EP0585171A1 - Flüssigkraftstoffeinspritzvorrichtung für einen Verbrennungsmotor und mit einer solchen Vorrichtung ausgestatteter Motor - Google Patents

Flüssigkraftstoffeinspritzvorrichtung für einen Verbrennungsmotor und mit einer solchen Vorrichtung ausgestatteter Motor Download PDF

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Publication number
EP0585171A1
EP0585171A1 EP93402079A EP93402079A EP0585171A1 EP 0585171 A1 EP0585171 A1 EP 0585171A1 EP 93402079 A EP93402079 A EP 93402079A EP 93402079 A EP93402079 A EP 93402079A EP 0585171 A1 EP0585171 A1 EP 0585171A1
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EP
European Patent Office
Prior art keywords
cavity
needle
liquid fuel
seat
injection
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Withdrawn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
EP93402079A
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English (en)
French (fr)
Inventor
Jean Frédéric Melchior
Thierry Andre-Talamon
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Individual
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Individual
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Publication date
Application filed by Individual filed Critical Individual
Publication of EP0585171A1 publication Critical patent/EP0585171A1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • 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
    • F02M47/06—Other fuel injectors peculiar thereto

Definitions

  • the invention relates to a device for injecting liquid fuel into at least one pressurized combustion chamber forming part of an internal combustion engine, device which comprises a member for pressurizing the liquid fuel to be injected, consisting of a first cavity, of variable volume, delimited by a first animated of an alternating volume inside a cylinder, which first cavity communicates on the one hand with liquid fuel reserve means at low pressure via a control member establishing cyclically such communication in synchronism with the periodic operation of said engine and on the other hand by through a passage with an injector consisting of a nozzle and a movable needle, of revolution, which nozzle has a second cavity, connected to the aforesaid passage and delimited laterally by a cylindrical wall of circular director and axially by a partially conical wall forming a seat and coaxial with said cylindrical wall, and at least one injection orifice opening into the chamber combustion, a space of small volume or "bag” being disposed between the above-mentioned seat and the injection orifice (s), which
  • the object of the invention is to arrange the injection device defined above in such a way that the decompression of the first cavity does not propagate in the second cavity by causing "injection tails" at low pressure, generating exhaust fumes and soot. It also aims to arrange this injection device in such a way that the needle drops back onto its seat as gently as possible at the end of each injection period while preserving the pressure level of liquid fuel which is necessary for spraying and penetration of fuel droplets into the combustion chamber, in particular towards the end of each injection period.
  • the injection device according to the invention is essentially characterized in that the first cavity is separated from the second cavity by a uni-directional valve, preferably with very low volume displacement and with very low inertia, oriented so as to allow the flow of liquid fuel from the first cavity to the second cavity and to prevent flow in the opposite direction and arranged in such a way that its closure, caused by the decompression of the first cavity, does not cause a substantial drop in pressure in the second cavity.
  • the above means of substantially constant pressurization of the accumulator are constituted by a supply of pressurized fuel and by communication with the above means for reserving low-pressure liquid fuel via a leakage orifice, with a variable passage section, equipped adjustment means arranged so as to maintain the liquid fuel in the accumulator at the above substantially constant pressure.
  • the aforesaid supply of pressurized fuel consists of a communication which is established between the first cavity and the third cavity and on which are interposed a uni-directlonnel valve and a calibrated orifice connected in series.
  • the above-mentioned supply of pressurized fuel consists of a communication between the second cavity and the third cavity and on which a calibrated orifice is interposed.
  • FIG. 1 of these drawings schematically represents the preferred embodiment of the prior art and as described in the above-mentioned French patent application No. 91 02208 of February 25, 1991.
  • Figures 2, 3 and 4 are diagrams illustrating the operation and the drawbacks of an injection device of known type.
  • FIG. 5 shows a detail of one of the uni-directional valves of FIGS. 1 and 9.
  • FIGS. 6, 7 and 8 are diagrams illustrating the operation and the advantages of the injection device according to the invention and corresponding respectively to those of FIGS. 2, 3 and 4.
  • FIGS 9 and 10 schematically each represent a preferred embodiment of the invention.
  • FIG. 11 illustrates, on a larger scale, a variant of the needle of FIGS. 9 and 10.
  • the injection device is intended to inject liquid fuel into a pressurized combustion chamber 1 of an internal combustion engine 2, the number of chambers 1 can be determined at will.
  • the injection device comprises a member for pressurizing the liquid fuel to be injected which is constituted by a first cavity 3, of variable volume, delimited by a piston 4 driven by an alternating movement inside a cylinder 5.
  • the first cavity 3 communicates on the one hand with low pressure liquid fuel reserve means (or tank) 6 via a control member (such as a rotary distributor) 7 establishing such communication in synchronism with the operation of the motor 2 and, on the other hand, via a passage 8, with an injector 9 consisting of a nozzle 10 and a movable needle 11 having a shape of revolution.
  • This nozzle 10 comprises a second cavity 12 connected to the passage 8 and delimited laterally by a cylindrical wall 13, of circular director, and axially by a partially conical wall 14 forming a seat and coaxial with the cylindrical wall 13.
  • the nozzle 10 also comprises at least an injection orifice 17 opening into the combustion chamber 1.
  • a space of small volume or "bag” 28 is disposed between the seat 14 and the injection orifice (s) 17.
  • the needle 11 comprises a cylindrical part 15 forming a piston and capable of sliding, with minimal operating clearance, inside the cylindrical wall 13 of the nozzle 10 and a conical part 16 cooperating with the seat 14.
  • the needle 11 is arranged so as to be maintained, at rest, in abutment on the seat 14 by return means which will be described below, so as to interrupt the communication between the second cavity 12 and the orifice (s) injection 17.
  • the needle 11 is further aqenced in the manner of a differential piston so that its bearing section on the seat 14, projected on a plane perpendicular to the axis XX of the needle 11, either less than the cross section of the cylindrical part 15, forming the piston, of the needle 11.
  • the pump piston 4 can receive its reciprocating movement either, as shown diagrammatically in FIG. 1, by a rotary cam 21 driven in synchronism with the motor 2, against the action of a return spring 22, or by hydraulic means an example of which is described in document FR-A-2,326,588, or any other equivalent means.
  • the cam 21 can act on the piston 4 either directly (as shown diagrammatically in FIG. 1), or more generally by means of a rocker arm (not shown).
  • the first cavity 3 communicates with the third cavity 19 by means of a calibrated orifice 41 and of a uni-directional (or non-return) valve 30 mounted in series and the aforementioned accumulator 20 communicates with the above-mentioned reserve means of low pressure liquid fuel 6 via a leakage orifice 25, with a variable passage section, equipped with adjustment means 26 arranged so as to maintain the pressure of the liquid fuel in the accumulator 20 at a value substantially constant, for each operating speed of the engine 2. As shown in FIG.
  • the unidirectional valve 30 can consist of a ball subjected to the action of a return spring 27 and is in any case arranged to allow the liquid fuel discharged by the piston 4 to reach the third cavity 19 and the accumulator 20 and to prevent it from returning in the opposite direction.
  • External pressurization means 43 supplied by the low pressure tank 6 can communicate through the conduit 42 with the above-mentioned accumulator 20.
  • the return means of the needle 11 on its seat 14 preferably further include a mechanical spring 29 sized to allow the device to operate when the engine 2 is started, while the pressure of the liquid fuel is not still established in the accumulator 20.
  • the adjustment means 26 are preferably sensitive to at least one operating parameter Pr of the motor 2 and arranged so as to control the substantially constant pressure prevailing in the accumulator 20 for this operating parameter.
  • the second cavity 12 communicates directly with the first cavity 3, the calibrated orifice 41 and the unidirectional valve 30 not being interposed on the conduit 8 connecting the first cavity 3 to the second cavity 12 but on a conduit 35 derived at 34 from passage 8 and leading to accumulator 20 which it also connects to the third cavity 19.
  • the needle 11 When the needle 11 is in abutment on its seat 14, it is subjected, in the closing direction, to the pressure prevailing in the third cavity 19 and acting on the entire section of its cylindrical part 15 and, in the direction of opening, at the pressure prevailing in the second cavity 12, on the difference between the section of the cylindrical part 15 and its section supporting on the seat 14.
  • the discharge port 46 of the pump 3, 4 is closed by the rotary distributor 7 and the pressure transmitted by the passage 8 in the second cavity 12 increases until its action on the needle 11 becomes predominant and the needle 11 moves away from its seat 14, which allows part of the pressurized liquid fuel admitted into the second cavity 12 to reach the orifice (s) 17 through the bag 28 and to be injected into the combustion chamber 1.
  • the differential effect of needle 11 brings this in full opening stop.
  • the control member 7 re-establishes the communication between the first cavity 3 and the low pressure liquid fuel reserve means 6, the pressure prevailing in the second cavity 12 drops and allows the pressure prevailing in the third cavity 19 to return the needle 11 to its seat 14. More precisely, when the injection pressure falls below the closing pressure of the needle 11 (this closing pressure being lower than the opening pressure, due to the differential effect, the needle 11 begins to fall back. The injection stops when the needle 11 falls back onto its seat 14 , the differential effect avoiding to some extent the rebound of the needle.
  • the unidirectional valve 30 maintains the pressure in the accumulator 20 during the suction stroke of the piston 4 (or when the first cavity 3 is put into discharge by the control member 7) and then prevents the accumulator 20 to empty through the passage 8 and thus interfere with the operation described above of the needle 11.
  • the constant value P RH at which the pressure is maintained in the accumulator 20 can be adapted to the operating conditions of the engine 2.
  • combustion is carried out in a non-homogeneous manner.
  • the droplets of finely pulverized liquid fuel are mixed in the combustion chamber with the air which is heated there by adiabatic compression, either directly (plurality of fuel jets in a calm environment: non-turbulent chamber), or indirectly (limited number of jets in an environment animated by intense movements: turbulent chamber).
  • the vaporized fuel ignites spontaneously as soon as the required pressure and temperature conditions are reached.
  • the reaction develops very quickly, causing intense local heating and causing the pulverized fuel to decompose, until cracking leads to the formation of soot.
  • Most of the soot thus produced during the first part of the combustion period is gradually burned and therefore does not (or only slightly) alter the composition of the exhaust gases.
  • the soot particles produced at the end of the combustion period are much more troublesome because the time available for their re-combustion is obviously shorter.
  • the thermodynamic conditions (pressure and temperature) in the combustion chamber are then less favorable for the continuation of the reaction. From this point of view, it is clear that the end of the injection period is much more critical than the start of this same period.
  • the needle 11 once removed from its seat 14, the injection pressure is established over the entire lower surface of the needle 11 (that is ie its surface located on the right of FIG. 1), upstream from the injection orifice (s) 17.
  • the injection process ends with the drop of the needle 11 on its seat 14, caused by the setting in communication of the cylinder (or first cavity) 3 of the injection pump 3, 4 with the reserve means 6 at low pressure, via the discharge orifice 46.
  • the curves in solid lines correspond to a slow needle 11 (damped or with high inertia), the major part of the fall of the needle being effected with a very low injection pressure (generally less than 200 bars), hence smoke and unburnt gas and reflux of gas, from chamber 1 to the injector.
  • the broken line curves correspond to a fast needle (light, with low inertia, or not damped), the closure of the needle being effected with a high injection pressure (generally greater than 200 bars) , hence impact on the seat 14 and embrittlement.
  • the first cavity 3 (that is to say the cavity delimited by the piston 4 of the pressurizing member) is separated from the second cavity 12 (that is to say the cavity located in the nozzle 10 upstream of the seat 14 of the needle 11) by the aforesaid one-way valve or non-return valve 30, preferably with very low volume displacement and very low inertia, oriented so as to allow the flow of liquid fuel from the first cavity 3 to the second cavity 12, and to prevent flow in the opposite direction.
  • the uni-directional valve 30 is shown in FIG. 9 as being of the same type as in FIG. 1, it is more advantageously constituted, as shown in FIG.
  • the volume displaced by the valve between its fully open position and its closed position that is to say the product of the unidirectional valve 30, means "volume displacement".
  • the conduit 35 is not derived from the passage 8, unlike Figure 1, but leaves the third cavity 19, which highlights the change of place of the one-way valve 30.
  • the calibrated orifice 41 communicating the first cavity 3 with the third cavity 19 is located downstream of the unidirectional valve 30 and interposed on a passage 40 communicating the second cavity 12 and the third cavity 19. According to the embodiment of FIG. 9, the passage 40 and the calibrated orifice 41 pass through the cylindrical part 15 of the needle 11.
  • valve 30 When the needle 11 is opened, the operation is the same as that described above, the valve 30 opening with practically no resistance to the flow of liquid fuel. On closing, the position, chosen in accordance with the invention, of the valve 30 modifies the operation in an original and unexpected manner, as will be explained.
  • the second cavity 12 communicates with the third cavity 19 through the passage 40 on which the calibrated orifice 41 is interposed.
  • This passage can be arranged in the body of the needle as shown in FIG. 9. It can be arranged both in the body of the nozzle 10.
  • the calibrated orifice can even be confused with the needle clearance existing between the outside diameter of the cylindrical part 15 of the needle 11 and the inside diameter of the cylindrical wall 13 of the nozzle 10 as will be explained below in look at Figure 11.
  • the calibrated orifice 41 merges with the passage 40.
  • the tolerance of the needle 11 can therefore be less tight, which will avoid the pairing of the needle 11 with its nozzle 10 and will reduce the cost of injection equipment.
  • a second communication is established in parallel between the first cavity 3 and the second cavity 19, a second calibrated orifice 44 being arranged in series with a second unidirectional valve 45 on a duct 35 derived in 34 from passage 8, as in the case of FIG. 1.
  • the calibrated orifice 41 can merge with the play existing between the outside diameter of the cylindrical part 15 of the needle 11 and the inside diameter of the cylindrical wall 13 of the nozzle 10.
  • the communication between the second cavity 12 and the third cavity 19 on the circuit of which the calibrated orifice 41 is interposed also comprises shutter means capable of interrupting this communication when the needle 11 is in abutment on its seat 14 and of re-establishing this communication when said needle 11 is moved away from its seat 14.
  • the cylindrical part 15 of the needle 11 is advantageously provided with at least one longitudinal groove 23 which can go, on one side, to the conical part 16 of the needle 11 but stopped, on the other side, by a shoulder 24.
  • the shoulder 24 isolates the cavities 12 and 19 from one another while, when the needle 11 begins to move away from its seat 14, the groove or grooves 23 make the cavities 12 and 19 communicate with each other.
  • the presence of communication between the second cavity 12 and the third cavity 19 can prevent the pressure in the second cavity 12 from rising above the value of the pressure allowing the opening of the needle 11 (and greater than the pressure in the third cavity 19; due to the differential effect of the needle 11 bearing on its seat 14). It is therefore preferable, thanks to the groove 23, not to establish this communication between the second cavity 12 and the third cavity 19 only when the needle 11 is raised from its seat 14.
  • the invention has been described in its application to a single-cylinder engine, it goes without saying that it can be applied with as much interest to an engine having at least two cylinders or combustion chambers 1.
  • the accumulator 20 may preferably be unique and communicate with the third cavities specific to each injector. More precisely in this case, each working chamber 1 is equipped with a fuel injection device according to the invention, but the accumulator 20 is common to all the injection devices.

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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)
EP93402079A 1992-08-27 1993-08-20 Flüssigkraftstoffeinspritzvorrichtung für einen Verbrennungsmotor und mit einer solchen Vorrichtung ausgestatteter Motor Withdrawn EP0585171A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9210322 1992-08-27
FR9210322A FR2695169B1 (fr) 1992-08-27 1992-08-27 Dispositif d'injection de combustible liquide pour moteur à combustion interne et moteur équipé d'un tel dispositif.

Publications (1)

Publication Number Publication Date
EP0585171A1 true EP0585171A1 (de) 1994-03-02

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP93402079A Withdrawn EP0585171A1 (de) 1992-08-27 1993-08-20 Flüssigkraftstoffeinspritzvorrichtung für einen Verbrennungsmotor und mit einer solchen Vorrichtung ausgestatteter Motor

Country Status (4)

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US (1) US5381772A (de)
EP (1) EP0585171A1 (de)
JP (1) JPH06213097A (de)
FR (1) FR2695169B1 (de)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2748783B1 (fr) * 1996-05-17 1998-08-14 Melchior Jean F Dispositif d'injection de combustible liquide pour moteur a combustion interne
US6360727B1 (en) 2000-03-14 2002-03-26 Alfred J. Buescher Reduce initial feed rate injector with fuel storage chamber
DE10256028A1 (de) * 2002-11-30 2004-06-24 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
US8079338B2 (en) * 2006-04-11 2011-12-20 Jacobs Vehicle Systems, Inc. Self adjusting valve catch with valve seating control
US7963464B2 (en) * 2008-01-23 2011-06-21 Caterpillar Inc. Fuel injector and method of assembly therefor

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2073669A5 (de) * 1969-12-12 1971-10-01 Allis Chalmers Mfg Co
GB2086473A (en) * 1980-10-31 1982-05-12 Daimler Benz Ag Fuel injection valve for compression ignition engines
EP0441738A2 (de) * 1990-02-07 1991-08-14 Ail Corporation Hochdruck-Kraftstoffeinspritzsystem

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1563799A (en) * 1975-10-03 1980-04-02 Lucas Industries Ltd Fuel injection system for an internal combustion engine
DE2806788A1 (de) * 1978-02-17 1979-08-23 Bosch Gmbh Robert Pumpe-duese fuer brennkraftmaschinen
DE3245142A1 (de) * 1982-12-07 1984-06-07 Robert Bosch Gmbh, 7000 Stuttgart Verfahren und vorrichtung zum einspritzen von kraftstoff
DE3844475A1 (de) * 1988-12-31 1990-07-05 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen, insbesondere pumpeduese
DE3924127A1 (de) * 1989-07-20 1991-01-31 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4105168A1 (de) * 1990-12-10 1992-06-11 Man Nutzfahrzeuge Ag Einspritzsystem fuer luftverdichtende brennkraftmaschinen
FR2673246B1 (fr) * 1991-02-25 1994-01-28 Melchior Jean Dispositif d'injection de liquide, notamment de combustible, dans au moins une chambre pressurisee d'une machine a fonctionnement periodique tel que moteur a combustion interne et moteur de ce type equipe de ce dispositif.

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2073669A5 (de) * 1969-12-12 1971-10-01 Allis Chalmers Mfg Co
GB2086473A (en) * 1980-10-31 1982-05-12 Daimler Benz Ag Fuel injection valve for compression ignition engines
EP0441738A2 (de) * 1990-02-07 1991-08-14 Ail Corporation Hochdruck-Kraftstoffeinspritzsystem

Also Published As

Publication number Publication date
US5381772A (en) 1995-01-17
FR2695169B1 (fr) 1994-11-04
FR2695169A1 (fr) 1994-03-04
JPH06213097A (ja) 1994-08-02

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