EP0153331B1 - Pumpedüse für die kraftstoffeinspritzung bei brennkraftmaschinen - Google Patents

Pumpedüse für die kraftstoffeinspritzung bei brennkraftmaschinen Download PDF

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Publication number
EP0153331B1
EP0153331B1 EP84902788A EP84902788A EP0153331B1 EP 0153331 B1 EP0153331 B1 EP 0153331B1 EP 84902788 A EP84902788 A EP 84902788A EP 84902788 A EP84902788 A EP 84902788A EP 0153331 B1 EP0153331 B1 EP 0153331B1
Authority
EP
European Patent Office
Prior art keywords
pump
piston
internal combustion
injection
cylinder head
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP84902788A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0153331A1 (de
Inventor
Jean Leblanc
François Rossignol
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to AT84902788T priority Critical patent/ATE23209T1/de
Publication of EP0153331A1 publication Critical patent/EP0153331A1/de
Application granted granted Critical
Publication of EP0153331B1 publication Critical patent/EP0153331B1/de
Expired 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps

Definitions

  • the invention is based on a pump nozzle according to the generic preamble of the main claim.
  • a pump nozzle of this type is already known (DE-A-32 26 238), in which the piston injection pump and the injection nozzle are combined in a common pump housing to form a structural unit attached to the cylinder head of the internal combustion engine.
  • the design arranged one behind the other is preferably at right angles to the longitudinal axis of the pump piston, also referred to as the line of action of the injection pump, and the longitudinal axis of the injection nozzle. This measure was taken to achieve a compact design and to absorb the pumping forces at a point on the cylinder head that is distant from the location hole for the injection nozzle.
  • the diameter and design of the injection nozzle and the wall thicknesses surrounding this nozzle can be optimally designed in the cylinder head. This is possible because the very high pumping forces, which are of the order of 2000 N, are absorbed at one point on the cylinder head, which can be dimensioned accordingly.
  • the pump nozzle described in FIG. 2 of the aforementioned publication is supported with an end support surface facing away from the camshaft on a corresponding surface of the cylinder head.
  • the injection nozzle which is arranged laterally at an angle to the longitudinal axis of the pump piston, projects into the working cylinder of the internal combustion engine, received by a receiving bore in the cylinder head, and has no transmission and clamping forces to be transmitted.
  • a disadvantage of this arrangement is that the positional tolerances of the support surfaces of the laterally mounted injection nozzle and the receiving bore in the cylinder head must be tolerated extremely tightly so that no clamping and clamping forces can act on the injection nozzle.
  • This is particularly critical because the cylinder head is subject to very large temperature differences and the thermal expansion of the cylinder head and the pump housing lead to deviations in the mounting position in addition to the manufacturing tolerances.
  • the aim of the invention is to intercept the pump forces in the cylinder head in such a way that even with large temperature deviations and the manufacturing tolerances that occur, no forces stressing the injection nozzle can act on them.
  • the outward-facing end face of the opposing piston forming the support bearing on the support bearing transmits the pumping forces emanating from the injection pressure in the pump working chamber directly into the cylinder head without these forces being introduced into the pump housing.
  • the injection nozzle attached to the housing attachment projecting at least approximately at right angles to the longitudinal axis of the pump piston and the associated receiving bore are completely relieved of the pump forces.
  • the pump forces transmitted from the pump piston to the counter-piston via the pressurized fuel are completely introduced into the support bearing.
  • the leakage fuel which is inevitable even with narrow tolerances, is discharged specifically into a leakage fuel line.
  • the spring element which is supported both on the counter-piston and on the pump housing, always provides non-positive support of the counter-piston on the support bearing, which is also effective during the suction stroke of the pump piston, and compensates with its preload force F 2 a corresponding mean preload force F, the plunger spring of the injection pump.
  • FIG. 1 shows the first exemplary embodiment on the basis of a pump nozzle, which is partly shown in longitudinal section and is shown in a highly simplified manner and is built into the cylinder head of the internal combustion engine, and FIG.
  • the pump housing designated 11 receives a piston injection pump 12 and additionally carries a pump pump 13 arranged at right angles to the longitudinal axis A
  • Nete injector 14 of a known type The injection nozzle 14 is connected to this pump work space 15 via a pressure channel 16 opening out laterally from a pump work space 15 and screwed to a housing projection 11 a of the pump housing 11 projecting laterally, at least approximately at right angles to the longitudinal axis A of the pump piston 13.
  • the injection nozzle 14 is inserted into a receiving bore 17 of a cylinder head 18 of the associated internal combustion engine and is fastened to the cylinder head 18 in a manner known per se via clamping claws or stud bolts 19. By means of this fastening, the entire pump nozzle 10 is held in the cylinder head 18, since an additional fastening of the injection pump part is unnecessary due to the inventive design of the pump nozzle 10 described in detail below.
  • the pump piston 13 slidably guided in a pump cylinder 21 is driven by a cam 22a of an engine camshaft 22 of the internal combustion engine with the interposition of a tappet 23 in the stroke direction, i.e. in the direction of its longitudinal axis A, actuates and acts on the pump work space 15.
  • This pump work space 15, which is formed by a section of the pump cylinder 21, is sealed pressure-tight on the one hand by the pump piston 13 and on the other hand by an inner end face 24a of a counter-piston 24 by means of a correspondingly close fit of the associated components.
  • An outward-facing end face 24b of the counter-piston 24 facing away from the inner end face 24a bears against a support bearing 25 under the hydraulic force of the fuel under pressure in the pump work chamber 15 and is therefore also referred to below as a support surface 24b.
  • This support bearing 25 is an integral part of the cylinder head 18 and absorbs the entire pumping or reaction force F, which originates from the pump piston drive and is transferred to the counter piston 24 via the pressurized fuel in the pump working chamber 15, so that the pump housing 11 is largely relieved.
  • the counter-piston 24 which is designed as a floating piston, is fitted in the region of an end section 11b of the pump housing 11 facing away from the motor camshaft 22 into an extension 21a of the pump cylinder 21 which has a constant diameter D up to this end section 11b.
  • the support surface 24b of the counter-piston 24 forms the outermost axial extension of the injection pump 12 in the direction of the longitudinal axis A of the pump piston A.
  • annular grooves 26, 27 and 28, one behind the other are incorporated from the pump work chamber 15, of which the one closest to the pump work chamber 15 is connected as one with a leak fuel line 29 Leak fuel return groove 26 is used.
  • the second annular groove 27 receives a sealing ring 31 which prevents leakage of fuel from escaping to the outside, and a snap ring 32 which forms a radial projection is inserted into the third annular groove 28.
  • the support surface 24b 'on the counter-piston 24' formed by the outward-facing end surface is pressed against the support bearing 25 'under the pretensioning force of a spring element 33 formed in the present example by a plate spring and is supported on the one hand on the radial projection of the counter-piston formed by the snap ring 32 24 'and on the other hand from the end section 11b of the pump housing 11.
  • the support bearing 25 'for the counter-piston 24' is formed by a screw part which is adjustable to adjust its installation position, is screwed into the cylinder head 18 of the internal combustion engine and is secured in position. This allows installation tolerances to be compensated for. The installation of the pump nozzle 10 'is also facilitated when the support bearing 25' is screwed out to the right, and the installation position of the counter-piston 24 'can be adjusted continuously. On the one hand, manufacturing tolerances can be compensated for and, on the other hand, the pretensioning force F 2 of the plate spring 33 can be changed so that it can be made equal to the force denoted by F 1 .
  • F 1 is the mean value of the pretensioning force transmitted from the plunger 23 to a plunger spring 34 during the lifting movements of the pump piston 13 and from this via a flange 35a of a guide sleeve 35 for the plunger 23 to the pump housing 11.
  • the arrows representing the forces F 1 and F 2 have been drawn in outwards for clarity. The purely space-related advantages of the selected design of the pump nozzle 10 'can be seen particularly clearly from FIG.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP84902788A 1983-07-29 1984-07-17 Pumpedüse für die kraftstoffeinspritzung bei brennkraftmaschinen Expired EP0153331B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84902788T ATE23209T1 (de) 1983-07-29 1984-07-17 Pumpeduese fuer die kraftstoffeinspritzung bei brennkraftmaschinen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19833327399 DE3327399A1 (de) 1983-07-29 1983-07-29 Pumpeduese fuer die kraftstoffeinspritzung bei brennkraftmaschinen
DE3327399 1983-07-29

Publications (2)

Publication Number Publication Date
EP0153331A1 EP0153331A1 (de) 1985-09-04
EP0153331B1 true EP0153331B1 (de) 1986-10-29

Family

ID=6205243

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84902788A Expired EP0153331B1 (de) 1983-07-29 1984-07-17 Pumpedüse für die kraftstoffeinspritzung bei brennkraftmaschinen

Country Status (5)

Country Link
US (1) US4615323A (enrdf_load_stackoverflow)
EP (1) EP0153331B1 (enrdf_load_stackoverflow)
JP (1) JPS60501909A (enrdf_load_stackoverflow)
DE (2) DE3327399A1 (enrdf_load_stackoverflow)
WO (1) WO1985000638A1 (enrdf_load_stackoverflow)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4396166T1 (de) * 1992-12-03 1995-01-26 Lucas Ind Plc Kraftstoffpumpe

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62159762A (ja) * 1986-01-08 1987-07-15 Honda Motor Co Ltd デイ−ゼルエンジン
DE3633136A1 (de) * 1986-09-30 1988-04-07 Daimler Benz Ag Aus pumpe und duese bestehende magnetventilgesteuerte einspritzvorrichtung fuer luftverdichtende brennkraftmaschinen
US5003161A (en) * 1987-06-23 1991-03-26 Robertshaw Controls Company Combination of an igniter for a gas furnace and a control unit therefor
DE3739108A1 (de) * 1987-11-19 1989-06-01 Opel Adam Ag Brennkraftmaschine mit einer kraftstoffeinspritzanlage
US5125383A (en) * 1990-07-18 1992-06-30 Volkswagen Ag Mounting arrangement for a fuel injection pump nozzle in a cylinder head
DE4202396A1 (de) * 1992-01-29 1993-08-05 Man Nutzfahrzeuge Ag Einspritzvorrichtung fuer luftverdichtende brennkraftmaschinen
JPH05269377A (ja) * 1992-10-23 1993-10-19 Dow Chem Co:The ｐＨが４未満の水の吸収方法
DE4322546A1 (de) * 1993-07-07 1995-01-12 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
US5329906A (en) * 1993-08-16 1994-07-19 Energy Conversions, Inc. Low emission dual fuel valve structure
JP3521555B2 (ja) * 1995-06-30 2004-04-19 日産自動車株式会社 直接噴射型火花点火機関の燃料供給装置
US5806499A (en) * 1997-03-18 1998-09-15 Cummins Engine Company, Inc. Dedicated overhead cam shaft for unit injector
US5832898A (en) * 1997-06-05 1998-11-10 Siemens Automotive Corporation Fuel injection system with pressure decay metering method
US6289876B1 (en) * 1999-03-29 2001-09-18 International Truck And Engine Corporation Fuel injector
US6405711B1 (en) * 2000-07-27 2002-06-18 Delphi Technologies, Inc. Fuel delivery module for fuel injected internal combustion engines
DE10119553B4 (de) * 2001-04-21 2005-06-23 Siemens Ag Saugstrahlpumpe und Verfahren zur Herstellung einer Düse für eine Saugstrahlpumpe
DE10242894A1 (de) * 2002-09-16 2004-03-25 Robert Bosch Gmbh Kraftstoff-Einspritzsystem und Zylinderkopf mit einem zentralen Kraftstoffspeicher
US20080230036A1 (en) * 2007-03-23 2008-09-25 Bauman William D Roller actuator for a mechanical fuel pump

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL42814C (enrdf_load_stackoverflow) *
US1863232A (en) * 1929-09-26 1932-06-14 Packard Motor Car Co Internal-combustion engine
FR768513A (fr) * 1933-02-17 1934-08-07 Dispositif d'injection solide pour machines à combustion interne
US2354403A (en) * 1940-07-20 1944-07-25 Caterpillar Tractor Co Fuel injection system
US2793078A (en) * 1955-08-08 1957-05-21 Gen Motors Corp Fuel injection
US3845748A (en) * 1972-09-29 1974-11-05 Mack Trucks Fuel injection nozzle holder installation
GB2102882B (en) * 1981-07-24 1985-09-11 Lucas Ind Plc Combined fuel injection pump and injector units for c.i. engines
JPS58204962A (ja) * 1982-05-25 1983-11-29 Toyota Motor Corp ユニットインジェクタ

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4396166T1 (de) * 1992-12-03 1995-01-26 Lucas Ind Plc Kraftstoffpumpe

Also Published As

Publication number Publication date
JPH0444104B2 (enrdf_load_stackoverflow) 1992-07-20
US4615323A (en) 1986-10-07
WO1985000638A1 (en) 1985-02-14
DE3327399A1 (de) 1985-02-21
DE3461113D1 (en) 1986-12-04
JPS60501909A (ja) 1985-11-07
EP0153331A1 (de) 1985-09-04

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