EP0153331A1 - Injecteur de pompe pour l'injection de carburant pour moteurs a combustion interne. - Google Patents

Injecteur de pompe pour l'injection de carburant pour moteurs a combustion interne.

Info

Publication number
EP0153331A1
EP0153331A1 EP84902788A EP84902788A EP0153331A1 EP 0153331 A1 EP0153331 A1 EP 0153331A1 EP 84902788 A EP84902788 A EP 84902788A EP 84902788 A EP84902788 A EP 84902788A EP 0153331 A1 EP0153331 A1 EP 0153331A1
Authority
EP
European Patent Office
Prior art keywords
pump
piston
counter
injection
internal combustion
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
EP84902788A
Other languages
German (de)
English (en)
Other versions
EP0153331B1 (fr
Inventor
Jean Leblanc
Francois 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/fr
Application granted granted Critical
Publication of EP0153331B1 publication Critical patent/EP0153331B1/fr
Expired legal-status Critical Current

Links

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 looks from a pump nozzle according to the generic preamble of the main claim.
  • a puape nozzle of this type known (DE-OS 32 26 238), in which the piston injection pump and injection nozzle are combined in a common pump housing to form a unit mounted on the cylinder head of the internal combustion engine.
  • the stroke 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 are at a right angle to one another. This measure was taken in order to achieve a compact construction and to absorb the Puap forces on a part of the cylinder head which is distant from the opening for the injection nozzle.
  • the diameter and shape of the injection nozzle and the wall thicknesses surrounding this nozzle are optimally designed in the cylinder head. This is possible because the very high pumping forces of around 2000 N at one point on the cylinder intercepted head, which can be dimensioned accordingly strong.
  • the pump nozzle described in FIG. 2 of the aforementioned disclosure 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, protrudes from a receiving bore in the cylinder head, into the working cylinder of the 3 rennkraft ⁇ aschine and has no pump and clamping forces to be transmitted.
  • a disadvantage of this arrangement is that the positional tolerances of the support surfaces, the laterally mounted injection nozzle and the receiving bore in the cylinder head must be tolerated extremely closely 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 means that the pumping forces emanating from the injection pressure in the pump work space are transmitted directly into the cylinder head without them Forces are 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 floating piston which is fitted as a floating piston into an extension of the pump cylinder having a constant diameter up to the end section of the pump housing, the pump forces transmitted from the pump piston via the pressurized fuel to the counter-piston are completely introduced into the support bearing.
  • it is also possible to form a pressure shoulder by means of small differences in diameter on the pump piston and counter-piston with the appropriately designed bore sections in the pump cylinder, which additionally compensates, for example, drive forces originating from the push spring.
  • the leak fuel that is unavoidable even with narrow tolerances is selectively discharged into a leak fuel line.
  • the spring element which is supported both on the counter-piston and on the pump housing, brings about an always 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 1 of the plunger spring of the injection pump.
  • FIG. 1 shows the first exemplary embodiment based on a pump nozzle which is partly shown in longitudinal section and is shown in a greatly simplified manner and is built into the cylinder head of the internal combustion engine
  • FIG. 2 shows a longitudinal section through the second, practically carried out exemplary embodiment.
  • the pump housing designated 11 receives a piston injection pump 12 and additionally carries an injection nozzle 14 of a known type arranged at right angles to the longitudinal axis A of a pump piston 13.
  • 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 is screwed to a housing extension 11 a of the pump housing 11 that projects laterally, at least approximately at right angles to the longitudinal axis A of the pump piston 13.
  • the injection nozzle 14 is in a receiving bore 17 of a cylinder head 18 of the associated internal combustion engine set and fastened in a known manner via clamping claws or stud bolts 19 to the cylinder head 13.
  • 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 configuration of the pump nozzle 10 described in detail below.
  • An outward-facing end face 24b of the counter-piston 24 applied to 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 15 and absorbs the entire pump or reaction force F, which originates from the pump piston drive and is transmitted 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 in the region of an end section 11b of the pump housing 11 facing away from the engine camshaft 22 into a diameter D of up to the same Sem end portion 11b carried out extension 21a of the pump cylinder 21 fitted.
  • 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 In the outer surface of the counter-piston 24 ', which is made from a fully cylindrical part of the same diameter without a collar, there are three annular grooves 26; 27 and 28 are incorporated, of which the one closest to the pump work space 15 serves as a leak fuel return groove 26 connected to a leak fuel line 29.
  • the second ring groove 27 receives a sealing ring 31 preventing leakage of fuel from escaping, and a snap ring 32 forming a radial projection is inserted into third ring groove 28.
  • the support surface 24b 'formed on the counter-piston 24' by the outwardly facing end face 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 by 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 bolt which can be adjusted 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 tappet 23 to a tappet 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 tappet 23 to the pump housing 11.
  • the arrows representing the forces F 1 and F 2 have been drawn in outwards for clarity of illustration. The purely space-related advantages of the selected type of 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)

Abstract

Injecteur de pompe (10) comprenant un gicleur d'injection (14) monté au moins approximativement à angle droit par rapport à l'axe longitudinal (A) sur le boîtier de pompe (11) de la pompe d'injection à piston (12). La pompe d'injection (12) s'appuie, par une face d'appui (24b) formant sa saillie axiale extrême, sur un palier d'appui (25) se trouvant à la culasse (18) du moteur à combustion interne. La surface d'appui (24b) est formée d'une face frontale, dirigée vers l'extérieur, d'un piston opposé (24) introduit en prolongement de l'axe longitudinal (A) du piston de pompe dans le cylindre de pompe (21) et fermant de manière étanche la chambre de travail de la pompe (15) par une surface frontale intérieure (24a). Les forces de pompe provenant du carburant mis sous pression dans la chambre de travail de la pompe (15) sont ainsi tenues à l'écart du boîtier de pompe (11) et recueillies à la culasse à un endroit éloigné d'une admission (17) pour le gicleur d'injection (14).
EP84902788A 1983-07-29 1984-07-17 Injecteur de pompe pour l'injection de carburant pour moteurs a combustion interne Expired EP0153331B1 (fr)

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
DE3327399 1983-07-29
DE19833327399 DE3327399A1 (de) 1983-07-29 1983-07-29 Pumpeduese fuer die kraftstoffeinspritzung bei brennkraftmaschinen

Publications (2)

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

Family

ID=6205243

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84902788A Expired EP0153331B1 (fr) 1983-07-29 1984-07-17 Injecteur de pompe pour l'injection de carburant pour moteurs a combustion interne

Country Status (5)

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

Families Citing this family (18)

* 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
GB9225341D0 (en) * 1992-12-03 1993-01-27 Lucas Ind Plc Fuel pump
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 (fr) *
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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8500638A1 *

Also Published As

Publication number Publication date
EP0153331B1 (fr) 1986-10-29
JPS60501909A (ja) 1985-11-07
DE3461113D1 (en) 1986-12-04
DE3327399A1 (de) 1985-02-21
US4615323A (en) 1986-10-07
JPH0444104B2 (fr) 1992-07-20
WO1985000638A1 (fr) 1985-02-14

Similar Documents

Publication Publication Date Title
EP0153331A1 (fr) Injecteur de pompe pour l'injection de carburant pour moteurs a combustion interne.
EP1727983B1 (fr) Pompe haute pression, notamment destinee a un dispositif d'injection de carburant d'un moteur a combustion interne
EP0461212B1 (fr) Pompe d'injection de carburant a commande electrique pour moteurs a combustion interne, en particulier pompe d'injection combinee avec l'injecteur
EP2108080A1 (fr) Injecteur pour injecter du carburant dans les chambres de combustion des moteurs à combustion interne
DE10118755A1 (de) Hochdruckpumpe
EP0446454A1 (fr) Installation de pompage avec une pompe à piston
DE10060089A1 (de) Kraftstoffeinspritzeinrichtung
WO2007098975A1 (fr) Dispositif d'injection de carburant pour moteur a combustion interne
WO1999002858A1 (fr) Pompe a piston radial pour alimentation haute pression en carburant
EP1045983B1 (fr) Soupape d'injection de carburant pour moteurs a combustion interne
DE10322603B4 (de) Kolbenpumpe, insbesondere Hochdruck-Kolbenpumpe für Brennkraftmaschinen mit Direkteinspritzung
WO2013092968A2 (fr) Pompe, en particulier pompe carburant haute pression pour un dispositif d'injection de carburant
EP0073967A1 (fr) Pompe d'injection de carburant pour moteurs à combustion interne
DE2348865A1 (de) Vorrichtung zur brennstoffeinspritzung
DE2705489A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
EP0597249B1 (fr) Dispositif d'injection de combustible, in particulier pompe-injecteur pour moteurs à combustion interne
DE2612973A1 (de) Einspritzgeraet einer einspritzpumpe fuer verbrennungsmotoren
EP1402174B1 (fr) Dispositif d'injection de carburant pour moteur a combustion interne
DE4227851A1 (de) Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE3409295A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
EP1413756B1 (fr) Pompe à combustible
EP1714026B1 (fr) Soupape d'injection de carburant
WO2014206843A1 (fr) Pompe haute pression
DE102022108081B4 (de) Pneumatische Ventilfeder
EP1347168B1 (fr) Injecteur pour moteurs à combustion interne

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19841222

AK Designated contracting states

Designated state(s): AT DE FR GB

17Q First examination report despatched

Effective date: 19860214

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT DE FR GB

REF Corresponds to:

Ref document number: 23209

Country of ref document: AT

Date of ref document: 19861115

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3461113

Country of ref document: DE

Date of ref document: 19861204

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19940630

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19940707

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19940729

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19940928

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19950717

Ref country code: AT

Effective date: 19950717

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19950717

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19960402

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19960430

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST