EP1478841B1 - Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine - Google Patents

Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine Download PDF

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Publication number
EP1478841B1
EP1478841B1 EP02792634A EP02792634A EP1478841B1 EP 1478841 B1 EP1478841 B1 EP 1478841B1 EP 02792634 A EP02792634 A EP 02792634A EP 02792634 A EP02792634 A EP 02792634A EP 1478841 B1 EP1478841 B1 EP 1478841B1
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EP
European Patent Office
Prior art keywords
pump
pump piston
pressure
working space
piston
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 - Lifetime
Application number
EP02792634A
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German (de)
English (en)
French (fr)
Other versions
EP1478841A1 (de
Inventor
Peter Boehland
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1478841A1 publication Critical patent/EP1478841A1/de
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Publication of EP1478841B1 publication Critical patent/EP1478841B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically

Definitions

  • the invention is based on a Fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is characterized by the US-A-5,709,341.
  • Another fuel injection device is through the EP 0 987 431 A2.
  • These Fuel injection device has a High-pressure fuel pump and a connected to this Fuel injector for each cylinder of Internal combustion engine.
  • the high-pressure fuel pump points one by the internal combustion engine in a reciprocating motion powered pump piston having a pump working space limited.
  • the fuel injection valve has one with the Pump work space associated pressure room and one Injection valve member, through which at least one Injection opening is controlled and by the in the Pressure chamber prevailing pressure against a closing force in Opening direction for releasing the at least one Injection opening is movable. It is a control valve provided by the connection of the pump working space controlled with a discharge space and a pressure source becomes.
  • the pump workspace becomes during the suction stroke of the pump piston with fuel from the Filled pressure source. It is desirable that through the High pressure pump already at low speed Internal combustion engine generates a high pressure, thus a high power and high torque Internal combustion engine is achieved.
  • the one by the High pressure pump generated pressure increases with the speed the internal combustion engine, wherein the maximum pressure generated must be limited to a sufficient durability of the Ensure high pressure pump.
  • the high-pressure pump and a predetermined Diameter of the pump piston must therefore be a compromise be found in the interpretation, on the one hand a sufficiently high pressure to achieve at low speed and on the other hand given the durability reasons not to exceed maximum pressure.
  • the fuel injection device with the Features according to claim 1 has the advantage that the pressure generated by the high pressure pump are limited can by putting the second pump piston in its passive position is brought and only the first pump piston fuel promotes. It can be provided that at lower Speed of the internal combustion engine both pump pistons coupled together and execute a delivery stroke, while at high speed, the second pump piston in his Passive position is arranged and only the first Pump piston performs a delivery stroke, so that the generated Pressure is reduced.
  • the first pump piston can be in Diameter be made so large that already at low speed a high pressure is generated.
  • Training according to claim 2 allows an advantageous arrangement of second pump piston in its passive position.
  • the Training according to claim 3 allows a simple Production of the first pump piston.
  • the training according to Claim 6 allows a pressure equalization between the Pump work space and the space in the first pump piston in Trap of a leak.
  • By training according to Claim 7 ensures that when together coupled pump piston through the through hole in second pump piston no fuel from the Pump work space can drain.
  • By training according to Claim 8 is a system of the second pump piston on the Limitation of the pump working space in the area of the inner Dead center of the pump piston ensured.
  • the Training according to claim 10 ensures that at in his Passiv ein arranged second pump piston at Delivery stroke of the first pump piston through the Through hole in the second pump piston no fuel can flow out of the pump workspace.
  • the Training according to claim 11 is a pressure equalization between the through hole in the second pump piston and the Pump workspace in the area of the inner dead center Pump piston reached.
  • training according to claim 12 is a safe system of the second pump piston at the Limit reached.
  • the embodiment according to claim 13 is simply an arrangement of the second Pump piston reached in its passive position.
  • FIG. 1 shows a Fuel injection device for an internal combustion engine in a schematic representation in a longitudinal section
  • Figure 2 a designated in Figure 1 with II section of Fuel injection device in an enlarged view with two pump pistons in a coupled state in one outer dead center
  • Figure 3 the detail II with the Pump piston in an inner dead center
  • Figure 4 den Section II with a arranged in a passive position Pump piston and one in an outer dead center arranged pump piston
  • Figure 5 the detail II with the Pump piston in decoupled state in an inner Dead center
  • Figure 6 shows a course of the pressure Injection openings of a fuel injection valve of Fuel injection device over time.
  • the internal combustion engine is preferably a self-igniting internal combustion engine.
  • the Fuel injection device is preferably as So-called pump-nozzle unit is designed and has for each cylinder of the internal combustion engine one each High-pressure fuel pump 10 and connected to this Fuel injection valve 12, which has a common Form building unit.
  • the Fuel injection device as a so-called pump-line-nozzle system be trained in which the High-pressure fuel pump and the fuel injection valve each cylinder is arranged separately from each other and over a line are connected together.
  • the High-pressure fuel pump 10 has a pump body 14 with a cylinder bore 16, in the two pump piston 18,118 are arranged, wherein a first pump piston 18 with large diameter in the cylinder bore 16 tightly guided is and at least indirectly by a cam 20 a Camshaft of the internal combustion engine against the force of a Return spring 19 is driven in a lifting movement.
  • One second pump piston 118 is within the first Pump piston 18 at least approximately coaxial with this arranged.
  • the pump piston 18,118 will be below explained in more detail.
  • the two pump pistons 18,118 limit in the cylinder bore 16 with their end faces a Pump work chamber 22, in which the delivery stroke of the pump piston 18,118 fuel is compressed under high pressure.
  • the Pump work chamber 22 becomes fuel from a Fuel tank 24 of the motor vehicle by means of a pressure source, which is preferably a feed pump 23, fed.
  • the fuel injection valve 12 has one with the Pump body 14 connected valve body 26, the may be formed in several parts, and in which at least one Injection valve member 28 in a bore 30th is guided longitudinally displaceable.
  • the valve body 26 indicates its the combustion chamber of the cylinder of the internal combustion engine facing end region at least one, preferably a plurality Injection openings 32.
  • the injection valve member 28 has at its the combustion chamber end facing a For example, about conical sealing surface 34, which with one in the valve body 26 in the combustion chamber facing End region formed valve seat 36 cooperates, from or after which the injection openings 32 dissipate.
  • valve body 26 is between the injection valve member 28 and the bore 30 to the valve seat 36 toward an annular space 38th present, in its the valve seat 36 facing away End region by a radial extension of the bore 30 in a pressure chamber 40 surrounding the injection valve member 28 passes.
  • the injection valve member 28 has the height of the Pressure chamber 40 by a cross-sectional reduction a Pressure shoulder 42 on.
  • a biased Closing spring 44 At the end of the combustion chamber facing away from the Injector member 28 engages a biased Closing spring 44, through which the injection valve member 28th is pressed toward the valve seat 36.
  • the closing spring 44 is arranged in a spring chamber 46 of the valve body 26, the adjoins the bore 30.
  • a second injection valve member at least approximately coaxially displaceable within the injection valve member 28 is arranged by the at least one second Injection opening is controlled.
  • the at least one second Injection opening is in the direction of the long axis of Injection valve member 28 to the at least one first Injection opening 32 arranged offset to the combustion chamber.
  • the second injection valve member is replaced by a second Closing spring acted upon in the closing direction. Besides that is the second injection valve member at least indirectly from the in a pressure chamber prevailing pressure in the closing direction applied.
  • a further bore 48th connect, in which a control piston 50 is tightly guided, which is connected to the injection valve member 28.
  • a control piston 50 In the Bore 48 is through the end face of the control piston 50th limited as a movable wall, a control pressure chamber 52.
  • the Control piston 50 Of the Control piston 50 is one opposite this in the Diameter smaller piston rod 51 with the Injection valve member 28 connected.
  • the control piston 50 can formed integrally with the injection valve member 28 is however, for reasons of assembly preferably as a separate Part connected to the injection valve member 28.
  • a channel 60 to the pressure chamber 40 of the Fuel injection valve 12.
  • a channel 62 leads to the control pressure chamber 52.
  • the control pressure chamber 52 also opens a channel 64, the makes a connection to a relief room when the at least indirectly, the fuel tank 24 or another area may serve in which a low pressure prevails.
  • From the pump chamber 22 or channel 60 leads a connection 66 to a discharge room, as the for example, at least indirectly the Fuel tank 24 or the pressure side of the Feed pump 23 can serve, and to the feed pump 23 from.
  • the Connection 66 is actuated by a first electrically operated Control valve 68 controlled.
  • the control valve 68 can be used as a 2/2-way valve be educated.
  • the connection 64 of Control pressure chamber 52 with the discharge chamber 24 is through controlling a second electrically operated control valve 70, which can be designed as a 2/2-way valve.
  • a throttle point 63 is provided in the Connection 62 of the control pressure chamber 52 with the Pump work chamber 22 and in the connection of the control pressure chamber 52 with the Relief space 24, a throttle point 65 is provided in the connection of the control pressure chamber 52 with the Relief space 24, a throttle point 65 is provided.
  • suitable dimensioning of the throttle bodies 63,65 the inflow of fuel from the pump working space 22 in the control pressure chamber 52 and the outflow of fuel the control pressure chamber 52 to a required extent be set.
  • a sufficient inflow of fuel in the control pressure chamber 52 is for a quick closing required and the fuel injection valve 12 sufficient drainage of fuel from the control pressure chamber 52 is for a quick opening of the Fuel injection valve 12 required.
  • the Control valves 68,70 may be an electromagnetic actuator or have a piezoelectric actuator and are by a electronic control device 72 is controlled.
  • the first pump piston 18 has a at least approximately coaxial in this running Blind bore 80, which is the pump working space 22nd limiting end face of the pump piston 18 is open.
  • the mouth of the blind bore 80 at the front of the first Pump piston 18 has an example at least approximately conical bevel 81, so that the Diameter of the blind bore 80 increases.
  • the first pump piston 18 a Cross hole 83, the blind bore 80 with an am Outer jacket of the pump piston 18 introduced, in Longitudinally extending longitudinal groove 84 connects.
  • the Longitudinal groove 84 extends from the transverse bore 83 both towards the pump working chamber 22 out as well as from this way.
  • the first pump piston 18 also has in a middle region of its longitudinal extension another Cross hole 85, the blind bore 80 with a further introduced on the outer casing of the pump piston 18 Longitudinal groove 86 connects.
  • the longitudinal groove 86 extends starting from the transverse bore 85 to the pump working space 22nd out.
  • a transverse bore 87th provided, which is connected to a low pressure area and with the longitudinal groove 84 of the first pump piston 18 via the entire stroke of the pump piston 18 is in communication. In the low pressure area, for example at least approximately atmospheric pressure.
  • the cylinder bore 16 has in its end, in which the pump working space 22nd is arranged, a section 116 with a slightly larger Diameter up than in its remaining area, in which the first pump piston 18 is guided tightly.
  • the cylinder bore 16 and thus the pump working space 22 formed in this has an at least approximately perpendicular to the longitudinal axis of the arranged first pump piston 18, the Pump work space 22 delimiting front side of the Pump piston 18 opposite boundary 17 on.
  • the second pump piston 118 is in the blind bore 80 of the first pump piston 18 slidably guided and protrudes his the pump working space 22 limiting end of the Blind hole 80 out. At his from the blind hole 80th projecting end, the second pump piston 118 in the Diameter enlarged section 150, on which a first pump piston 18 facing annular shoulder 151 formed is.
  • the second pump piston 118 has a in the Longitudinally extending passageway 180, which as Through hole may be formed extending from the the pump working space 22 limiting end face up to the the bottom 82 of the blind bore 80 in the first pump piston 18th opposite end face of the second pump piston 118th extends. In the through hole 180 of the second Pump piston 118 is a throttle point 181 is provided.
  • the boundary 17 of the pump working space 22 opposite end face of the second pump piston 118th is tapered, for example, conical, that this in radial direction inwards to the mouth of the Through hole 180 is recessed towards. This is at the End face of the second pump piston 118 at the radial outer edge an annular edge present, the one Sealing surface 152 forms.
  • a spring 158 clamped, for example, as one the section 154 of the second Pump piston 118 surrounding coil spring formed is.
  • a Cross hole 160 provided, the through hole 180th with an outer jacket of the second pump piston 118 introduced annular groove 161 connects.
  • the second pump piston 118 is in the blind bore 80 of the first pump piston 18th at least in its area between the transverse bore 160 and the protruding from the blind bore 80 section 150 with tight match.
  • the second one Pump piston 118 at least in a part of the range between the transverse bore 160 and the annular shoulder 155 with little game led tightly in the blind bore 80.
  • both pump pistons 18,118 coupled together can be and as a unit a delivery hub To run.
  • the pump pistons move 18,118 starting from an outer dead center in which this as shown in Figure 2 farthest from the Cylinder bore 16 protrude, to an internal dead center, in the these as shown in Figure 3 furthest in the Cylinder bore 16 are immersed. If both pump pistons 18,118 are coupled together, so the second appears Pump piston 118 in the blind bore 80 of the first Pump piston 18 until it with its sealing surface 156 at the bottom 82 of the blind bore 80 is applied, as in the Figures 2 and 3 is shown.
  • the second pump piston 118 moves during the suction stroke due to the on the end face acting pressure in the pump working chamber 22 also from inner dead center away when the by the im Pump working space 22 prevailing pressure on the second Pump piston 118 generated force is greater than that counteracting force, which is the sum of the force of the spring 158 and by the prevailing in room 153 low pressure force generated on the second pump piston 118.
  • the second Pump piston 118 moves during the suction stroke of the inner Dead center away and reaches with its sealing surface 156th at the latest when reaching the outer dead center in Appendix the bottom 82 of the blind bore 80 in the first pump piston 18th During the subsequent delivery stroke, the pump pistons move 18,118 then again as unity inward to the inner Dead center.
  • the second pump piston 118th can be optionally arranged in a passive position, in who does not carry out a delivery stroke and only the first one Pump piston 18 performs a delivery stroke. This is in the Figures 4 and 5 shown. In his passive position is the second pump piston 118 with his Sealing surface 152 in contact with the boundary 17 of Pump workspace 22. The through hole 180 in the second Pump piston 118 is then through the sealing surface 152 of Pump work space 22 separated. Should be between the Sealing surface 152 and the limit of a leak be present, so can a small amount of fuel from the Pump work chamber 22 through the through hole 180 in the Room 153 and drain to the low pressure area, the Flow through the throttle point 181 is limited.
  • An arrangement of the second pump piston 118 in his Passiv ein takes place during the suction stroke depending on Operating parameters of the internal combustion engine, in particular depending on their speed.
  • the second pump piston 118 is to be arranged in its passive position, so will during the suction stroke, the first control valve 68 through the Control device 72 at a given time and for closed a certain period of time, so that the connection the pump working chamber 22 with the feed pump 23rd is interrupted and in the pump working chamber 22 no Fuel can flow.
  • the first pump piston 18 moves caused by the return spring 19 according to the Shape of the cam 20 from the inner dead center away to the outer one Dead center.
  • the volume of the Pump workspace 22 increases and there is no fuel in this inflow drops the pressure in the pump chamber 22 from under the delivery pressure of the feed pump 23.
  • the lower to the first pump piston 18 out directed force is generated on the second pump piston 118 as the counteracting force as the sum of the force of Spring 158 and by the acting in space 153 Low pressure generated force.
  • the second pump piston 118 moves inward until he is with his Sealing surface 152 at the boundary 17 of the pump working space 22 comes to the plant.
  • the first control valve 68 through the Control device 72 opened again, so that the pressure in Pump workspace 22 rises again.
  • the pressure in the Pump working space 22 acts in its passive position arranged second pump piston 118 on these, however not on its face towards the first Pump piston 18 out but on the annular shoulder 151 of the second pump piston 118 and thus to the limit 17 out and generates a pressing force on the second pump piston 118 to the limit 17 out.
  • the first pump piston 18 leads a suction stroke to the outer dead center and then a delivery stroke to the inner dead center.
  • first Pump piston 18 reaches the region of the inner dead center, so is the through hole 180 of the second pump piston 118 via the transverse bore 160, the annular groove 161 and the Transverse bore 85 and the longitudinal groove 86 in the first pump piston 18, in the section 116 of the cylinder bore 16th immersed, connected to the pump working space 22.
  • On the boundary 17 facing end face of the second Pump piston 118 then affects the pressure in the pump working space 22, so that the second pump piston 118 with his Sealing surface 152 lifts from the boundary 17.
  • the second pump piston 118 in its passive position can be arranged or, if the first Control valve 68 is constantly open, the second Pump piston 118 the suction stroke of the first pump piston 18th follow, so that the two pump pistons 18,118 coupled stay.
  • the first control valve 68 as above explained during the suction stroke is closed to ensure that the second pump piston 118 in its passive position is arranged.
  • the closing of the first control valve 68th omitted because then it is ensured that the second Control piston 118 due to the pressure drop in Pump workspace 22 arranged in its passive position becomes.
  • an arrangement of the second pump piston 118 in its passive position depends on operating parameters of Internal combustion engine, in particular depending on the load, he follows. It can be provided, for example, that at high load, the two pump pistons 18,118 are coupled and perform a delivery stroke together, while at lower Load the second pump piston 118 in its passive position is arranged and only the first pump piston 18 a Carrying stroke performs. At low load thus takes place Fuel injection with a lower pressure than at high load. By the shape of the cam 20 in the area, in the suction stroke of the first pump piston 18 takes place the speed of the first pump piston 18 during the suction stroke certainly.
  • FIG. 6 the Course of the pressure p at the injection openings 32 of the Fuel injection valve 12 over the time t during a Injection cycle shown.
  • the suction stroke of the pump piston 18 gets this fuel from the fuel tank 24 supplied.
  • the first control valve 68 by the controller 72nd is closed, so that the pump chamber 22 from Relief space 24 is disconnected.
  • the second control valve 70 is also opened so that the control pressure chamber 52 connected to the discharge chamber 24 is. In this case, in the control pressure chamber 52 no Build high pressure, as this to the relief space 24 out is relieved.
  • Control valve 70 is closed, so that the control pressure chamber 52nd is separated from the discharge space 24.
  • the first control valve 68 remains in its closed position. in the Control pressure chamber 52 builds up high pressure as in Pumping work chamber 22, so that on the control piston 50th a large pressure force acts in the closing direction. There now the on the injection valve member 28 in the opening direction 29th acting force is less than the sum of the force of Closing spring 44 and the pressure force on the control piston 50th closes the fuel injection valve 12.
  • the Pre-injection corresponds to one in Figure 6 with I designated injection phase.
  • the second control valve 70 For a subsequent main injection, the one in FIG 6 corresponds to II designated injection phase, the second control valve 70 by the controller 72nd opened, so that the pressure in the control pressure chamber 52 decreases.
  • the Fuel injection valve 12 then opens as a result of reduced pressure force on the control piston 50 and the Injector member 28 moves above its maximum Opening stroke.
  • With opened second control valve 70 flows a small amount of fuel through the throttle bodies 63,65 to the relief space 24 from, however, the throttle bodies 63,65 be formed with a small flow area, so that the outflowing fuel quantity and the reduction the pressure in the pump working space 22 is low.
  • the first Control valve 68 by the controller 72 in his opened switch position, so that the Pump working space 22 connected to the discharge chamber 24 is and on the injection valve member 28 in the opening direction 29 only a small pressure force acts and that Fuel injection valve 12 due to the force of Closing spring 44 and by the control pressure in the space 52nd prevailing residual pressure on the control piston 50 generated Strength closes.
  • the second control valve 70 may be for Completion of the main injection in its open or closed position.
  • both pump pistons 18,118 When controlling the two control valves 68,70 through the It is fuel injection control means 72 required that in the controller 72 a Information is available about whether both pump pistons 18,118 perform a delivery stroke or only the first Pump piston 18 performs a delivery stroke, as appropriate the pressure in the fuel injection is different is.
  • a Information is available about whether both pump pistons 18,118 perform a delivery stroke or only the first Pump piston 18 performs a delivery stroke, as appropriate the pressure in the fuel injection is different is.
  • the control piston 50, the control pressure chamber 52 and the Connection with the relief room controlling second Control valve 70 may also be omitted.
  • the Fuel injection is then only through the first Control valve 68 controlled by this to Fuel injection is closed, so that the Pump working space 22 is separated from the discharge space 24, and for the interruption or termination of the Fuel injection is opened, so that the Pump workspace 22 to the discharge chamber 24 out relieved of pressure.

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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)
EP02792634A 2002-02-20 2002-12-06 Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine Expired - Lifetime EP1478841B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10207045A DE10207045A1 (de) 2002-02-20 2002-02-20 Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10207045 2002-02-20
PCT/DE2002/004479 WO2003071124A1 (de) 2002-02-20 2002-12-06 Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP1478841A1 EP1478841A1 (de) 2004-11-24
EP1478841B1 true EP1478841B1 (de) 2005-07-13

Family

ID=27635165

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02792634A Expired - Lifetime EP1478841B1 (de) 2002-02-20 2002-12-06 Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine

Country Status (6)

Country Link
US (1) US6886535B2 (zh)
EP (1) EP1478841B1 (zh)
JP (1) JP2005517864A (zh)
CN (1) CN1329654C (zh)
DE (2) DE10207045A1 (zh)
WO (1) WO2003071124A1 (zh)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10233099A1 (de) * 2002-07-20 2004-02-05 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
US8597849B2 (en) * 2005-08-30 2013-12-03 GM Global Technology Operations LLC Pressure activated shut-off valve
DE102005060274A1 (de) * 2005-12-16 2007-06-21 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102006027330A1 (de) * 2006-06-13 2007-12-20 Robert Bosch Gmbh Kraftstoffinjektor
GB2567011B (en) * 2017-10-02 2021-01-20 Caterpillar Motoren Gmbh & Co Fuel injection system for engine system
DE102018200715A1 (de) * 2018-01-17 2019-07-18 Robert Bosch Gmbh Kraftstofffördereinrichtung für kryogene Kraftstoffe
US11933257B2 (en) * 2022-03-18 2024-03-19 Caterpillar Inc. Fuel injector lift control

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3847510A (en) * 1973-11-26 1974-11-12 Cav Ltd Fuel pumps for internal combustion engines
JPH0759919B2 (ja) * 1986-04-04 1995-06-28 日本電装株式会社 デイ−ゼルエンジン用燃料噴射制御装置
US5709341A (en) * 1996-05-03 1998-01-20 Caterpillar Inc. Two-stage plunger for rate shaping in a fuel injector
DE19703765C1 (de) * 1997-02-01 1998-06-10 Fissler Gmbh Dampfdruckkochtopf
DE19732802A1 (de) * 1997-07-30 1999-02-04 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
CN2319141Y (zh) * 1997-12-19 1999-05-19 中国矿业大学 捷线等厚筛面
GB9820237D0 (en) * 1998-09-18 1998-11-11 Lucas Ind Plc Fuel injector
DE19949818A1 (de) * 1999-10-15 2001-04-26 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
JP2002305354A (ja) * 2001-04-05 2002-10-18 Furukawa Electric Co Ltd:The 面発光型半導体レーザ素子
DE10339980B4 (de) * 2003-08-29 2011-01-05 Osram Opto Semiconductors Gmbh Halbleiterlaser mit reduzierter Verlustwärme

Also Published As

Publication number Publication date
CN1483109A (zh) 2004-03-17
JP2005517864A (ja) 2005-06-16
CN1329654C (zh) 2007-08-01
DE50203647D1 (de) 2005-08-18
WO2003071124A1 (de) 2003-08-28
DE10207045A1 (de) 2003-08-28
US6886535B2 (en) 2005-05-03
EP1478841A1 (de) 2004-11-24
US20040182951A1 (en) 2004-09-23

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