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
  • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
  • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
• • 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
  • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
  • F02M55/025—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
  • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
  • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • 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
  • F02M63/0205—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 for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
  • F02M63/0215—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 for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by draining or closing fuel conduits
• • 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 injection system for an internal combustion engine according to the preamble of claim 1.
• a fuel injection system of the aforementioned type is known from DE 195 48 610 Al. It is in this system, the volume of the downstream injection injector supplied limiting and additional as a quantity limiting valve also differential pressure dependent and working as a check valve, external energy controlled 2/2-way valve provided.
• the actuating device associated with the valve operates magnetically, and the valve body can be loaded in the direction of its open position via a restoring force formed by a variable electromagnetic field. This is intended to make possible an operation of the valve in which this is controlled as a function of operating parameters of the internal combustion engine, in particular as a function of the respectively permissible maximum injection volume of the downstream fuel injector.
• Such a design requires a high control effort and requires differential pressure dependent high actuating forces.
• the invention has the object of providing an injection system of the type mentioned in such a way that both the control effort and the energy requirements of the actuator are reduced, and this configuration due to a total of reduced energy consumption.
• the energy requirement of the valve is tiles limited in the upper limit substantially at the value ⁇ be required to overcome the differential force during normal operation that builds up in the respective phase between successive injections. If the injection injector operates without leakage or at least without leakage, only slight differences in pressure result, and the actuating force in the opening direction resulting from the pressure differences, that is to say from the differential pressure, is only slight. Greater pressure differences are an indicator of impermissible leakage or other disturbances in the transition from the valve to the subsequent injector, and such pressure differences corresponding forces should not be overcome consciously in the inventive solution, so that appropriate restoring forces are not applied.
• the overflow of the valve body of the injection injector on the upstream side valve preferably substantially throttle-free, so that resulting from such a throttling restoring forces are also not overcome in the supply of the fuel injector also corresponding throttle losses are avoided which reduces overall energy requirements.
• the actuating force of the actuating device for safe working also has to be only a relatively small safety threshold above the closing force, which corresponds to the pressure difference effective on the valve body during trouble-free operation of the injection injector and the injured injection injector, then no high safety marches are required for the design of the actuating device required, so that structurally simple and easy adjusting devices are used, in particular magnetic adjusting devices.
• the application of the teaching according to the invention is not limited to in the direction of the valve body of the injection injector on the upstream side valve overflowable ⁇ valves, but also in connection with valves to reali ⁇ Sieren whose valve body is traversed across the direction of adjustment and thus in his leadership differential pressure dependent is loaded, resulting from this differential pressure-dependent load of the respective adjustment counteracting frictional forces, so that these frictional forces have to be considered for the design of the adjusting device.
• valve upstream of the injection injector according to the invention can also be used in conjunction with injection injectors which, by design, operate with larger leaks.
• the valve can also work with throttled or unthrottled overflow of the valve body, structurally preferred but designed in particular with regard to an unthrottled or substantially unthrottled flow, it proves to be useful in the bypass valve to a storage unit be provided, which balances the respective leakage volume biased to operating pressure within the permissible leaks.
• a storage unit for such a storage unit according to the invention is a structure in which in a housing-side receiving space, a valve piston is provided displaceably adjustable and pressure-dependent adjustable against spring force, so that the piston can be moved to compensate for the leakage volume.
• the outlet-side bypass connection between the valve and the storage volume can be designed to extend over the storage volume, so that in the described structure of the storage With a displaceably guided in the receiving space, the storage volume delimiting valve piston the tightly guided valve piston can also be used to shut off the Spei ⁇ chervolumen against the drain-side connection to the injector, so that in uncontrolled outflow of fuel through the injector in case of malfunction of the injector on the Storage unit also a shut-off function can be perceived.
• a Mengenbegrenzungsventil which is designed as throttled overflowed Mengenbegrenzungsventil and the function of the uncontrolled supply of fuel to the combustion chamber of each cylinder to be supplied through Failure of the injector, for example, tearing off the nozzle cap and / or in case of failure of the valve, in particular snagging of the valve in its open position to prevent a further feed of fuel to the internal combustion engine.
• 1 is a schematic representation of an internal combustion engine with its fuel injection system
• valve 2 is a schematic sectional view of the valve according to the invention lying in the line connection of a high pressure source to an injector of the fuel injection system according to the invention in a preferred, inventive embodiment with overflow in the direction of adjustment
• 3 is a further schematic view in which the valve upstream of an overflowable Congressnbegrenzungsventil is part of a valve assembly
• FIG. 4 shows in a representation corresponding to FIG. 3 a valve arrangement in which the valve lies in the bypass to a flow control valve which can not be overflowed, upstream of which there is provided an overflowable quantity limiting valve, and
• Fig. 5 shows another design of a valve usable in the context of the invention in the scheme, wherein the valve is overflowed transversely to the direction of adjustment.
• FIG. 1 shows a fuel injection system 2 for an internal combustion engine 1 operating as a diesel engine.
• the injection takes place, as shown in the figure for a cylinder of the multi-cylinder internal combustion engine 1, each to a combustion chamber 3 via an injection nozzle 12 of an injection injector 7, which is connected to a fuel supply line 11, starting from a fuel tank 10, a low-pressure fuel pump , and arranged downstream as a high-pressure source, a high-pressure fuel pump 5 with downstream high-pressure accumulator 6 are arranged.
• a high-pressure fuel pump 5 with downstream high-pressure accumulator 6 From the high-pressure accumulator 6 from branching the supply of the individual cylinders associated injection injectors 7, wherein each of the injectors 7 is preceded by a respective valve assembly 8.
• the control of the injectors 7 takes place, as indicated schematically, via a control and regulation unit 4.
• the valve arrangement 8 shown only schematically in FIG. 1 is, as illustrated in FIGS. 3 and 4, formed by a valve 14 controlled according to the invention with external energy, or comprises such a valve 14.
• a valve 14 is shown in FIG Embodiment shown, the direction of flow is illustrated by the arrow 31.
• the valve 14 has as an adjustable locking member to a valve body 23 and comprises between inlet side and outlet-side sections 15 and 16 of the fuel supply line 11 lying and connected to these end pieces 27, 28 which are connected via an axial clamping connection 29 sealingly, wherein the clamping connection 29 is realized by designed as a hat-like clamping sleeves 36, 37 housing halves, the radial shoulders of the end pieces 27, 28 overlap.
• the outlet side, the portion 16 associated end piece 28 is formed as a receptacle for the valve body 23 and has a corresponding bore 30, which is widened in diameter relative to the cross section of the section 16 of the fuel supply line 11.
• the guided in the bore 30 valve body 23 runs with a poppet 33 on a seat surface 32 in the transition of the bore 30 on the section 16.
• the valve cone 33 is in turn connected to a shaft part of the valve body 23, which forms the armature 34 of a magnetic actuator 26 formed as a hollow shaft.
• the magnetic actuator 26 comprises a magnetic coil 35 which is arranged to surround the end piece 28 in a radial recess of the clamping sleeve 37 and in axial extension of a threaded neck of the clamping sleeve 36, which is overlapped by a discontinuing provided for clamping sleeve 37 collar and screwed against it.
• the valve body 23 flows centrally, in the region of the valve cone 33 overflowed circumferentially, and the respective free flow cross sections correspond in the open position of the valve body 23 substantially the flow cross sections in the sections 15, 16, so that in the Open position of the valve body 23 is given an at least largely unthrottled flow or overflow, which has at most a small actuating force in the direction of the closed position of the valve body 23, which is shown in Fig. 2, the result.
• Such a force in the closing direction instead of and / or in addition, are also applied via a support spring 46, as it is preferably arranged in extension of the armature 34 forming hollow shaft in support against the tail 27.
• the at least largely unthrottled flow or overflow is expedient, since the valve 14 is open during the injection phase and a reduction of the injection pressure would be associated with the throttling. Therefore, it is particularly the application of spring force to the valve body 23.
• the magnetic actuator 26 is energized as part of the generally designated 25 actuating device via the line connection 38, in the time range of injection of the injection injector 7, in the fuel supply line 11, the valve assembly 8, ie in particular the valve 14 according to the invention, which, as shown in FIG 1 indicated by dashed lines, thereby easily achieve that over the control and regulating unit 4 takes place an approximately simultaneous energization of the injector 7 and the magnetic actuator 26.
• the supply of fuel to the injector 7 is released via the valve 14 in the time range of the injection, and with completion of the respective injection is blocked via the valve cone 33 and the fuel flow in the direction of the injection injector 7.
• the injection injector 7 If the injection injector 7 operates leak-free or virtually leak-free, the injection injector 7 thus shows trouble-free operating behavior in accordance with its respective design, then there is substantially no pressure drop in the operating phase lying between successive injections in the outflow-side section 16 of the fuel feed line 11. Thus, there is no pressure difference between the inlet-side line section 15 and the outlet-side line section 16, which would prevent opening of the valve 14 by adjusting the valve body 23 via the magnetic actuator 26 whose actuating force is designed for undisturbed operation.
• Fig. 3 shows as part of the valve assembly upstream of the valve 14 a flow control valve 50.
• This includes a housing 51 and a receiving space 52 which lies in the flow path of the fuel supply line 11, wherein of the housing-side line parts of the inlet-side line part with 54 and the outgoing-side line part are designated by 55.
• valve piston 53 Between these line parts is located within the receiving space 52 of the valve piston 53, which is supported against the inlet direction (arrow 31) via a spring 56 and the counter to the spring force from its inlet-side stop position is adjustable in a drain-side stop position.
• the related stroke is designated H.
• a stroke volume H corresponding to the stroke H is delimited via the valve piston 53, which is at least equal, but preferably greater, than the maximum injection volume of the injection injector 7.
• Open valve 14 provided that the valve piston 53 is adjusted due to the given inflow side pressure against the force of the spring 56 by a stroke, to the a stroke volume correlates, which corresponds to the injection volume. If a discharge volume exceeding the tolerance value exceeds the maximum permissible injection volume, then the valve piston 53 moves into its blocking position.
• valve piston 53 moves only over a partial area of its maximum stroke H, and the displacement volume displaced so far is compensated in the injection pauses of the downstream injection injector 7, ie when the fuel supply to the combustion chamber 3 is switched off, by
• a leaking guide can be achieved by appropriate play measurement between valve piston 53 and receptacle 52, or else by throttling overflow paths provided elsewhere Ring collars 57 in the receptacle 52 sealingly guided and there are associated with these annular collars 57 throttling overflow 58.
• valve piston 63 This also lies axially between an inlet 64 and a drain 65, the inlet side being connected to the inlet-side connection 15 and the outlet side to the outlet-side connection 16 of the valve 14.
• the valve piston 63 is again loaded via a spring 66 on its inlet-side stop position, and to move against the force of the spring 66 in response to the pressure difference between the inlet side and outlet side in its drain-side stop position.
• the shut off via the valve piston 63 stroke volume is only with the outlet side port 16th the valve, or between the valve 14 and the injection injector 7 lying portion of the fuel supply line 11 in conjunction.
• valve 14 Closes the valve 14, so enter through the injector-side leakage outflow losses that would lead to a downstream pressure drop, if they were not compensated by the stored in the storage element 60 and pressurized fuel volume. If these outflow losses resulting in the respective phases of the non-injection are greater than permissible, they can no longer be compensated for via the volume of the storage unit 60. Accordingly, there are differences in pressure between the inlet side and the outlet side of the valve 14, by which this is kept closed. If the losses remain within the permissible limits, the storage volume in the injection phases is replenished in each case.
• Fig. 4 analogous to Fig. 3, upstream of the valve 14 upstream of a flow control valve 50 is provided which corresponds in construction and function that of FIG. 3. Reference is made to the relevant comments above.
• a solution for a valve 14 in the design of a slide valve 70 is shown in Fig. 5, which is overflowed to the direction of ü rule.
• the guer to the direction of flow überströmbare slider is designated 71, the overflow direction in turn illustrated by the arrow 31.
• the slide 71 assumes its blocking position, the adjusting device 72 is in turn illustrated as a magnetic adjusting device.
• the slider 71 is provided with an overflow opening 73, which is indicated by dashed lines.
• the situation shown corresponds to a closed position, and at a pressure difference between inflow side and outflow side of the slide 71 is acted upon guer to its direction of adjustment, resulting in the slide 71 to be intercepted shear forces corresponding frictional forces against the slide housing 74.
• the conditional by such pressure differences supporting forces between the slide 71 and the housing 74 are illustrated as transverse forces to the direction of adjustment of the slider by arrows 75.
• a corresponding power supply can, as already described, be limited according to the invention, so that at correspondingly high pressure differences of the corresponding, required to adjust the slide 71 actuating force requirement can not be met, with the result that at pressure differences exceeding the corresponding limits, the slider 71st remains in its blocking position and thus can not be adjusted in its open position despite appropriate action on the adjusting device 72, wherein with respect to the power requirement to take into account that possibly also the force of acting in the direction of the closed position spring 46 is overcome.

Landscapes

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

Applications Claiming Priority (2)

Publications (2)

Family

ID=37055099

Family Applications (2)

Family Applications Before (1)

Country Status (6)

Families Citing this family (4)

Family Cites Families (19)

• 2005
  • 2005-08-02 DE DE102005036780A patent/DE102005036780A1/de not_active Withdrawn
• 2006
  • 2006-07-31 DE DE502006005872T patent/DE502006005872D1/de active Active
  • 2006-07-31 EP EP06776522A patent/EP1920155B1/fr not_active Not-in-force
  • 2006-07-31 KR KR1020087005101A patent/KR101358851B1/ko not_active IP Right Cessation
  • 2006-07-31 WO PCT/EP2006/007560 patent/WO2007014734A1/fr active Application Filing
  • 2006-07-31 AT AT06776523T patent/ATE513987T1/de active
  • 2006-07-31 JP JP2008524416A patent/JP5122455B2/ja not_active Expired - Fee Related
  • 2006-07-31 KR KR1020087005103A patent/KR101231701B1/ko not_active IP Right Cessation
  • 2006-07-31 EP EP06776523A patent/EP1920156B1/fr not_active Not-in-force
  • 2006-07-31 AT AT06776522T patent/ATE454550T1/de active
  • 2006-07-31 WO PCT/EP2006/007559 patent/WO2007014733A1/fr active Application Filing
  • 2006-07-31 JP JP2008524417A patent/JP4869346B2/ja not_active Expired - Fee Related

Non-Patent Citations (1)

Also Published As

Similar Documents

Legal Events