EP0757174A2 - Procédé de changement de l'avance d'une pompe d'injection de carburant et pompe d'injection de carburant - Google Patents

Procédé de changement de l'avance d'une pompe d'injection de carburant et pompe d'injection de carburant Download PDF

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Publication number
EP0757174A2
EP0757174A2 EP96111818A EP96111818A EP0757174A2 EP 0757174 A2 EP0757174 A2 EP 0757174A2 EP 96111818 A EP96111818 A EP 96111818A EP 96111818 A EP96111818 A EP 96111818A EP 0757174 A2 EP0757174 A2 EP 0757174A2
Authority
EP
European Patent Office
Prior art keywords
roller
bolt
fuel injection
tappet
injection pump
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.)
Granted
Application number
EP96111818A
Other languages
German (de)
English (en)
Other versions
EP0757174B1 (fr
EP0757174A3 (fr
Inventor
Hans Werner
Erhard Hilliger
Klaus Merseburg
Frank Prautzsch
Peter Teichert
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.)
WOODWARD GOVERNOR GERMANY GmbH
Original Assignee
WOODWARD GOVERNOR GERMANY 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 WOODWARD GOVERNOR GERMANY GmbH filed Critical WOODWARD GOVERNOR GERMANY GmbH
Publication of EP0757174A2 publication Critical patent/EP0757174A2/fr
Publication of EP0757174A3 publication Critical patent/EP0757174A3/fr
Application granted granted Critical
Publication of EP0757174B1 publication Critical patent/EP0757174B1/fr
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
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/48—Assembling; Disassembling; Replacing
    • 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
    • F02M59/102—Mechanical drive, e.g. tappets or cams

Definitions

  • the invention relates to a method for changing the start of delivery of fuel injection pumps for internal combustion engines, in particular diesel engines, and a suitable fuel injection pump.
  • the delivery start setting of injection pumps for internal combustion engines is carried out by adjusting the stroke, ie setting the distance between the pump support flange and the associated roller tappet or camshaft. With the adjustment of the advance stroke, the ignition timing, the stroke of the pump piston from the bottom dead center of the cam to the start of delivery, is changed.
  • Various solutions for setting the start of delivery of injection pumps are already known from literature and practice. In practice, for example, injection pumps are used in which the pump piston is actuated via adjustable fuel cams mounted on the camshaft. The start of delivery of the injection pump can be changed by rotating the two-part fuel cam. This solution has the disadvantage that the maximum possible shaft diameter is not available for transmitting the torque from the camshaft to the pump piston.
  • DE 40 03 469 A1 discloses a delivery start setting in which the dead center of the respective associated engine cylinder is determined by means of a piston distance measurement and is used as the basis for the delivery start setting. The actual adjustment is done by placing spacers under it. Placing shims or spacers requires repeated disassembly and assembly of the injection pump as well as the fuel supply, the lubricating oil supply and the injection pressure line.
  • the invention had for its object to provide a method for changing the start of delivery of fuel injection pumps with a roller tappet drive, which, even with injection pumps already mounted on the engine, including those with an integrated roller tappet drive, significantly reduces dismantling and assembly work, and is safe and reliable Correction of the injection time enables. Furthermore, it is an object of the invention to provide a correspondingly suitable fuel injection pump.
  • the object is achieved in that the securing and fastening elements for the roller bolt are solved, the roller bolt with the roller is displaced in the transverse direction to the camshaft axis and aligned by means of test gauges of the roller bolts in the desired start of delivery position and then fixed to the roller tappet.
  • This new procedure enables for the first time a correction of the ignition timing of injection pumps mounted on the engine with very little disassembly and assembly effort.
  • the transverse displacement of the roller pin with the roller transversely to the camshaft axis changes the horizontal distance between the roller of the roller tappet and the camshaft path, depending on the required adjustment, and the forward stroke of the pump piston is thereby adjusted.
  • the roller bolt is arranged to be displaceable transversely to the axis of the camshaft, the bores in the roller bolt for fastening the roller bolt to the roller tappet being designed as elongated holes which run transversely to the longitudinal axis of the roller bolt.
  • the contact surfaces between the roller pin and the roller tappet are designed in a form-fitting manner in such a way that after the roller pin has been moved with the roller transverse to the camshaft axis, a secure, accurate positional fixation of the roller pin on the roller tappet is ensured.
  • the roller pin can thus be non-positively and positively connected to the roller tappet.
  • Control means for example markings
  • a marking can be provided on the roller bolt and / or roller tappet for checking the position of the roller bolt.
  • a positioning screw or a positioning step can also be attached to the roller tappet on both sides in order to be able to check the exact alignment and the distance of the squeeze shift by means of a gauge.
  • the form-fitting formation of the contact surfaces between the roller tappet and the roller bolt can be carried out in various ways.
  • the contact surfaces are flat and are profiled.
  • the profiles run parallel to the longitudinal axis of the roller pin and the profiles between the roller tappet and the roller pin correspond to each other.
  • the profiles are designed so that they allow the roller bolt to be shifted at intervals of a few tenths of a millimeter.
  • the profiles After moving and aligning the roller bolt into the desired position, the profiles snap into place and ensure that the roller bolt cannot slip when the roller bolt is screwed onto the roller tappet.
  • Sawtooth-like profiling is particularly suitable.
  • the profiles of the two contact surfaces can also be designed as tongues and grooves, as pins and holes or as a hemisphere and hemispherical recess.
  • the width of the profiled surface on the roller tappet is larger than on the roller bolt.
  • the length of the elongated holes on the roller pin should be adapted to the desired maximum pre-stroke change on the pump piston.
  • each of these In order to prevent lubricating oil from escaping through the elongated holes due to the lubrication of the roller mounted on the roller bolt, it is expedient to cover each of these with a plate which is held by the fastening screw.
  • the plate can be marked in a visible position, which enables the exact alignment and transverse displacement of the roller bolt to be checked.
  • To feed the lubricating oil into the bearing points between the roller and roller bolt there is an annular channel around a section of the fastening screw arranged, which is connected to the lubrication channel system of the roller pin.
  • the injection pump shown in Figure 1 consists of a one-piece pump housing 1, in which a pump cylinder 2, which has an axial bore in which the pump piston 3 is axially and rotatably guided, the stroke of the pump piston 3 is limited.
  • a pump work chamber 4 Above the pump piston 3 is a pump work chamber 4, which is connected via inlet bores 5 to the fuel chamber 6 incorporated in the pump housing 1 when the pump piston 3 is in the bottom dead center position.
  • the inlet bores 5 are sealed.
  • the fuel is fed into the fuel chamber 6 via pipelines which are connected to a fuel reservoir, which is not shown in detail.
  • the pump piston 3 is provided in its upper region with a helical control edge 7 for realizing different useful strokes.
  • a helical groove 8 and a vertically running groove 9 are incorporated, via which a connection between the pump working chamber 4 and the fuel chamber 6 can be established via the inlet bores 5 after the injection has taken place.
  • a spring-loaded pressure valve 10 is arranged at the upper end of the pump work chamber 4 and is connected to the injection valve via a bore 12 arranged in the valve carrier 11 and an injection pressure line. The pressure line, the injection valve and the injection nozzle are not shown in the drawing.
  • the pump cylinder 2 is followed by a spring chamber 13, in which a pump spring 14 is arranged, which ensures that the roller 17 of the roller tappet 16 attached to the pump piston 3 is constantly in contact with the injection cam 18 of the camshaft 19 (FIG. 2 ) stands.
  • a lubricating oil chamber with a lubricating oil supply and lubricating oil discharge line is arranged in a manner known per se.
  • a leakage barrier is provided in the lower region of the pump piston 3, which prevents fuel leaks from entering the camshaft chamber of the engine via the spring chamber 13.
  • the operation of the injection pump is as follows. The pump piston 3 is driven via the camshaft 19 mounted in the engine housing with the injection cam 18.
  • the stroke movement of the injection cam 18 is transmitted to the pump piston 3 via the roller 17 of the roller tappet 16.
  • the pump work chamber 4 is filled with fuel, which is drawn in from the fuel chamber 6 via the inlet bores 5.
  • the inlet bores 5 in the pump cylinder 2 are closed after a certain stroke and the fuel is compressed.
  • the pressure valve 10 is opened and fuel is pressed into the combustion chamber of the engine under high pressure through the bore 12 in the valve carrier 11, the injection pressure line, the injection valve and the injection nozzle.
  • the very small flow cross-sections of the nozzle bores in relation to the pump piston area cause the pressure to rise sharply.
  • the injection is ended by the helical groove 8 and the vertical groove 9 in the pump piston 3 when the connection of the pump working chamber 4 via the inlet bores 5 to the fuel chamber 6 is restored via these two grooves .
  • the pressure in the pump working space suddenly collapses and the injection is ended by the closing of the spring-loaded nozzle needle.
  • the continuous change in the injection quantity is achieved by a relative rotary movement of the pump piston 3 to the pump cylinder 2, which is initiated via a regulating shaft of the motor, not shown, and is transmitted to the pump piston by a regulating rod and regulating sleeve.
  • a spring-loaded check valve ensures a defined residual pressure in the injection pressure line after the injection has ended.
  • the roller tappet 16 is integrated in the pump housing 1 and attached to the pressure piece 15 of the injection pump.
  • the structural design of the roller tappet 16 with the roller 17 for transmitting the lifting movement for the pump piston 3 is shown in more detail in FIGS. 2 to 4.
  • FIG. 2 shows the roller tappet 16 with the roller 17 in cooperation with the injection cam 18 of the camshaft 19.
  • the roller 17, which is rotatably mounted on the roller pin 20, runs on the cam track of the injection cam 18.
  • the roller 17 is kept in constant contact with the cam track of the injection cam 18 via the pressure piece 15 under spring pressure and the roller tappet 16.
  • the roller pin 20 is fastened to the roller tappet 16 by means of two fastening screws 21 which are guided through the roller pin.
  • the two bores of the roller bolt 20 for the fastening screws 21 are designed as elongated holes 22 which are arranged transversely to the longitudinal axis of the roller bolt 20 (FIG. 4).
  • the roller pin 20 has a flat, flat region 23 at both ends, with a sawtooth-like profile 25, which is arranged around the elongated holes 22.
  • the teeth of the profile 25 run parallel to the longitudinal axis of the roller bolt 20 and are each identical.
  • the rows of teeth are formed by milling or driving in using a suitable device.
  • the axial distance between the injection cam 18 and the roller 17 is changed and thus the forward stroke of the pump piston 3 of the injection pump and thus the ignition point, as the stroke of the pump piston from the bottom dead center of the cam to the start of the delivery .
  • more parallel rows of teeth are arranged on the contact surfaces of the roller tappet 16 than on the roller pin.
  • roller bolt This enables the roller bolt to be shifted by 5 rows of teeth from the center position to the right or left, resulting in a change in the start of injection by ⁇ 2 o crankshaft angle.
  • Two position pins 26 are attached to the roller plunger 16 on one side and two corresponding markings are attached to the roller bolt 20, making it possible to check the desired displacement and exact alignment of the roller bolt by means of a distance gauge. Depending on the requirements of the engine manufacturer, the correction of the position of the roller pin can be repeated as often as required.
  • a channel 27 is provided on the roller tappet 16, which opens into an annular channel 28 which is guided over a section around the fastening screw 21 and into an axial channel 29 of the roller bolt 20 opens, from which a channel 30 leads to the lubrication point ( Figure 3).
  • the elongated holes 22 in the roller bolt 20 are covered by a plate 31 held by the fastening screw 21. At a visible location of the roller pin 20 and the plate 31, markings can be made at which the transverse displacement of the roller pin 20 can be read.
  • the change in the start of delivery of the injection pump which is usually required by the engine manufacturer, can now be carried out in a very simple and quick manner for injection pumps already mounted on the engine.
  • the two fastening screws on the roller bolt 20 are loosened until the roller bolt has come loose from the toothing with the corresponding contact surface 24 on the roller tappet and is freely displaceable.
  • the roller bolt 20 is brought into the desired position with the roller 17, pressed upwards until the respective rows of teeth lock together and at the same time the fastening screws are tightened again.
  • the distance between the respective positioning screw and the marking on the roller pin is checked and, if necessary, changed using a test gauge.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
EP96111818A 1995-07-31 1996-07-23 Procédé de changement de l'avance d'une pompe d'injection de carburant et pompe d'injection de carburant Expired - Lifetime EP0757174B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19527720 1995-07-31
DE19527720A DE19527720A1 (de) 1995-07-31 1995-07-31 Verfahren zur Veränderung des Förderbeginns von Kraftstoffeinspritzpumpen und Kraftstoffeinspritzpumpe

Publications (3)

Publication Number Publication Date
EP0757174A2 true EP0757174A2 (fr) 1997-02-05
EP0757174A3 EP0757174A3 (fr) 1997-11-26
EP0757174B1 EP0757174B1 (fr) 2002-03-20

Family

ID=7768090

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96111818A Expired - Lifetime EP0757174B1 (fr) 1995-07-31 1996-07-23 Procédé de changement de l'avance d'une pompe d'injection de carburant et pompe d'injection de carburant

Country Status (5)

Country Link
EP (1) EP0757174B1 (fr)
JP (1) JPH09100760A (fr)
AT (1) ATE214787T1 (fr)
DE (2) DE19527720A1 (fr)
DK (1) DK0757174T3 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2324123A (en) * 1997-01-28 1998-10-14 Cummins Engine Co Inc A fuel pump with means to minimise side loads on plunger
EP1076174A2 (fr) * 1999-08-13 2001-02-14 Robert Bosch Gmbh Pompe à haute pression monocylindrique
EP1312801A2 (fr) * 2001-11-16 2003-05-21 Robert Bosch Gmbh Etage de pompe refroidi avec le carburant pompé

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19729793A1 (de) * 1997-07-11 1999-01-14 Bosch Gmbh Robert Kolbenpumpe zur Kraftstoffhochdruckversorgung
DE19857376A1 (de) * 1998-12-12 2000-06-15 Mahle Ventiltrieb Gmbh Rollenstößel
JP3905282B2 (ja) 2000-04-18 2007-04-18 トヨタ自動車株式会社 高圧ポンプ
DE102016224347B4 (de) * 2016-12-07 2018-06-21 Robert Bosch Gmbh Pumpe, insbesondere Hochdruckpumpe eines Kraftstoffeinspritzsystems, mit einer Stößel-Baugruppe die eine Verdrehsicherung und eine Schmierstoffversor- gung der Laufrolle durch einen verlängerten Lagerbolzen aufweist

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5765806A (en) * 1980-10-07 1982-04-21 Hitachi Zosen Corp Computer controlling diesel engine
JPS6267278A (ja) * 1985-09-20 1987-03-26 Mitsubishi Heavy Ind Ltd 燃料噴射タイミング変更装置
DE3643271A1 (de) * 1986-12-18 1988-06-23 Kloeckner Humboldt Deutz Ag Einspritzpumpe mit integrierter spritzverstellvorrichtung
DE4003469A1 (de) * 1990-02-06 1991-08-08 Kloeckner Humboldt Deutz Ag Foerderbeginneinstellung von einzeleinspritzpumpen bei der motorenmontage von mehrzylindermotoren

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5765806A (en) * 1980-10-07 1982-04-21 Hitachi Zosen Corp Computer controlling diesel engine
JPS6267278A (ja) * 1985-09-20 1987-03-26 Mitsubishi Heavy Ind Ltd 燃料噴射タイミング変更装置
DE3643271A1 (de) * 1986-12-18 1988-06-23 Kloeckner Humboldt Deutz Ag Einspritzpumpe mit integrierter spritzverstellvorrichtung
DE4003469A1 (de) * 1990-02-06 1991-08-08 Kloeckner Humboldt Deutz Ag Foerderbeginneinstellung von einzeleinspritzpumpen bei der motorenmontage von mehrzylindermotoren

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 006, no. 146 (M-147), 5.August 1982 & JP 57 065806 A (HITACHI ZOSEN CORP), 21.April 1982, *
PATENT ABSTRACTS OF JAPAN vol. 011, no. 263 (M-619), 26.August 1987 & JP 62 067278 A (MITSUBISHI HEAVY IND LTD), 26.März 1987, *

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2324123A (en) * 1997-01-28 1998-10-14 Cummins Engine Co Inc A fuel pump with means to minimise side loads on plunger
GB2324123B (en) * 1997-01-28 2000-11-08 Cummins Engine Co Inc High pressure fuel pump assembly
EP1076174A2 (fr) * 1999-08-13 2001-02-14 Robert Bosch Gmbh Pompe à haute pression monocylindrique
EP1076174A3 (fr) * 1999-08-13 2003-11-19 Robert Bosch Gmbh Pompe à haute pression monocylindrique
EP1312801A2 (fr) * 2001-11-16 2003-05-21 Robert Bosch Gmbh Etage de pompe refroidi avec le carburant pompé
EP1312801A3 (fr) * 2001-11-16 2004-05-12 Robert Bosch Gmbh Etage de pompe refroidi avec le carburant pompé

Also Published As

Publication number Publication date
EP0757174B1 (fr) 2002-03-20
EP0757174A3 (fr) 1997-11-26
DE19527720A1 (de) 1997-02-06
DK0757174T3 (da) 2002-07-15
JPH09100760A (ja) 1997-04-15
DE59608903D1 (de) 2002-04-25
ATE214787T1 (de) 2002-04-15

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