EP0153491A1 - Kraftstoffeinspritzpumpe für Brennkraftmaschinen - Google Patents

Kraftstoffeinspritzpumpe für Brennkraftmaschinen Download PDF

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Publication number
EP0153491A1
EP0153491A1 EP84116244A EP84116244A EP0153491A1 EP 0153491 A1 EP0153491 A1 EP 0153491A1 EP 84116244 A EP84116244 A EP 84116244A EP 84116244 A EP84116244 A EP 84116244A EP 0153491 A1 EP0153491 A1 EP 0153491A1
Authority
EP
European Patent Office
Prior art keywords
valve
valve seat
plate
seat body
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.)
Withdrawn
Application number
EP84116244A
Other languages
German (de)
English (en)
French (fr)
Inventor
Walter Ing. Häfele
Reinhard Dipl.-Ing. Schwartz
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
Publication of EP0153491A1 publication Critical patent/EP0153491A1/de
Withdrawn legal-status Critical Current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
    • 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
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion

Definitions

  • the invention relates to a fuel injection pump for internal combustion engines of the type specified in the preamble of claim 1.
  • the two valves are combined to form a double-acting valve with a single plate-shaped, resilient circular valve plate having a central passage, which lies in the area of its outer circumference on a first valve seat and in the area of its passage on a second valve seat which is arranged opposite the first valve seat.
  • the valve plate lifts off the valve seat on the outer circumference in the conveying direction and opens in the opposite direction in the area of its passage.
  • the central passage of the valve plate lies with play around a pin, so that between The pin and inner wall of the valve plate set a narrow annular gap with throttling effect (DE-OS 18 15 254).
  • the fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage, on the one hand, of being extremely flat like the known double-acting valve and, on the other hand, of offering the advantages of a two-valve arrangement, namely the sufficiently precise setting of the opening pressure and the clean closing and opening of the valves both in the funding and in the relief phase. Due to the design, extremely small dead spaces and the associated extremely low harmful volume, a high injection pressure can be achieved.
  • the fuel injection pump for an internal combustion engine which can be seen in detail in longitudinal section in FIG. 1, has a pump housing 10 with a bore 11 in which, on the one hand, a cylinder liner 12, in which a pump piston 13 is guided axially displaceably, and on the other hand, a two-valve arrangement, hereinafter referred to as a constant pressure valve 14 , is used.
  • Pump piston 13, cylinder liner 12 and the lower end face 15 of the constant pressure valve 14 delimit a pump working space 16 of the fuel injection pump.
  • a connection channel 17 opens for a pressure line leading to an injection nozzle, not shown.
  • the constant pressure valve 14 has, in spatial succession, a pressure valve 18 which opens in the fuel delivery direction, that is to say from the pump working chamber 16 to the connecting duct 17, and a relief valve 19 which opens in the opposite direction.
  • the pressure valve 18 controls the K raftstoff begang to the injection nozzle, while the relief valve is necessary to prevent so-called afterdrip the injection nozzle and the avoidance of cavitation damage due to pressure waves 19, which develop during the closing of the injector and be reflected several times at closed discharge line.
  • the pressure valve 18 is designed as a plate or plate seat valve. It has a valve seat body 20, a valve plate 21 designed as an annular disk and a flat-conical disk-like valve closing spring 22 with a central passage 24.
  • the valve closing spring 22 is designed here as a plate spring (FIG. 2).
  • the valve seat body 20 has a plurality of through bores 25 which are arranged at a radial distance from the valve axis and offset in the circumferential direction, which are open to the pump working chamber 16 on the one hand and can be covered by the valve plate 21 on the other hand.
  • the valve closing spring 22 lies in the region of its passage 24 on the valve plate 21 and presses against a valve seat 26 on the end face 27 of a connecting piece 28 in the vicinity of its outer periphery, as a result of which the valve plate 21 is pressed onto the valve seat body 20.
  • the connection piece 28 carries the central connection channel 17, the opening of which in the front face 27 is essentially aligned with the passage 24 of the valve closing spring 22 and the ring opening 29 of the valve plate 21 designed as an annular disk. Due to this design, the valve closing spring 22 of the pressure valve 18 also forms the valve closing or opening member of the relief valve 19.
  • a spacer ring 30 is arranged, in the ring opening 31, the valve plate 21 is centered.
  • an axial groove 33 is arranged, which is in liquid-conducting connection with a radial groove 34, which at the same time the End face 35 of the valve seat body 20 forming the valve seat is arranged and opens into one of the through bores 2.
  • This radial groove 34 acts in the relief phase, that is to say when the relief valve 19 is open, as a backflow throttle for the fuel from the connection channel 17 to the pump work space 16.
  • the spacer ring 30 can be designed in one piece with both the connection piece 28 and the valve seat body 20, but is made from manufacturing reasons preferably carried out as a single part.
  • the connector 28, the spacer ring 30 and the valve seat body 20 are surrounded on the outside by a high-pressure seal 36, which on the free end face 15 of the valve seat body. 20 overlaps with a flange 37 and is positively connected to the connector 28 by beads 38.
  • connection channel 17 If, however, the pressure in the connection channel 17 is higher than the spring force of the plate spring 23, which is now effective as a valve member for the relief valve 19, this springs on the outer circumference of its valve seat 26 on the connection piece 28, so that fuel now flows in the opposite direction from the connection channel 17 Via the axial groove 33, the radial groove 34 acting as a backflow throttle and a through hole 25 can flow to the pump working space 16.
  • the relief valve 19 thus determines the standing pressure remaining in the pressure line to the injection nozzle, and the backflow throttle 34 dampens the relief process in the desired manner.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP84116244A 1984-02-10 1984-12-22 Kraftstoffeinspritzpumpe für Brennkraftmaschinen Withdrawn EP0153491A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8404020U 1984-02-10
DE19848404020 DE8404020U1 (de) 1984-02-10 1984-02-10 Kraftstoffeinspritzpumpe für Brennkraftmaschinen

Publications (1)

Publication Number Publication Date
EP0153491A1 true EP0153491A1 (de) 1985-09-04

Family

ID=6763406

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84116244A Withdrawn EP0153491A1 (de) 1984-02-10 1984-12-22 Kraftstoffeinspritzpumpe für Brennkraftmaschinen

Country Status (3)

Country Link
EP (1) EP0153491A1 (enrdf_load_stackoverflow)
JP (1) JPS60145277U (enrdf_load_stackoverflow)
DE (1) DE8404020U1 (enrdf_load_stackoverflow)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2275522A (en) * 1993-02-26 1994-08-31 Caterpillar Inc Compact reverse flow check valve assembly for a unit fluid pump-injector

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB729763A (en) * 1952-07-21 1955-05-11 Napier & Son Ltd Improvements in surge reducing or pressure reducing valves for the fuel injection apparatus of internal combustion engines
WO1980002180A1 (en) * 1979-04-09 1980-10-16 Caterpillar Tractor Co Safety check valve for unit fuel pump-injector

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1815254A1 (de) * 1968-12-18 1970-08-13 Maschf Augsburg Nuernberg Ag Einrichtung zur Gleichdruckentlastung an Brennstoffeinspritzpumpendruckleitungen

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB729763A (en) * 1952-07-21 1955-05-11 Napier & Son Ltd Improvements in surge reducing or pressure reducing valves for the fuel injection apparatus of internal combustion engines
WO1980002180A1 (en) * 1979-04-09 1980-10-16 Caterpillar Tractor Co Safety check valve for unit fuel pump-injector

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2275522A (en) * 1993-02-26 1994-08-31 Caterpillar Inc Compact reverse flow check valve assembly for a unit fluid pump-injector
GB2275522B (en) * 1993-02-26 1996-09-18 Caterpillar Inc Compact reverse flow check valve assembly for a unit fluid pump-injector

Also Published As

Publication number Publication date
JPS60145277U (ja) 1985-09-26
JPH041338Y2 (enrdf_load_stackoverflow) 1992-01-17
DE8404020U1 (de) 1985-06-13

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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): DE FR GB IT

17Q First examination report despatched

Effective date: 19860724

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

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19861203

RIN1 Information on inventor provided before grant (corrected)

Inventor name: HAEFELE, WALTER, ING.

Inventor name: SCHWARTZ, REINHARD, DIPL.-ING.