EP1546544A1 - Fuel injection device for an internal combustion engine - Google Patents

Fuel injection device for an internal combustion engine

Info

Publication number
EP1546544A1
EP1546544A1 EP03724838A EP03724838A EP1546544A1 EP 1546544 A1 EP1546544 A1 EP 1546544A1 EP 03724838 A EP03724838 A EP 03724838A EP 03724838 A EP03724838 A EP 03724838A EP 1546544 A1 EP1546544 A1 EP 1546544A1
Authority
EP
European Patent Office
Prior art keywords
pump
pressure pump
opening
fuel
connection
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.)
Withdrawn
Application number
EP03724838A
Other languages
German (de)
French (fr)
Inventor
Andreas Holl
Achim Koehler
Sascha Ambrock
Martin Klander
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1546544A1 publication Critical patent/EP1546544A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/0275—Arrangement of common rails
    • F02M63/028—Returnless common rail 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • 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
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves
    • 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
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/005—Pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/007—Venting means

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 known from DE 198 53 103 AI.
  • This fuel injection device has a delivery pump, through which fuel is delivered to at least one high-pressure pump, the high-pressure pump delivering fuel under high pressure to a reservoir. Furthermore, a fuel metering device is provided, which is arranged between the feed pump and the high-pressure pump.
  • Fuel metering device is used to control the amount of fuel delivered by the high-pressure pump into the memory depending on the operating parameters of the internal combustion engine.
  • the fuel metering device comprises an actuator in the form of an electromagnet and a control valve actuated by it, which has a slide-shaped valve member which is guided in a cylinder bore of a valve housing and can be displaced by an armature of the electromagnet against a return spring. In cooperation with a drain opening, the valve member controls the valve housing via its
  • the outer jacket has a flow cross-section from the feed pump to the high-pressure pump.
  • this is with its outer jacket in Cover with the drain opening so that the flow cross-section is completely closed.
  • the valve member since the valve member must be displaceable in the cylinder bore of the valve housing, there is a small gap between the outer casing and the cylinder bore through which a leakage amount of fuel can pass and reach the high-pressure pump via the drain opening, even if due to the operating parameters of the internal combustion engine, for example in the Thrust operation, through which the high-pressure pump is not allowed to deliver fuel, with a so-called zero delivery.
  • a throttled connection to a relief area can be provided, but then fuel constantly flows into the relief area after the fuel metering device and there is also an increased pressure level between the fuel metering device and the high-pressure pump.
  • the opening pressure of at least one suction valve of the high-pressure pump must be set correspondingly high, but this has an adverse effect on the delivery rate of the high-pressure pump.
  • a complex structure and a complex production of the fuel injection device are therefore required.
  • the fuel injection device with the features according to claim 1 has the advantage that the valve member, when this closes the flow cross-section between the feed pump and the high-pressure pump for zero delivery, opens a connection to a relief region into which the fuel delivered by the delivery pump or as a result a leak in the fuel metering device High pressure pump fuel can drain. Fuel therefore only flows into the relief area at zero delivery if no fuel is to be delivered by the high-pressure pump. Thus, especially when starting the internal combustion engine, when a large amount of fuel has to be delivered by the high-pressure pump, a loss of fuel is narrowly avoided.
  • Delivery pump and the fuel metering the delivery pressure of the delivery pump is maintained, which causes discontinuities in the pressure curve before
  • Fuel metering device are avoided and thereby an improved setting of the pressure in the memory is made possible by means of the fuel metering device.
  • the structure and manufacture of the fuel injection device are correspondingly simplified by the features of claim 1, since no additional measures for zero delivery are required.
  • Fuel injection device for an internal combustion engine in a schematic representation, Figure 2 in an enlarged view a fuel metering device
  • Fuel injection device according to a first embodiment with a valve member in a first position
  • Figure 3 shows the fuel metering device with the valve member in a second position
  • Figure 4 shows the fuel metering device according to a second embodiment
  • Figure 5 shows the fuel metering device according to a third embodiment.
  • FIG. 1 shows a fuel injection device for an internal combustion engine, for example of a motor vehicle.
  • the internal combustion engine is preferably a self-igniting internal combustion engine and has one or more cylinders.
  • the motor vehicle has a fuel reservoir 10 in which fuel is stored for the operation of the internal combustion engine.
  • the fuel injection device has a feed pump 12, through which fuel is fed from the fuel tank 10 to at least one high-pressure pump 14.
  • the high-pressure pump 14 pumps fuel into a reservoir 16, which can be tubular, for example, or in any other form.
  • Lines 18 lead from the store 16 to injectors 20 arranged on the cylinders of the internal combustion engine. There is one on each of the injectors 20 electrical .
  • Control valve 22 is arranged, through which an opening of the injectors is controlled so as to effect fuel injection by the respective injector 20 or to prevent fuel injection.
  • the control valves.-22 are controlled by an electronic
  • Control device 23 is controlled by which the time and duration of the fuel injection by the injectors 20 is determined as a function of operating parameters of the internal combustion engine, such as speed, load, temperature and others.
  • a return for unused fuel leads from the injectors 20, at least indirectly, for example via a line 24 common to all injectors, into a return leading to the fuel reservoir 10.
  • a line 26 can also return from the reservoir 16 as a return to the fuel reservoir 10, in which a pressure limiting valve 28 is arranged in order to prevent an inadmissibly high pressure from building up in the reservoir 16.
  • the high pressure pump 14 is mechanically by the
  • the feed pump 12 can also be driven mechanically by the internal combustion engine, wherein a common drive shaft can be provided for the high pressure pump 14 and the feed pump 12.
  • the feed pump 12 may alternatively also have an electric motor drive, for example.
  • the high-pressure pump 14 can be designed as a radial piston pump and has at least one, preferably a plurality of pump elements 30 arranged at a uniform angular distance from one another, each of which has a pump piston 34 driven in a stroke movement by a polygon 32 in connection with an eccentric shaft and guided in a cylinder bore 33, the one
  • a check valve 38 opening towards the accumulator 16 is arranged as an outlet valve, by means of which the separation between the pump work chamber 36 and the accumulator 16 takes place during the suction stroke of the pump piston 34.
  • Pump work chamber 36 with the feed pump 12 is a check valve 39 opening towards the pump work chamber 36 as a suction valve, through which the separation between the pump work chamber 36 and the feed pump 12 takes place during the delivery stroke of the pump piston 34.
  • Fuel reservoir 10 are preferably arranged one or more filters.
  • a coarse filter 40 can be provided first, followed by a fine filter 42, whereby the fine filter 42 or the coarse filter 40 can additionally have a water separator.
  • the return line 24 of the injectors 20 can also lead into the line between the filter 40 and the feed pump 12.
  • a fuel metering device 44 is arranged between the feed pump 12 and the high pressure pump 14.
  • the fuel metering device 44 has, for example, an electrical actuator 45, preferably one
  • Electromagnets or a piezo actuator, operated Control valve 46 through which the flow from the feed pump 12 to the high pressure pump 14 is continuously adjustable.
  • the fuel metering device 44 is also controlled by the control device 23, in such a way that a fuel quantity is supplied to the high-pressure pump 14 by the feed pump 12, which in turn is then pumped under high pressure into the memory 16 by the high-pressure pump 14 in order to have a predetermined value in the memory 16 to maintain pressure dependent on operating parameters of the internal combustion engine.
  • a pressure sensor 17 is arranged on the accumulator 16, which is connected to the control device 23 and which supplies a signal for the actual pressure in the accumulator 16.
  • the fuel metering device 44 is shown enlarged according to a first embodiment.
  • the fuel metering device 44 has a valve housing 50, in which a valve member 54 designed as a hollow piston is displaceably guided in a cylinder bore 52.
  • the valve member 54 is cup-shaped, the bottom 55 and the jacket of which may also be separate components which are connected to one another.
  • the bottom 55 of the valve member 54 can also form a magnet armature of the actuator 45.
  • the bottom 55 of the valve member 54 has at least one opening 57.
  • an opening 56 of an outlet leading to the high-pressure pump 14 opens into the cylinder bore 52 in the valve housing 50 at least approximately axially.
  • the valve member 54 faces the opening 56 with its open side.
  • the valve member is through the at least one opening 57 in the base 55
  • the actuator 45 engages it.
  • a support disk 58 is inserted, for example pressed in, into the cylinder bore 52, between which and the bottom of the valve member 54 a spring 60 is clamped, which plunges into the valve member 54.
  • the position of the support disk 58 can be adjustable in the direction of the longitudinal axis 53 of the cylinder bore 52 so as to enable the prestressing of the spring 60 to be adjusted.
  • the support disk 58 has an opening for the passage of the fuel escaping through the opening 56.
  • An inlet from the pressure side of the feed pump 12 opens into the jacket of the cylinder bore 52 with at least one opening 62.
  • a plurality of openings 62 can also be provided, which are arranged distributed over the circumference of the cylinder bore 52.
  • the opening 62 can be formed as a slot extending over part of the circumference of the cylinder bore 52.
  • the valve member 54 has in its jacket according to the arrangement and number of openings 62 of the cylinder bore 52 at least one opening 64, which can also be formed as a slot extending over part of the circumference of the valve member 54. Through the valve member 54 with its at least one opening 64 in cooperation with the at least one
  • Opening 62 of the cylinder bore 52 controls the size of a flow cross section in the connection between the feed pump 12 and the high pressure pump 14.
  • a flow cross section of different sizes is released.
  • the size of the flow cross section is changed by the valve member 54 depending on its position in the direction of the longitudinal axis 53 of the cylinder bore 52.
  • the valve member 54 is shown in an axial position in which its opening 64 completely overlaps with the opening 62 of the cylinder bore 52 and thus the maximum flow cross-section is released.
  • the valve member 54 is shown in an axial position in which it is displaced to the left by the actuator 45 against the spring 60 and the opening 64 is no longer in Overlap with the opening 62 of the cylinder bore 52, so that the flow cross section is closed.
  • At least one further opening 66 from which a connection leads to a relief area, opens out on the jacket of the cylinder bore 52 in the direction of the longitudinal axis 53 of the cylinder bore 52 to the opening 62, offset from the support disk 58.
  • a return line 24 to the fuel storage container 10 or, as shown in broken lines in FIG. 1, the suction side of the feed pump 12 can serve as the relief region.
  • the valve member 54 has at least one further opening 68 offset in its jacket in the direction of the longitudinal axis 53 toward the opening 64 towards the bottom. Through the valve member 54, the connection to the relief region is controlled with its opening 68.
  • the openings 66, 68 in the cylinder bore 52 and in the valve member 54 are arranged such that the opening 68 is not in register with the opening 66 when the valve member 54 is in axial positions, in which a flow cross-section at the openings 62, 64 is released as shown in Figure 2. In this position of the valve member 54, the connection to the relief region is closed thereby, so that fuel delivered by the feed pump 12 can only reach the high-pressure pump 14.
  • Flow cross-section is released while the connection to the relief area remains closed.
  • the fuel metering device 44 maintains the delivery pressure of the delivery pump 12. This ensures a reliable setting of the pressure in the accumulator 16 by the fuel metering device 44, since only a small amount in the feed from the feed pump 12 to the latter
  • the inlet from the feed pump 12 and the outlet to the high pressure pump 14 are interchanged.
  • the inlet from the feed pump 12 then opens axially into the cylinder bore 52 in the opening 56 and the outlet to the high-pressure pump 14 opens into the cylinder bore 52 in the openings 62.
  • the inlet from the feed pump 12 is thus through the valve member 54 connected to the relief area.
  • FIG. 4 shows the fuel metering device according to a second exemplary embodiment, in which the structure is essentially the same as in the first exemplary embodiment.
  • the valve member 54 in the second exemplary embodiment has only the at least one opening 64 through which the size of the flow cross section between the feed pump 12 and the high-pressure pump 14 is controlled.
  • the cylinder bore 52 has in its jacket the at least one opening 62 and the at least one further opening 66 which is arranged at a relatively large axial distance therefrom and which forms the connection to the relief region.
  • the opening of the opening 66 and thus the connection to the relief area is controlled by the valve member 54 with its jacket such that the opening 66 is closed when the valve member 54 completely overlaps the opening 66 and that the opening 66 is opened when the valve member 54 does not or only partially covers the opening 66.
  • the opening 66 and thus the connection to the relief region is closed by the valve member 54 as long as a flow cross-section is released by the valve member 54 with the openings 62, 64. Only when the flow cross-section at the openings 62, 64 is at least approximately closed by the valve member 54, is the opening 66 and thus the connection to the relief region released.
  • the inlet from the feed pump 12 and the outlet to the high-pressure pump 14 can also be interchanged in the second embodiment, so that the inlet in the opening 56 and the outlet in the openings 62 open into the cylinder bore 52.
  • FIG. 5 shows the fuel metering device according to a third exemplary embodiment, in which the structure is again essentially the same as in the first exemplary embodiment. Different from the first
  • Embodiment opens the inlet of the Delivery pump 12 forth in an axially arranged opening 156, for example, into the cylinder bore 152 and at least one opening 162 of the outlet to the high-pressure pump 14 opens out at the jacket of the cylinder bore 152.
  • At the jacket of the cylinder bore 152 at least one further opening opens in the axial direction to the opening 162 166, which connects to a relief area.
  • the valve member 154 ' has at least one opening 164 in its jacket, which in cooperation with the opening 162 controls the flow cross section of the connection between the feed pump 12 and the high pressure pump 14.
  • the valve member 154 has in its jacket at least one groove 168 running in the direction of the longitudinal axis 153 and over part of the circumference, through which a connection between the opening 162 and the opening 166 is controlled. If a flow cross-section is released through the valve member 154 at the openings 162, 164, the groove 168 is not in register with the opening 162, so that fuel can only reach the high-pressure pump 14 from the feed pump 12 through the openings 162, 164. If through that
  • Valve member 154 of the flow cross-section is at least approximately completely closed, since the opening 164 no longer or almost no longer overlaps the opening 162, the groove 168 is in overlap with the opening 162 and establishes a connection to the opening 166. Fuel then flows from port 162 directly to port 166 and into the relief area.
  • the inlet from the feed pump 12 and the outlet to the high-pressure pump 14 can be interchanged, so that the inlet from the feed pump 12 in the openings 162 and the outlet in the opening 156 in the Cylinder bore 152 opens.
  • the actuator 45 of the fuel metering device 44 is controlled by the control device 23 such that the valve member 54 or 154 the flow cross-section of the connection between the feed pump 12 and the high-pressure pump 14 closes completely and the sequence of the
  • Fuel metering device 44 to the high pressure pump 14 is connected to the relief area. There is therefore only a low pressure on the suction side of the high-pressure pump 14 with zero delivery. Only a small amount of fuel passes through the fuel metering device 44 as a result of a possible leakage between the valve member 54 or 154 and the cylinder bore 52 or 152, which can flow off to the relief area. This enables a low opening pressure of the suction valve 39 of the at least one pump element of the high-pressure pump 14 to be set. This in turn enables a good filling of the pump working space 36 and a good pump delivery rate when the fuel is pumped by the high-pressure pump 14.
  • the spring 60 can be designed with a relatively high rigidity, as a result of which an advantageous characteristic curve of the fuel metering device 44 and thus of the high-pressure pump 14 can be achieved.
  • a large opening 64 or 164 can be opened
  • connection between the feed pump 12 and the high pressure pump 14 can be upstream of the
  • Fuel metering device 44 discharges a bypass connection 70 into a drive area of high-pressure pump 14, in which a throttle point 72 and a pressure valve 74 are arranged. If there is a sufficiently high pressure downstream of the feed pump 12, the pressure valve 74 opens and releases the bypass connection 70. About the Bypass connection 70 is supplied to the drive area of high-pressure pump 14 for lubrication thereof. The throttle point 72 limits the amount of fuel that flows through the bypass connection 70. Fuel flows from the drive area to the return
  • Fuel tank 10 from. It can be provided that a pressure-increasing device 76 is arranged between the accumulator 16 and the injectors 20, by means of which the pressure prevailing in the accumulator 16 is increased, so that fuel injection by the injectors 20 is higher
  • a return line 78 can lead away from the pressure increasing device 76 and opens into the connection between the feed pump 12 and the high pressure pump 14 upstream of the fuel metering device 44.
  • a check valve 80 which opens towards the connection is arranged in the return 78.
  • a further bypass connection 82 may be located upstream dissipate with a restrictor 83 to a return to the fuel reservoir 10, which allows venting before the fuel metering 44th
  • a further bypass connection 84 can lead away from the connection between the feed pump 12 and the high-pressure pump 14 upstream of the fuel metering device 44, which leads to the suction side of the feed pump 12 or into the return line 24 and into which one leads to the suction side of the feed pump 12 or to the return line 24 towards opening pressure valve 85 is arranged.
  • the bypass connection 84 with the pressure valve 85 limits the pressure prevailing in the connection between the delivery pump 12 and the high-pressure pump 14.

Landscapes

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

Abstract

The fuel injection device comprises a delivery pump (12) via which fuel is delivered to the induction side of a high-pressure pump (14). The high-pressure pump (14) delivers fuel to a reservoir (16) according to operating parameters of the internal combustion engine. The fuel injection device also comprises a fuel metering device (44) for adjusting the amount of fuel delivered by the high-pressure pump (14) to the reservoir (16). Said fuel metering device (44) comprises an actuator (45) and a control valve (46) that is actuated thereby. The control valve (46) has a valve element (54), which is guided inside a cylinder bore (52) of a valve housing (50), which can be displaced by the actuator (45) counter to a restoring force (60), and which, while interacting with an opening (62) of an inlet from the delivery pump (12), said opening leading to the lateral surface of the cylinder bore (52), or while interacting with an outlet to the high-pressure pump (14), controls a flow area at the junction between the delivery pump (12) and the high-pressure pump (14).

Description

Kraftstoffeinspritzeinrichturig für eine BrennkraftmaschineFuel injection device for an internal combustion engine
Stand der TechnikState of the art
Die Erfindung geht aus von einer Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention relates to a fuel injection device for an internal combustion engine according to the preamble of claim 1.
Eine solche Kraftstoffeinspritzeinrichtung ist durch die DE 198 53 103 AI bekannt. Diese Kraftstoffeinspritzeinrichtung weist eine Förderpumpe auf, durch die Kraftstoff zu wenigstens einer Hochdruckpumpe gefördert wird, wobei die Hochdruckpumpe Kraftstoff unter Hochdruck in einen Speicher fördert . Weiterhin ist eine Kraftstoffzumeßeinrichtung vorgesehen, die zwischen der Förderpumpe und der Hochdruckpumpe angeordnet ist. DieSuch a fuel injection device is known from DE 198 53 103 AI. This fuel injection device has a delivery pump, through which fuel is delivered to at least one high-pressure pump, the high-pressure pump delivering fuel under high pressure to a reservoir. Furthermore, a fuel metering device is provided, which is arranged between the feed pump and the high-pressure pump. The
Kraftstoffzumeßeinrichtung dient zur Steuerung der durch die Hochdruckpumpe in den Speicher geförderten Kraftstoffmenge abhängig von Betriebsparametern der Brennkraftmaschine. Die Kraftstoffzumeßeinrichtung umfaßt einen Aktor in Form eines Elektromagneten und ein durch diesen betätigtes Regelventil, das ein in einer Zylinderbohrung eines Ventilgehäuses geführtes schieberförmiges Ventilglied aufweist, das durch einen Anker des Elektromagneten gegen eine Rückstellfeder verschiebbar ist . Das Ventilglied steuert in Zusammenwirkung mit einer AblaufÖffnung des Ventilgehäuses über seinenFuel metering device is used to control the amount of fuel delivered by the high-pressure pump into the memory depending on the operating parameters of the internal combustion engine. The fuel metering device comprises an actuator in the form of an electromagnet and a control valve actuated by it, which has a slide-shaped valve member which is guided in a cylinder bore of a valve housing and can be displaced by an armature of the electromagnet against a return spring. In cooperation with a drain opening, the valve member controls the valve housing via its
Außenmantel hubabhängig einen Durchflußquerschnitt von der Förderpumpe zur Hochdruckpumpe. In einer Schließstellung des Ventilglieds befindet sich dieses mit seinem Außenmantel in Überdeckung mit der AblaufÖffnung, so daß der Durchflußquerschnitt vollständig verschlossen wird. Da das Ventilglied in der Zylinderbohrung des Ventilgehäuses jedoch verschiebbar sein muß ist zwischen dessen Außenmantel und der Zylinderbohrung ein geringer Spalt vorhanden, durch den eine Leckmenge an Kraftstoff hindurchtreten und über die Ablauföffnung zur Hochdruckpumpe gelangen kann, auch wenn aufgrund der Betriebsparameter der Brennkraftmaschine, beispielsweise im Schubbetrieb, durch die Hochdruckpumpe kein Kraftstoff gefördert werden darf, bei einer sogenannten Nullförderung. Es sind daher Maßnahmen erforderlich, um diese Leckmenge an Kraftstoff abzuführen, so daß diese nicht zur Hochdruckpumpe gelangen kann und die Nullförderung erreicht wird. Hierzu kann eine gedrosselte Verbindung zu einem Entlastungsbereich vorgesehen werden, wobei dann aber ständig Kraftstoff nach der Kraftstoffzumeßeinrichtung in den Entlastungsbereich abfließt und außerdem ein erhöhtes Druckniveau zwischen der Kraftstoffzumeßeinrichtung und der Hochdruckpumpe vorhanden ist . Um zu verhindern, daß die Hochdruckpumpe Kraftstoff ansaugt, muß der Öffnungsdruck wenigstens eines Saugventils der Hochdruckpumpe entsprechend hoch eingestellt sein, wodurch jedoch der Liefergrad der Hochdruckpumpe ungünstig beeinflußt wird. Insgesamt ist somit ein aufwendiger Aufbau und eine aufwendige Fertigung der Kraftstoffeinspritzeinrichtung erforderlich.Depending on the stroke, the outer jacket has a flow cross-section from the feed pump to the high-pressure pump. In a closed position of the valve member, this is with its outer jacket in Cover with the drain opening so that the flow cross-section is completely closed. However, since the valve member must be displaceable in the cylinder bore of the valve housing, there is a small gap between the outer casing and the cylinder bore through which a leakage amount of fuel can pass and reach the high-pressure pump via the drain opening, even if due to the operating parameters of the internal combustion engine, for example in the Thrust operation, through which the high-pressure pump is not allowed to deliver fuel, with a so-called zero delivery. Measures are therefore necessary in order to discharge this amount of fuel leakage so that it cannot reach the high-pressure pump and zero delivery is achieved. For this purpose, a throttled connection to a relief area can be provided, but then fuel constantly flows into the relief area after the fuel metering device and there is also an increased pressure level between the fuel metering device and the high-pressure pump. In order to prevent the high-pressure pump from sucking fuel, the opening pressure of at least one suction valve of the high-pressure pump must be set correspondingly high, but this has an adverse effect on the delivery rate of the high-pressure pump. Overall, a complex structure and a complex production of the fuel injection device are therefore required.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Kraftstoffeinspritzeinrichtung mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, daß durch das Ventilglied, wenn dieses zur Nullförderung den Durchflußquerschnitt zwischen der Förderpumpe und der Hochdruckpumpe verschließt, eine Verbindung zu einem Entlastungsbereich geöffnet wird, in den durch die Förderpumpe geförderter Kraftstoff oder infolge einer Leckage in der Kraftstoffzumeßeinrichtung noch zur Hochdruckpumpe gelangender Kraftstoff abfließen kann. Kraftstoff strömt somit nur bei Nullförderung in den Entlastungsbereich ab, wenn durch die Hochdruckpumpe kein Kraftstoff gefördert werden soll . Somit ist insbesondere auch beim Starten der Brennkraftmaschine, wenn eine große Kraftstoffmenge durch die Hochdruckpumpe gefördert werden muß, ein Verlust an Kraftstoff enge vermieden. Zwischen der Kraftstoffzumeßeinrichtung und der Hochdruckpumpe ergibt sich nur ein geringer Druck, da durch das Ventilglied der Durchflußquerschnitt verschlossen und die Verbindung zum Entlastungsbereich geöffnet ist, <-durch die von der Förderpumpe geförderter Kraftstoff oder infolge der Leckage noch zur Hochdruckpumpe gelangender Kraftstoff abgeleitet wird, so daß der Öffnungsdruck wenigstens eines Saugventils der Hochdruckpumpe niedrig eingestellt werden kann und dennoch die Nullförderung sichergestellt ist. Dies ermöglicht eine gute Befüllung und einen guten Liefergrad der Hochdruckpumpe. Vorteilhaft bei der Verbindung des Ablaufs der Kraftstoffzumeßeinrichtung zur Hochdruckpumpe hin mit dem Entlastungsbereich ist, daß dabei zwischen derThe fuel injection device according to the invention with the features according to claim 1 has the advantage that the valve member, when this closes the flow cross-section between the feed pump and the high-pressure pump for zero delivery, opens a connection to a relief region into which the fuel delivered by the delivery pump or as a result a leak in the fuel metering device High pressure pump fuel can drain. Fuel therefore only flows into the relief area at zero delivery if no fuel is to be delivered by the high-pressure pump. Thus, especially when starting the internal combustion engine, when a large amount of fuel has to be delivered by the high-pressure pump, a loss of fuel is narrowly avoided. There is only a small pressure between the fuel metering device and the high-pressure pump, since the flow cross-section is closed by the valve member and the connection to the relief area is open, <-through which the fuel delivered by the feed pump or due to the leakage fuel reaching the high-pressure pump is discharged, so that the opening pressure of at least one suction valve of the high-pressure pump can be set low and zero delivery is nevertheless ensured. This enables good filling and a good delivery rate of the high pressure pump. It is advantageous when connecting the flow of the fuel metering device to the high-pressure pump with the relief area that between the
Förderpumpe und der Kraftstoffzumeßeinrichtung der Förderdruck der Förderpumpe aufrechterhalten bleibt, wodurch Unstetigkeiten im Druckverlauf vor derDelivery pump and the fuel metering the delivery pressure of the delivery pump is maintained, which causes discontinuities in the pressure curve before
Kraftstoffzumeßeinrichtung vermieden werden und dadurch eine verbesserte Einstellung des Drucks im Speicher mittels der Kraftstoffzumeßeinrichtung ermöglicht ist. Außerdem sind durch die Merkmale des Anspruchs 1 der Aufbau und die Fertigung der Kraftstoffeinspritzeinrichtung entsprechend vereinfacht, da keine zusätzlichen Maßnahmen für die Nullförderung erforderlich sind.Fuel metering device are avoided and thereby an improved setting of the pressure in the memory is made possible by means of the fuel metering device. In addition, the structure and manufacture of the fuel injection device are correspondingly simplified by the features of claim 1, since no additional measures for zero delivery are required.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Kraftstoffeinspritzeinrichtung angegeben. Die Merkmale gemäß den Ansprüchen 2 bis 6 ermöglichen einen einfachen Aufbau der Kraftstoffzumeßeinrichtung. ZeichnungAdvantageous refinements and developments of the fuel injection device according to the invention are specified in the dependent claims. The features according to claims 2 to 6 allow a simple structure of the fuel metering device. drawing
Mehrere Ausführungsbeispiele der Erfindung sind in derSeveral embodiments of the invention are in the
Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert . Es zeigen Figur 1 eineDrawing shown and explained in more detail in the following description. 1 shows a
Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine in schematischer Darstellung, Figur 2 in vergrößerter Darstellung eine Kraftstoffzumeßeinrichtung derFuel injection device for an internal combustion engine in a schematic representation, Figure 2 in an enlarged view a fuel metering device
Kraftstoffeinspritzeinrichtung gemäß einem ersten Ausführungsbeispiel mit einem Ventilglied in einer ersten Stellung, Figur 3 die Kraftstoffzumeßeinrichtung mit dem Ventilglied in einer zweiten Stellung, Figur 4 die Kraftstoffzumeßeinrichtung gemäß einem zweiten Ausführungsbeispiel und Figur 5 die Kraftstoffzumeßeinrichtung gemäß einem dritten Ausführungsbeispiel .Fuel injection device according to a first embodiment with a valve member in a first position, Figure 3 shows the fuel metering device with the valve member in a second position, Figure 4 shows the fuel metering device according to a second embodiment and Figure 5 shows the fuel metering device according to a third embodiment.
Beschreibung der AusführungsbeispieleDescription of the embodiments
In Figur 1 ist eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine beispielsweise eines Kraftfahrzeugs dargestellt . Die Brennkraftmaschine ist vorzugsweise eine selbstzündende Brennkraftmaschine und weist einen oder mehrere Zylinder auf . Das Kraftfahrzeug weist einen Kraftstoffvorratsbehälter 10 auf, in dem Kraftstoff für den Betrieb der Brennkraftmaschine bevorratet ist . Die Kraftstoffeinspritzeinrichtung weist eine Förderpumpe 12 auf, durch die Kraftstoff aus dem Kraftstoffvorratsbehälter 10 zu wenigstens einer Hochdruckpumpe 14 gefördert wird. Die Hochdruckpumpe 14 fördert Kraftstoff in einen Speicher 16, der beispielsweise rohrförmig oder in beliebiger anderer Form ausgebildet sein kann. Vom Speicher 16 führen Leitungen 18 zu an den Zylindern der Brennkraftmaschine angeordneten Injektoren 20 ab. An den Injektoren 20 ist jeweils ein elektrisches. Steuerventil 22 angeordnet, durch das eine Öffnung der Injektoren gesteuert wird, um so eine Kraftstoffeinspritzung durch den jeweiligen Injektor 20 zu bewirken oder eine Kraftstoffeinspritzung zu verhindern. Die Steuerventile.-22 werden durch eine elektronischeFIG. 1 shows a fuel injection device for an internal combustion engine, for example of a motor vehicle. The internal combustion engine is preferably a self-igniting internal combustion engine and has one or more cylinders. The motor vehicle has a fuel reservoir 10 in which fuel is stored for the operation of the internal combustion engine. The fuel injection device has a feed pump 12, through which fuel is fed from the fuel tank 10 to at least one high-pressure pump 14. The high-pressure pump 14 pumps fuel into a reservoir 16, which can be tubular, for example, or in any other form. Lines 18 lead from the store 16 to injectors 20 arranged on the cylinders of the internal combustion engine. There is one on each of the injectors 20 electrical . Control valve 22 is arranged, through which an opening of the injectors is controlled so as to effect fuel injection by the respective injector 20 or to prevent fuel injection. The control valves.-22 are controlled by an electronic
Steuereinrichtung 23 angesteuert, durch die in Abhängigkeit von Betriebsparametern der Brennkraftmaschine, wie beispielsweise Drehzahl, Last, Temperatur und weiteren, der Zeitpunkt und die Dauer der Kraftstoffeinspritzung durch die Injektoren 20 bestimmt wird. Von den Injektoren 20 führt ein Rücklauf für nicht verbrauchten Kraftstoff zumindest mittelbar beispielsweise über eine für alle Injektoren gemeinsame Leitung 24 in einen zum Kraftstoffvorratsbehälter 10 führenden Rücklauf. Vom Speicher 16 kann ebenfalls eine Leitung 26 als Rücklauf zum Kraftstoffvorratsbehälter 10 zurückführen, in der ein Druckbegrenzungsventil 28 angeordnet ist, um zu verhindern, daß sich im Speicher 16 ein unzulässig hoher Druck aufbaut.Control device 23 is controlled by which the time and duration of the fuel injection by the injectors 20 is determined as a function of operating parameters of the internal combustion engine, such as speed, load, temperature and others. A return for unused fuel leads from the injectors 20, at least indirectly, for example via a line 24 common to all injectors, into a return leading to the fuel reservoir 10. A line 26 can also return from the reservoir 16 as a return to the fuel reservoir 10, in which a pressure limiting valve 28 is arranged in order to prevent an inadmissibly high pressure from building up in the reservoir 16.
Die Hochdruckpumpe 14 wird mechanisch durch dieThe high pressure pump 14 is mechanically by the
Brennkraftmaschine und damit proportional zur Drehzahl der Brennkraftmaschine angetrieben. Die Förderpumpe 12 kann ebenfalls mechanisch durch die Brennkraftmaschine angetrieben werden, wobei für die Hochdruckpumpe 14 und die Förderpumpe 12 eine gemeinsame Antriebswelle vorgesehen sein kann. Die Förderpumpe 12 kann alternativ auch beispielsweise einen elektromotorischen Antrieb aufweisen.Internal combustion engine and thus driven proportional to the speed of the internal combustion engine. The feed pump 12 can also be driven mechanically by the internal combustion engine, wherein a common drive shaft can be provided for the high pressure pump 14 and the feed pump 12. The feed pump 12 may alternatively also have an electric motor drive, for example.
Die Hochdruckpumpe 14 kann als Radialkolbenpumpe ausgebildet sein und weist wenigstens ein, vorzugsweise mehrere mit gleichmäßigem Winkelabstand voneinander angeordnete Pumpenelemente 30 auf, die jeweils einen durch einen Polygon 32 in Verbindung mit einer Exzenterwelle in einer Hubbewegung angetriebenen, in einer Zylinderbohrung 33 geführten Pumpenkolben 34 aufweisen, der einenThe high-pressure pump 14 can be designed as a radial piston pump and has at least one, preferably a plurality of pump elements 30 arranged at a uniform angular distance from one another, each of which has a pump piston 34 driven in a stroke movement by a polygon 32 in connection with an eccentric shaft and guided in a cylinder bore 33, the one
Pumpenarbeitsraum 36 begrenzt. In der Verbindung des Pumpenarbeitsraums 36 mit dem Speicher 16 ist ein zum Speicher 16 hin öffnendes Rückschlagventil 38 als Auslaßventil angeordnet, durch das die Trennung zwischen dem Pumpenarbeitsraum 36 und dem Speicher 16 beim Saughub des Pumpenkolbens 34 erfolgt. In der Verbindung desPump working space 36 limited. In the connection of the Pump work chamber 36 with the accumulator 16, a check valve 38 opening towards the accumulator 16 is arranged as an outlet valve, by means of which the separation between the pump work chamber 36 and the accumulator 16 takes place during the suction stroke of the pump piston 34. In the connection of the
Pumpenarbeitsraums 36 mit der Förderpumpe 12 ist ein zum Pumpenarbeitsraum 36 hin öffnendes Rückschlagventil 39 als Saugventil angeordnet, durch das die Trennung zwischen dem Pumpenarbeitsraum 36 und der Förderpumpe 12 beim Förderhub des Pumpenkolbens 34 erfolgt. Während eines jeweiligenPump work chamber 36 with the feed pump 12 is a check valve 39 opening towards the pump work chamber 36 as a suction valve, through which the separation between the pump work chamber 36 and the feed pump 12 takes place during the delivery stroke of the pump piston 34. During each
Saughubs des Pumpenkolbens 34, wenn dieser sich radial nach innen bewegt, ist der Pumpenarbeitsraum 36 bei geöffnetem Saugventil 39 mit dem Auslaß der Förderpumpe 12 verbunden und wird mit Kraftstoff befüllt, wobei der Pumpenarbeitsraum 36 durch das geschlossene Auslaßventil 38 vom Speicher 16 getrennt ist. Während eines jeweiligen Förderhubs des Pumpenkolbens 34, wenn dieser sich radial nach außen bewegt, ist der Pumpenarbeitsraum 36 bei geöffnetem Auslaßventil 38 mit dem Speicher 16 verbunden und durch das geschlossene Saugventil 39 vom Auslaß der Förderpumpe 12 getrennt.Suction stroke of the pump piston 34, when it moves radially inward, the pump work chamber 36 is connected to the outlet of the feed pump 12 when the suction valve 39 is open and is filled with fuel, the pump work chamber 36 being separated from the accumulator 16 by the closed outlet valve 38. During a respective delivery stroke of the pump piston 34, when the latter moves radially outward, the pump working space 36 is connected to the accumulator 16 when the outlet valve 38 is open and is separated from the outlet of the delivery pump 12 by the closed suction valve 39.
Zwischen der Förderpumpe 12 und demBetween the feed pump 12 and the
Kraftstoffvorratsbehälter 10 sind vorzugsweise ein oder mehrere Filter angeordnet. Es kann beispielsweise ausgehend vom Kraftstoffvorratsbehälter 10 zunächst ein Grobfilter 40 und diesem nachgeordnet ein Feinfilter 42 vorgesehen sein, wobei der Feinfilter 42 oder der Grobfilter 40 zusätzlich einen Wasserabscheider aufweisen kann. Der Rücklauf 24 der Injektoren 20 kann auch in die Leitung zwischen dem Filter 40 und der Fδrderpumpe 12 führen.Fuel reservoir 10 are preferably arranged one or more filters. For example, starting from the fuel reservoir 10, a coarse filter 40 can be provided first, followed by a fine filter 42, whereby the fine filter 42 or the coarse filter 40 can additionally have a water separator. The return line 24 of the injectors 20 can also lead into the line between the filter 40 and the feed pump 12.
Zwischen der Förderpumpe 12 und der Hochdruckpumpe 14 ist eine Kraftstoffzumeßeinrichtung 44 angeordnet . Die Kraftstoffzumeßeinrichtung 44 weist ein beispielsweise durch einen elektrischen Aktor 45, vorzugsweise einenA fuel metering device 44 is arranged between the feed pump 12 and the high pressure pump 14. The fuel metering device 44 has, for example, an electrical actuator 45, preferably one
Elektromagneten oder einen Piezoaktor, betätigtes Regelventil 46 auf, durch das der Durchfluß von der Förderpumpe 12 zur Hochdruckpumpe 14 kontinuierlich verstellbar ist. Die Kraftstoffzumeßeinrichtung 44 wird ebenfalls durch die Steuereinrichtung 23 angesteuert, in der Weise, daß durch die Förderpumpe 12 eine Kraftstoffmenge der Hochdruckpumpe 14 zugeführt wird, die dann wiederum durch die Hochdruckpumpe 14 unter Hochdruck in den Speicher 16 gefördert wird, um im Speicher 16 einen vorgegebenen, von Betriebsparametern der Brennkraftmaschine abhängigen Druck aufrechtzuerhalten. Am Speicher 16 ist dabei ein Drucksensor 17 angeordnet, der mit der Steuereinrichtung 23 verbunden ist und dieser ein Signal für den tatsächlichen Druck im Speicher 16 zuführt.Electromagnets or a piezo actuator, operated Control valve 46 through which the flow from the feed pump 12 to the high pressure pump 14 is continuously adjustable. The fuel metering device 44 is also controlled by the control device 23, in such a way that a fuel quantity is supplied to the high-pressure pump 14 by the feed pump 12, which in turn is then pumped under high pressure into the memory 16 by the high-pressure pump 14 in order to have a predetermined value in the memory 16 to maintain pressure dependent on operating parameters of the internal combustion engine. A pressure sensor 17 is arranged on the accumulator 16, which is connected to the control device 23 and which supplies a signal for the actual pressure in the accumulator 16.
In den Figuren 2 und 3 ist die Kraftstoffzumeßeinrichtung 44 vergrößert gemäß einem ersten Ausführungsbeispiel dargestellt. Die Kraftstoffzumeßeinrichtung 44 weist als Teil des Regelventils 46 ein Ventilgehäuse 50 auf, in dem in einer Zylinderbohrung 52 ein als hohler Kolben ausgebildetes Ventilglied 54 verschiebbar geführt ist. Das Ventilglied 54 ist topfförmig ausgebildet, wobei dessen Boden 55 und dessen Mantel auch getrennte Bauteile sein können, die miteinander verbunden sind. Der Boden 55 des Ventilglieds 54 kann auch einen Magnetanker des Aktors 45 bilden. Der Boden 55 des Ventilglieds 54 weist wenigstens eine Öffnung 57 auf. In die Zylinderbohrung 52 im Ventilgehäuse 50 mündet beispielsweise zumindest annähernd axial eine Öffnung 56 eines zur Hochdruckpumpe 14 hin führenden Ablaufs. Das Ventilglied 54 weist mit seiner offenen Seite zur Öffnung 56 hin. Durch die wenigstens eine Öffnung 57 im Boden 55 ist das Ventilglied2 and 3, the fuel metering device 44 is shown enlarged according to a first embodiment. As part of the control valve 46, the fuel metering device 44 has a valve housing 50, in which a valve member 54 designed as a hollow piston is displaceably guided in a cylinder bore 52. The valve member 54 is cup-shaped, the bottom 55 and the jacket of which may also be separate components which are connected to one another. The bottom 55 of the valve member 54 can also form a magnet armature of the actuator 45. The bottom 55 of the valve member 54 has at least one opening 57. For example, an opening 56 of an outlet leading to the high-pressure pump 14 opens into the cylinder bore 52 in the valve housing 50 at least approximately axially. The valve member 54 faces the opening 56 with its open side. The valve member is through the at least one opening 57 in the base 55
54 zumindest annähernd druckausgeglichen. Auf der der Öffnung 56 abgewandten Seite des Ventilglieds 54 greift der Aktor 45 an diesem an. In die Zylinderbohrung 52 ist eine Abstützscheibe 58 eingesetzt, beispielsweise eingepresst, zwischen der und dem Boden des Ventilglieds 54 eine Feder 60 eingespannt ist, die in das Ventilglied 54 eintaucht. Die Abstützscheibe 58 kann in ihrer Lage in Richtung der Längsachse 53 der Zylinderbohrung 52 verstellbar sein, um so eine Einstellung der Vorspannung der Feder 60 zu ermöglichen. Die Abstützscheibe 58 weist eine Öffnung für den Durchtritt des durch die Öffnung 56 austretenden Kraftstoffs auf .54 at least approximately pressure equalized. On the side of the valve member 54 facing away from the opening 56, the actuator 45 engages it. A support disk 58 is inserted, for example pressed in, into the cylinder bore 52, between which and the bottom of the valve member 54 a spring 60 is clamped, which plunges into the valve member 54. The The position of the support disk 58 can be adjustable in the direction of the longitudinal axis 53 of the cylinder bore 52 so as to enable the prestressing of the spring 60 to be adjusted. The support disk 58 has an opening for the passage of the fuel escaping through the opening 56.
Am Mantel der Zylinderbohrung 52 mündet mit wenigstens einer Öffnung 62 ein Zulauf von der Druckseite der Förderpumpe 12 her. Es können auch mehrere Öffnungen 62 vorgesehen sein, die über den Umfang der Zylinderbohrung 52 verteilt angeordnet sind. Die Öffnung 62 kann als sich über einen Teil des Umfangs der Zylinderbohrung 52 erstreckender Schlitz ausgebildet sein. Das Ventilglied 54 weist in seinem Mantel entsprechend der Anordnung und Anzahl der Öffnungen 62 der Zylinderbohrung 52 wenigstens eine Öffnung 64 auf, die ebenfalls als sich über einen Teil des Umfangs des Ventilglieds 54 erstreckender Schlitz ausgebildet sein kann. Durch das Ventilglied 54 wird mit dessen wenigstens einer Öffnung 64 in Zusammenwirkung mit der wenigstens einenAn inlet from the pressure side of the feed pump 12 opens into the jacket of the cylinder bore 52 with at least one opening 62. A plurality of openings 62 can also be provided, which are arranged distributed over the circumference of the cylinder bore 52. The opening 62 can be formed as a slot extending over part of the circumference of the cylinder bore 52. The valve member 54 has in its jacket according to the arrangement and number of openings 62 of the cylinder bore 52 at least one opening 64, which can also be formed as a slot extending over part of the circumference of the valve member 54. Through the valve member 54 with its at least one opening 64 in cooperation with the at least one
Öffnung 62 der Zylinderbohrung 52 die Größe eines Durchflußquerschnitts in der Verbindung zwischen der Förderpumpe 12 und der Hochdruckpumpe 14 gesteuert . Je nach dem wie stark sich die Öffnung 64 des Ventilglieds mit der Öffnung 62 der Zylinderbohrung 52 überdeckt wird ein unterschiedlich großer Durchflußquerschnitt freigegeben. Die Größe des Durchflußquerschnitts wird durch das Ventilglied 54 abhängig von dessen Stellung in Richtung der Längsachse 53 der Zylinderbohrung 52 verändert. In Figur 2 ist das Ventilglied 54 in einer axialen Stellung dargestellt, in der sich dessen Öffnung 64 vollständig mit der Öffnung 62 der Zylinderbohrung 52 überdeckt und somit der maximale Durchflußquerschnitt freigegeben ist . In Figur 3 ist das Ventilglied 54 in einer axialen Stellung dargestellt, in der dieses durch den Aktor 45 gegen die Feder 60 nach links verschoben ist und sich dessen Öffnung 64 nicht mehr in Überdeckung mit der Öffnung 62 der Zylinderbohrung 52 befindet, so daß der Durchflußquerschnitt verschlossen ist.Opening 62 of the cylinder bore 52 controls the size of a flow cross section in the connection between the feed pump 12 and the high pressure pump 14. Depending on the extent to which the opening 64 of the valve member overlaps the opening 62 of the cylinder bore 52, a flow cross section of different sizes is released. The size of the flow cross section is changed by the valve member 54 depending on its position in the direction of the longitudinal axis 53 of the cylinder bore 52. In Figure 2, the valve member 54 is shown in an axial position in which its opening 64 completely overlaps with the opening 62 of the cylinder bore 52 and thus the maximum flow cross-section is released. In Figure 3, the valve member 54 is shown in an axial position in which it is displaced to the left by the actuator 45 against the spring 60 and the opening 64 is no longer in Overlap with the opening 62 of the cylinder bore 52, so that the flow cross section is closed.
Am Mantel der Zylinderbohrung 52 mündet außerdem in Richtung der Längsachse 53 der Zylinderbohrung 52 zur Öffnung 62 von der Abstützscheibe 58 weg versetzt wenigstens eine weitere Öffnung 66, von der eine Verbindung zu einem Entlastungsbereich abführt. Als Entlastungsbereich kann wie in Figur 1 dargestellt ein Rücklauf 24- zum Kraftstoffvorratsbehälter 10 oder wie in Figur 1 gestrichelt dargestellt die Saugseite der Förderpumpe 12 dienen. Das Ventilglied 54 weist in seinem Mantel in Richtung der Längsachse 53 zur Öffnung 64 zum Boden hin versetzt wenigstens eine weitere Öffnung 68 auf. Durch das Ventilglied 54 wird mit seiner Öffnung 68 die Verbindung zum Entlastungsbereich gesteuert. Die Öffnungen 66,68 in der Zylinderbohrung 52 und im Ventilglied 54 sind derart angeordnet, daß die Öffnung 68 mit der Öffnung 66 nicht in Überdeckung ist, wenn sich das Ventilglied 54 in axialen Stellungen befindet, in denen an den Öffnungen 62,64 ein Durchflußquerschnitt freigegeben wird wie in Figur 2 dargestellt. In dieser Stellung des Ventilglieds 54 wird durch dieses die Verbindung zum Entlastungsbereich verschlossen, so daß von der Förderpumpe 12 geförderter Kraftstoff nur zur Hochdruckpumpe 14 gelangen kann. DieAt least one further opening 66, from which a connection leads to a relief area, opens out on the jacket of the cylinder bore 52 in the direction of the longitudinal axis 53 of the cylinder bore 52 to the opening 62, offset from the support disk 58. A return line 24 to the fuel storage container 10 or, as shown in broken lines in FIG. 1, the suction side of the feed pump 12 can serve as the relief region. The valve member 54 has at least one further opening 68 offset in its jacket in the direction of the longitudinal axis 53 toward the opening 64 towards the bottom. Through the valve member 54, the connection to the relief region is controlled with its opening 68. The openings 66, 68 in the cylinder bore 52 and in the valve member 54 are arranged such that the opening 68 is not in register with the opening 66 when the valve member 54 is in axial positions, in which a flow cross-section at the openings 62, 64 is released as shown in Figure 2. In this position of the valve member 54, the connection to the relief region is closed thereby, so that fuel delivered by the feed pump 12 can only reach the high-pressure pump 14. The
Verbindung zum Entlastungsbereich wird durch das Ventilglied 54 geöffnet, wenn dieses bewirkt durch den Aktor 45 in axialer Richtung gegen die Feder 60 so weit verschoben ist, daß der Durchflußquerschnitt vollständig verschlossen ist, da sich die Öffnungen 62,64 nicht mehr überdecken, wie dies in Figur 3 dargestellt ist. Von der Förderpumpe 12 dann geförderter Kraftstoff kann nicht mehr zur Hochdruckpumpe 14 gelangen. Infolge einer Leckage zwischen dem Ventilglied 54 und der Zylinderbohrung 52 noch zur Hochdruckpumpe 14 gelangender Kraftstoff fließt durch die Öffnungen 66,68 zum Entlastungsbereich ab. In Zwischenstellungen des Ventilglieds 54 zwischen den beiden Endstellungen gemäß den Figuren 2 und 3 befindet sich die Öffnung 64 des Ventilglieds 54 nur teilweise in Überdeckung mit der Bohrung 62 am Mantel der Zylinderbohrung 52, so daß entsprechend ein kleinerer Durchflußquerschnitt als der maximaleConnection to the relief area is opened by the valve member 54 when this is caused by the actuator 45 in the axial direction against the spring 60 so far that the flow cross section is completely closed, since the openings 62, 64 no longer overlap, as shown in Figure 3 is shown. Fuel then delivered by the feed pump 12 can no longer reach the high-pressure pump 14. As a result of a leakage between the valve member 54 and the cylinder bore 52, fuel still reaching the high-pressure pump 14 flows out through the openings 66, 68 to the relief region. In intermediate positions of the Valve member 54 between the two end positions according to Figures 2 and 3, the opening 64 of the valve member 54 is only partially in register with the bore 62 on the jacket of the cylinder bore 52, so that accordingly a smaller flow cross-section than the maximum
Durchflußquerschnitt freigegeben wird, während die Verbindung zum Entlastungsbereich geschlossen bleibt. Es kann auch eine Stellung des Ventilglieds 54 geben, in der die Öffnung 68 des Ventilglieds 54 in teilweise Überdeckung mit der Öffnung 66 gelangt, so dass die Verbindung zum Entlastungsbereich freigegeben wird, während sich die Öffnung 64 des Ventilglieds 54 noch in teilweiser Überdeckung mit der Öffnung 62 befindet.Flow cross-section is released while the connection to the relief area remains closed. There may also be a position of the valve member 54 in which the opening 68 of the valve member 54 comes in partial overlap with the opening 66 so that the connection to the relief area is released while the opening 64 of the valve member 54 is still in partial overlap with the Opening 62 is located.
Zwischen der Förderpumpe 12 und derBetween the feed pump 12 and the
Kraftstoffzumeßeinrichtung 44 bleibt der Förderdruck der Förderpumpe 12 aufrechterhalten. Hierdurch wird eine zuverlässige Einstellung des Drucks im Speicher 16 durch die Kraftstoffzumeßeinrichtung 44 sichergestellt, da im Zulauf von der Förderpumpe 12 zu dieser nur geringeThe fuel metering device 44 maintains the delivery pressure of the delivery pump 12. This ensures a reliable setting of the pressure in the accumulator 16 by the fuel metering device 44, since only a small amount in the feed from the feed pump 12 to the latter
Druckschwankungen auftreten. Abweichend zu der vorstehend erläuterten Ausführung der Kraftstoffzumeßeinrichtung 44 kann auch vorgesehen sein, daß der Zulauf von der Förderpumpe 12 her und der Ablauf zur Hochdruckpumpe 14 hin miteinander vertauscht sind. Der Zulauf von der Förderpumpe 12 her mündet dann in der Öffnung 56 axial in die Zylinderbohrung 52 und der Ablauf zur Hochdruckpumpe 14 hin mündet in den Öffnungen 62 in die Zylinderbohrung 52. Bei der Nullförderung ist somit durch das Ventilglied 54 der Zulauf von der Förderpumpe 12 her mit dem Entlastungsbereich verbunden.Pressure fluctuations occur. In a departure from the embodiment of the fuel metering device 44 explained above, it can also be provided that the inlet from the feed pump 12 and the outlet to the high pressure pump 14 are interchanged. The inlet from the feed pump 12 then opens axially into the cylinder bore 52 in the opening 56 and the outlet to the high-pressure pump 14 opens into the cylinder bore 52 in the openings 62. At zero delivery, the inlet from the feed pump 12 is thus through the valve member 54 connected to the relief area.
In Figur 4 ist die Kraftstoffzumeßeinrichtung gemäß einem zweiten Ausführungsbeispiel dargestellt, bei dem der Aufbau im wesentlichen gleich ist wie beim ersten Ausführungsbeispiel . Abweichend zum ersten Ausführungsbeispiel weist das Ventilglied 54 beim zweiten Ausführungsbeispiel nur die wenigstens eine Öffnung 64 auf, durch die die Größe des Durchflußquerschnitts zwischen der Förderpumpe 12 und der Hochdruckpumpe 14 gesteuert wird. Die Zylinderbohrung 52 weist in ihrem Mantel die wenigstens eine Öffnung 62 und die in relativ großem axialem Abstand von dieser angeordnete wenigstens eine weitere Öffnung 66 auf, die die Verbindung zum Entlastungsbereich bildet . Die Freigabe der Öffnung 66 und damit die Verbindung zum Entlastungsbereich wird durch das Ventilglied 54 mit seinem Mantel derart gesteuert, daß die Öffnung 66 verschlossen ist, wenn sich das Ventilglied 54 mit der Öffnung 66 vollständig überdeckt, und daß die Öffnung 66 freigegeben wird, wenn sich das Ventilglied 54 nicht oder nur teilweise mit der Öffnung 66 überdeckt. Wie beim erstenFIG. 4 shows the fuel metering device according to a second exemplary embodiment, in which the structure is essentially the same as in the first exemplary embodiment. Different from the first In the exemplary embodiment, the valve member 54 in the second exemplary embodiment has only the at least one opening 64 through which the size of the flow cross section between the feed pump 12 and the high-pressure pump 14 is controlled. The cylinder bore 52 has in its jacket the at least one opening 62 and the at least one further opening 66 which is arranged at a relatively large axial distance therefrom and which forms the connection to the relief region. The opening of the opening 66 and thus the connection to the relief area is controlled by the valve member 54 with its jacket such that the opening 66 is closed when the valve member 54 completely overlaps the opening 66 and that the opening 66 is opened when the valve member 54 does not or only partially covers the opening 66. Like the first
Ausführungsbeispiel wird die Öffnung 66 und damit die Verbindung zum Entlastungsbereich durch das Ventilglied 54 verschlossen, solange durch das Ventilglied 54 mit den Öffnungen 62,64 ein Durchflußquerschnitt freigegeben wird. Erst wenn durch das Ventilglied 54 der Durchflußquerschnitt an den Öffnungen 62,64 zumindest annähernd verschlossen ist, wird die Öffnung 66 und damit die Verbindung zum Entlastungsbereich freigegeben.In the exemplary embodiment, the opening 66 and thus the connection to the relief region is closed by the valve member 54 as long as a flow cross-section is released by the valve member 54 with the openings 62, 64. Only when the flow cross-section at the openings 62, 64 is at least approximately closed by the valve member 54, is the opening 66 and thus the connection to the relief region released.
Wie beim ersten Ausführungsbeispiel angegeben können auch beim zweiten Ausführungsbeispiel der Zulauf von der Förderpumpe 12 her und der Ablauf zur Hochdruckpumpe 14 hin miteinander vertauscht sein, so daß der Zulauf in der Öffnung 56 und der Ablauf in den Öffnungen 62 in die Zylinderbohrung 52 mündet.As indicated in the first exemplary embodiment, the inlet from the feed pump 12 and the outlet to the high-pressure pump 14 can also be interchanged in the second embodiment, so that the inlet in the opening 56 and the outlet in the openings 62 open into the cylinder bore 52.
In Figur 5 ist die Kraftstoffzumeßeinrichtung gemäß einem dritten Ausführungsbeispiel dargestellt, bei dem der Aufbau wiederum im wesentlichen gleich ist wie beim ersten Ausführungsbeispiel. Abweichend zum erstenFIG. 5 shows the fuel metering device according to a third exemplary embodiment, in which the structure is again essentially the same as in the first exemplary embodiment. Different from the first
Ausführungsbeispiel mündet jedoch der Zulauf von der Förderpumpe 12 her in einer beispielsweise axial angeordneten Öffnung 156 in die Zylinderbohrung 152 und wenigstens eine Öffnung 162 des Ablaufs zur Hochdruckpumpe 14 hin mündet am Mantel der Zylinderbohrung 152. Am Mantel der Zylinderbohrung 152 mündet außerdem in axialer Richtung zur Öffnung 162 versetzt wenigstens eine weitere Öffnung 166, die eine Verbindung zu einem Entlastungsbereich bildet. Das Ventilglied 154' weist in seinem Mantel wenigstens eine Öffnung 164 auf, die in Zusammenwirkung mit der Öffnung 162 den Durchflußquerschnitt der Verbindung zwischen der Förderpumpe 12 und der Hochdruckpumpe 14 steuert . Das Ventilglied 154 weist in seinem Mantel wenigstens eine in Richtung der Längsachse 153 und über einen Teil des Umfangs verlaufende Nut 168 auf, durch die eine Verbindung zwischen der Öffnung 162 und der Öffnung 166 gesteuert wird. Wenn durch das Ventilglied 154 an den Öffnungen 162,164 ein Durchflußquerschnitt freigegeben wird, so befindet sich die Nut 168 nicht in Überdeckung mit der Öffnung 162, so daß Kraftstoff nur von der Förderpumpe 12 durch die Öffnungen 162,164 zur Hochdruckpumpe 14 gelangen kann. Wenn durch dasEmbodiment, however, opens the inlet of the Delivery pump 12 forth in an axially arranged opening 156, for example, into the cylinder bore 152 and at least one opening 162 of the outlet to the high-pressure pump 14 opens out at the jacket of the cylinder bore 152. At the jacket of the cylinder bore 152, at least one further opening opens in the axial direction to the opening 162 166, which connects to a relief area. The valve member 154 ' has at least one opening 164 in its jacket, which in cooperation with the opening 162 controls the flow cross section of the connection between the feed pump 12 and the high pressure pump 14. The valve member 154 has in its jacket at least one groove 168 running in the direction of the longitudinal axis 153 and over part of the circumference, through which a connection between the opening 162 and the opening 166 is controlled. If a flow cross-section is released through the valve member 154 at the openings 162, 164, the groove 168 is not in register with the opening 162, so that fuel can only reach the high-pressure pump 14 from the feed pump 12 through the openings 162, 164. If through that
Ventilglied 154 der Durchflußquerschnitt zumindest annähernd vollständig verschlossen wird, da sich die Öffnung 164 nicht mehr oder fast nicht mehr mit der Öffnung 162 überdeckt, so ist die Nut 168 in Überdeckung mit der Öffnung 162 und stellt eine Verbindung zur Öffnung 166 her. Kraftstoff fließt dann von der Öffnung 162 direkt zur Öffnung 166 und in den Entlastungsbereich.Valve member 154 of the flow cross-section is at least approximately completely closed, since the opening 164 no longer or almost no longer overlaps the opening 162, the groove 168 is in overlap with the opening 162 and establishes a connection to the opening 166. Fuel then flows from port 162 directly to port 166 and into the relief area.
Auch bei der Kraftstoffzumeßeinrichtung 44 gemäß dem dritten Ausführungsbeispiel können der Zulauf von der Förderpumpe 12 her und der Ablauf zur Hochdruckpumpe 14 hin miteinander vertauscht sein, so daß der Zulauf von der Förderpumpe 12 her in den Öffnungen 162 und der Ablauf in der Öffnung 156 in die Zylinderbohrung 152 mündet. Bei Nullförderung, wenn durch die Hochdruckpumpe 14 kein Kraftstoff in den Speicher 16 gefördert werden darf, wird der Aktor 45 der Kraftstoffzumeßeinrichtung 44 durch die Steuereinrichtung 23 derart angesteuert, daß das Ventilglied 54 bzw. 154 den Durchflußquerschnitt der Verbindung zwischen der Förderpumpe 12 und der Hochdruckpumpe 14 vollständig verschließt und der Ablauf von derAlso in the fuel metering device 44 according to the third embodiment, the inlet from the feed pump 12 and the outlet to the high-pressure pump 14 can be interchanged, so that the inlet from the feed pump 12 in the openings 162 and the outlet in the opening 156 in the Cylinder bore 152 opens. In the event of zero delivery, if no fuel may be conveyed into the accumulator 16 by the high-pressure pump 14, the actuator 45 of the fuel metering device 44 is controlled by the control device 23 such that the valve member 54 or 154 the flow cross-section of the connection between the feed pump 12 and the high-pressure pump 14 closes completely and the sequence of the
Kraftstoffzumeßeinrichtung 44 zur Hochdruckpumpe 14 hin mit dem Entlastungsbereich verbunden ist . Es herrscht somit bei Nullförderung auf der Saugseite der Hochdruckpumpe 14 nur ein geringer Druck. Durch die Kraftstoffzumeßeinrichtung 44 gelangt nur eine geringe Kraftstoffmenge infolge einer möglichen Leckage zwischen dem Ventilglied 54 bzw. 154 und der Zylinderbohrung 52 bzw. 152, die zum Entlastungsbereich abfließen kann. Dies ermöglicht eine Einstellung eines geringen Öffnungsdrucks des Saugventils 39 des wenigstens einen Pumpenelements der Hochdruckpumpe 14. Dies ermöglicht wiederum bei einer Kraftstofförderung durch die Hochdruckpumpe 14 eine gute Befüllung des Pumpenarbeitsraums 36 und einen guten Pumpenliefergrad. Die Feder 60 kann mit relativ hoher Steifigkeit ausgeführt werden, wodurch eine vorteilhafte Kennlinie der Kraftstoffzumeßeinrichtung 44 und damit der Hochdruckpumpe 14 erreicht werden kann. Durch das Ventilglied 54 bzw. 154 der Kraftstoffzumeßeinrichtung 44 kann mit dessen Öffnung 64 bzw. 164 ein großerFuel metering device 44 to the high pressure pump 14 is connected to the relief area. There is therefore only a low pressure on the suction side of the high-pressure pump 14 with zero delivery. Only a small amount of fuel passes through the fuel metering device 44 as a result of a possible leakage between the valve member 54 or 154 and the cylinder bore 52 or 152, which can flow off to the relief area. This enables a low opening pressure of the suction valve 39 of the at least one pump element of the high-pressure pump 14 to be set. This in turn enables a good filling of the pump working space 36 and a good pump delivery rate when the fuel is pumped by the high-pressure pump 14. The spring 60 can be designed with a relatively high rigidity, as a result of which an advantageous characteristic curve of the fuel metering device 44 and thus of the high-pressure pump 14 can be achieved. Through the valve member 54 or 154 of the fuel metering device 44, a large opening 64 or 164 can be opened
Durchflußquerschnitt freigegeben werden, so daß auch große Fördermengen der Hochdruckpumpe 14 gesteuert werden können.Flow cross section are released so that even large flow rates of the high pressure pump 14 can be controlled.
Von der Verbindung zwischen der Förderpumpe 12 und der Hochdruckpumpe 14 kann stromaufwärts vor derThe connection between the feed pump 12 and the high pressure pump 14 can be upstream of the
Kraftstoffzumeßeinrichtung 44 eine BypassVerbindung 70 in einen Antriebsbereich der Hochdruckpumpe 14 abführen, in der eine Drosselstelle 72 und ein Druckventil 74 angeordnet sind. Wenn stromabwärts nach der Förderpumpe 12 ein ausreichend hoher Druck herrscht, so öffnet das Druckventil 74 und gibt die Bypassverbindung 70 frei. Über die Bypassverbindung 70 wird dem Antriebsbereich der Hochdruckpumpe 14 Kraftstoff zu dessen Schmierung zugeführt. Durch die Drosselstelle 72 wird die Kraftsto fmenge, die über die Bypassverbindung 70 abfließt, begrenzt. Vom Antriebsbereich fließt Kraftstoff in den Rücklauf zumFuel metering device 44 discharges a bypass connection 70 into a drive area of high-pressure pump 14, in which a throttle point 72 and a pressure valve 74 are arranged. If there is a sufficiently high pressure downstream of the feed pump 12, the pressure valve 74 opens and releases the bypass connection 70. About the Bypass connection 70 is supplied to the drive area of high-pressure pump 14 for lubrication thereof. The throttle point 72 limits the amount of fuel that flows through the bypass connection 70. Fuel flows from the drive area to the return
Kraftstoffvorratsbehälter 10 ab. Es kann vorgesehen sein, daß zwischen dem Speicher 16 und den Injektoren 20 eine Druckerhδhungseinrichtung 76 angeordnet ist, durch die der im Speicher 16 herrschende Druck erhöht wird, so daß eine Kraftstoffeinspritzung durch die Injektoren 20 mit höheremFuel tank 10 from. It can be provided that a pressure-increasing device 76 is arranged between the accumulator 16 and the injectors 20, by means of which the pressure prevailing in the accumulator 16 is increased, so that fuel injection by the injectors 20 is higher
Druck als dem im Speicher 16 herrschenden Druck erfolgt. Von der Druckerhöhungseinrichtung 76 kann ein Rücklauf 78 abführen, der in die Verbindung zwischen der Förderpumpe 12 und der Hochdruckpumpe 14 stromaufwärts vor der Kraftstoffzumeßeinrichtung 44 mündet. Im Rücklauf 78 ist ein zur Verbindung hin öffnendes Rückschlagventil 80 angeordnet.Pressure takes place as the pressure prevailing in the memory 16. A return line 78 can lead away from the pressure increasing device 76 and opens into the connection between the feed pump 12 and the high pressure pump 14 upstream of the fuel metering device 44. A check valve 80 which opens towards the connection is arranged in the return 78.
Von der Verbindung zwischen der Förderpumpe 12 und der ■ Hochdruckpumpe 14 kann stromaufwärts vor der Kraftstoffzumeßeinrichtung 44 eine weitere Bypassverbindung 82 mit einer Drosselstelle 83 zu einem Rücklauf in den Kraftstoffvorratsbehälter 10 abführen, die eine Entlüftung ermöglicht. Außerdem kann von der Verbindung zwischen der Förderpumpe 12 und der Hochdruckpumpe 14 stromaufwärts vor der Kraftstoffzumeßeinrichtung 44 noch eine weitere Bypassverbindung 84 abführen, die zur Saugseite der Förderpumpe 12 oder in den Rücklauf 24 führt und in der ein zur Saugseite der Förderpumpe 12 oder zum Rücklauf 24 hin öffnendes Druckventil 85 angeordnet ist. Durch die Bypassverbindung 84 mit dem Druckventil 85 wird der in der Verbindung zwischen der Fδrderpumpe 12 und der Hochdruckpumpe 14 herrschende Druck begrenzt. From the connection between the feed pump 12 and the ■ high-pressure pump 14 is a further bypass connection 82 may be located upstream dissipate with a restrictor 83 to a return to the fuel reservoir 10, which allows venting before the fuel metering 44th In addition, a further bypass connection 84 can lead away from the connection between the feed pump 12 and the high-pressure pump 14 upstream of the fuel metering device 44, which leads to the suction side of the feed pump 12 or into the return line 24 and into which one leads to the suction side of the feed pump 12 or to the return line 24 towards opening pressure valve 85 is arranged. The bypass connection 84 with the pressure valve 85 limits the pressure prevailing in the connection between the delivery pump 12 and the high-pressure pump 14.

Claims

Ansprüche Expectations
1. Kraftstoffeinspritzeinrichtung für eine1. Fuel injector for one
Brennkraftmaschine mit einer Förderpumpe (12) , durch die Kraftstoff aus einem Kraftstoffvorratsbehälter (10) zur Saugseite wenigstens einer Hochdruckpumpe (14) gefördert wird, wobei die Hochdruckpumpe (14) abhängig von Betriebsparametern der Brennkraftmaschine Kraftstoff in einen Speicher (16) fördert, mit einerInternal combustion engine with a feed pump (12), through which fuel is conveyed from a fuel reservoir (10) to the suction side of at least one high-pressure pump (14), the high-pressure pump (14) delivering fuel into a memory (16) depending on operating parameters of the internal combustion engine, with a
Kraftstoffzumeßeinrichtung (44) zur Einstellung der durch die Hochdruckpumpe (14) in den Speicher (16) geförderten Kraftstoffmenge, wobei die Kraftstoffzumeßeinrichtung (44) einen Aktor (45) und ein durch diesen betätigtes RegelventilFuel metering device (44) for setting the amount of fuel delivered by the high-pressure pump (14) into the accumulator (16), the fuel metering device (44) having an actuator (45) and a control valve actuated by it
(46) aufweist, wobei das Regelventil (46) ein in einer Zylinderbohrung (52;152) eines Ventilgehäuses (50;150) geführtes Ventilglied (54 ,-154) aufweist, das durch den Aktor (45) gegen eine Rückstellkraft (60) verschiebbar ist, und wobei das Ventilglied (54; 154) in Zusammenwirkung mit einer am Mantel der Zylinderbohrung (52,-152) mündenden Öffnung (62,-162) eines Zulaufs von der Förderpumpe (12) her oder eines Ablaufs zur Hochdruckpumpe (14) hin einen Durchflußquerschnitt in der Verbindung der Förderpumpe (12) mit der Hochdruckpumpe (14) steuert, dadurch gekennzeichnet, daß durch das Ventilglied (54; 154) der Durchflußquerschnitt zumindest annähernd vollständig verschließbar ist und daß durch das Ventilglied (54; 154) außerdem eine Verbindung des Zulaufs von der Förderpumpe (12) her oder des Ablaufs zur Hochdruckpumpe (14) hin mit einem Entlastungsbereich gesteuert wird, die durch das Ventilglied (54; 154) freigegeben wird, wenn durch dieses der Durchflußquerschnitt verschlossen wird.(46), the control valve (46) having a valve member (54, -154) guided in a cylinder bore (52; 152) of a valve housing (50; 150), which is actuated by the actuator (45) against a restoring force (60) is displaceable, and the valve member (54; 154) in cooperation with an opening (62, -162) opening at the jacket of the cylinder bore (52, -152) of an inlet from the feed pump (12) or an outlet to the high-pressure pump (14 ) controls a flow cross-section in the connection of the feed pump (12) to the high-pressure pump (14), characterized in that the flow cross-section can be at least approximately completely closed by the valve member (54; 154) and that the valve member (54; 154) also a connection of the inlet from the feed pump (12) or the outlet to the high-pressure pump (14) is controlled with a relief area, which is controlled by the valve member (54; 154) is released when the flow cross-section is closed by this.
2. Kraf stoffeinspritzeinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der Ablauf zur Hochdruckpumpe (14) hin in einer Öffnung (56) in die Zylinderbohrung (52) mündet, daß der Zulauf von der Förderpumpe (12) her und die Verbindung zum Entlastungsbereich in jeweils wenigstens einer Öffnung (62,66) am Mantel der Zylinderbohrung (52) münden und daß durch das Ventilglied (54) mit seinem Mantel in Zusammenwirkung mit den Öffnungen (62,66) der Durchflüßquerschnitt in der Verbindung zwischen' der Förderpumpe (12) und der Hochdruckpumpe (14) und die Verbindung zum Entlastungsbereich gesteuert wird.2. Kraf material injection device according to claim 1, characterized in that the outlet to the high pressure pump (14) opens into an opening (56) in the cylinder bore (52) that the inlet from the feed pump (12) and the connection to the relief area in in each case at least one opening (62, 66) opens on the jacket of the cylinder bore (52) and that through the valve member (54) with its jacket, in cooperation with the openings (62, 66), the flow cross-section in the connection between ' the feed pump (12) and the high pressure pump (14) and the connection to the relief area is controlled.
3. Kraftstoffeinspritzeinrichtung nach Anspruch 2 , dadurch gekennzeichnet, daß das Ventilglied (54) hohl ausgebildet ist und in seinem Mantel jeweils wenigstens eine Öffnung (64; 68) aufweist, durch die in Zusammenwirkung mit den Öffnungen (62,66) am Mantel der Zylinderbohrung (52) der Durchflußquerschnitt in der Verbindung zwischen der Förderpumpe (12) und der Hochdruckpumpe (14) und die Verbindung zum Entlastungsbereich gesteuert wird.3. Fuel injection device according to claim 2, characterized in that the valve member (54) is hollow and each has at least one opening (64; 68) in its jacket, through which in cooperation with the openings (62,66) on the jacket of the cylinder bore (52) the flow cross section in the connection between the feed pump (12) and the high pressure pump (14) and the connection to the relief area is controlled.
4. Kraftstoffeinspritzeinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der Ablauf zur Hochdruckpumpe (14) hin und die Verbindung zum Entlastungsbereich jeweils in wenigstens einer Öffnung (162,166) am Mantel der Zylinderbohrung (152) münden, daß der Zulauf von der Förderpumpe (12) her in einer Öffnung (156) in die4. Fuel injection device according to claim 1, characterized in that the outlet to the high pressure pump (14) and the connection to the relief area each open into at least one opening (162, 166) on the jacket of the cylinder bore (152) that the inlet from the feed pump (12) forth in an opening (156) in the
Zylinderbohrung (152) mündet und daß durch das Ventilglied (154) mit seinem Mantel in Zusammenwirkung mit den Öffnungen (162,166) am Mantel der Zylinderbohrung (152) der Durchflußquerschnitt in der Verbindung zwischen der Förderpumpe (12) und der Hochdruckpumpe (14) und die Verbindung des Ablaufs zur Hochdruckpumpe (14) hin mit dem Entlastungsbereich gesteuert wird.Cylinder bore (152) opens and that through the valve member (154) with its jacket in cooperation with the openings (162,166) on the jacket of the cylinder bore (152) the flow cross section in the connection between the feed pump (12) and the high pressure pump (14) and Connection of the drain to the high pressure pump (14) is controlled with the relief area.
5. Kraftstoffeinspritzeinrichtung nach Anspruch 4, dadurch gekennzeichnet, daß das Ventilglied (154) in seinem5. Fuel injection device according to claim 4, characterized in that the valve member (154) in its
Außenmantel eine sich in Richtung von dessen Längsachse (153) erstreckende Nut (168) aufweist, die zur Freigabe der Verbindung zwischen dem Ablauf zur Hochdruckpumpe (14) hin und der Verbindung zum Entlastungsbereich mit der Öffnung (162) des Ablaufs am Mantel der Zylinderbohrung (152) in Überdeckung gelangt .Outer jacket has a groove (168) extending in the direction of its longitudinal axis (153), which to release the connection between the outlet to the high-pressure pump (14) and the connection to the relief area with the opening (162) of the outlet on the jacket of the cylinder bore ( 152) overlap.
6. Kraftstoffeinspritzeinrichtung nach Anspruch 4 oder 5, dadurch gekennzeichnet, daß das Ventilglied (154) hohl ausgebildet ist und in seinem Mantel wenigstens eine Öffnung (164) aufweist, durch die in Zusammenwirkung mit der Öffnung (162) des Ablaufs zur Hochdruckpumpe (14) hin am Mantel der Zylinderbohrung (152) der Durchflußquerschnitt in der Verbindung zwischen der Förderpumpe (12) und der Hochdruckpumpe (14) gesteuert wird.6. Fuel injection device according to claim 4 or 5, characterized in that the valve member (154) is hollow and in its jacket has at least one opening (164) through which in cooperation with the opening (162) of the outlet to the high pressure pump (14) the flow cross-section in the connection between the feed pump (12) and the high-pressure pump (14) is controlled towards the jacket of the cylinder bore (152).
7. Kraftstoffeinspritzeinrichtung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß die wenigstens eine Hochdruckpumpe (14) wenigstens ein Pumpenelement (30) mit einem Pumpenarbeitsraum (36) aufweist und daß zwischen der Kraftstoffzumeßeinrichtung (44) und dem Pumpenarbeitsraum (36) ein zum Pumpenarbeitsraum (36) hin öffnendes Saugventil (39) angeordnet ist. 7. Fuel injection device according to one of the preceding claims, characterized in that the at least one high-pressure pump (14) has at least one pump element (30) with a pump work space (36) and that between the fuel metering device (44) and the pump work space (36) to the pump work space (36) opening suction valve (39) is arranged.
EP03724838A 2002-09-25 2003-03-18 Fuel injection device for an internal combustion engine Withdrawn EP1546544A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10244551 2002-09-25
DE10244551A DE10244551A1 (en) 2002-09-25 2002-09-25 Fuel injection device for an internal combustion engine
PCT/DE2003/000883 WO2004029447A1 (en) 2002-09-25 2003-03-18 Fuel injection device for an internal combustion engine

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EP1546544A1 true EP1546544A1 (en) 2005-06-29

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US (1) US7156076B2 (en)
EP (1) EP1546544A1 (en)
JP (1) JP2006500504A (en)
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WO (1) WO2004029447A1 (en)

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DE10244551A1 (en) 2004-04-08
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JP2006500504A (en) 2006-01-05
US20050241616A1 (en) 2005-11-03

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