EP2310662A1 - Kraftstoff-injektor - Google Patents
Kraftstoff-injektorInfo
- Publication number
- EP2310662A1 EP2310662A1 EP09779562A EP09779562A EP2310662A1 EP 2310662 A1 EP2310662 A1 EP 2310662A1 EP 09779562 A EP09779562 A EP 09779562A EP 09779562 A EP09779562 A EP 09779562A EP 2310662 A1 EP2310662 A1 EP 2310662A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- fuel
- injector
- guide
- injection valve
- 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
Links
Classifications
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- 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
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
- F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
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- 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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
- F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
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- 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
- F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
- F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid pressure
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- 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
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- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
- F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
- F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
- F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
- F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions
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- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
- F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
- F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion
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- 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
- F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
- F02M2547/003—Valve inserts containing control chamber and valve piston
-
- 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
- F02M57/00—Fuel-injectors combined or associated with other devices
- F02M57/02—Injectors structurally combined with fuel-injection pumps
- F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
- F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
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- 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
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
- F02M63/008—Hollow valve members, e.g. members internally guided
Definitions
- the invention relates to a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.
- a trained as a common rail injector fuel injector which has a two-part injection valve element, which via a control valve (servo-valve) can be controlled.
- the two parts of the injection valve element are coupled together via a hydraulic coupler.
- the known fuel injector is low leakage, ie executed without low pressure stage.
- a closing throttle is introduced in a connection channel supplying fuel to a lower nozzle chamber.
- a disadvantage of the known fuel injector is that the two parts of the injection valve element do not react as a single part, but delayed in a control of the injection valve element. This can only be compensated by very fast switching control valves, which, however, is associated with higher costs.
- the invention is therefore based on the object to propose an alternative fuel injector, in which at least two injection valve element parts are coupled together via a low-leakage hydraulic coupler.
- the invention is based on the idea of achieving strong compression of the two separate injector element parts coupled by means of the hydraulic coupler in that the hydraulic coupler, more precisely a coupler space of the coupler, in particular permanently, with a low pressure source, in particular a connected to an injector return low pressure region of the injector is connected. Due to the reduced pressure within the hydraulic coupler compared to the high-pressure region of the fuel injector, the injection valve element parts are permanently and substantially interconnected during operation of the fuel injector, so that from a functional point of view they can be considered as one-piece.
- a fuel injector designed according to the concept of the invention provides that both guides are surrounded at least in sections radially outward with fuel under high pressure.
- the at least one injector component which delimits the guide gap radially outwardly, is surrounded by high-pressure fuel in an area radially outward of the respective guide gap formed between the at least one injector component and the injection valve element, thereby expanding the guide gaps by penetrating into the guide gaps High pressure fuel is avoided.
- a low-pressure stage is realized, which causes a force acting in the closing direction of the injection valve element hydraulic force.
- the injection valve element switching time can be accelerated. Since the closing force generated by the low-pressure stage, hydraulic, acting on the injection valve element, closing force is rail horrin, this closing force acts not only during the injection, as in a closing throttle, but permanently.
- an additional closing throttle which reduces the fuel pressure in the region of the injection valve element support in comparison to the fuel pressure in the region of an inlet passage of the fuel injector, is dispensed with. By providing a closing throttle, the effective injection pressure would be reduced by up to 150 bar.
- the low-pressure stage is preferably realized by reducing the diameter of the nozzle-hole-adjacent injection valve member member (nozzle needle) as compared to the diameter of the nozzle-hole-remote injector member member in a hydraulic coupler-limiting portion (something).
- the guide diameter of the guide facing the nozzle hole arrangement is preferably somewhat smaller than the guide diameter of the other, the hydraulic coupler axially delimiting (in particular upper) guide.
- the hydraulic coupler is connected via a connecting channel to a low pressure region of the fuel injector.
- the connecting channel at least approximately, throttle-free, prevails within the hydraulic coupler, at least approximately, low pressure, preferably in a pressure range between about 0 and 20 bar.
- At least one of the two, the hydraulic coupler limiting guides is formed by a sleeve-shaped extension of a plate member, said sleeve-shaped extension, at least partially, preferably completely, radially outwardly surrounded by under high pressure fuel is. It is particularly preferred to provide a portion of the connecting channel, in particular as a radial channel, in the plate element, which connects the hydraulic coupler to the low-pressure region of the fuel injector. In the low-pressure region of the fuel injector, not only the named connection channel but also a discharge channel from a control chamber, via which fuel flows out of the control chamber in the direction of the injector return when the control valve is open, preferably discharges.
- the plate member at least one, preferably throttle-free, axial channel is provided, can flow through the fuel with the injector element open in the axial direction of the nozzle hole arrangement. It is particularly expedient if the plate element is arranged between an (upper) injector body and a (lower) nozzle nozzle arrangement having a nozzle body, that is clamped between these housing parts. Preferably, the nozzle body is screwed by means of a union nut with an external thread of the injector body.
- At least one of the couplers axially delimiting guides is formed by a sleeve arranged in a high-pressure chamber, in particular spring-loaded sleeve.
- a sleeve arranged in a high-pressure chamber, in particular spring-loaded sleeve.
- the sleeve is pressed by the spring in the axial direction against the previously explained plate element is particularly expedient.
- this spring is at the same time the closing spring acting on an injection valve element part in the direction of the nozzle hole arrangement, which is located at one end on the sleeve and at other ends on the injection valve element part, in particular on a circumferential collar or a retaining ring of the injection valve element. element part, supports.
- the hydraulic coupler is placed at the low pressure applied to the injector return.
- the pressure in the hydraulic coupler is dimensioned such that it lies under the high pressure of the fuel outside the guides delimiting the hydraulic coupler but above the low pressure in the region of the injector return.
- at least one throttle is preferably applied in the connecting channel connecting the hydraulic coupler to the low-pressure region. assigns. This is adjusted so that the pressure in the hydraulic coupler is higher than in the area of the injector return. By implementing a higher (low) pressure in the hydraulic coupler compared to the low pressure in the injector return region, the component load in the area of the hydraulic coupler is reduced.
- the pressure in the hydraulic coupler is now load-dependent, it is preferred, in the case of providing such a throttle, to dispense with a low-pressure stage in the hydraulic coupler, so that the hydraulic coupler no longer has the function of a hydraulic Closing force to produce, but only a coupling function. Due to the slightly increased pressure in the hydraulic coupler, the already small amount of leakage, which flows through the guides into the hydraulic coupler and thus into the low-pressure area, is further reduced.
- the throttle is designed so that the pressure in the hydraulic coupler corresponds approximately to half the rail pressure.
- a closing throttle is preferably provided for generating a hydraulic closing force, which is dimensioned such that the pressure in the region of the tip of the injection valve element is lower, preferably by about 50 to 200 bar, than the rail pressure.
- An embodiment in which such a closing throttle is arranged in an injector component which delimits a control chamber radially on the inside is structurally particularly elegant.
- an inlet throttle for the control chamber and an outlet throttle from the control chamber and possibly also a filling throttle are preferred in this injector component. Throttle introduced for accelerated refilling the control chamber.
- Fig. 1 shows a first embodiment of a fuel injector with a connected to a low pressure region of the fuel Inj ector hydraulic coupler with low pressure stage and
- Fig. 2 shows an embodiment of a fuel injector with connected to a low pressure region of the fuel injector hydraulic coupler without low pressure stage and arranged in a connecting channel between the hydraulic coupler and the low pressure region throttle for adjusting the pressure in the hydraulic coupler.
- Fig. 1 is designed as a common rail injector fuel Inj ector 1 for injecting fuel into a combustion chamber, not shown, of an internal combustion engine an presented a motor vehicle.
- a high pressure pump 2 delivers fuel from a reservoir 3 in a high-pressure fuel storage 4 (Rail).
- this fuel especially diesel or gasoline, under high pressure, stored in this embodiment about 2000 bar.
- the fuel injector 1 is connected, among other injectors, not shown, via a supply line 5.
- the supply line 5 opens into a supply channel 6 of the fuel injector 1, which opens into a high-pressure chamber 7 of the fuel injector 1.
- the high-pressure chamber 7 forms a mini-rail, due to which pressure oscillations are minimized.
- a return line 8 a low-pressure region 9 of the fuel injector 1 is connected to the reservoir 3. Via an injector return port 10 and the return line 8, a control amount to be explained later as well as a small amount of leakage of fuel from the fuel injector 1 to the reservoir 3 can flow off.
- the fuel injector 1 has a housing 11, which has an injector body 12 into which the supply channel 6 is introduced and comprises a lower nozzle body 13. Between the injector body 12 and the nozzle body 13, a plate element 14 to be explained later is clamped, wherein the nozzle body 13 is braced against the plate element 14 by means of a union nut 15 and this in turn against the nozzle body 13.
- the union nut 15 is screwed to an external thread of the injector body 12.
- the head part of the housing 11 is formed by a clamping nut 16, which is screwed to the injector body 12, and which clamps a cover element 17, comprising the injector return port 10, against an electromagnet arrangement 18 of an electromagnetic actuator 19 to be explained later. which in turn rests in the axial direction on an inner shoulder 20 of the clamping nut 16.
- a two-part injection valve element 21 is accommodated in the housing 11, more precisely in the injector body 12 and in the duplex body 13, a two-part injection valve element 21 is accommodated.
- This comprises an upper, first part 22 (control rod) and a lower, second part 23 (nozzle needle).
- the first and the second part 22, 23 of the injection valve element 21 are coupled to each other via a hydraulic coupler 24 to be explained later and behave like a single component.
- the second, lower part 23 of the injection valve element 21 is guided in a guide bore 25 in the nozzle body 13.
- axial channels 26 are formed on the outer circumference of the second part 23 in an area within the guide bore 25, through which fuel can flow from the high-pressure chamber 7 into a lower annular space 67 when the injection valve element 21 is open, in which substantially the same fuel pressure prevails as in the high-pressure space 7.
- the axial channels 26 designed as bevels and an axial channel 66 in the plate element 14 are (at least approximately) throttle-free.
- the fuel pressure in a gap 27 formed between the plate element 14 and the guide bore 25 also corresponds to the fuel pressure within the high-pressure space 7.
- the closing throttle otherwise required in the prior art is used in the embodiment. Measure Fig. 1 (in contrast to the later still to be explained embodiment of FIG. 2) deliberately omitted.
- the injection valve element 21, more precisely the second part 23, has at its tip 28 a closing surface 29 with which the injection valve element 21 can be brought into tight contact with an injection valve element seat 30 (nozzle needle seat) formed inside the nozzle body 13.
- an injection valve element seat 30 nozzle needle seat
- the injection valve element 21 abuts against its injection valve element seat 30, i. is in a closed position, the fuel outlet from a Düsenlochanord- tion 31 is locked. If, on the other hand, it is lifted from its injection valve element seat 30 and is in an open position, here fuel can flow from the high-pressure chamber 7 via the intermediate space 27 and the lower annular space 67 past the injection valve element seat 30 to the nozzle hole arrangement 31 and essentially there under high pressure (rail pressure) standing in the combustion chamber are injected.
- a Steuerkam- mer 35 is limited, via a radially extending in the sleeve-shaped portion 33 inlet throttle 36 with high pressure Stagnant fuel from the high-pressure chamber 7 is supplied.
- the control chamber 35 is connected to a valve chamber 39 of a control valve 40 (servo-valve) via a drain throttle 38 provided in an upper, plate-shaped section 37 of the injector component 34.
- the valve chamber 39 is bounded radially outwardly by a sleeve-shaped control valve member 41, which is integral with one with the electromagnetic actuator 19 cooperating armature plate 42 is formed.
- the sleeve-shaped control valve element 41 is pressure balanced in its closed position in the axial direction.
- the control chamber 35 is bounded axially upward by a guide pin 43 which is axially supported on the cover member 17 and on the one hand has the task to guide the control valve member 41 during its adjustment and on the other hand to seal the valve chamber 39 in the axial direction upwards.
- the pressure in the control chamber 35 decreases rapidly, whereby the injection valve element 21 experiences a resulting opening force and abuts in the sequence with an end-side abutment portion 45 on the ceiling of the sleeve-shaped portion 33.
- the injection valve element 21 thus lifts off from its injection valve element seat 30, so that fuel can flow out through the nozzle hole arrangement 31.
- the energization of the solenoid assembly 18 of the electromagnetic actuator 19 is interrupted.
- the sleeve-shaped control valve element 41 moves back onto its control valve seat 44.
- the fuel flowing in through the inlet throttle 36 rapidly increases the pressure in the control chamber 35, as a result of which the injection valve element 21 is supported by the Spring force of a closing spring 47, is moved back to its injection valve element seat 30, which in turn the fuel flow from the Düsenlochan- Regulation 31 is interrupted in the combustion chamber.
- the filling of the control chamber 35 via the inlet throttle 36 is accelerated via a Ruddrossel 61 which connects the high pressure chamber 7 permanently hydraulically with the valve chamber 39. Possibly. can also be dispensed with this Feedbackrossel 61.
- the first and second parts 22, 23 of the injection valve element 21 are hydraulically coupled together in the hydraulic coupler 24, more specifically in a coupler space 48, and behave as a single component. This is due to the fact that the hydraulic coupler 24, or the coupler chamber 48 is permanently connected via a multi-part connecting channel 49 with the arranged in the injector low-pressure region 9 of the fuel injector 1, and thus during operation of the fuel injector 1 permanently low pressure.
- the connecting channel 49 is formed by a radial channel 50 provided in the plate element 14, an annular space 51 radially between the plate element 14 and the union nut 15 and a vertical channel 52 in the injector body 12.
- the hydraulic coupler 24 is limited in the embodiment shown in the axial direction upward by a first guide 53 for the first part 22 of the injection valve element 21 and in the axial direction down from a second guide 54 for the second, lower part 23 of the injection valve element 21st
- the first guide 53 comprises a first guide gap 55 (annular gap) radially between a sleeve-shaped extension 56 of the plate member 14 and a lower portion of the first part 22 of the injection valve element 21.
- the second guide 54 comprises a second guide gap 57 (annular gap) radially between a
- the closing spring 47 is supported at one end on the lower end face of the sleeve 58 and at the other end on a circumferential collar 59 of the second part 23 of the injection valve element 21 from the closing spring 47 spring-loaded sleeve 58 and an upper portion of the second part 23 of the injection valve element 21.
- the guide gaps 55, 57 are comparatively fuel-tight. This is primarily attributable to the fact that the first guide 53, more precisely the sleeve-shaped extension 56, is arranged inside the high-pressure chamber 7, that is to say is surrounded radially on the outside by high-pressure fuel. As a result, the first guide gap 55 experiences no expansion radially outward due to the low leakage flowing through the first guide gap 55 into the coupler space 48.
- the second guide 54 more precisely, the sleeve 58 is disposed within the gap 27, in which approximately the same pressure prevails as in the high-pressure chamber 7, so that the second guide gap 57 is not widened because the sleeve 58 radially outward from under high pressure Fuel is surrounded. As a result, the lever, which flows via the guides 53, 54 into the hydraulic coupler 24, is level, which continues to flow via the connecting channel 49 in the low-pressure region 9, low.
- a low-pressure stage 60 is realized in the hydraulic coupler 24, which has a force acting in the closing direction on the injection valve element 21.
- the low-pressure stage 60 is realized in that the diameter O 1 of the first part 21 in the region of the first guide 53 is (slightly) greater than the diameter Du of the second part 23 of the injection valve element 21 in the region of the second guide 54.
- the injection valve element 21 should only open when the control valve 40 can already be operated non-ballistically. Without the realized low-pressure stage 60, the start of injection can be delayed only for a mechanically soft injection valve element 21 or a small drain / inlet throttle ratio. Both measures lead to disadvantages in the injector behavior: While a soft injection valve element 21 leads to a poorer multiple injection suitability, a small drain / feed throttle ratio reduces the increase in the jet force of the injection jet and generally leads to emission disadvantages.
- a throttle 62 is integrated in the connecting channel 49, more precisely in the radial channel 50 between the hydraulic coupler 24 and the low-pressure region 9. This is designed so that approximately half the pressure prevails in the hydraulic coupler 24, more precisely in the coupler chamber 48, as in the high-pressure chamber 7 and in the intermediate space 27. This is achieved by the pressure drop across the guides 53, 54 being approximately equal to the Pressure drop at the throttle 62 corresponds.
- the effluent via the guide gaps 55, 56 leakage amount is further reduced.
- the component load of the plate member 14 and the sleeve 58 is reduced.
- the diameters O 1 and Du of the first and second part 22, 23 of the injection valve element 21 in the region of the guides 53, 54 are the same size - so it became aware of the realization of a low-pressure stage in the hydraulic coupler 24 omitted, since the pressure in the hydraulic coupler 24 by the provision of the throttle 62 is load-dependent and thus fluctuates during operation, which would result in fluctuating closing forces in the event that a low pressure stage would be provided in the coupler 24.
- the embodiment of FIG. 2 with a low pressure stage to equip for certain applications analogous to the embodiment of FIG. Due to the omission of a low-pressure stage, production-related and / or temperature-dependent guide leakage fluctuations on the guides 53, 54 do not affect the injector function.
- the fuel injector 1 according to FIG. 2 is equipped with an additional closing throttle 63, which is introduced into the sleeve-shaped section 33 of the injector component 34.
- This connects the high-pressure chamber 7 with an annular, additional inlet chamber 64, which surrounds the sleeve-shaped section 33 radially on the outside in comparison with FIG. 1, and which is sealed by way of an annular sealing element 65 with respect to the high-pressure space 7 serving as a minirail.
- the closing throttle 63 is designed in the illustrated embodiment so that the pressure in the high-pressure chamber 7 is about 50-200 bar less than the rail pressure in Zulaufhoffm 64.
- the inlet throttle 36 and the Golfdrossel 61 do not open the high-pressure chamber 7, but from the inlet chamber 64.
- the throttle 62 can, as shown, be designed as a simple throttle bore. Due to the necessary small flow cross sections which are necessary in the throttle 62, a conventional throttle bore, however, is relatively difficult to produce for reasons of tolerance. Therefore, it is preferable to perform the throttle 62 as an annular gap throttle. This can be achieved, for example, by positioning an insert part, for example a pin, in the actual throttle bore, on which the Fuel must flow past radially outside. The advantage of such a construction is the easier manufacturability.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200810040680 DE102008040680A1 (de) | 2008-07-24 | 2008-07-24 | Kraftstoff-Injektor |
PCT/EP2009/056467 WO2010009932A1 (de) | 2008-07-24 | 2009-05-27 | Kraftstoff-injektor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2310662A1 true EP2310662A1 (de) | 2011-04-20 |
EP2310662B1 EP2310662B1 (de) | 2013-01-02 |
Family
ID=41168644
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09779562A Not-in-force EP2310662B1 (de) | 2008-07-24 | 2009-05-27 | Kraftstoff-injektor |
Country Status (4)
Country | Link |
---|---|
US (1) | US8864054B2 (de) |
EP (1) | EP2310662B1 (de) |
DE (1) | DE102008040680A1 (de) |
WO (1) | WO2010009932A1 (de) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009000181A1 (de) * | 2009-01-13 | 2010-07-15 | Robert Bosch Gmbh | Kraftstoff-Injektor |
DE102013225384A1 (de) | 2013-12-10 | 2015-06-11 | Robert Bosch Gmbh | Kraftstoffinjektor |
DE102014205093A1 (de) | 2014-03-19 | 2015-09-24 | Robert Bosch Gmbh | Kraftstoffinjektor |
GB201421885D0 (en) * | 2014-12-09 | 2015-01-21 | Delphi International Operations Luxembourg S.�.R.L. | Fuel injector |
US10006429B2 (en) * | 2016-03-31 | 2018-06-26 | GM Global Technology Operations LLC | Variable-area poppet nozzle actuator |
CN114060193A (zh) * | 2020-08-04 | 2022-02-18 | 温特图尔汽柴油公司 | 大型柴油机的燃料喷射阀以及大型柴油机 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19500706C2 (de) | 1995-01-12 | 2003-09-25 | Bosch Gmbh Robert | Zumeßventil zur Dosierung von Flüssigkeiten oder Gasen |
JP2002529654A (ja) * | 1998-11-10 | 2002-09-10 | ガンサー−ハイドロマグ アーゲー | 内燃機関用燃料噴射バルブ |
DE10229418A1 (de) * | 2002-06-29 | 2004-01-29 | Robert Bosch Gmbh | Einrichtung zur Dämpfung des Nadelhubes an Kraftstoffinjektoren |
DE10248379A1 (de) * | 2002-10-17 | 2004-04-29 | Robert Bosch Gmbh | Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine |
DE102004005452B4 (de) * | 2004-02-04 | 2014-01-09 | Robert Bosch Gmbh | Düsenhalterkombination mit direktgesteuertem Einspritzventilglied |
DE102004035313A1 (de) * | 2004-07-21 | 2006-02-16 | Robert Bosch Gmbh | Kraftstoffinjektor mit zweistufigem Übersetzer |
DE102005016796A1 (de) * | 2005-04-12 | 2006-10-19 | Robert Bosch Gmbh | Zweistufig öffnender Kraftstoffinjektor |
DE102006008648A1 (de) | 2006-02-24 | 2007-08-30 | Robert Bosch Gmbh | Kraftstoffeinspritzvorrichtung für eine Brennkraftmaschine |
DE102007001363A1 (de) | 2007-01-09 | 2008-07-10 | Robert Bosch Gmbh | Injektor zum Einspritzen von Kraftstoff in Brennräume von Brennkraftmaschinen |
-
2008
- 2008-07-24 DE DE200810040680 patent/DE102008040680A1/de not_active Withdrawn
-
2009
- 2009-05-27 EP EP09779562A patent/EP2310662B1/de not_active Not-in-force
- 2009-05-27 WO PCT/EP2009/056467 patent/WO2010009932A1/de active Application Filing
- 2009-05-27 US US13/055,599 patent/US8864054B2/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO2010009932A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE102008040680A1 (de) | 2010-01-28 |
US20110139906A1 (en) | 2011-06-16 |
US8864054B2 (en) | 2014-10-21 |
EP2310662B1 (de) | 2013-01-02 |
WO2010009932A1 (de) | 2010-01-28 |
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