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
  • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
  • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
  • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
  • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
  • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
  • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
  • F02M51/0635—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding
• • 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
  • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
  • F02M61/167—Means for compensating clearance or thermal expansion
• • 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
  • F02M63/0057—Means for avoiding fuel contact with valve actuator, e.g. isolating actuators by using bellows or diaphragms
• • 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
  • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
  • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
• • 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
  • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator
• • 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
  • F02M2200/708—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with hydraulic chambers formed by a movable sleeve
• • 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
  • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
  • F02M2200/8046—Fuel injection apparatus manufacture, repair or assembly the manufacture involving injection moulding, e.g. of plastic or metal
• • 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
  • F02M2200/90—Selection of particular materials
  • F02M2200/9015—Elastomeric or plastic materials
• • 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
• • 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 injector according to the preamble of claim 1.
• the object of the invention is to provide a fuel injector according to the preamble of claim 1, which is inexpensive to produce.
• the object is with a fuel injector with an injector housing, which has a high-pressure fuel connection, which with a central
• High-pressure fuel source outside and with one Pressure chamber within the Injektorgehauses in conjunction from which, depending on the pressure in a control chamber, high-pressure fuel injected into a combustion chamber of an internal combustion engine, when a nozzle needle opens, solved by the pressure in the control chamber by a Magnetic actuator is controlled directly.
• the magnetic actuator has the advantage that it represents a robust and well-known technique and also has a long service life and low production costs under high pressure.
• a preferred embodiment of the fuel injector is characterized in that the solenoid actuator comprises a coil cooperating with an armature which, when the coil is activated, carries out an armature stroke by a magnetic force.
• the coil is encapsulated to seal against the fuel, for example, in epoxy resin.
• a further preferred exemplary embodiment of the fuel injector is characterized in that the armature is coupled to the nozzle needle via a hydraulic coupler which reduces the armature stroke and translates the magnetic force. Due to a high system pressure of up to 2000 bar, very large switching forces may be required to open the nozzle needle. These forces can be realized by the translation of the magnetic force.
• a high power conversion of about 4 to 10 is used.
• the necessary Duseno réelleskraft of about 250 to 500 Newton can be generated from the power range of the Magnetaktors of about 40 to 100 Newtons.
• the armature stroke is reduced to a desired level by means of the hydraulic coupler.
• the hydraulic coupler has a coupler piston which is mechanically coupled to the armature and whose end close to the combustion chamber limits the control chamber.
• the coupler piston is a first translator piston.
• a plunger can be integrated.
• a further preferred exemplary embodiment of the fuel injector is characterized in that the control chamber is delimited by the combustion chamber distal end of the nozzle needle.
• the nozzle needle is a second translator piston.
• the control chamber In the axial direction between the combustion chamber remote end of the nozzle needle and the combustion chamber near the end of the coupler piston, the control chamber is arranged, which is also referred to as a coupler space.
• the nozzle needle is hydraulically coupled to the coupler piston via the coupler chamber.
• a further preferred exemplary embodiment of the fuel injector is characterized in that the end of the coupler piston close to the combustion chamber has a smaller diameter than the end of the nozzle needle remote from the combustion chamber.
• a further preferred exemplary embodiment of the fuel injector is characterized in that the hydraulic coupler has a coupler piston which is mechanically coupled to the armature and whose end close to the combustion chamber delimits a partial control chamber remote from the combustion chamber.
• the pressure in the combustion chamber remote sub-control room can be selectively changed by a movement of the coupler piston, in particular lowered.
• a further preferred embodiment of the fuel injector is characterized in that the partial combustion chamber remote from the combustion chamber is delimited by a spring-biased sleeve, which is guided at the end of the coupler piston close to the combustion chamber and abuts against a throttle plate with a biting edge.
• the spring biasing force is sufficiently small and is preferably between 10 and 20 Newtons.
• the throttle plate has a through-hole which connects the partial combustion chamber remote from the combustion chamber to a partial control chamber close to the combustion chamber, which is delimited by the combustion chamber distal end of the nozzle needle. Through the through hole, a pressure reduction is transferred from the combustion chamber remote to the partial combustion chamber near the combustion chamber.
• Another preferred exemplary embodiment of the fuel injector is characterized in that the end of the coupler piston close to the combustion chamber has a larger diameter than the end of the nozzle needle remote from the combustion chamber.
• the combustion chamber near End of the coupler piston preferably has a diameter of about 8 mm.
• the combustion chamber remote end of the nozzle needle preferably has a diameter of about 3.5 mm.
• Another preferred exemplary embodiment of the fuel injector is characterized in that the end of the coupler piston remote from the combustion chamber limits a compensation volume which communicates with a storage volume in which the end of the coupler piston near the combustion chamber is arranged. This ensures that the control piston is completely pressure compensated.
• Another preferred embodiment of the fuel injector is characterized in that the coupler piston is guided by a Kopplerkolben- guide portion which connects the storage volume with a Magnetaktorfactraum in which the magnetic actuator is accommodated.
• the diameter of the coupler piston guide portion is selected so that the leakage from the storage volume into the solenoid actuator housing space is minimized.
• the fuel injector is characterized in that the solenoid actuator accommodating space communicates with a pressure relief space.
• the leakage occurring at the coupler piston guide portion is discharged into the pressure relief space.
• the fuel injector described in the previous sections allows multiple injection while optimizing overall hydraulic efficiency.
• the fuel injector comprises an integrated damping volume or storage volume.
• the fuel injector according to the invention enables the avoidance of leakage losses or control quantities. It is provided an economically producible direct switching fuel injector with solenoid actuator. By integrating the magnetic actuator in a holding body of the injector, the length of the fuel injector can be reduced.
• the associated operating principle allows an optimization of the overall hydraulic efficiency, which allows the use of smaller high-pressure pumps. Since the number of injections or control quantities is no longer included in the total quantity balance of the system, higher optional degrees of freedom can be achieved. By avoiding a hydraulic reaction (Ab Kunststoffenfin) on the magnetic actuator, the performance of the injector can be improved. In particular, the representation of a cost-effective system by eliminating a rail and a pressure control valve is made possible, which is achieved by a targeted leakage of pressure reduction.
• a further preferred exemplary embodiment of the fuel injector is characterized in that the control chamber is delimited by a control chamber limiting sleeve, which acts under sealing effect the combustion chamber remote end of the nozzle needle is guided.
• the control room which is also referred to as a coupling room, may also comprise a plurality of sub-coupling spaces communicating with each other.
• Another preferred exemplary embodiment of the fuel injector is characterized in that the magnetic actuator is arranged in an actuator chamber, which is acted upon by high-pressure fuel.
• the actuator room also serves as a damping and storage volume.
• a further preferred exemplary embodiment of the fuel injector is characterized in that the actuator chamber communicates with the control chamber.
• the connection can by appropriate
• Coupler gaps can be realized, which are provided for example between the coupler piston and the Injektorgehause.
• the nozzle needle has a double seat.
• the nozzle needle then has a plurality of flow channels, which allow a central fuel supply to the needle tip.
• the spray holes are preferably sealed by two sealing seats of the nozzle needle. When opening the nozzle needle, the two Seal seats open at the same time, which can have a relatively large diameter, without generating large needle forces. As a result, the nozzle is de-edged with a small nozzle needle stroke, for example at 50 ⁇ m.
• Figure 1 is a simplified representation of a fuel injector according to the invention in longitudinal section and
• FIG. 2 shows a fuel injector according to a second embodiment in longitudinal section.
• FIG. 1 shows a longitudinal section of a fuel injector with an injector housing 1.
• the injector housing 1 comprises a nozzle body 2, which projects with its lower free end into a combustion chamber of an internal combustion engine to be supplied with fuel. With its upper end surface remote from the combustion chamber, the nozzle body 2 is clamped axially against an intermediate body 3 and an injector body 4 by means of a clamping nut (not shown).
• the injector body 4 has substantially the shape of a circular cylinder jacket-shaped sleeve, whose one end face is closed by the intermediate body 3 and the other end face by an injector head 5.
• an axial guide bore 6 is recessed, in which a nozzle needle 8 is guided axially displaceable.
• a sealing edge 10 is formed, which cooperates with a sealing seat or a sealing surface 11 in order to selectively release or close two injection holes 13 and 14 as a function of the position of the nozzle needle 8.
• the nozzle needle 8 has a pressure chamber section 15, followed by a truncated conical widening section 16, which is also referred to as a pressure shoulder.
• the pressure shoulder is arranged in a pressure chamber 17 which is formed between the nozzle needle 8 and the nozzle body 2.
• On the pressure shoulder 16 is followed by a guide portion 18 which is guided in the guide bore 6 movable back and forth.
• a fluid connection between the pressure chamber 17 and a nozzle spring chamber 22 is provided.
• the nozzle spring chamber 22 communicates via a connecting channel 24, which is formed in the intermediate body 3, with an actuator chamber 25, which in turn communicates via an inlet channel or an inlet line 26 with a high-pressure fuel source 28, which is also referred to as a common rail. net becomes.
• a solenoid actuator 30 is arranged in the acted upon with high pressure actuator space 25, in the acted upon with high pressure actuator space 25, in the acted upon with high pressure actuator space 25, a solenoid actuator 30 is arranged.
• the solenoid actuator 30 includes an electromagnet 31 which is fixed to the injector body 4.
• a magnetic coil 34 is arranged, which is connected via lines 35, 36 to a power source.
• the magnet coil 34 cooperates with an armature 38, which is arranged movable in an axial direction in an armature space 37.
• the armature 38 has the shape of a circular disk 39 which is fixed to a coupler piston 40.
• the coupler piston 40 is acted upon by a prestressed actuator spring 41, which is clamped between the coupler piston 40 and a support mandrel 42, which starts from the injector head 5.
• the combustion chamber near the end of the coupler piston 40 protrudes into a coupler 44, which is also referred to as a control room.
• the coupler space 44 is bounded in the radial direction by a control chamber limiting sleeve 46, which is guided under sealing action on a combustion chamber-remote end section 48 of the nozzle needle 8.
• a collar 49 extends radially outward. Between the collar 49 and the Steuerraumbegren- tion sleeve 46, a nozzle spring 50 is clamped in the nozzle spring chamber 22.
• the nozzle spring chamber 22 is connected via the flats 19 and 20 with the pressure chamber 17 and via the high-pressure connection channel 24 with the armature chamber 37 in connection.
• the armature space 37 in turn is over a further high-pressure connection channel 52 with the actuator chamber 25 in communication, which is filled via the fuel supply line 26 with high-pressure fuel.
• the coupler piston 40 is biased by the actuator spring 41 in its rest position. In the idle state of the fuel injector prevails in the coupler space 44 high pressure, which is also referred to as rail pressure. The nozzle needle 8 is closed. At rest, the magnetic actuator 30 is not energized. To drive the injector, the magnetic actuator 30 is energized and thereby pulls the coupler piston 40 upwards, ie towards the injector head 5. In this case, the pressure in the coupler chamber 44 decreases and the nozzle needle 8 opens.
• the nozzle needle 8 Since the diameter of the coupler piston 40 is smaller than the diameter of the nozzle needle 8 in the end portion 48, the nozzle needle 8 is acted upon by an increased force relative to the magnetic force exerted by the magnet actuator 30. To close the nozzle needle 8, the energization is stopped. Then, the coupler piston 40 by the prestressed compression spring 41 back down, that is to the combustion chamber, pressed and the nozzle needle 8 closes.
• the electrical contacting of the magnetic actuator 30 is carried out in a suitable high pressure-tight manner, for example by a Glaseinschmelzung of the lines 35, 36th
• FIG. 2 shows a longitudinal section of a fuel injector with an injector housing 81.
• the injector housing 81 comprises a nozzle body 82, with its lower free end 89 in a Combustion chamber of an internal combustion engine protrudes. With its upper end remote from the combustion chamber, the nozzle body 82 is clamped against a holding body 85 with the interposition of a throttle plate 83 with the aid of a clamping nut 84.
• a nozzle needle 88 which opens or closes at least one injection opening at the end 89 of the nozzle body 82 as a function of the pressure in a control space, is accommodated in the nozzle body 82.
• the control chamber 90 comprises a partial combustion chamber 91 close to the combustion chamber, which is delimited in the axial direction by the combustion chamber distal end of the nozzle needle 88 and the throttle plate 83. In the radial direction of the combustion chamber near the partial control chamber 91 is bounded by a spring-biased sleeve 95, which rests with a biting edge close to the throttle plate.
• the partial combustion chamber 91 close to the combustion chamber communicates via a through-hole 93, which extends through the throttle plate 83, with a partial control chamber 92 remote from the combustion chamber.
• the combustion chamber remote sub-control chamber 92 is limited in the axial direction, that is, in the direction of a longitudinal axis 86 of the fuel injector of the throttle plate 83 and the combustion chamber near the end of a coupler piston 102. In the radial direction, the partial combustion chamber 92 remote from the combustion chamber is delimited by a spring-biased sleeve 108, which rests against the throttle plate 83 with a biting edge.
• the throttle plate 83 has radially outside the through-hole 93 connecting channels 97, 98, which has an annular space 96, which in the nozzle body 82nd is provided radially outside of the nozzle needle 88, connect to a storage volume 100 which is provided in the holding body 85 radially outside of the coupler piston 102.
• the coupler piston 102 has a combustion piston near coupler piston portion 103 with an outer diameter 106 of about 8 mm.
• the combustion chamber near the coupler piston portion 103 is integrally connected to a combustion chamber remote coupler piston portion 104 having an outer diameter 105 of 3.5 mm.
• the sleeve 108 is guided at the end of the combustion chamber near the combustion chamber near coupler piston portion 103.
• the sleeve 95 is guided at the combustion chamber-end of the nozzle needle 88, which has an outer diameter 107 of 3.5 mm.
• the outer diameter 107 of the combustion chamber distal end of the nozzle needle 88 is thus equal to the outer diameter 105 of the combustion chamber remote coupler piston portion 104.
• the sleeve 108 is biased by a helical compression spring 109 which is clamped between the sleeve 108 and a collar 110 which is attached to the combustion chamber near coupler piston portion 103 ,
• the coupler piston 102 is guided with its combustion chamber remote coupler piston portion 104 in a through hole 112 which is provided in the holding body 85 and is also referred to as Kopplerkolben adjustmentssab- section.
• the through-hole 112 connects the storage volume 100 to a solenoid actuator accommodating space 115.
• a magnetic actuator 120 Disposed in the solenoid actuator accommodating space 115 is a magnetic actuator 120 including an armature 121 fixed to the coupler piston portion 104 remote from the combustion space.
• the anchor 104 is biased by a spring 122 toward the combustion chamber.
• the spring 122 is clamped between the armature 121 and the combustion chamber distal end of the Garkorpers 85.
• a magnet or a magnetic coil 124 is disposed in the Magnetaktorfactraum 115 within the Garkorpers 85.
• the solenoid coil 124 When the solenoid coil 124 is energized, the armature 121 is attracted toward the solenoid coil 124.
• the associated armature stroke is designated 140 and amounts to 30 microns.
• connection 125 serves to dissipate leakage which occurs at the high-pressure passage of the combustion chamber-remote coupler piston section 104 through the through-hole 112 between the high-pressure accumulator volume 100 and the low-pressure magnetic actuator accommodating space 115.
• the combustion chamber remote end of the remote Kopplerkolbenabitess 104 is guided in a blind hole 128 in the combustion chamber remote end of Garkorpers 85 and limited with its front side a compensation volume 130.
• the equalization volume 130 is connected via a high-pressure connection line 132 with a high-pressure fuel source in connection, which is indicated by an arrow 134.
• a high-pressure line 136 in which a throttle 138 is provided, the high-pressure fuel source 134 and the high-pressure fuel line 132 communicate with the storage volume 100.
• the magnetic actuator 120 which is also referred to as a magnetic actuator, can only produce smaller forces in the order of 50 to 100 Newton.
• the area ratio between the coupler piston section 103 close to the combustion chamber and the end of the nozzle needle 88 remote from the combustion chamber is selected so that a needle stroke of 140 to 240 ⁇ m can be achieved with the magnetic actuator 120.
• a needle stroke of 180 microns can be achieved.
• the injection process is initiated by energizing the solenoid coil 124. Proportional to the stroke of the armature 121, the pressure in the control chamber 90 is lowered, so that the nozzle needle 88 lifts after falling below the opening pressure from the seat.
• the coupler piston 102 is completely pressure-balanced in itself. In order to ensure a safe closing, the closing operation takes place after the magnetic coil 124 has been switched off by the spring 122 attached to the armature 121.
• the pretensioning force of the spring 122 is between 50 and 100 Newton, preferably between 70 and 90 Newton.
• the throttle 138 in the high pressure line 136 serves to reduce the high pressure in the storage volume 100 with respect to the equalization volume 130.
• the biasing force of the spring 109 is preferably between 10 and 20 Newtons.
• the solenoid actuator receiving space 115 may be subjected to low pressure, as indicated by the angled arrow 125. However, the solenoid actuator receiving space 115 may also be subjected to high pressure.
• high pressure During installation at low pressure, permanent leakage occurs at the high-pressure passages of the coupler piston section 104 remote from the combustion chamber in the holding body 85.
• a desired quantity balance in the overall system can be achieved, in particular because there are no control amounts in the illustrated injector concept.
• With permanent leakage it is possible to reduce the pressure during overrun of the vehicle. In the case of an integration of the magnetic actuator 120 in the high pressure, it may be necessary to use more expensive seals for the magnetic coil 124 and the electrical contacting.

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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)
• Electromagnetism (AREA)
• Fuel-Injection Apparatus (AREA)

Applications Claiming Priority (3)

Publications (2)

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Family Applications (1)

Country Status (7)

Cited By (1)

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• 2007
  • 2007-01-18 DE DE102007002758A patent/DE102007002758A1/de not_active Withdrawn
  • 2007-02-16 AT AT07704610T patent/ATE518058T1/de active
  • 2007-02-16 EP EP07704610A patent/EP2004983B1/fr not_active Not-in-force
  • 2007-02-16 US US12/294,266 patent/US20090108093A1/en not_active Abandoned
  • 2007-02-16 WO PCT/EP2007/051487 patent/WO2007115853A1/fr active Application Filing
  • 2007-02-16 CN CN2007800124271A patent/CN101415934B/zh not_active Expired - Fee Related
  • 2007-02-16 JP JP2009503507A patent/JP2009532622A/ja active Pending

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