetermined pressure in the low pressure region and can flow fuel from the low pressure region in the discharge area.
  • the opening pressure of the overflow valve 52 is determined by a spring 54, which acts on a valve member 55 of the spill valve 52 in a closing direction.
  • the spill valve 52 is disposed downstream of the drive section 37 between it and the fuel metering device 50.
  • the entire amount of fuel delivered by the feed pump 10 first flows through the drive region of the high-pressure pump 20 before it is sucked in by the high-pressure pump 20.
  • the pressure prevailing in the low-pressure region between the fuel filter 22 and the suction side of the high-pressure pump 20 is detected by a pressure sensor 56, which is connected to the control device 46.
  • the pressure sensor 56 is arranged in the low-pressure region between the fuel filter 22 and the drive region of the high-pressure pump 20, so that a possible pressure drop in the flow through the fuel filter 22 is taken into account in the pressure detection in the low-pressure region.
  • the delivery rate of the high-pressure pump 20, which corresponds to the load of the internal combustion engine is considered as an operating parameter.
  • the speed of the internal combustion engine which is proportional to the speed of the High pressure pump 20 is to be considered.
  • the fuel temperature which is detected by means of a fuel temperature sensor 58, which is connected to the control device 46, is taken into account as the operating parameter.
  • the drive 14 of the feed pump 10 is driven such that promoted by the feed pump 10 in the low pressure range at high load, and thus large flow of the high-pressure pump 20, and / or high speed of the engine and the high-pressure pump 20, a larger amount of fuel and so that a higher pressure is generated than at low load and flow rate and / or low speed. It may be provided that with increasing load of the internal combustion engine and thus increasing flow rate of the high-pressure pump 20 by the controller 46, the electric drive 14 of the feed pump 10 is driven such that funded by the feed pump 10, an increasingly larger amount of fuel and thus an increasingly higher pressure is generated in the low pressure range.
  • the drive 14 of the feed pump 10 is controlled by the control device 46 such that at high fuel temperature by the feed pump 10 promotes a larger amount of fuel and thus a higher pressure in the low pressure region is generated than at low fuel temperature. It may be provided that with increasing fuel temperature of the drive 14 of the feed pump 10 is controlled by the controller 46 such that promoted by the feed pump 10 an increasing amount of fuel in the low pressure region and thus a higher pressure in the low pressure region is generated. As a result, adequate lubrication and / or cooling of the drive region 37 of the high-pressure pump 20 is likewise ensured, since the lubricating effect of the fuel deteriorates with increasing fuel temperature.
  • setpoint values for the pressure in the low-pressure region are stored in the control device 46 in a characteristic diagram, the electric drive 14 of the feed pump 10 then being controlled by the control device 46 in such a way that such a fuel quantity is conveyed into the low-pressure region by the feed pump 10, like this one to set the pressure set point.
  • the characteristic of the overflow valve 52 is determined so that an increasing amount of fuel is diverted into the discharge area by this with increasing pressure in the low pressure region.
  • the overflow valve 52 may, for example, have an at least approximately linear characteristic, so that, proportional to the pressure in the low-pressure region, the amount of fuel diverted by the overflow valve 52 increases. In FIG.
  • FIG. 2 a diagram is shown in the exemplary illustrated the area A, in which the funded by the feed pump 10 Fuel quantity V is plotted against the pressure prevailing in the low pressure range pND.
  • the characteristic curve of the overflow valve 52 is shown by way of example with reference to B, this being the amount of fuel V which is diverted by this fuel as a function of the pressure pND prevailing in the low-pressure region.
  • the working range of the overflow valve 52 which is the pressure range in which fuel is removed from the low-pressure region by the overflow valve 52, is marked C in FIG.
  • the overflow valve 52 is designed in such a way that this fuel can be diverted from the low-pressure region by the fuel pumped by the feed pump 10, regardless of the setting of the fuel metering device 50.
  • the spill valve 52 thus a variable adjustment of the pressure in the low pressure region and thus the delivery rate of the feed pump 10 is made possible regardless of the amount of fuel to be pumped from the high-pressure pump 20.
  • the lubrication and / or cooling of the drive region of the high-pressure pump 20 can be improved as required, regardless of the fuel quantity to be delivered by the high-pressure pump 20.
  • the pressure generated by the pump 10 in the low pressure range can be kept low, for which the feed pump 10 needs to promote only a small amount of fuel, whereby the load of the feed pump 10, in particular of their electric drive 14, and thus the demand for electrical energy for its supply can be kept low.
  • the feed pump 10 with the electric drive 14 can therefore be designed for a lower average load, wherein the Design compared to a design with a constant flow rate can be simplified or compared to this design an increased life can be achieved.
  • an increased peak load with a large flow rate of the feed pump 10 may be permitted, since this is only required for a short time.
  • the load of the fuel filter 22 is reduced because it is not constantly flowed through by the maximum flow rate of the feed pump 10 but only by the actual required flow rate of the feed pump 10.
  • the fuel filter 22 can therefore compared to a conventional design for constant flow of the feed pump 10 are dimensioned smaller or can reach a longer life with the same dimensions.
  • occurring as a result of contamination of the fuel filter 22 at its flow pressure drop can be at least partially offset by the feed pump 10 by the amount of fuel delivered by this is increased.

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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)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
EP07728522A 2006-06-14 2007-04-25 Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine Active EP2032832B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006027486A DE102006027486A1 (de) 2006-06-14 2006-06-14 Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
PCT/EP2007/054067 WO2007144227A1 (de) 2006-06-14 2007-04-25 Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP2032832A1 EP2032832A1 (de) 2009-03-11
EP2032832B1 true EP2032832B1 (de) 2010-12-15

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ID=38282879

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07728522A Active EP2032832B1 (de) 2006-06-14 2007-04-25 Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine

Country Status (7)

Country Link
US (1) US8205596B2 (ko)
EP (1) EP2032832B1 (ko)
JP (1) JP4909406B2 (ko)
KR (1) KR101087430B1 (ko)
AT (1) ATE491879T1 (ko)
DE (2) DE102006027486A1 (ko)
WO (1) WO2007144227A1 (ko)

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Also Published As

Publication number Publication date
EP2032832A1 (de) 2009-03-11
KR20090007644A (ko) 2009-01-19
US20100012096A1 (en) 2010-01-21
DE502007005964D1 (de) 2011-01-27
DE102006027486A1 (de) 2007-12-20
JP2009540205A (ja) 2009-11-19
JP4909406B2 (ja) 2012-04-04
KR101087430B1 (ko) 2011-11-25
WO2007144227A1 (de) 2007-12-21
ATE491879T1 (de) 2011-01-15
US8205596B2 (en) 2012-06-26

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