EP0228632A2 - Système d'injection de combustible dans le cylindre d'un moteur à combustion interne à piston - Google Patents

Système d'injection de combustible dans le cylindre d'un moteur à combustion interne à piston Download PDF

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Publication number
EP0228632A2
EP0228632A2 EP86117289A EP86117289A EP0228632A2 EP 0228632 A2 EP0228632 A2 EP 0228632A2 EP 86117289 A EP86117289 A EP 86117289A EP 86117289 A EP86117289 A EP 86117289A EP 0228632 A2 EP0228632 A2 EP 0228632A2
Authority
EP
European Patent Office
Prior art keywords
injection
piston
fuel
cylinder
pressure chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP86117289A
Other languages
German (de)
English (en)
Other versions
EP0228632A3 (fr
Inventor
Hans Scherrer
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.)
Sulzer AG
Original Assignee
Sulzer AG
Gebrueder Sulzer AG
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 Sulzer AG, Gebrueder Sulzer AG filed Critical Sulzer AG
Publication of EP0228632A2 publication Critical patent/EP0228632A2/fr
Publication of EP0228632A3 publication Critical patent/EP0228632A3/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Withdrawn legal-status Critical Current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
    • 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
    • F02M45/066—Having specially arranged spill port and spill contour on the piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention relates to an injection system for fuel injection into a cylinder of a piston internal combustion engine, in particular a diesel engine, in which system the total amount of fuel injected per cycle is controlled in a load-dependent manner and is divided into two partial injections, a pre-injection and a main injection, the system being a fuel pump contains with a piston moving in the pressure chamber of a cylinder and the pressure chamber for fuel injection is connected to a suction chamber of relatively low pressure via controlled released and closed connections.
  • the invention can be used both in injection systems in which the load-dependent control of the fuel injection takes place via oblique control edges in a pump piston, and in those in which valves take over this control.
  • Injection systems of the type mentioned above are known, for example, from GB-PS 571,485, US-PS 3,792,692, US-PS 2,306,364 or EP-PS 0 020 249.
  • This division of the total amount of fuel required per cycle into a preliminary and a main injection is used in a known manner to achieve optimum fuel utilization, that is to say optimal consumption, given the combustion and medium pressure of the internal combustion engine.
  • the known constructions mentioned partly allow variations in the time intervals for the pre-injection, the pause and / or the main injection, there is no possibility with these arrangements to shrink the pause to "O" at small loads, ie the separation into pre and Repeal main injection. For small loads, i.e.
  • the object of the invention is therefore to improve the known systems in such a way that the subdivision into pre-injection and main injection becomes possible with small loads and that when this subdivision is used the pause between the partial injections does not occur suddenly, but changes continuously with increasing loads becomes.
  • This object is achieved with the invention in that the separation into two partial injections takes place only at a minimum load specified in the design of the engine.
  • a control groove is provided with an upper and a lower control edge, which extend in the circumferential direction helically with mutually different pitch, for the control of the end of the pre-injection and the beginning of the main injection in the piston, wherein further in Stroke direction of the piston in front of the fuel feed connection in the cylinder wall, there is at least one overflow connection to a space of low pressure, which can be connected to a flow path that is permanently open to the pressure space and runs in the longitudinal direction of the piston, results in a structurally advantageous construction for the solution of the task, if the flow path permanently connected to the pressure chamber ends on the pressure chamber side at an axial distance in front of the overflow connection, and furthermore the height between the control edges in the control groove in a first circumferential region of the piston is smaller than this axial distance nd is and widens in the circumferential direction to values greater than this distance.
  • the flow path in the longitudinal direction of the piston extends from the pressure chamber of the cylinder to the area of the piston stroke influenced by the control edges; If the height between the two control edges is now less than the distance of the short-circuit connection from the overflow opening, it is closed by the lower control edge before the upper control edge clears the flow path in the longitudinal direction of the piston from the pressure chamber. Damii, however, prevents intermediate relief of the pressure chamber during the injection stroke, so that in this case the injection takes place "in one go”. At a load selected differently from motor to motor between 20 and 50% of the full load, the height between the control edges exceeds the distance mentioned. As soon as the height is greater than the distance, there is an intermediate relief, the duration of which corresponds to the difference between the height and the distance.
  • VIT variable injection timing
  • the measure can be taken in a known manner that the upper control edge is stepped in the radial direction of the piston.
  • a pump is accommodated in a pump housing 1, to which a fuel supply system is connected via bores 2.
  • a plunger or piston 5 is axially movable, which puts the fuel in the pressure chamber 4 under high pressure and injects into the cylinder, not shown, of the internal combustion engine.
  • the injection takes place through a bore 6 which is provided concentrically with the pressure chamber 4 in the cover 7 which closes off the cylinder 2 at the top.
  • an overflow or suction chamber 8 of relatively low pressure is provided, which axially surrounds the cylinder of the pump at the level of the pressure chamber 4 and in the stroke area of the piston 5.
  • the bores 2 end in this suction chamber 8, as a result of which the suction chamber is connected to the fuel supply system; on the other hand, fuel feed openings 9 connect the suction chamber 8 to the pressure chamber 4.
  • overflow openings 10 are present, which extend in the stroke direction of the piston in front of the 8 feed openings 9 from the suction chamber / through the cylinder wall into the area of the cylinder bore covered by the piston movement.
  • the injection pump is constructed in a known manner symmetrically to its vertical axis 11 in order to avoid one-sided pressure loads, in particular on the piston 5.
  • the piston or plunger 5 has a first control edge 12 at its free end; this is interrupted on the circumference by a longitudinal groove 13 which leads from the pressure chamber 4 into an annular chamber 14 of the piston 5. Between the control edge 12 and the annular space 14 is a helical further control edge 15 arranged.
  • the control edges 12 and 15 together with the fuel feed openings 9 form a conventional load-dependent control of the fuel injection in the known manner of an inclined edge injection pump. The injection begins when the edge 12 covers the openings 9 and ends when the edge 15 clears these openings 9 again.
  • connection 16 has an axial distance a from the overflow opening 10 that is determined when the injection system is designed.
  • a further control groove 17 is provided in the piston 5, which axially connects an upper control edge 18 and a lower control edge 19.
  • These two control edges 18 and 19 run helically on part of the piston circumference, their pitches being different, which can be clearly seen in FIG. 2.
  • the height h 1 or h 2 of the control groove 17 in a first circumferential region U 1 is smaller than the distance a and widens as one progresses in the circumferential direction - which is equivalent to a movement from left to right in FIG. 2 - to Values greater than this distance a.
  • this rotation corresponds to a relative displacement of the openings 16 and 10 from left to right, for example from the position shown in broken lines to that shown in full lines.
  • One designates the angle through which the piston 5 is rotated depending on the load 3 is the angle as the abscissa in FIG and the stroke w is plotted as the ordinate, during which the piston 5 effectively delivers fuel.
  • an "O position" ⁇ 0 which corresponds to the position at which the longitudinal groove 13 no longer covers the feed opening / and the control edges 12 and 15 touch the bore 9, the injection begins.
  • the injection duration increases continuously and in a straight line up to a load or an angle f 1 of the piston 5 at which the height h 1 of the control groove 17 corresponds exactly to the distance a between the openings 10 and 16.
  • this limit angle g l is exceeded , the separation of the previously single-stage injection into a pre-injection V (FIG. 3) and the main injection H begins.
  • the main injection H itself is ended by the pressure relief of the pressure chamber 4 when the control edge 15 opens a connection of this pressure chamber 4 to the feed openings 9 in a conventional manner.
  • the embodiment of the pump according to FIG. 4 differs from that according to FIG. 1 only in the details that, on the one hand, the short-circuit connection 16, which in FIG. 1, for example, has two bores through the cylinder which are parallel to one another and perpendicular to it and partially closed again 3 is realized, is replaced by a longitudinal groove 26, for example manufactured by means of electrical erosion. Furthermore, a step 20 is provided on the upper control edge 18 of the control groove 17, which should dampen the impact load and reduce the risk of cavitation when pressure is relieved on this edge.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP86117289A 1986-01-09 1986-12-11 Système d'injection de combustible dans le cylindre d'un moteur à combustion interne à piston Withdrawn EP0228632A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH44/86 1986-01-09
CH4486 1986-01-09

Publications (2)

Publication Number Publication Date
EP0228632A2 true EP0228632A2 (fr) 1987-07-15
EP0228632A3 EP0228632A3 (fr) 1988-10-19

Family

ID=4178056

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86117289A Withdrawn EP0228632A3 (fr) 1986-01-09 1986-12-11 Système d'injection de combustible dans le cylindre d'un moteur à combustion interne à piston

Country Status (4)

Country Link
EP (1) EP0228632A3 (fr)
JP (1) JPS62168960A (fr)
DK (1) DK595986A (fr)
FI (1) FI864598A7 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2219356A (en) * 1988-04-18 1989-12-06 Hatz Motoren A fuel injection pump for an internal combustion engine having pre-injection and main injection of fuel
GB2275739A (en) * 1993-03-01 1994-09-07 Caterpillar Inc Flexible injection rate shaping device for a hydraulically-actuated fuel injector
EP4357603A4 (fr) * 2021-06-17 2025-06-25 Weichai Power Co., Ltd. Procédé de commande pour système de combustion, système de combustion et moteur diesel

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB571485A (en) * 1942-09-16 1945-08-27 Bendix Aviat Corp Improvements in or relating to fuel injection apparatus
US2590575A (en) * 1945-08-02 1952-03-25 Gardiner M Rogers Fuel injector
GB641575A (en) * 1948-01-03 1950-08-16 Cav Ltd Improvements relating to liquid fuel injection pumps
JPH0652067B2 (ja) * 1983-08-17 1994-07-06 日産自動車株式会社 分配型燃料噴射ポンプの噴射率制御装置

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2219356A (en) * 1988-04-18 1989-12-06 Hatz Motoren A fuel injection pump for an internal combustion engine having pre-injection and main injection of fuel
GB2219356B (en) * 1988-04-18 1992-03-18 Hatz Motoren A fuel injection pump for an internal combustion engine having pre-injection and main injection of fuel
GB2275739A (en) * 1993-03-01 1994-09-07 Caterpillar Inc Flexible injection rate shaping device for a hydraulically-actuated fuel injector
GB2275739B (en) * 1993-03-01 1995-12-13 Caterpillar Inc Flexible injection rate shaping device for a hydraulically-actuated fuel injection system
EP4357603A4 (fr) * 2021-06-17 2025-06-25 Weichai Power Co., Ltd. Procédé de commande pour système de combustion, système de combustion et moteur diesel

Also Published As

Publication number Publication date
EP0228632A3 (fr) 1988-10-19
JPS62168960A (ja) 1987-07-25
DK595986A (da) 1987-07-10
FI864598A0 (fi) 1986-11-12
FI864598A7 (fi) 1987-07-10
DK595986D0 (da) 1986-12-11

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Inventor name: SCHERRER, HANS