EP0962648A1 - Dispositif d'injection de combustible - Google Patents

Dispositif d'injection de combustible Download PDF

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Publication number
EP0962648A1
EP0962648A1 EP98110176A EP98110176A EP0962648A1 EP 0962648 A1 EP0962648 A1 EP 0962648A1 EP 98110176 A EP98110176 A EP 98110176A EP 98110176 A EP98110176 A EP 98110176A EP 0962648 A1 EP0962648 A1 EP 0962648A1
Authority
EP
European Patent Office
Prior art keywords
pressure
fuel
delivery piston
fuel injection
delay
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.)
Withdrawn
Application number
EP98110176A
Other languages
German (de)
English (en)
Inventor
Wolfgang Dr. Heimberg
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to EP98110176A priority Critical patent/EP0962648A1/fr
Priority to AU45067/99A priority patent/AU4506799A/en
Priority to EP99927875A priority patent/EP1084343A1/fr
Priority to PCT/EP1999/003876 priority patent/WO1999063217A1/fr
Publication of EP0962648A1 publication Critical patent/EP0962648A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • F02M59/107—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 pneumatic drive, e.g. crankcase pressure 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • 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
    • F02M51/04—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
    • 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
    • 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
    • F02M59/205—Quantity of fuel admitted to pumping elements being metered by an auxiliary metering device
    • 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
    • F02M59/22—Varying quantity or timing by adjusting cylinder-head space
    • 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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/12—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel comprising a fuel-displaced free-piston for intermittently metering and supplying fuel to injection nozzles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B13/00—Pumps specially modified to deliver fixed or variable measured quantities

Definitions

  • the invention relates to a fuel injection device for Internal combustion engines.
  • Such fuel injectors are e.g. from the DD-PS 213 472, WO 96/34196, EP 0 630 442 B1, DB 195 15 782 A1, WO 93/18297 and DE 42 06 817 C2 are known.
  • Such a fuel injection device has a reciprocating pump with an accelerator and a one Fuel-containing space-limiting feed piston element on (see e.g. DD-PS 213 472).
  • a reciprocating pump with an accelerator and a one Fuel-containing space-limiting feed piston element on (see e.g. DD-PS 213 472).
  • the accelerator body stores kinetic energy.
  • the accelerator hits on the delivery piston element, which suddenly the kinetic energy of the delivery piston element on the Fuel is transferred.
  • the fuel becomes an injection nozzle through a pressure line transported with which the fuel in a Combustion chamber of an internal combustion engine is injected.
  • DE 42 06 817 C2 describes one based on the solid-state energy storage principle working fuel injector known, which instead of the accelerator and Delivery piston element has only one delivery piston, during an almost resistance-free acceleration phase Feeds fuel into a volume storage element (e.g. Fig. 1 DE 42 06 817 C2).
  • the volume storage element has one elastic membrane on the ingress of fuel in the volume storage element yields and the volume of the volume storage element changed. Is the maximum volume of the Volume storage element reached, so suddenly further delivery of fuel into the volume storage element interrupted and the energy stored in the delivery piston transfer the fuel that is injected through an injector becomes.
  • the elastic membrane is supported by a spring held the starting position. The spring hardness of the membrane acted upon spring is chosen so low that accordingly the teaching of this patent the acceleration phase of the piston is essentially unresistible.
  • FIG. 6 Another embodiment is evident from DE 42 06 817 C2 (Fig. 6), in which the delivery piston is axially displaceable in Anchor is stored.
  • the delivery piston is axially displaceable in Anchor is stored.
  • the guide part of the piston is one Spring applied, which is relatively soft and itself with its other end at the bottom of the anchor's blind hole supports. The spring serves to keep the piston and the armature in the starting position between two injection processes Be kept clear and is soft so that the resistance-free acceleration of the armature during the acceleration phase is not affected.
  • Fuel injectors can handle very high injection pressures from 60 to 80 bar.
  • FIG. 5 shows the pressure profile of a conventional injection device, which has a reciprocating piston pump as the delivery element and which operates in particular according to the solid-state energy storage principle.
  • the pressure at the injection nozzle suddenly rises to the maximum pressure P max at a time t 1 .
  • the injection pressure is not constant, but can fluctuate considerably.
  • pressure troughs frequently occur (in FIG. 5 at t 2 ), which lead to a substantial deterioration in the injection behavior and in particular in the droplet quality.
  • the pressure can drop below the nozzle opening pressure of the injection nozzle, so that there can be brief interruptions in the injection process. This can lead to considerable impairments in the ignition and combustion behavior in the combustion chamber of the internal combustion engine.
  • the injection pressure gradually decreases due to the continuously slowing delivery piston, so that the initially good atomizing effect (at P max ) decreases.
  • These undefined pressure states at the end of the injection pulse are additionally superimposed by a bouncing of the nozzle needle, as a result of which both the droplet size and the amount of fuel become uncontrollable.
  • common rail systems To achieve high injection pressures are used in automotive engineering so-called common rail systems are used. These common rail systems have a directly adjacent to the combustion chamber High-pressure fuel storage reservoir, in which Fuel, for example, is stored at 100 to 200 bar. Of the Fuel is opened by opening and closing a valve injected a combustion chamber.
  • the common rail system can be compared to that based on the solid state energy storage principle working fuel injectors generate higher injection pressures.
  • the pressure over the entire injection process is essentially constant, which makes a very even and fine atomized fuel jet sprayed from the injector becomes.
  • a disadvantage of the common rail system is the enormously high technical Effort for the formation of the high-pressure fuel storage reservoir and the corresponding pump equipment, to keep up the pressure.
  • the injection devices having a reciprocating pump are much smaller, simpler, lighter and provide the print only when needed. These are essential Advantages over the common rail system.
  • the invention has for its object a fuel injection device to create with a reciprocating pump, which in Comparison to the conventional, especially according to the solid-state energy storage principle working fuel injectors a better and more even energy input having.
  • the fuel injection device has a Delay device on the transmission of energy delayed from the delivery piston to the fuel.
  • the delay device is designed such that preferably in Range of the opening pressure of the injector the movement of the Delivery piston decelerated so that the pressure in the fuel does not rise suddenly.
  • the inventor of the present invention recognized that cannot open the injector suddenly. During one over a period of e.g. 0.5 ms opening phase is because of the only partially open injector Fuel flow rate limited, so that between the Delivery piston and fuel injector located in the injector opposes the delivery piston a considerable resistance and slows it down.
  • the sudden Energy transfer generated pressure on the not yet or only partially opened injector reflected, causing counter pressure waves directed towards the conveying direction arise additionally brake the delivery piston and thus withdraw energy from it.
  • the energy available for injection is not be fully exploited.
  • the energy transfer is delayed at least during the region of the opening phase of the injection nozzle, so that the energy transfer from the delivery piston to the fuel column is reduced during this opening phase.
  • the braking effect explained above is reduced and the generation of pressure waves reflected at the partially open injection nozzle is substantially reduced.
  • the duration of the opening phase is largely independent of the pressure applied to the injection nozzle, provided that it is greater than the opening pressure P nozzle . This means that additional energy introduced during the opening phase does not significantly shorten the opening phase, but instead leads to the generation of reflected pressure waves and greater braking of the delivery piston.
  • the energy transfer from the delivery piston to the fuel column is not delayed until the opening pressure P nozzle of the injection nozzle is reached, so that the opening pressure P nozzle is essentially suddenly reached in order to obtain the fastest possible response of the pump-nozzle system.
  • the part of the conventional injectors brake the reflected pressure waves when the injector is open not only the delivery piston, but also between the injection nozzle and the delivery piston reflected back and forth, which causes the pressure at the injector Fluctuations.
  • These pressure fluctuations lead to a undesirable, uneven droplet formation in the fuel jet. Since in the injector according to the invention the pressure fluctuations are significantly reduced, the Pressure fluctuations at the injection nozzle eliminated and one more uniform droplet formation is achieved.
  • Delay element formed as an elastic element that Energy is temporarily stored and pressure valleys can be compensated for Pressure fluctuations can be further reduced.
  • Fig. 1 shows schematically a first embodiment of the invention Cross section of the injection device.
  • This injector has an approximately tubular housing 3, that at the rear in the conveying direction 4 through a housing cover 5 is completed.
  • the front in the conveying direction 4 End forms a connection opening 7 for receiving a Pressure line 8, which leads to an injection nozzle 9.
  • the armature 12 has a substantially cylindrical shape Base body 14 on with its jacket wall the inner wall of the tubular housing 3 abuts. At the rear end of the base body 14 is the guide socket 13 scheduled.
  • the armature 12 On the front end in the conveying direction the armature 12 is a blind hole-like, approximately hollow cylindrical Recess 15 introduced. A distance from the front end face of the armature 12 is in the recess 15 a guide area 16 through a concentric guide recess with a larger inner diameter than the rest of the recess 15 trained.
  • the guide area 16 is thus both in conveying direction 4 as well as opposite to the conveying direction 4 delimited by an annular edge 17, 18.
  • a conveying piston 20 is arranged upstream of the armature 12 in the conveying direction 4, the one with its rear end in the recess 15 of the armature 12 protrudes.
  • the rear end of the delivery piston 20 forms a guide part 22 which protrudes outwards and engaging in the guide area 16 of the armature 12 Ring web 23 has.
  • the guide part 22 is in the recess 15 slidably mounted, the relative movement between the armature 12 and the delivery piston 20 through the ring edges 17, 18 is limited, which as stops for the ring web 23rd serve the guide part 22.
  • Compression spring 25 is used with bias, which the guide part 22 of the delivery piston 20 against the front ring edge 18 presses.
  • the front end of the delivery piston 20 in the conveying direction 4 is supported in a guide bushing 27.
  • the guide bushing 27 is in one from the inner wall of the tubular housing 3 internally projecting ring land 28 used.
  • the ring web 28 limits one in the tubular housing 3 between it and the rear cover 5 formed anchor space 30, in which the anchor 12 is slidably disposed.
  • the guide bushing 27 protrudes a little towards the rear into the armature space 30 and has an outwardly projecting at its front end Ring web 32 with which it the ring web 28 of the housing 3 engages behind.
  • the return spring is a very soft spring with no or very little preload is used so that it is only in the reset of the Anchor 12 overcomes its frictional forces, but the movement the armature 12 in the conveying direction 4 no significant resistance opposed.
  • a fuel supply opening 36 introduced, which extends radially inwards from the outside through the Housing 3 and the guide bushing 27 extends. Is outside at the fuel supply opening 36 on the housing 3, a connecting piece 37 for connecting a fuel supply line (not shown) trained.
  • a check valve 38 is arranged, the one Shuts off fuel flow back into the fuel supply line.
  • a parking pressure valve 40 is arranged, which blocks the connection to the injection nozzle 9, provided that the pressure applied to the parking pressure valve 40 is less than a certain passage pressure P through .
  • the passage pressure is generally considerably lower than the opening pressure P nozzle of the injection nozzle 9, at which the injection nozzle 9 opens.
  • the through the check valve 38, the parking pressure valve 40 and the front face of the delivery plunger in the conveying direction 20 limited area forms a pressure chamber 42.
  • Electromagnet 44 arranged for actuating the armature 12.
  • the armature 12 lies in the starting position shown in FIG. 1 with its rear end face on the guide bushing 11 and the delivery piston 20 rests with its guide part 22 the front ring edge 18 of the armature 12.
  • the armature 12 is driven in the conveying direction 4 by the electromagnet 44, the delivery piston 20 being first pressed by the armature 12 against the fuel located in the pressure chamber 42 and in the pressure line 8 without the relative position thereof changing (at a in FIG. 6 ).
  • the delivery piston 20 pressurizes the fuel, wherein when the passage pressure P is reached by the auxiliary pressure valve 40, the auxiliary pressure valve 40 opens and releases the connection to the injection nozzle 9.
  • the injector 9 opens and fuel is injected from the injector 9 into the combustion chamber (not shown).
  • the pressure build-up to the nozzle opening pressure P nozzle takes place almost instantaneously, because of the incompressibility of the fuel and the armature and Delivery piston existing unit performs only a minimal movement until the nozzle opening pressure P nozzle is reached.
  • the delivery piston 20 is pushed from a certain pressure in the pressure chamber 42 or in the high-pressure line 8, which is hereinafter referred to as deceleration pressure P V , into the recess 15 against the spring action of the compression spring 25, whereby the further pressure build-up is delayed.
  • the armature moves 12 with a guide speed in the conveying direction 4.
  • the delivery piston 20 is at a reduced speed moves in the direction of conveyance 4 because the delivery piston opposes the spring action of the spring 25 into the recess of the armature 12 immersed (at b in Fig. 6). There is therefore a relative speed between the delivery piston 20 and the armature 12. Due to this reduced speed compared to the anchor 12 of the delivery piston 20, the energy transfer from the armature 12 reduced on the delivery piston 20 or on the fuel.
  • the spring hardness of the compression spring 25 and the stroke of the guide part 23 in the guide area 16 is preferably dimensioned such that the pressure build-up is delayed at least during a first part of the opening phase of the injection nozzle 9, during which the injection nozzle 9 opens only slowly.
  • P End 1.5P jet up to 3P jet
  • the delivery piston 20 is moved at the guide speed of the armature 12 in the delivery direction 4, so that the pressure continues to increase at the maximum rate of increase to the maximum pressure P MAX (at c in FIG. 6).
  • the nozzle opening pressure P nozzle is typically in the range from 1 to 5 MPa and the cross-sectional area A piston of the delivery piston 20 is usually 5 to 20 mm 2 .
  • the deceleration pressure P V is set to the opening pressure of the injector 9.
  • the pressure in the fuel to be delivered rises to the maximum pressure P MAX , which is higher than in comparable conventional injection devices, since only a relatively small amount of energy is input during the opening phase of the injection nozzle, so that a higher energy yield is achieved and less disturbing pressure reflections are generated .
  • the fuel is then injected at an approximately constant pressure P MAX , since the reflections of the pressure waves are largely avoided (at d in FIG. 6). Should pressure troughs nevertheless occur (dashed line at t 2 in FIG. 6), the energy stored with the pressure spring 25 ensures that these do not drop below the nozzle opening pressure, since such deep pressure troughs are compensated for by the energy stored in the pressure spring.
  • the injector according to the invention works during the opening phase of the injection valve of the armature 12 is not against the pressure waves running counter to the conveying direction and the injector that is not yet fully open braked fuel column, but transmits the one in it The energy introduced is only completely on the fuel column after the injector is fully open.
  • Another significant advantage of this invention Injector is that at the end of the injection pulse, when through the electromagnet to the armature / piston unit exerted force becomes lower and this increases generated delivery pressure reduced, the stored in the compression spring 25 Energy drives the delivery piston 20 until it moves with its guide part 22 abruptly on the front ring edge 18 of the anchor 12 strikes and is stopped. The injection pulse is thus abruptly ended and points to his End an abrupt drop (at e in Fig. 6).
  • exact pressure ratios at the end of the injection pulse achieved, which both the spray behavior (uniform droplet size) as well as the meterability of the Improve fuel significantly.
  • FIG. 2 A second embodiment of an injection device according to the invention is shown in Fig. 2.
  • This embodiment has essentially the same Structure as the first embodiment, which is why the same Parts are provided with the same reference numerals.
  • a flat cylindrical Damping recess 50 with a jacket wall 51 brought in.
  • a flat cylindrical damping plunger 54 formed with a lateral surface 55, which is essentially the same cross-sectional shape as the damping recess 50 has, so that the damping ram 54 with little Game fits into the damping recess 50.
  • the ring web 23 of the delivery piston 20 is provided with longitudinal grooves (not shown) so that the delivery piston as long as the Damping stamp 54 is located outside the damping recess 50 located, essentially resistance-free in the fuel filled recess 15 of the armature 12 can be moved can.
  • the resistance-free displacement path X is shown in FIG. 2.
  • the armature 12 is moved by the electromagnet 44 in the conveying direction 4 moves, along the displacement path X for storage kinetic energy accelerated essentially without resistance becomes.
  • the damping plunger 54 penetrates into the damping recess 50 a, between the jacket wall 51 of the damping recess 50 and the outer surface 55 of the damping ram 54 a narrow gap forms, so that the between the Damping stamp 54 and the damping recess 50 located Only gradually escape fuel and the damping stamp 54 delayed only by the damping in the damping recess 50 can penetrate.
  • This delay occurs from the beginning of the injection pulse and lasts at least until the Injector 9 is fully open.
  • the duration of the delay can by the depth of the damping recess 50 or the gap width between the damping ram 54 and the damping recess 50 can be set. Because of this delay The energy transfer will only partially reflect the opened injector 9 and the associated disadvantages avoided.
  • the delay device a mechanical damping device to delay the build-up of pressure consisting of the damping ram 54 and the damping recess 50.
  • the damping device also be different, e.g. from a plastically deformable damping stamp, which is when it hits of the armature on the delivery piston plastically deformed and so the pressure build-up in the fuel is delayed.
  • FIG. 3 A third exemplary embodiment of the invention is shown in FIG. 3 shown.
  • This embodiment is similar to the two described above Embodiments carried out so that the same Parts are provided with the same reference numerals.
  • the delivery piston 20 and the armature 12 are in one piece executed.
  • the delay chamber 55 is like a blind hole with a jacket wall 58 and a bottom wall 59 executed and has a hollow cylindrical shape.
  • a delay piston 57 slidably mounted, the flush ends with the jacket wall 58 of the delay chamber 55.
  • Delay piston 57 is a recess for receiving a Compression spring 60 introduced into the bottom wall 59, the preload between the delay piston 57 and that in the bottom wall 59 introduced recess is inserted.
  • the armature / piston unit is moved by the magnet 44 in the conveying direction 4, as a result of which fuel is displaced from the pressure chamber 42 to the injection nozzle 9. If the deceleration pressure P V set in the deceleration chamber 55 by the pretension of the compression spring 60 is reached in the pressure chamber 42, fuel escapes into the deceleration chamber 55, the deceleration piston 57 being inserted into the deceleration chamber 55. As a result, the pressure build-up in the pressure chamber 42 and consequently in the high-pressure line 8 is delayed, so that the pressure does not increase suddenly, but rather increases gradually. The deceleration process ends when the deceleration piston 57 strikes the bottom wall 59.
  • the delay period is determined by the spring hardness of the spring 60 and the stroke of the delay piston 57 in the delay chamber 55. As a result, reflections of the pressure waves are avoided in the same way as in the first exemplary embodiment described above, and the pressure curve shown in FIG. 6 is achieved.
  • FIG. 4 A fourth embodiment of the invention is shown in FIG. 4 shown. This embodiment is similar to the third Embodiment formed, which is why the same parts the same reference number.
  • the armature 12 and the delivery piston 20 are separate components formed, the armature 12 made of a cylindrical Base body 14 with one with respect to the conveying direction 4 rear end of the attached guide socket 13.
  • the armature is in turn by a return spring 34, the ring web projecting inwards into the housing 3 28 supports, pressed against the conveying direction 4.
  • the return spring 34 is used with little or no preload, so that the armature 12 when moving in the conveying direction practically no resistance and this when actuated by the electromagnet 44 essentially can be accelerated without resistance.
  • the delivery piston 20 is inserted into the ring land 28 Guide bushing 27 slidably mounted in the axial direction.
  • the Delivery piston 20 is essentially rod-shaped with an on its front end radially outwardly projecting ring land 70 formed of the front end in the conveying direction 4 of the Engages behind guide bushing 27.
  • a delivery piston return spring 71 used to oppose the delivery piston the conveying direction 4 presses, so that in the shown in Fig. 4 Starting position of the ring web 70 on the front Front face of the guide bush 27 strikes.
  • the method of operation of the fourth exemplary embodiment essentially corresponds to that of the third exemplary embodiment, but when the magnet 44 is excited, the armature 12 alone is accelerated essentially without resistance. After the armature 12 has covered the path X, it strikes the delivery piston 20 and suddenly transfers its kinetic energy to the delivery piston 20. The delivery piston 20 displaces the fuel in the pressure chamber 42, the further one after reaching the deceleration pressure P V Pressure build-up as in the third exemplary embodiment is delayed by the delay device (delay chamber 55, delay piston 57, compression spring 60).
  • This embodiment thus combines that from the prior art known solid-state energy storage principle and the delay of pressure build-up according to the invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
EP98110176A 1998-06-04 1998-06-04 Dispositif d'injection de combustible Withdrawn EP0962648A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP98110176A EP0962648A1 (fr) 1998-06-04 1998-06-04 Dispositif d'injection de combustible
AU45067/99A AU4506799A (en) 1998-06-04 1999-06-04 Pumping device
EP99927875A EP1084343A1 (fr) 1998-06-04 1999-06-04 Dispositif de pompage
PCT/EP1999/003876 WO1999063217A1 (fr) 1998-06-04 1999-06-04 Dispositif de pompage

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP98110176A EP0962648A1 (fr) 1998-06-04 1998-06-04 Dispositif d'injection de combustible

Publications (1)

Publication Number Publication Date
EP0962648A1 true EP0962648A1 (fr) 1999-12-08

Family

ID=8232054

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98110176A Withdrawn EP0962648A1 (fr) 1998-06-04 1998-06-04 Dispositif d'injection de combustible

Country Status (1)

Country Link
EP (1) EP0962648A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4426198A (en) * 1979-05-28 1984-01-17 Societe D'etudes De Thermiques S.E.M.T. Fuel-injection pump for internal combustion engine
GB2170557A (en) * 1984-11-13 1986-08-06 Diesel Kiki Co Fuel injection pumps
EP0315564A1 (fr) * 1987-11-02 1989-05-10 Stanadyne Automotive Corp. Pompe-injecteur combinée à commande électronique
DE4206817A1 (de) * 1991-10-07 1993-04-29 Ficht Gmbh Kraftstoff-einspritzvorrichtung nach dem festkoerper-energiespeicher-prinzip fuer brennkraftmaschinen
US5655501A (en) * 1996-05-09 1997-08-12 Caterpillar Inc. Rate shaping plunger/piston assembly for a hydraulically actuated fuel injector

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4426198A (en) * 1979-05-28 1984-01-17 Societe D'etudes De Thermiques S.E.M.T. Fuel-injection pump for internal combustion engine
GB2170557A (en) * 1984-11-13 1986-08-06 Diesel Kiki Co Fuel injection pumps
EP0315564A1 (fr) * 1987-11-02 1989-05-10 Stanadyne Automotive Corp. Pompe-injecteur combinée à commande électronique
DE4206817A1 (de) * 1991-10-07 1993-04-29 Ficht Gmbh Kraftstoff-einspritzvorrichtung nach dem festkoerper-energiespeicher-prinzip fuer brennkraftmaschinen
US5655501A (en) * 1996-05-09 1997-08-12 Caterpillar Inc. Rate shaping plunger/piston assembly for a hydraulically actuated fuel injector

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