EP1799999A1 - Systeme de carburant pour un moteur a combustion interne - Google Patents

Systeme de carburant pour un moteur a combustion interne

Info

Publication number
EP1799999A1
EP1799999A1 EP05791897A EP05791897A EP1799999A1 EP 1799999 A1 EP1799999 A1 EP 1799999A1 EP 05791897 A EP05791897 A EP 05791897A EP 05791897 A EP05791897 A EP 05791897A EP 1799999 A1 EP1799999 A1 EP 1799999A1
Authority
EP
European Patent Office
Prior art keywords
pressure
fuel system
limiting device
valve
pressure limiting
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP05791897A
Other languages
German (de)
English (en)
Other versions
EP1799999B1 (fr
Inventor
Helmut Rembold
Richard Lorenz
Oliver Albrecht
Uwe Mueller
Tilman Miehle
Bernd Schroeder
Timm Hollmann
Christian Wiedmann
Stefan Smetana
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 EP1799999A1 publication Critical patent/EP1799999A1/fr
Application granted granted Critical
Publication of EP1799999B1 publication Critical patent/EP1799999B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0049—Combined valve units, e.g. for controlling pumping chamber and injection valve
    • 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
    • F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
    • 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
    • F02M63/005—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
    • F02M63/0012—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
    • F02M63/0052—Pressure relief valves with means for adjusting the opening pressure, e.g. electrically controlled
    • 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

Definitions

  • the invention relates to a fuel system for an internal combustion engine, with a Kraftstoff ⁇ pump, which promotes from a low pressure region in a high pressure region, with a metering device, with a reaching to the fuel pump volume flow can be changed, with a pressure limiting device, which limits a pressure in the high pressure region and a on the one hand by a spring and on the other side by the pressure prevailing in the high-pressure region pressure valve element has, and with a coupling device, which mechanically, at least temporarily and at least indirectly coupled to an actuating device of the metering device.
  • the invention also provides a method for operating a fuel system, as well as a corresponding computer program, and a method for producing a fuel system.
  • a fuel system of the aforementioned type is known from EP 0 974 008 B1.
  • the force acting in the closing direction of the pressure limiting device spring is supported in the known fuel system on a valve spool of the metering device.
  • the spring When open metering device, the spring is compressed, resulting in a correspondingly higher ⁇ fmungstik the pressure limiting device.
  • the spring When the metering device is closed, the spring is largely relaxed, so that the pressure limiting device is open.
  • This fuel system has the disadvantage that a large stroke of the valve spool of the metering device is required to effect a change in the ⁇ fmungstiks the pressure limiting device.
  • the Pressure limiting function of the pressure limiting device when the maximum holding pressure of the pressure limiting device in case of failure is less than the permissible pressure in the high pressure range, restricted. Is the maximum holding pressure of
  • Pressure limiting device in case of error greater than the permissible pressure in the high pressure area, an additional pressure relief device must be used.
  • Object of the present invention is to develop a fuel system of the type mentioned so that it can be produced inexpensively, compact builds, and the safety and reliability is guaranteed in all operating situations.
  • Valve element of the pressure limiting device at least indirectly acted upon by a force acting in ⁇ réelles ⁇ direction of the pressure limiting device force.
  • a single pressure relief device which serves as a safety device for protecting the high pressure area, and which can be used to set a desired pressure in the high pressure region with closed or almost closed metering device.
  • no additional actuator for the operation of the pressure limiting device is required, since this is the actuator of the metering device is used.
  • the actuating device of the metering device does not have to carry out a particularly large additional stroke in order to influence the pressure in the high-pressure region, since this influencing is not or at least not substantially accomplished by a stroke, but by a force acting in the direction of opening of the valve element of the pressure-limiting device.
  • the normal ⁇ ffhungstik the pressure limiting device can be set to a constant above the maximum occurring during normal operation of the fuel system fuel pressure, but below a critical pressure, for example, would lead to damage of the parts used in the high pressure area, or in which a function of injectors, which are connected to the high pressure area, is no longer guaranteed. This safety function is not affected by the coupling with the actuator.
  • the pressure limiting device can be used by the defined force that can exert the actuator of the metering device on the valve element of Druckbegrenzungs ⁇ device, also to an active pressure reduction or pressure control in certain operating situations of the fuel system.
  • active pressure reduction is, for example, desirable in a coasting operation or when the internal combustion engine is switched off, in order to have a lower pressure available when the internal combustion engine is put back into service.
  • a pressure reduction after switching off the engine for safety reasons and in the event of failure, service, or crash advantage.
  • valve element of the pressure limiting device only then at least indirectly applied to the force when the metering device is completely closed. This has the advantage that in normal operation, the pressure in the high-pressure region can be controlled or regulated exclusively by the volume flow control by means of the metering device. Such a fuel system works with very high efficiency.
  • the coupling device it is also possible for the coupling device to already act on the valve element of the pressure-limiting device at least indirectly with the force when the metering device is not yet completely closed.
  • the coupling device for example, is for lubrication - A - or cooling the fuel pump a certain minimum volume flow available.
  • the fuel system according to the invention is particularly compact when the metering device and the pressure limiting device are integrated in a common housing, in particular in a housing of the fuel pump.
  • the metering device comprises a valve slide on which a driver is attached or formed, which can engage a corresponding driver, which is coupled to the valve element of the pressure limiting device.
  • valve spool is received in a cylinder element and at its end facing away from the actuator has a pressure piece which can be pressed into the cylinder element and preferably receives the sealing seat of the pressure limiting device, it is possible to adjust the opening pressure of the pressure limiting device by a defined pressing of the pressure element in the cylinder element.
  • the individual components may be subject to higher tolerances, which reduces the manufacturing costs. Nevertheless, the opening pressure of the pressure limiting device can be optimally adjusted.
  • valve spool is connected via a connecting element with the actuating device.
  • the fuel system can be mounted in a particularly flexible manner and at the same time a possibly existing axial offset between the actuator and the valve spool can be compensated.
  • connection between the connecting element and the actuating device and / or between the connecting element and the valve slide is formed as a latching connection, the assembly of the elements designed as particularly simple and fast.
  • the pressure-limiting device comprises a plunger, which is coaxial with the valve slide, or a coaxial coupling element which is at least temporarily coupled to the valve element and to which the driver is present. Consequently certain liberties remain in the design of the valve element.
  • the plunger or the coaxial coupling element are integral with the valve element and preferably the driver. This reduces the manufacturing and in particular the assembly costs.
  • the coupling element has at least one support structure for the driver, which is latchably inserted into the valve spool is particularly advantageous. This construction makes it possible that the coupling element can be inserted into the valve slide, without a driver would have to be mounted separately.
  • valve slide of the metering device comprises a cavity into which the plunger or the coupling element protrudes and which forms a flow path for the outflowing when the pressure relief valve fuel.
  • the cavity is connected via at least one opening in the valve slide with the inlet of the metering device.
  • the force acting in the opening direction of the valve element of the pressure-limiting device depends on a current pressure prevailing in the high-pressure region.
  • the pressure limiting device can thus be used in this case for a regulation of the pressure prevailing in the high pressure region.
  • the assembly of the fuel system is particularly simple and flexible.
  • a reference volume flow of Metering unit and the ⁇ ffiiungstik the pressure limiting device can be easily adjusted and / or adapted.
  • Figure 1 is a schematic representation of a first embodiment of a fuel system of an internal combustion engine having a metering device and a coupled thereto pressure limiting device;
  • FIG. 2 shows a highlighted illustration of the metering device and the pressure limiting device of FIG. 1;
  • Figure 3 is a view similar to Figure 1 of an alternative embodiment of a fuel system
  • FIG. 4 shows a diagram in which a volume flow flowing through the metering device, an opening pressure of the pressure-limiting device, and a control stroke of a
  • Actuating the metering device are applied over a force exerted by the Betschistsein ⁇ direction force;
  • FIG. 5 shows a partial section through a specific embodiment of the metering device and the pressure limiting device of FIG. 1 in a first operating state
  • FIG. 6 shows a representation similar to FIG. 5, in a second operating state
  • Figure 7 is a perspective view of an element of the pressure limiting device of Figures 5 and 6;
  • Figure 8 is a perspective view of a driver of the metering device of Figures 5 and 6; 9 shows a partial section through a further concrete embodiment of the
  • FIG. 10 shows a section from FIG. 9
  • Figure 11 is a perspective view of an element of the pressure limiting device according to Figures 9 and 10;
  • Figure 12 is a perspective view of a driver of the metering device according to Figures 9 and 10;
  • FIG. 13 is a perspective view of assembly groups of the embodiment according to FIGS. 9 to 12.
  • a fuel system as a whole carries the reference numeral 100. It comprises a fuel reservoir 1, which is connected via a delivery line 2 to a prefeed pump 3. This pumps the fuel via a delivery line 4 into a control unit 5, to which reference will be made in detail below.
  • a fuel flow is adjusted and passed via a line 6 to a high-pressure pump 7.
  • the lines 4 and 6 are part of a low pressure area. Downstream of the feed pump 3 is connected to the delivery line 4, not shown in the figure mechanical pressure control valve, which ensures a defined inlet pressure of the high-pressure pump 7. From the pressure control valve, a return line, also not shown, leads back to the fuel tank 1.
  • the fuel In the high-pressure pump 7, the fuel is compressed to a high pressure. From the high pressure pump 7, the fuel passes under high pressure via a delivery line 8 in a
  • High-pressure accumulator 9 (common rail), which both form a high pressure area. This is connected to injection valves 10, which inject the fuel in only symbolically shown combustion chambers 11 of an internal combustion engine (without reference numeral). Via a line 12, the control unit 5 is hydraulically connected to the high-pressure accumulator 9. At the high-pressure accumulator 9, a pressure sensor 13 is further arranged, which is connected via a data line 14 with a control and regulating device 15. This is also connected via a data line 16 to the control unit 5. Via data lines 17 and 18, the control and regulating device 15 also receives signals from various sensors of the internal combustion engine.
  • control unit 5 is shown highlighted. It comprises a metering device 102 and a pressure limiting device 24.
  • the fuel passes from the fuel reservoir 1 via the line 4 into the control unit 5.
  • a throttle slide 20 of the metering device 102 measures the fuel, which then reaches the high pressure pump 7 via the line 6.
  • the throttle valve is positioned by an electromagnetic actuator 21 ("actuator") operating against a spring 22.
  • the pressure limiting device 24 In normal operation, the pressure limiting device 24 is closed; a spring 25, which acts on a non-visible in Figures 1 and 2 valve element of the pressure control device 24 in the closing direction, is correspondingly strongly biased.
  • the metering device 102 and the pressure control device 24 can be coupled together by two drivers 23 and 26. These two drivers form a coupling device 106 so far.
  • the first driver 23 is fixedly connected to the throttle slide 20 of the metering device 102 and the second driver 26 with the valve element of the pressure limiting device 24.
  • the electromagnetic actuator 21 of the throttle slide 20 In order to reduce the opening pressure of the pressure limiting device 24, the electromagnetic actuator 21 of the throttle slide 20 must move the driver 23 far as shown in Figures 1 and 2 to the right that he hits the driver 26 of the pressure limiting device 24 and exerts a force on this, the opposite acting in the closing direction of the pressure limiting device 24 force of the spring 25 acts. In total, this reduces the opening force or the opening pressure of the pressure limiting device 24.
  • FIG. 3 shows a variant of the fuel system 100.
  • those elements and regions which have equivalent functions to elements and regions of FIGS. 1 and 2 bear the same reference numerals. They are not explained again in detail.
  • the amount of fuel diverted by the pressure limiting device 24 is guided here via a separate line 19 to the fuel tank 1.
  • Metering device 102 are thus not directly connected to each other hydraulically.
  • An advantage of this embodiment may lie in a better fuel cooling.
  • FIG. 4 shows the basic profile of a volume flow Q through the throttle slide 20 of the metering device 102, the course of an opening pressure p of the pressure limiting device 24, and a control stroke s of the electromagnetic actuator 21 via its force F.
  • the electromagnetic actuator 21 is formed by a proportional magnet.
  • a force F 1 according to FIG. 4 thus corresponds to an energization I 1 of an electromagnet 37.
  • the volume flow Q reaching the high-pressure pump 7 is set by the metering device 102 the flow cross section of the throttle slide 20 is varied by a corresponding positioning of the electromagnetic actuator 21.
  • the stroke s of the throttle slide 20 is between Si and S 2 .
  • Pressure limiting device 24 is lowered.
  • the electromagnetic actuator 21 generates a force F 4 , prevails, still at a control stroke S 3 , equilibrium between the force acting in the closing direction spring 25 of the pressure limiting device 24 and the of Driver 23 and 26 applied in the direction of opening force, the ⁇ ffiiungstik the pressure limiting device 24 is thus zero in this case.
  • the force F 3 is greater than the force F 2 , as in
  • the excess amount of fuel discharged via the pressure limiting device 24 can be done both controlled and regulated.
  • the pressure in the high-pressure accumulator 9 is reported by the pressure sensor 13 to the control and regulating device 15 and compared with a desired value.
  • the drive for the electromagnetic actuator 21 is recalculated and output.
  • the force F 3 in which the driver 23 of the metering device 102 starts to engage the driver 26 of the pressure limiting device 24, smaller than the force F 2 , in which the metering device 102 is fully closed.
  • the valve element of the pressure limiting device 24 is thus opened by the stroke S 2 -S 3 .
  • a certain fuel volume flow continues to the high-pressure pump 7. This may be necessary for reasons of lubrication or cooling of the high-pressure pump 7. Again, the removal of excess fuel can be controlled or regulated.
  • the adjustment of the force exerted by the electromagnetic actuator 21 force can be carried out according to a computer program, which is stored in the control and regulating device 15 on a storage medium.
  • 5 shows a concrete embodiment of the control unit 5, wherein FIG. 5 shows an operating state in which the metering device 102 is decoupled from the pressure limiting device 24, whereas FIG. 6 shows an operating state in which the metering device 102 with the pressure limiting device 24 is coupled.
  • the throttle or valve spool 20 includes a piston 30 having a control edge 27 which is slidably received in a cylinder 31 forming a housing.
  • the driver 23 is fixed in the form of a disc in a slot (without reference numeral) of the piston 30.
  • An inlet opening 33 is hydraulically connected to the line 4 not shown in FIGS. 5 and 6.
  • An outlet opening 32 is hydraulically connected to the line 6, also not shown in Figures 5 and 6, which leads to the high-pressure pump 7.
  • the spring 22 presses a magnet armature 34 together with the piston 30 on a spacer 35, which is supported on the cylinder 31.
  • the outlet opening 32 is open, so that the fuel can pass from the inflow bore 33 via the outlet opening 32 to the high-pressure pump 7.
  • the magnetic coil 37 and the armature 34 of the electromagnetic actuator 21 includes in a conventional manner a counter-pole 38 which is connected via a preferably non-magnetic sleeve 39 with a connecting piece 36, which in turn is fixedly connected to the cylinder 31.
  • a pot 40th for magnetic return and for fixing the solenoid coil 37 is a pot 40th
  • the pressure limiting device 24 comprises the already mentioned in connection with the figures 1 and 3 spring 25, which is supported on a disc-shaped spring holder 41. This is welded to a plunger 108, at one end of a spherical valve element 42 is attached. This works with a stationary and rigidly connected to the cylinder 31
  • the end plate 26 forming the driver of the pressure limiting device 24 has on its lateral surface two opposing flattenings 52 (compare FIG.
  • the plunger 108 of the pressure limiting device 24 also has a flattening 53 between the valve element 42 and the spring holder 41.
  • the spring holder 41 shows several Through holes 54. Their function will be discussed below. Valve element 42, plunger 108, spring holder 41 and end plate 26 are made in one piece.
  • the piston 30 is provided in its left in Figures 5 and 6 area with a coaxial with its longitudinal axis and stepped cavity 48. In this projecting the plunger 108 with the driver or the end plate 26 into it.
  • the drive plate 23, which is shown in detail in Figure 8, is inserted at the left in Figures 5 and 6 end of the piston 30 in a slot (without reference numeral) of the wall of the piston 30, wherein a bore 55 in the drive plate 23 in Mounting position as a guide for the plunger 108 of the pressure limiting device 24 is used.
  • this has a slot 56.
  • the end plate 26 of the pressure limiting device 24 is located within the cavity 48 between the drive plate 23 and the piston 30th
  • a first axial position of the piston 30 there are a plurality of bores 49 leading out from the hollow space 48 (see FIG. Its axial position is chosen so that the cavity 48 is always connected to the inlet openings 33 in the cylinder 31, regardless of the position of the piston 30.
  • Sealing elements 44 and 45 serve to seal between a low-pressure region of the metering device 102 and a high-pressure region of the pressure-limiting device 24.
  • a sealing element 46 serves to seal between the inlet openings 33 and the outlet openings 32.
  • a sealing element 47 seals the structural unit shown in FIGS. 5 and 6 outward.
  • the control unit 5 shown in FIGS. 5 and 6 operates as follows:
  • the spring 22 acts on the armature 34 and the connected thereto piston 30 in Figures 5 and 6 to the left.
  • the solenoid 37 In the de-energized state of the solenoid 37 is thereby the Magnetic armature 34 pressed against the spacer 35, through which the inflated end position of the metering device 102 is defined. In this state, fuel passes unrestricted from the line 4, the inlet openings 33, and the outlet openings 32 to the line 6 and on to the high-pressure pump. 7
  • the fuel flows between the sealing seat 43 and the valve element 42, the flattening 53 on the plunger 108, the bores 54 in the spring holder 41, and the flats 52 on the end plate 26 in the Cavity 48 into it. From there, the fuel passes through the holes 49 and the inlet ports 33 in the line 4.
  • the line 4 is constantly connected via the holes 50 with the space (without reference numeral), in which the magnet armature 34 is arranged.
  • the lowering of the opening pressure of the pressure limiting device 24 by a corresponding energization of the electromagnet 37 comes into question above all when the internal combustion engine is operating in coasting mode and the injection valves 10 do not poll for fuel from the high-pressure reservoir 9, as well as when the internal combustion engine is switched off.
  • the control of the electromagnet 37 can also take place in the context of a closed loop on the basis of the signals that are transmitted from the pressure sensor 13 via the data line 14 to the control and regulating device 15.
  • the cylinder 31 forms a common housing for the metering device 102 and the pressure limiting device 24.
  • FIG. 9 shows a further embodiment of the metering device and the pressure limiting device when they are arranged in a pump housing; these are together part of a fuel system 100 '.
  • the fuel system 100 ' comprises a metering device, designated as a whole by 102', which can be actuated by an actuating device 21 'and can be coupled to a pressure-limiting device 24'.
  • the actuating device 21 ' has an electrical connection 201 in order to be able to energize a magnetic coil 202.
  • the magnet coil 202 is arranged on a winding support 203, which in turn is arranged in a magnet pot 40 '.
  • the actuator 21 'further includes a magnet armature 34', which with a
  • Magnetic needle 211 is connected.
  • the magnetic needle 211 is mounted in bushings 35 'and 35 ", and the bushing 35' is received in a connecting piece 36 'which has one end in the actuating device 21' and at its other end in its pump housing 110 is included.
  • the bush 35 " is received in a counter-pole element 38 ', which is connected to a closing element 205 of the actuating device 21'.
  • the connecting piece 36 ' is fastened via a weld 103 to the aforementioned pump housing 110.
  • the weld 103 seals the pump housing 110 to the outside.
  • the pump housing is shown only in sections and takes the metering unit 102 'and the pressure limiting device 24' on.
  • the pump housing 110 is supplied with fuel via the delivery line 4 and passes into a first annular space 60 via the metering device 102 'to a second annular space 62 and from there to an inlet valve 64.
  • the inlet valve 64 is followed by a working space 66 of a pump piston 68.
  • the pump piston 68 can be driven via a cam 70 so that high pressure can be applied to fuel present in the working space 68 and can be fed to the delivery line 8 via an outlet valve 72.
  • the pressure limiting device 24 ' has at its end remote from the actuating device 21' a pressure piece 260 which is pressed into a bore 58 which is provided in the pump housing 110. From the bore 58, a line 74 leads to the delivery line 8 in the high pressure region of the fuel system 100 '.
  • the connecting piece 36 ' is shown only in sections in FIG. 10 and has a cylindrical receptacle 218 on the side facing the pressure limiting device 24' into which a flange of a cylindrical element 31 'is pressed and secured there by means of a flanging 219.
  • the cylinder element 31 ' serves to receive a valve slide 30', which is acted upon by a spring 22 'with a compressive force.
  • the spring 22 ' is supported at its right end in FIG. 10 on the valve slide 30' and at its left end in FIG. 10 on the connecting piece 36 '.
  • the cylinder element 31 ' has an inlet opening 33' which extends beyond that shown in FIG.
  • Annulus 60 is connected to the line 4.
  • the cylinder element 31 'further has an outlet opening 32', which communicates via the annular space 62 shown in FIG. 9 with a line (not numbered) which is connected to the Inlet valve 64 leads.
  • the valve spool 30 ' is connected via a connecting element 220 to the actuating device 21' or via a needle head 212 to the magnetic needle 211 of the actuating device 21 '.
  • the connecting element 220 also has retaining elements 221 shown in FIG. 11, between which recesses 223 are provided, so that the retaining elements 221 are yielding in the radial direction.
  • the needle head 212 of the magnetic needle 211 is latchingly inserted into the connecting element 220.
  • the connecting element 220 has on the side facing away from the needle head 212 a total of four holding elements 222, between which recesses 224 are also provided.
  • the holding elements 222 are elastically yielding, so that they can dodge radially inward and can be inserted into the valve slide 30 'in order to engage there behind a shoulder 231 shown in FIG. 10 with projections 225 in a latching manner.
  • a coupling element designated as a whole by 280 which has a carrier structure 284 for carrier 26 'designated by 284 in FIG. 12, emerges in this cavity.
  • the support structure 284 is elongated and elastic, so that the coupling element 280 can be inserted latching in the valve slide 30 '.
  • the coupling element 280 has on its side facing away from the drivers 26 'a spring holder 41' on which a spring 25 'is supported. This spring is supported at its other end on an annular shoulder 244 of the cylinder member 31 'from.
  • a Kugelhanf ⁇ g 272 Adjacent to the guide portion 283, a Kugelhanf ⁇ g 272 is provided, in which a designed as a ball valve element 42 'is added.
  • the valve element 42 ' forms the sealing body for a sealing seat 43'.
  • the sealing seat 43 ' is pressed into the pressure piece 260 via a press-fit surface 264.
  • the pressure piece itself is pressed via a press-fit surface 263 in the bore 58 of the pump housing 110 shown in FIG.
  • FIGS. 9 and 10 show the metering unit 102 'and the pressure-limiting device 24' in their unactuated state.
  • the metering unit 102 ' supplies a maximum volume flow in this unactuated state, since a control edge 27' (see FIG.
  • valve slide 30 produces an unthrottled connection between inlet opening 33' and outlet opening 32 '.
  • the valve spool 30 ' is held in this position by means of the spring 22'.
  • the magnet armature 34' is moved together with the magnetic needle 211 in the direction of the end element 205 of the actuating device 21 '.
  • the spring 22 ' is compressed.
  • the magnetic needle 211 can transmit the movement to the valve spool 30 'via the needle head 212 and the connecting element 220.
  • the control edge 27 ', the outlet port 32' gradually close, so that the volume flow supplied to the downstream pump is throttled.
  • the described Abugeung of fuel can be done, for example. In overrun mode or when switching off the engine.
  • the Abberichtung can also be done when the fuel demand of the internal combustion engine is smaller than the leakage amount between Valve spool 30 'and the cylinder member 31' is formed. However, it is preferred if the Abgresung takes place only in overrun mode or when switching off the internal combustion engine.
  • a mounting unit which consists of a magnet assembly 291 and a
  • Hydraulic assembly 292 composed.
  • the latter includes u. a. the connecting piece 36 ', the cylinder element 31', the pressure piece 260 and the sealing seat 43 '.
  • the magnet assembly comprises the magnet pot 40 'with the electrical connection 201 and also the termination element 205.
  • the assembly of the fuel system 100 ' will be described in detail below.
  • the armature 34 ' is pressed by a defined amount on the magnetic needle 211.
  • the bush 35 is press-fitted into the opposite pole 38 'and the bush 35' is pressed into the joint 36.
  • the magnetic needle 211 is inserted into the bushings 35 'and 35".
  • the opposite pole 38 'and the connecting piece 36' are pressed into a sleeve 215.
  • the connector 220 is inserted into the valve slide 30 'detent, wherein provided on the holding elements 222 projections 225 engage behind the valve slide 30' provided paragraph 231 latching.
  • the spring 22' in the connector 36 ' is inserted.
  • the connecting piece 220 which is already connected to the valve slide 30 ', is pressed onto the needle head 212 so that it is latched within the holding elements 221.
  • a radial clearance may be present in order to be able to compensate for a deagification between said components.
  • valve slide 30 ' is inserted into the space 243 formed in the cylinder element 31'.
  • the cylinder element 31 ' is pre-pressed into the receptacle 218 of the connecting piece 36'.
  • the hydraulic module produced up to this point in time can be inserted into a test device and be adjusted so that a predetermined or desired volume flow (reference volume flow) results.
  • the hydraulic assembly is flowed through with a test medium.
  • the spring 22 ' With the aid of a magnetic coil of the test device, the spring 22 'is acted upon by a defined force, wherein the control edge 27' of the valve spool 30 'occupies a defined position.
  • the adjustment to the reference volume flow takes place by the cylinder element 31 'is pressed further into the receptacle 218 of the connecting piece 36' until the reference volume flow is established.
  • the cylinder member 31 'by means of flanging 219 on the connecting piece 36' additionally be secured.
  • an adjustment of the control behavior can also be made by the
  • Positions of the components to be positioned to be detected by a laser It is provided that the cylinder element 31 'within the receptacle 218 of the connecting piece 36' is displaced until a predetermined distance between the inlet opening 33 'and / or outlet opening 32' to the control edge 27 'is made. This distance corresponds to a predetermined volume flow.
  • the inlet opening 33 'and the outlet opening 32' can also be integrated in the valve slide 30 ', wherein the control edge is then formed by the cylinder element 31'. Also in this case, the setting of a desired control behavior as described above can be done with a test medium or by optical measurement.
  • the pressure limiting device 24 ' is mounted. First, the spring 25 'in the cylinder member 31' is inserted. Subsequently, the coupling element 280 in the spring 25 'and the valve slide 30' is used until the driver 26 'engage in recesses 232 which are formed in the valve slide 30'. In this case, the spring 25 'comes with the
  • This actual pressure value can be detected by a pressure sensor 13 shown in FIG. 1, to which the control or regulation unit 15 is transmitted in order to communicate there with one in the control and / or
  • Control device stored desired pressure value can be compared. From the difference value between the detected actual pressure value and the stored desired pressure value, the energization of the actuating device 21 'can be adjusted.
  • the adaptation can be carried out once, for example during commissioning of the internal combustion engine, but can also be carried out continuously or at specific time intervals, for example in order to be able to compensate for changes in the components during a long service life.
  • the opening pressure of the pressure limiting device 24 ' can also take place if it is mechanically coupled to the metering unit 102'.
  • a desired opening pressure correlates with a certain magnetic force, which can be applied, for example, by a mounting coil.
  • an association between the activation of the actuating device 21 'and thus the position of the armature 34' and the valve spool 30 'with the ⁇ ff Trentsdruck the pressure limiting device 24' is determined in the event that the pressure limiting device 24 'is coupled to the metering unit 102' ,
  • the sealing element 46 ' is mounted on the cylinder element 31'.
  • the assembly of the magnet assembly 291 ( Figure 13) is carried out by the coil 202 is wound on the winding support 203.
  • the coil 202 with the winding support 203 become relative positioned to the magnet pot 40 'and overmoulded with a plastic material.
  • the electrical connection 201 is formed.
  • the assembly of the thus formed hydraulic assembly 292 and the magnet assembly 291 in the pump housing 110 is carried out as follows: First, the hydraulic assembly 292 is inserted into the pump housing 110. When mounting the hydraulic assembly 292, the pressure piece 260 is pressed into the bore 58 of the pump housing 110. On the one hand, a fuel-tight connection can be achieved by the pressure and, on the other hand, the pressure force acting on the pressure piece 260 can be introduced into the pump housing 110. The hydraulic assembly 292 can be pressed into the pump housing 110 until the
  • Connecting piece 36 ' comes to rest with a formed in the pump housing 110 stop 266 ( Figure 9).
  • the required press-in force can, for example, be introduced via the connecting piece 36 '.
  • the sealing element 46 ' By the sealing element 46 ', the annular spaces 60 and 62 are sealed to each other.
  • the connector 36 ' is fixed to the pump housing 110 by means of the weld 103.
  • the weld 103 forms a fuel-tight connection.
  • the magnet assembly 291 is joined to the hydraulic assembly 292.
  • the pot 40 ' is pressed onto the connecting piece 36'.
  • the closing element 205 is pressed onto the opposite pole 38 '.

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

Système de carburant (100) pour un moteur à combustion interne qui possède une pompe (7) à carburant refoulant d'une zone de basse pression (4, 6) vers une zone de haute pression (8, 9). Un dispositif de dosage (102) modifie le débit volumétrique arrivant à la pompe (7) à carburant. La pression dans la zone de haute pression (8, 9) est limitée par un dispositif de limitation (24) de pression qui possède un élément soupape (42) subissant d'un côté l'action d'un ressort et de l'autre côté l'action de la pression régnant dans la zone de haute pression (8, 9). Ledit système comporte en outre un dispositif de couplage (106) qui couple mécaniquement, au moins temporairement et au moins indirectement, un dispositif d'actionnement (21) du dispositif de dosage (102) et le dispositif de limitation de pression (24). Selon la présente invention, le dispositif de couplage (106) exerce, en cas de fermeture ou de quasi-fermeture du dispositif de dosage (102), au moins indirectement une force agissant dans le sens d'ouverture du dispositif de limitation (24) de pression sur l'élément soupape (42) dudit dispositif de limitation de pression (24).
EP05791897A 2004-10-06 2005-08-24 Systeme de carburant pour un moteur a combustion interne Not-in-force EP1799999B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102004048598 2004-10-06
DE102005033636A DE102005033636A1 (de) 2004-10-06 2005-07-19 Kraftstoffsystem für eine Brennkraftmaschine
PCT/EP2005/054148 WO2006037693A1 (fr) 2004-10-06 2005-08-24 Systeme de carburant pour un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1799999A1 true EP1799999A1 (fr) 2007-06-27
EP1799999B1 EP1799999B1 (fr) 2010-01-06

Family

ID=35427958

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05791897A Not-in-force EP1799999B1 (fr) 2004-10-06 2005-08-24 Systeme de carburant pour un moteur a combustion interne

Country Status (3)

Country Link
EP (1) EP1799999B1 (fr)
DE (2) DE102005033636A1 (fr)
WO (1) WO2006037693A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080022974A1 (en) * 2006-07-28 2008-01-31 Caterpillar Inc. Multi-stage relief valve having different opening pressures
DE102008059638A1 (de) * 2008-11-28 2010-06-02 Continental Automotive Gmbh Hochdruckpumpe
JP5157976B2 (ja) * 2009-03-13 2013-03-06 株式会社デンソー 流量制御電磁弁
US8240291B2 (en) 2009-10-23 2012-08-14 Caterpillar Inc. Pressure relief valve
DE102013215085A1 (de) * 2013-06-24 2014-12-24 Robert Bosch Gmbh Druckregelventil mit Seitenkanal am Ventilstift

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19612413B4 (de) * 1996-03-28 2006-06-29 Siemens Ag Druckfluid-Versorgungssystem, insbesondere für ein Kraftstoff-Einspritzsystem
GB9610819D0 (en) * 1996-05-22 1996-07-31 Lucas Ind Plc Valve arrangement
DE19714489C1 (de) * 1997-04-08 1998-10-01 Siemens Ag Einspritzsystem, Druckventil und Volumenstromregelventil und Verfahren zum Regeln eines Kraftstoffdruckes

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2006037693A1 *

Also Published As

Publication number Publication date
EP1799999B1 (fr) 2010-01-06
DE502005008841D1 (de) 2010-02-25
DE102005033636A1 (de) 2006-04-20
WO2006037693A1 (fr) 2006-04-13

Similar Documents

Publication Publication Date Title
DE19640826B4 (de) Speicherkraftstoffeinspritzvorrichtung und Druckregelvorrichtung hierfür
DE19612413B4 (de) Druckfluid-Versorgungssystem, insbesondere für ein Kraftstoff-Einspritzsystem
EP2684200B1 (fr) Actionneur électromagnétique
EP1492954B1 (fr) Soupape reglable de regulation de pression pour systemes d'injection de carburant
WO2007009828A1 (fr) Pompe a carburant haute pression pour systeme d'injection de carburant de moteur a combustion interne
EP2888469B1 (fr) Système common rail
DE10320592A1 (de) Förderpumpe, insbesondere Hochdruck-Kraftstoffpumpe für eine Brennkraftmaschine
DE102010042194A1 (de) Vorrichtung zur Steuerung eines hydraulischen Speichers eines Hydrauliksystems
EP1509694B1 (fr) Accumulateur haute pression pour systemes d'injection de carburant avec soupape de regulation de pression integree
EP1561026A1 (fr) Unite de dosage de carburant pour systemes d'injection de carburant de moteurs a combustion
EP1799999B1 (fr) Systeme de carburant pour un moteur a combustion interne
EP1865192B1 (fr) Injecteur de carburant doté d'une assistance adaptative à la direction
EP2310662B1 (fr) Injecteur de carburant
EP2825766B1 (fr) Soupape de régulation de pression destinée à réguler la pression dans un réservoir de carburant à haute pression pour un moteur à combustion interne
EP3055549B1 (fr) Ensemble piston-conduit de fluide, en particulier ensemble piston de commande-alésage de commande
WO2002073028A2 (fr) Soupape a siege/coulisse comportant une tige de compensation de pression
DE102006000268A1 (de) Fluideinspritzventil
EP1262659A2 (fr) Système de combustible pour un moteur à combustion interne
EP2466108A1 (fr) Soupape d'injection de combustible
WO2002059475A1 (fr) Distributeur 3/2
WO2017097498A1 (fr) Soupape d'admission à commande électromagnétique et pompe haute pression munie d'une soupape d'admission
WO2017067715A1 (fr) Soupape d'admission à commande électromagnétique et pompe haute pression munie d'une soupape d'admission
DE102016219722A1 (de) Steuerbares Saugventil für eine Hochdruckpumpe, Hochdruckpumpe
DE102013224960A1 (de) Kraftstoffinjektor
DE102004048594A1 (de) Kraftstoffsystem, für eine Brennkraftmaschine, sowie Verfahren zum Betreiben eines Kraftstoffsystems

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20070507

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR IT

17Q First examination report despatched

Effective date: 20070917

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE FR IT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR IT

REF Corresponds to:

Ref document number: 502005008841

Country of ref document: DE

Date of ref document: 20100225

Kind code of ref document: P

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20101007

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100106

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20110502

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100831

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20131025

Year of fee payment: 9

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502005008841

Country of ref document: DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502005008841

Country of ref document: DE

Effective date: 20150303

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150303