WO1988005129A1 - Soupape de surete pour pompes d'injection de carburant - Google Patents

Soupape de surete pour pompes d'injection de carburant Download PDF

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Publication number
WO1988005129A1
WO1988005129A1 PCT/DE1987/000568 DE8700568W WO8805129A1 WO 1988005129 A1 WO1988005129 A1 WO 1988005129A1 DE 8700568 W DE8700568 W DE 8700568W WO 8805129 A1 WO8805129 A1 WO 8805129A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
recesses
relief
piston
pressure relief
Prior art date
Application number
PCT/DE1987/000568
Other languages
German (de)
English (en)
Inventor
Karl Konrath
Klaus Krieger
Hermann Schmidt
Rolf Lutz
Johann Oberl
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 WO1988005129A1 publication Critical patent/WO1988005129A1/fr

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
    • 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

Definitions

  • the invention is based on a pressure relief valve for fuel injection pumps according to the type of the main claim.
  • the pressure relief valve has a considerable influence on the quality of the fuel injection.
  • the pressure relief valve is arranged between the pump work chamber of the fuel injection pump and the injection nozzle on the internal combustion engine in the pressure line and thus acts on the fuel injection quantity that has already been metered.
  • the pressure valve has a double task.
  • the pressure relief valve serves as a non-return valve, in order to prevent the fuel located in the pressure line from being sucked back to the pump working chamber during the suction stroke of this pump piston.
  • the relief piston of the pressure relief valve causes a relief of the high pressure in the line section located between the pressure relief valve and the injection nozzle, in that the relief piston draws a corresponding volume from the pressure line by immersing it in the guide bore.
  • This relief is necessary above all to avoid that a high fuel pressure remaining in the pressure line, in particular in connection with pressure waves, leads to the fuel injector opening again and fuel being re-injected into the combustion chamber.
  • Such spraying leads to a substantial deterioration of the exhaust gases, as well as to other disadvantages, such as coking of the spray openings of the injection nozzle.
  • the stroke volume of the relief piston is very precisely matched to the assigned elements of the injection system. This applies in particular to the length of the pressure line in connection with its cross section and to the construction of the injection nozzle. In every injection system, the pressure relief valve is therefore very precisely adapted to the circumstances. In the case of large series production, the position and width of the relief piston and thus its stroke volume - or also the consideration of an adjustment grinding - are taken into account in accordance with the individual engine-specific requirements by corresponding controls of the processing tools in the production automation.
  • the radial guidance of the valve member in the guide bore is of particular importance.
  • the pressure relief valve according to the invention for fuel injection pumps with the characterizing features of the main claim has the advantage that the guidance of the valve is extended considerably beyond the stem, namely up to the collar edge of the relief piston, which faces away from the recesses. This extension is achieved above all by eliminating the puncture between the relief collar and the recesses.
  • the guide length is extended by 60%.
  • the end walls of the recesses simultaneously form the ring end wall of the relief piston, interrupted by the remaining guide webs of the shaft.
  • the recesses are evenly distributed over the circumference of the shaft and there are a maximum of six such recesses.
  • the movable valve member is machined _>, the tool being machined transverse to the valve axis and the relief piston side depending on the bevel.
  • a closing edge of the recesses running parallel to the valve seat can be very easily achieved in this way, so that the back suction thus begins very precisely with the axial position when this edge is immersed in the guide bore
  • FIG. 1 shows, in a highly simplified manner, the arrangement of a pressure relief valve in a distributor injection pump, partly shown in longitudinal section, and
  • FIG. 2 shows the pressure relief valve according to the invention from FIG. 1 on an enlarged scale.
  • a pump piston 1 is driven in a reciprocating and at the same time rotating movement according to the arrows indicated by means not shown. With its end face 2 facing away from the drive, it delimits one side in one
  • a suction channel 5 opens into the pump work space 4, which can be controlled via longitudinal grooves 6 provided in the pump piston.
  • the pump piston 1 has a central axial bore 7, from which a radial bore 8 branches off, which merges into a distributor groove 9, which is likewise arranged in the pump piston 1 and opens into the lateral surface thereof.
  • this distributor groove 9, which is designed as a longitudinal groove pressure lines 11, which begin in the cylinder liner 3 when the pump piston 1 is rotating, are connected to the pump working chamber 4, the inputs of these pressure lines 11 being evenly distributed in the cylinder liner 3 around the pump piston 1 are and correspond in number to the number of strokes of the pump piston 1 during one revolution and thus to the number of engine cylinders to be supplied.
  • a control slide is axially displaceable on the pump piston 1
  • Feed pump pressure standing suction chamber 14 is connected, from which the suction channel 5 branches off.
  • a pressure relief valve 16 is arranged in each of the pressure lines 11, which lead to an injection nozzle 15 on the engine.
  • the pressure valve 16 has a movable valve member 17, the shaft 18 of which is guided in a guide bore 19 of a valve carrier 21 and in the closing direction by a closing spring 22 with its closing cone 23 to a valve seat 24 is burdened.
  • Longitudinal groove-like recesses 25 are provided in the shaft 18, the shaft 18 having radial guide surfaces 26 on the remaining webs 27 for guidance in the guide bore 19. These webs merge into a collar upstream of the closing cone 23, which slides radially in the guide bore 19 as a relief piston 28 and has a lower end edge 31 which is interrupted in its circulation around the valve member 17 by the width of the guide surfaces 26 of the webs 27 is.
  • An annular groove-like recess 29 is present between the closing cone 23 and this relief piston 28.
  • the fuel injection pump works as follows: During the downward suction stroke of the pump piston 1
  • the suction channel 5 is then blocked by the pump piston 1 and the radial bore 8 or distributor groove 9 by a the pressure lines 11 are turned on, so that the fuel from the pump work chamber 4 is conveyed under pressure via the axial bore 7, the radial bore 8, the distributor groove 9 and the pressure line 11 to the injection nozzle 15.
  • the fuel flows in this pressure line 11 via the pressure relief valve 16.
  • the movable valve member 17 of this pressure relief valve 16 is displaced against the closing spring 22, the closing cone 23 lifting off the valve seat 24, so that after replacement a certain "relief stroke", the relief piston 28 emerges from the guide bore 19 and the fuel delivered can flow via the recesses 27 to the injection nozzle 15.
  • the transverse bore 13 is closed by the control slide 12
  • the injection nozzle 15 closes and the pressure relief valve 16 almost simultaneously.
  • the pressure relief valve 16 closes, the guide surfaces 26 of the webs 27 slide in the guide bore 19, the relief piston 28 with its after a forward stroke lower end edge 31 dips into the guide bore 19, so that the relief piston from this passage of the end edge 31 on the valve seat 24, from the pressure line section between the pressure relief valve 16 and the injector 15, sucks back a certain amount of fuel from this line section, thereby relieving the pressure takes place.
  • This relief is ended when the closing cone 23 rests on the valve seat 24.
  • the relief volume corresponds to the cross-section of the relief piston 28 times its height, the height resulting when the valve is closed from the distance of the control edge 31 of the relief piston 28 to the sealing point of the closing cone 23 on the valve seat 24. As a result, the guide surface of the valve member is over

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

Une soupape de sureté (16) pour pompes d'injection de carburant comporte un piston de décharge (28) qui plonge dans un alésage de guidage (19) d'un porte-soupape (21) afin d'évacuer le trop-plein de pression de la canalisation de pression. L'élément de soupape (17) présente, en amont et en aval du piston de décharge (28), des évidements (25) destinés à la canalisation de carburant lorsque la soupape est ouverte, et ménagés dans une tige (18), avec laquelle l'élément mobile de soupape (17) est guidé dans l'alésage de guidage (19). Les parties (27) de la tige (18) qui délimitent les évidements (25) font corps avec le piston (28), de sorte que les parois frontales des évidements (25) constituent en même temps la paroi frontale dudit piston.
PCT/DE1987/000568 1986-12-29 1987-12-04 Soupape de surete pour pompes d'injection de carburant WO1988005129A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP3644595.9 1986-12-29
DE19863644595 DE3644595A1 (de) 1986-12-29 1986-12-29 Druckentlastungsventil fuer kraftstoffeinspritzpumpen

Publications (1)

Publication Number Publication Date
WO1988005129A1 true WO1988005129A1 (fr) 1988-07-14

Family

ID=6317309

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1987/000568 WO1988005129A1 (fr) 1986-12-29 1987-12-04 Soupape de surete pour pompes d'injection de carburant

Country Status (2)

Country Link
DE (1) DE3644595A1 (fr)
WO (1) WO1988005129A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3843819A1 (de) * 1988-09-09 1990-03-22 Bosch Gmbh Robert Druckventil
JP3251283B2 (ja) * 1989-11-13 2002-01-28 ローベルト ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング 圧力弁
FR2654468B1 (fr) * 1989-11-13 1993-05-21 Bosch Gmbh Robert Soupape de pression pour installation d'injection, en particulier pour moteur a combustion interne.

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR877778A (fr) * 1940-12-21 1942-12-16 Hannoversche Maschb Ag Vormals Soupape de refoulement destinée en particulier aux pompes d'injection de combustible des moteurs diesel
DE1045167B (de) * 1957-07-04 1958-11-27 Maihak Ag Kraftstoffeinspritzvorrichtung
US2922581A (en) * 1954-06-14 1960-01-26 Bendix Aviat Corp Fuel injection apparatus
FR1349516A (fr) * 1963-01-09 1964-01-17 Michigan Tool Co Rectifieuse dans laquelle on a fait osciller une pièce à usiner sur un arbre vertical, la meule étant montée sur une broche en vue de son déplacement axial vers cet arbre
US3203139A (en) * 1963-02-14 1965-08-31 Tomlinson Ind Inc Machine and method for surface finishing objects
DE1236863B (de) * 1954-06-14 1967-03-16 Bendix Corp Brennstoffeinspritzvorrichtung fuer Brennkraftmaschinen
FR2298008A1 (fr) * 1975-01-15 1976-08-13 Vysoke Uceni Tech Brne Pompe a injection pour moteurs diesel
GB2031989A (en) * 1978-09-28 1980-04-30 Bosch Gmbh Robert Fuel injection pump for internal combustion engines

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR877778A (fr) * 1940-12-21 1942-12-16 Hannoversche Maschb Ag Vormals Soupape de refoulement destinée en particulier aux pompes d'injection de combustible des moteurs diesel
US2922581A (en) * 1954-06-14 1960-01-26 Bendix Aviat Corp Fuel injection apparatus
DE1236863B (de) * 1954-06-14 1967-03-16 Bendix Corp Brennstoffeinspritzvorrichtung fuer Brennkraftmaschinen
DE1045167B (de) * 1957-07-04 1958-11-27 Maihak Ag Kraftstoffeinspritzvorrichtung
FR1349516A (fr) * 1963-01-09 1964-01-17 Michigan Tool Co Rectifieuse dans laquelle on a fait osciller une pièce à usiner sur un arbre vertical, la meule étant montée sur une broche en vue de son déplacement axial vers cet arbre
US3203139A (en) * 1963-02-14 1965-08-31 Tomlinson Ind Inc Machine and method for surface finishing objects
FR2298008A1 (fr) * 1975-01-15 1976-08-13 Vysoke Uceni Tech Brne Pompe a injection pour moteurs diesel
GB2031989A (en) * 1978-09-28 1980-04-30 Bosch Gmbh Robert Fuel injection pump for internal combustion engines

Also Published As

Publication number Publication date
DE3644595A1 (de) 1988-07-07

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