EP1613856B1 - Injecteur de carburant comportant un transmetteur de pression commande par une soupape asservie - Google Patents

Injecteur de carburant comportant un transmetteur de pression commande par une soupape asservie Download PDF

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Publication number
EP1613856B1
EP1613856B1 EP04717030A EP04717030A EP1613856B1 EP 1613856 B1 EP1613856 B1 EP 1613856B1 EP 04717030 A EP04717030 A EP 04717030A EP 04717030 A EP04717030 A EP 04717030A EP 1613856 B1 EP1613856 B1 EP 1613856B1
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EP
European Patent Office
Prior art keywords
pressure
servo valve
space
piston
chamber
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.)
Expired - Fee Related
Application number
EP04717030A
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German (de)
English (en)
Other versions
EP1613856A1 (fr
Inventor
Matthias Eisenmenger
Hans-Christoph Magel
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Priority claimed from DE10325620A external-priority patent/DE10325620A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1613856A1 publication Critical patent/EP1613856A1/fr
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Publication of EP1613856B1 publication Critical patent/EP1613856B1/fr
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • 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
    • 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
    • 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
    • F02M57/026—Construction details of pressure amplifiers, e.g. fuel passages or check valves arranged in the intensifier piston or head, particular diameter relationships, stop members, arrangement of ports or 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
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • F02M63/0029—Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
    • 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
    • F02M63/0043—Two-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves

Definitions

  • a fuel injection device for internal combustion engines with a fuel injector with a pressure booster for increasing the injection pressure is known.
  • the pressure booster has a pressure booster piston which is exposed to respective pressure surfaces of a working space, a differential pressure chamber and a compression space.
  • the pressure intensifier and an injection valve member are driven by a servo valve comprising a switching element and a servo valve piston.
  • the servo valve piston acts on a valve member which, with a first sealing seat, separates a first hydraulic space under system pressure from a second hydraulic chamber connected to low pressure and connected to the return system.
  • the first hydraulic space is also connected via a control line to the differential space.
  • an opening force is exerted on the valve member via the valve piston, which opens the first valve seat and closes the second valve seat, which is assigned to a connection to the system pressure.
  • This is the result Control line, which leads into the differential pressure chamber of the pressure booster, connected via the opened first sealing seat with the low pressure side, so that the differential pressure chamber is disconnected from the system pressure.
  • the system pressure acting on the working space presses the pressure booster piston into the compression space, whereby fuel is compressed there and passed through a high-pressure line into a nozzle needle pressure chamber, thereby lifting the nozzle needle from the nozzle needle seat and injecting the fuel with the injection pressure boosted by the system pressure.
  • DE 101 23 914 has the subject of a fuel injection device for internal combustion engines with a fuel injector which can be supplied by a high-pressure fuel source. Between the fuel injector and the high-pressure fuel source is connected to a movable pressure booster piston having pressure booster.
  • the pressure booster piston separates a connectable to the high-pressure fuel source space from a high-pressure chamber connected to the fuel injector. By filling a rear space of the pressure booster device with fuel or by emptying the rear space of fuel, the fuel pressure in the high-pressure chamber can be varied.
  • the fuel injector has a movable closing piston for opening and closing injection openings.
  • the closing piston protrudes into a closing pressure chamber, so that the closing piston can be acted upon by fuel pressure in order to achieve a force acting on the closing piston in the closing direction.
  • the closing pressure chamber and the rear space are formed by a common closing pressure-return chamber, wherein all portions of the closing pressure-return space are permanently interconnected to exchange fuel.
  • a high-pressure chamber communicates with the high-pressure fuel source in such a way that, apart from pressure oscillations, at least the fuel pressure of the high-pressure fuel source can constantly be present in the high-pressure chamber, the pressure chamber and the high-pressure chamber passing through a common injection space be formed. All sections of the injection space are permanently connected to each other for the exchange of fuel.
  • DE 102 294 15.1 refers to a device for Nadelhubdämpfung pressure-controlled fuel injectors.
  • a device for injecting fuel into a combustion chamber of an internal combustion engine which comprises a fuel injector which can be acted upon by a high-pressure source with high-pressure fuel.
  • the fuel injector is actuated via a metering valve, wherein an injection valve member is enclosed by a pressure chamber and the injection valve member can be acted upon in the closing direction by a closing force.
  • the injection valve member is associated with a independently movable damping element, which limits a damping chamber and at least one overflow channel for connecting the damping chamber having a further hydraulic space.
  • the control of the fuel injector with a 3/2-way valve which may represent a cost effective and space-saving injector, but this valve has a relatively large return flow rate of the pressure booster has to control.
  • a servo valve designed as a 3/2-way valve which has a hydraulically effective surface which can be acted upon in the opening direction and which is constantly subjected to system pressure.
  • the system pressure corresponds to the pressure level prevailing in the high-pressure reservoir.
  • the invention proposed designed as a 3/2-way valve servo valve in the idle state does not occur on a guide portion leakage currents.
  • a sealing seat formed on the servo valve piston of the servo valve is formed as a flat seat
  • the housing of the servo valve can advantageously be designed as a multi-part housing, whereby an axial offset of components relative to one another can be compensated.
  • This compensation possibility production-related component tolerances and the good accessibility for the production of the sealing seat ensures a simple and cost manufacturability of the invention proposed servo valve.
  • FIG. 1 is a first embodiment of an inventively proposed 3/2-servo valve for controlling a fuel injector containing a pressure booster refer.
  • a working space 5 of a pressure booster 3 is acted upon by high-pressure fuel via a pressure source 1 and a high-pressure feed line 2 adjoining it.
  • the working space 5 is permanently acted upon by the high pressure fuel of the pressure source 1.
  • the pressure booster 3 comprises an integrally formed booster piston 4, which separates the working space 5 from a differential pressure chamber 6 (back space).
  • the booster piston 4 is acted upon by a return spring 8, which is supported on the one hand on a recessed in an injector body 19 support disk 7 and on the other hand on a mounted on a pin of the booster piston 4 stop disc.
  • the pressure booster 3 further comprises a compression chamber 9 which communicates via an overflow line 10 with a control chamber 12 for an injection valve member 14 in connection. In the overflow line 10 from the differential pressure chamber 6 (back space) to the control chamber 12 for the injection valve member 14, a first throttle body 11 is added.
  • a spring element 13 is received, which acts on an end face of the needle-shaped injection valve member 14.
  • the injection valve member 14 includes a pressure stage which is enclosed by a pressure chamber 16.
  • the pressure chamber 16 is acted upon by a pressure chamber inlet 17, which branches off from the compression chamber 9 of the pressure booster 3, with fuel under pressure translated.
  • a discharge line 21 extends into the first housing part 26 of the servo valve housing 25.
  • the compression space 9 of the pressure booster 3 acting end face of the booster piston 4 is identified by reference numeral 20. Due to the pressure level at the injection valve member 14, this causes an opening movement when the pressure chamber 16 is pressurized, so that injection openings 22 flow from the pressure chamber 16 along an annular gap and into a combustion chamber 23 of a self-igniting internal combustion engine.
  • the injection chamber 14 acting on the control chamber 12 is connected via a second throttle point 15 to the compression chamber 9 of the pressure booster 3 in hydraulic communication.
  • a servo valve housing 25 which receives a servo valve 24.
  • the servo valve housing 25 is formed in two parts and includes a first housing part 26 and a second housing part 27.
  • the two-part design of the servo valve housing 25 according to the in FIG. 1 illustrated embodiment allows good accessibility for processing of the sealing seat and a slide edge, resulting in a simple and cost manufacturability of the servo valve 24 results.
  • a supply line 29 branches off into the valve housing 25.
  • the supply line 29 opens into a first hydraulic chamber 38 of the first housing part 26 of the servo valve housing 25.
  • the first hydraulic chamber 38 encloses a servo valve piston 32, which comprises a passage 33.
  • a third throttle body 34 is formed in the passage 33 of the servo valve piston 32.
  • fuel flows from the first hydraulic chamber 38 into a control chamber 36 of the servo valve 24.
  • a pressure relief of the control chamber 36 takes place upon actuation of a switching valve 30, at its opening control volume from the control chamber 36 via a flow restrictor 37 (fourth throttle) containing return is connected to a further low-pressure side return 31 and fuel is derivable in these.
  • the control chamber 36 of the servo valve 24 is limited by an end face 35 at the top of the servo valve piston 32. This is located at the head of the servo valve piston 32 an effective in the opening direction of the servo valve piston 32 annular surface, which is acted upon by the pressure prevailing in the first hydraulic chamber 38, opposite.
  • a first sealing seat 40 in a second hydraulic chamber 39 and a control edge 41 are formed on the servo valve piston 32.
  • the control edge 41 which in the in FIG. 1 illustrated variant of the servo valve 24 is formed as a slide sealing edge 43, the pressurized under system pressure first hydraulic chamber 38 is sealed in a vertically moving servo valve piston 32 against the second hydraulic chamber 39.
  • the two returns 28, 31 on the low pressure side are combined as possible to a return, which opens into a fuel tank.
  • first embodiment of the servo valve 24 allows an extremely compact design of the servo valve 24.
  • the first sealing seat 40 of the servo valve 24 is shown in the illustration FIG. 1 formed as a flat seat, but could also be used as a conical seat (see FIG. 2 ) Ball seat or as a slide edge are formed.
  • Ball seat or as a slide edge are formed.
  • the first sealing seat 40 can be designed either as a sealing edge or as a sealing surface.
  • the sealing force can be adjusted via the pressure surface with respect to the flow control chamber 42.
  • FIG. 2 shows a further embodiment of the present invention proposed servo valve, wherein the first sealing seat is designed as a conical seat.
  • FIG. 2 The representation after FIG. 2 is also a fuel injector 18 can be seen, which contains a pressure booster 3.
  • the working space 5 of the pressure booster 3 is supplied via a pressure source 1 (common rail) via high-pressure line 2 with high-pressure fuel.
  • the booster piston 4 of the pressure booster 3 according to the illustrations in FIG. 2 formed in several parts.
  • a support plate 7 is inserted, which constitutes an upper abutment surface for the upper part of the multi-part booster piston 4.
  • the lower part of the booster piston 4 is acted upon by a return spring 8 which is supported on the housing side; the compression space 9 of the pressure booster 3 is limited over the end face 20 of the lower part of the booster piston 4.
  • a first throttle point 11 containing overflow line 10 branches off.
  • the overflow line 10 connects the differential pressure chamber 6 (back space) of the pressure booster 3 to the control chamber 12 for controlling the lifting movement of the needle-shaped injection valve member 14.
  • From the compression chamber 9 of the pressure booster 3 runs the pressure chamber inlet 17, which opens into the pressure chamber 16 surrounding the injection valve member 14.
  • the injection valve member 14 includes a pressure stage having a hydraulically effective area. At this attacks the im Pressure chamber 16 pending fuel pressure and opens the injection valve member 14 so that fuel is injected via released when opening the injection valve member 14 injection openings 22, which open into the combustion chamber 23 of the self-igniting internal combustion engine.
  • a damping piston 51 is added to the control chamber 12 for the injection valve member 14.
  • the damping piston 51 is traversed by a vertically extending channel 53.
  • the channel 53 is hydraulically connected via a fifth throttle point 52 in the conversion of the damping piston 51 with the control chamber 12.
  • a formed on the damping piston 51 annular surface 55 is acted upon by a housing side supporting spring element 54.
  • From the control chamber 12 for the injection valve member 14 extends a filling line 56 which contains a refill valve 50, which may be formed as a check valve to the compression chamber 9 of the pressure booster 3.
  • a refill valve 50 which may be formed as a check valve
  • the servo valve 24 according to the in FIG. 2 illustrated embodiment is added to the valve body 25.
  • the servo valve 24 includes the control chamber 36, which is relieved of pressure via the switching valve 30 in the second low-pressure side return 31. Between the control chamber 36 and the switching valve 30, an outlet throttle 37 (fourth throttle point) is added.
  • an outlet throttle 37 (fourth throttle point) is added.
  • the control chamber 36 in the valve body 25 of the servo valve 24 Opposite the control chamber 36 in the valve body 25 of the servo valve 24 is the first hydraulic chamber 38, which is separated by the control edge 41 from the second, here conically configured second hydraulic chamber 39.
  • the second hydraulic chamber 39 is connected via the diversion line 21 to the differential pressure chamber 6 (back space) of the pressure booster 3.
  • the control edge 41 is formed as a slider sealing edge 43. Unlike in FIG.
  • the first sealing seat 40 of the servo valve piston 32 is formed as a conical seat.
  • the drain control space 42 formed below the servovalve piston 32 in the valve body 25 is sealed so that the first low-pressure-side return 28 is closed.
  • a pressurization of the control chamber 36 and the first hydraulic chamber 38 takes place in parallel via the supply line 29, which branches off from the working space 5 of the pressure booster 3. Consequently, the system pressure in the first hydraulic chamber 38, which is acted on via the second supply line section 58, is present via the supply line 29 as well as via a first supply line section 57, the third throttle point Containing 34, in the control chamber 36 of the servo valve 24 at. Due to the identity of the pressures in the first hydraulic chamber 38 and in the control chamber 36, a pilot leakage along the head of the servo valve piston 32 is excluded. The servo valve piston 32 is guided in the valve body 25 high pressure-tight.
  • the basic mode of operation of the inventively proposed fuel injector which is controlled via the servo valve 24, is based on the illustration in accordance with FIG. 1 described.
  • the working space 5 of the pressure booster 3 is constantly connected to the pressure source 1 and is constantly under the prevailing pressure level there.
  • the compression chamber 9 of the push-type translator 3 is constantly connected via the pressure chamber inlet 17 to the pressure chamber 16 which surrounds the injection valve member 14.
  • the pressure booster 3 further includes the differential pressure space 6 (back space) for controlling the pressure booster 3 either at system pressure, i. pressurized in the pressure source 1 prevailing pressure level or separated from this pressure in the low-pressure side return 28 is relieved of pressure.
  • the supply line 29 is connected to the pressure accumulator 1, so that the pressures in the working chamber 5 and the differential pressure chamber 6 (back space) of the pressure booster correspond to each other and the booster piston 4 is balanced and no pressure boost takes place.
  • a pressure relief of the differential pressure chamber 6 (back space).
  • the switching valve 30 is activated, ie opened and the control chamber 36 of the servo valve 24 in the low-pressure side return 31 via the outlet throttle 37 relieved of pressure. Due to the falling pressure in the control chamber 36, the servo valve piston 32 moves upward in the vertical direction, moved by the pressing force acting on the opening surface 44 in the first hydraulic space 38. As a result, the first sealing seat 40 is opened while the control edge 41 is closed, since the slide edge 43 covers the opposite housing edge of the valve body 25.
  • the throttle body 34 in the passage 33 of the servo valve piston 32 and the outlet throttle 37 is the movement speed of the servo valve piston 32 at its opening movement freely adjustable. Due to the defined opening surface 44 on the underside of the head of the servo valve 24, the servo valve piston 32 is constantly in compression in the opening direction. This allows a precise movement of the servo valve piston 32 and thus a stable persistence of the same at the opening stop in the open state of the servo valve piston 32 bring about.
  • servo valve piston 32 When located in its open position servo valve piston 32 is a decoupling of the differential pressure chamber 6 (back space) of the pressure booster 3 from the system pressure, i. of the prevailing pressure in the accumulator 1 pressure levels.
  • a control quantity flows out of the differential pressure chamber 6 (back space) via the outlet line 21 into the second hydraulic chamber 39, via the opened first sealing seat 40 into the process control chamber 42. From this flows the fluid which has been diverted from the differential pressure chamber 6 (backspace) Fuel quantity in the low-pressure side return 28 from.
  • the first sealing seat 40 can be used both as a flat seat, which allows a high surface pressure, and as a conical seat (comparisons according to FIG FIG. 2 ) are formed as a ball seat or as a slide edge.
  • a flat seat which allows a high surface pressure
  • a conical seat comparisons according to FIG FIG. 2
  • the in FIG. 1 illustrated flat seat as the first sealing seat 40 can compensate for any production-related axial offset.
  • the generation of a sufficient closing force so that at the first sealing seat 40 in its closed position, a high surface pressure arises and thus a good sealing effect is ensured.
  • FIG. 2 illustrated embodiment using a damping piston 51 which acts on the injection valve member 14, a reduction in the opening speed of the needle-shaped injection valve member 14 can be achieved.
  • the damping behavior of the damping piston 51 can be adjusted by the dimensioning of this acting spring element 54 and by the dimensioning of the formed in the wall of the damping piston 51 throttle element 52.
  • the refilling of the compression chamber 9 of the pressure booster 3 does not take place via the second throttle point 15 as in the embodiment according to FIG. 1 but via a branching from the control chamber 12 of the injection valve member 14 filling line 56 in which a designed as a check valve refill valve 50 is added.
  • the inventively proposed 3/2-servo valve 24 can be used to control all pressure booster 3, which are controlled via a pressure change of their differential pressure chamber 6 (backspace).
  • FIG. 3 is a variant of a 3/2-Servovalve with a servo valve piston refer to which a control sleeve is added.
  • FIG. 3 illustrated embodiment of a fuel injector 18 with pressure booster 3 is acted upon by a high pressure source 1 via the high pressure supply line 2 with high pressure fuel.
  • the working space 5 of the pressure booster 3 is filled with system pressure, in which a return spring 8 is added, which is supported on the one hand on a support plate 7 and on the other hand via a stop surface biases the booster piston 4, which separates the working chamber 5 from the differential pressure chamber 6.
  • the end face 20 of the booster piston 4 limits the compression chamber 9, which is acted upon by the activation of the pressure booster 3 via the pressure chamber inlet 17 of the pressure chamber 16 with high pressure fuel.
  • the fuel injector 18 includes the control chamber 12, which is bounded by a control chamber sleeve 62.
  • the control chamber sleeve 62 is biased by the spring 13, wherein the spring 13 is supported on a collar of the injection valve member 14.
  • feed surfaces 64 formed as polished portions are formed below the collar. Via these inflow surfaces 64, the fuel flows from the pressure chamber to injection openings 22, which open into the combustion chamber 23 of the self-igniting internal combustion engine.
  • the control chamber 12 of the fuel injector 18 is acted upon on the one hand via a first throttle point 11, which branches off from the pressure chamber inlet 17 with fuel; the pressure relief of the control chamber 12 via the second throttle body 15 upon actuation of a switching valve 60. If the switching valve 60 is actuated, a Abberichtmenge via the second throttle point 15 is derived in an injector 61 return.
  • the pressure booster 3 is actuated via the servo valve 24.
  • the servo valve 24 includes the valve piston 32 having a servo valve piston portion 65.
  • the servo valve piston 32, 65 is controlled via the pressurization or pressure relief of the control chamber 36.
  • the control chamber 36 of the servo valve 24 is acted upon by the high-pressure fuel via the first supply line section 57, in which the throttle restriction 34 is accommodated.
  • a pressure relief of the control chamber 36 of the servo valve 24 via an actuation of the switching valve 30.
  • the servo valve 24 comprises a housing 25, which comprises a plurality of housing parts 26, 27.
  • the servo valve piston 32, 65 is enclosed by the first hydraulic chamber 38 and the second hydraulic chamber 39.
  • the first hydraulic chamber 38 is acted upon by the supply line 29, which branches off from the high-pressure line 2, with high-pressure fuel.
  • In the second hydraulic chamber 39 opens the Abtechnisch 21, via which a pressure relief of the differential pressure chamber 6 (back space) of the pressure booster 3 takes place.
  • the servo valve piston 32 also includes the hydraulic surface 44, on which a force acting on the servo valve piston 32 in the open position pressure force upon pressure relief of the control chamber 36 of the servo valve 24 attacks.
  • first recesses 63 are formed, which have slide sealing edges 43.
  • the slider sealing edges 43 of the first recesses 63 cooperate with a control edge 41 formed on the second housing part 27.
  • a control sleeve 67 is received, which is biased by a control sleeve spring 68, which in turn is supported on the first housing part 26 of the servo valve housing 25.
  • the control sleeve 67 has a sleeve recess 71.
  • the first sealing seat 40 according to the in FIG. 3 illustrated embodiment is designed as a flat seat and seals the Abêtraum 42 (low pressure space) against the low-pressure side return 28 from.
  • the functioning of in FIG. 3 illustrated embodiment of the controlled via the servo valve 24 Kraftsoffinjektors 18 with pressure booster 3 is as follows:
  • the first sealing seat 40 can be designed in many ways. In addition to the in FIG. 3 illustrated embodiment of the first sealing seat 40 as a flat seat, this can according to the embodiments, in FIG. 2 is shown, also formed as a conical seat or ball seat. Particularly advantageous is the in FIG. 3 represented by a multipart valve body, such as housing parts 26, 27 and 66, a simple manufacture of the valve seat of the first sealing seat 40 can be achieved. By the in FIG. 3 flat seat shown is compensated for any axial misalignment of the valve body to each other. In the FIG. 3 illustrated embodiment also has a large closing pressure force exerted by the pending in the control chamber 36 fuel pressure on the first sealing seat 40, which adjusts to this a high surface pressure and thus an excellent sealing effect.
  • the first sealing seat 40 When opening, first the first sealing seat 40 is opened and the slider sealing edge 43 is brought into register with the control edge 41.
  • the control sleeve 67 is now employed by the hydraulic pressure force in the second hydraulic chamber 39 to the third housing part 66, whereby a high-pressure-tight connection is achieved. Only then is an opening of the slide seal 69, when the servo valve piston section 65, the sleeve recess 71 releases. As a result, no short-circuit leakage current flows from the first hydraulic chamber 38 into the return line.
  • the differential pressure chamber 6 (back space) of the pressure booster 3 is now connected via the second hydraulic chamber 39, the slide seal 69, the first sealing seat 40 and the Abêtraum 42 (low pressure space) with the low-pressure side return 28 and the pressure booster 3 thus activated.
  • the servo valve piston 32, 65 moves through the force acting in the closing direction hydraulic pressure force in the control chamber 36 in its starting position.
  • the hydraulic closing force ensures a precisely defined closing movement over the entire area of the servo valve piston 32, 65.
  • a spring force can be provided to assist the closing movement.
  • the representation according to FIG. 4 is a variant with stretched trained Servoventilkolben a servo valve to remove.
  • the servo valve piston 32 has a stretched servo valve piston section 65.
  • 65 second recesses 70 are formed on the the Ab Kunststoffraum 42 (low pressure space) facing the end of the Servoventilkolbenabterrorismes 65.
  • the slide seal 69 is integrated directly into the first housing part 26 of the servo valve housing 25.
  • the servo valve piston section 65 in FIG. 3 illustrated control sleeve 67 omitted.
  • FIG. 4 illustrated embodiment is identical to that in connection with FIG. 3 illustrated operation of this embodiment of the fuel injector 18th
  • FIG. 4 is formed at the Abêtraum 42 (low pressure space) facing end face of the Servoventilkolbenabiteses 65 a flat seat.
  • the servo valve 24 may also be formed as a pure slide-valve slide. In this case, care must be taken for a sufficient overlap length at the slide seal 69 in order to keep the leakage flow in the idle state of the fuel injector 18 small.
  • the servo valve 24 may also be formed as a 4/2-way valve, in which the function of the check valve is integrated into the slide valve.

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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

L'invention concerne un injecteur de carburant destiné à injecter du carburant dans la chambre de combustion (23) d'un moteur à combustion interne. Ledit injecteur (18) comporte un transmetteur de pression (3) dont le piston de transmission (4) sépare une chambre de travail (5) recevant du carburant sous l'effet d'un accumulateur de pression (1, 2), d'une chambre de pression différentielle (6) pouvant être déchargée de la pression. Une variation de pression dans la chambre différentielle (6) est obtenue par actionnement d'une soupape asservie (24) libérant ou refermant une connexion hydraulique (21, 39, 42) de la chambre de pression différentielle (6) avec une première conduite de retour (28) côté basse pression. La soupape asservie (24) comporte un piston (32) logé entre une chambre de commande (36) et une première chambre hydraulique (38). Une surface hydraulique (44) amenant en continu le piston (32) en position d'ouverture en cas d'application de pression système, et un siège d'étanchéité (40) refermant ou libérant une conduite de retour (28) côté basse pression, sont formés sur ledit piston.

Claims (16)

  1. Injecteur de carburant pour injecter du carburant dans une chambre de combustion (23) d'un moteur à combustion interne comprenant un démultiplicateur de pression (3) dont le piston démultiplicateur (4) sépare une chambre de travail (5) sollicitée en permanence par du carburant venant d'une source de pression (1, 2) et une chambre de différence de pression (6), qui peut être déchargée en pression,
    une variation de pression dans la chambre de différence de pression (6) se faisant par l'actionnement d'une servovanne (24) qui libère ou ferme la communication hydraulique (21, 39, 42) de la chambre de différence de pression (6) par rapport à un retour (28) côté basse pression,
    la servovanne (24) ayant un piston de servovanne (32, 65) guidé entre une chambre de commande (36) et une première chambre hydraulique (38), et
    le piston de servovanne (32) comporte un premier siège d'étanchéité (40) fermant ou libérant le retour (28) côté basse pression ainsi qu'une arête de commande (41) séparant la première chambre hydraulique (38) d'une seconde chambre hydraulique (39),
    caractérisé en ce que
    la chambre de commande (36) est délimitée par une surface frontale (35) du piston de servovanne (32, 65), ayant au niveau de la tête du piston de servovanne (32, 65), une surface annulaire active réalisée par une surface hydraulique active (44) sollicitée par une pression de système agissant en permanence dans le sens de l'ouverture du piston de servovanne (32, 65).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la chambre de commande (36) et la première chambre hydraulique (38) sont sollicitées par la pression du système par l'intermédiaire d'une conduite d'alimentation (29) issue de l'accumulateur de pression (1).
  3. Injecteur de carburant selon la revendication 2,
    caractérisé en ce que
    la chambre de commande (36) de la servovanne (24) est sollicitée par la pression du système par un canal traversant (33) s'étendant à travers le piston de servovanne (32) à partir d'une première chambre hydraulique (38) dans laquelle débouche la conduite d'alimentation (29).
  4. Injecteur de carburant selon la revendication 3,
    caractérisé en ce que
    le canal traversant (33) du piston de servovanne (32) comporte un point d'étranglement (34), intégré.
  5. Injecteur de carburant selon la revendication 2,
    caractérisé en ce que
    la chambre de commande (36) est sollicitée par la pression du système par un second segment de conduite (58) dérivé de la conduite d'alimentation (29), et la première chambre hydraulique (38) est sollicitée par la pression du système, en parallèle, par un segment de conduite d'alimentation (58) dérivé de la conduite d'alimentation (29).
  6. Injecteur de carburant selon la revendication 5,
    caractérisé en ce que
    le premier segment de conduite d'alimentation (57) comporte un premier point d'étranglement (34).
  7. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    le premier siège d'étanchéité (40) est réalisé sous la forme d'un siège plat ou d'un siège conique et il ferme une chambre de commande de sortie (42) prévue du côté basse pression.
  8. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    l'arête de commande (41) est réalisée sous la forme d'une arête d'étanchéité de tiroir (43).
  9. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la chambre de différence de pression (6) qui se décharge en pression dans le retour (28) côté basse pression par l'intermédiaire de la servovanne (24), est couplée hydrauliquement à une chambre de commande (12) recevant un piston d'amortissement (51) pour une aiguille d'injecteur (14), le piston d'amortissement (51) comprenant un point d'étranglement (52) qui définit la vitesse d'ouverture de l'aiguille d'injecteur (14), et la chambre de commande (12) communique pour l'actionnement de l'aiguille d'injecteur (14) par l'intermédiaire d'une conduite de remplissage (56) soit avec la chambre de commande (12) soit avec l'une des chambres hydrauliques (5, 6, 9) du démultiplicateur de pression (3).
  10. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    l'actionnement de la servovanne (24) se fait par l'intermédiaire d'une soupape de commutation (30) reliant la chambre de commande (36) à un retour (31).
  11. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    le piston de servovanne (32) comprend un segment de piston de servovanne (65) de diamètre réduit, sur lequel est monté un manchon de commande (67) précontraint.
  12. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    le manchon de commande (67) forme une arête de commande de tiroir (69) avec le segment de piston de servovanne (65).
  13. Injecteur de carburant selon la revendication 12,
    caractérisé en ce que
    l'arête de commande de tiroir (69) commande la liaison avec le retour côté basse pression (28).
  14. Injecteur de carburant selon la revendication 11,
    caractérisé en ce que
    le segment de piston de servovanne (65) du piston de servovanne (32) comporte des premières cavités (63) ayant une arête d'étanchéité de tiroir (43), coopérant avec une arête de commande (41) réalisée du côté du boîtier de la servovanne.
  15. Injecteur de carburant selon la revendication 11,
    caractérisé en ce que
    le manchon de commande (67) est sollicité par un élément de ressort (68) qui s'appuie contre une partie (26) du boîtier de servovanne (25).
  16. Injecteur de carburant selon la revendication 11,
    caractérisé en ce que
    le segment de piston de servovanne (65) du piston de servovanne (32) comporte des premières cavités (63) entre la première chambre hydraulique (38) et la seconde chambre hydraulique (39) ainsi que des secondes cavités (70) réalisant une étanchéité de tiroir (69).
EP04717030A 2003-04-02 2004-03-04 Injecteur de carburant comportant un transmetteur de pression commande par une soupape asservie Expired - Fee Related EP1613856B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10315014 2003-04-02
DE10325620A DE10325620A1 (de) 2003-04-02 2003-06-05 Servoventilangesteuerter Kraftstoffinjektor mit Druckübersetzer
PCT/DE2004/000413 WO2004088122A1 (fr) 2003-04-02 2004-03-04 Injecteur de carburant comportant un transmetteur de pression commande par une soupape asservie

Publications (2)

Publication Number Publication Date
EP1613856A1 EP1613856A1 (fr) 2006-01-11
EP1613856B1 true EP1613856B1 (fr) 2008-07-09

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EP04717030A Expired - Fee Related EP1613856B1 (fr) 2003-04-02 2004-03-04 Injecteur de carburant comportant un transmetteur de pression commande par une soupape asservie

Country Status (4)

Country Link
US (1) US7320310B2 (fr)
EP (1) EP1613856B1 (fr)
JP (1) JP2006522254A (fr)
WO (1) WO2004088122A1 (fr)

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DE102004022267A1 (de) * 2004-05-06 2005-12-01 Robert Bosch Gmbh Verfahren und Vorrichtung zur Formung des Einspritzdruckes an einem Kraftstoffinjektor
JP3994990B2 (ja) * 2004-07-21 2007-10-24 株式会社豊田中央研究所 燃料噴射装置
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US9163597B2 (en) * 2008-10-01 2015-10-20 Caterpillar Inc. High-pressure containment sleeve for nozzle assembly and fuel injector using same
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Also Published As

Publication number Publication date
US7320310B2 (en) 2008-01-22
US20060243252A1 (en) 2006-11-02
JP2006522254A (ja) 2006-09-28
EP1613856A1 (fr) 2006-01-11
WO2004088122A1 (fr) 2004-10-14

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