EP0171667A1 - Soupape de commande pour dispositif d'injection de combustible - Google Patents

Soupape de commande pour dispositif d'injection de combustible Download PDF

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Publication number
EP0171667A1
EP0171667A1 EP85109245A EP85109245A EP0171667A1 EP 0171667 A1 EP0171667 A1 EP 0171667A1 EP 85109245 A EP85109245 A EP 85109245A EP 85109245 A EP85109245 A EP 85109245A EP 0171667 A1 EP0171667 A1 EP 0171667A1
Authority
EP
European Patent Office
Prior art keywords
pressure side
piston
control valve
valve
seat
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
EP85109245A
Other languages
German (de)
English (en)
Other versions
EP0171667B1 (fr
Inventor
Reda R. Rizk
Hans-Gottfried Michels
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.)
Kloeckner Humboldt Deutz AG
Original Assignee
Kloeckner Humboldt Deutz AG
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 Kloeckner Humboldt Deutz AG filed Critical Kloeckner Humboldt Deutz AG
Priority to AT85109245T priority Critical patent/ATE41042T1/de
Publication of EP0171667A1 publication Critical patent/EP0171667A1/fr
Application granted granted Critical
Publication of EP0171667B1 publication Critical patent/EP0171667B1/fr
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
    • 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
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • 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

Definitions

  • the invention relates to a control valve for a fuel injection device, in particular an electromagnetically actuated control valve for a fuel injection device of air-compressing, self-igniting internal combustion engines, with a valve body designed as a piston slide valve, which is provided in a housing space provided with at least one high-pressure side and one low-pressure side connection axially into a through one housing-side valve seat and a piston valve-side seat surface edge certain closing and an opening position is movable.
  • Such a generic control valve for a fuel injection device is known from DE-OS 30 02 361, which on the one hand controls the intake port of an injection pump to control the injection times (start and end of injection) and on the other hand connects an outflow port to a high-pressure port of the injection pump.
  • the control valve itself has a valve body in the form of a spool, which is provided with a valve seat, a high-pressure chamber (high-pressure side spool area) and a low-pressure chamber (low-pressure side spool area) being formed on both sides of the valve seat.
  • the opposite pressure attack surfaces of the high pressure side and the The low-pressure chamber are dimensioned differently.
  • a fixed throttle is provided in the outflow channel, so that an exact closed position of the spool can be assumed without counter-opening movements. Overall, a considerable amount of manufacturing and assembly work is required for this.
  • this generic control valve has the decisive disadvantage that, despite the effort involved in this valve, precise control of the injection process is not possible and, moreover, the operating behavior of the internal combustion engine is disadvantageously changed. This is particularly due to the fact that upon impact of the spool-side seat edge in the valve housing side valve seat, it comes inevitable to ückprallambaen R. Material and production-related and due to preload tolerances of the springs provided here for the closing process are in multi-cylinder internal combustion engines such. B. thus different rebound movements inevitable in the control valves to be provided per cylinder unit. As a result, the equal funding for the respective cylinder units is greatly impaired by the function-related disadvantages of the control valve of the generic type.
  • the invention according to claim 1 is characterized in that the valve housing space either between its valve seat and the high-pressure side connection on the one hand and the high-pressure side spool area adjacent to the seat surface edge on the other hand or between its valve seat and the low-pressure side connection on the one hand and the low-pressure side adjacent to the seat surface edge Piston slide area, on the other hand, each have a section with the same diameter.
  • the main advantage of this solution is that the spool stops the connection between the high-pressure side connection and the low-pressure side connection during its closing movement when the seat edge of the spool area reaches the valve housing section with the same diameter. This happens before the seat edge of the spool opens in the valve seat of the valve housing space.
  • the sealing overlap area between the piston slide and the valve housing space is preferably provided on the high-pressure side of the piston slide.
  • the development according to the invention according to claim 2 includes the essential advantage that uneven pressure distributions on the spool due to the lack of pressure application surfaces on the high-pressure side spool area can exert no interference either in the closed position or during the opening phase of the spool, so that overall an absolutely stable behavior of the spool in all operating areas is ensured.
  • the manufacturing outlay for the control valve is considerably reduced as a result.
  • the valve seat on the housing is designed such that it covers the piston valve by an undercut. This ensures that the necessary space for processing the valve seat is given.
  • the low-pressure side spool area is preferably formed with a smaller diameter overall than the high-pressure side spool area (claim 4). This ensures that, in principle, in the high pressure phase during an injection process a resulting compressive force is present in the closing direction. This includes the decisive advantage of the absolute tightness of the control valve in the high-pressure phase for the operating result, particularly in the case of the very high injection pressures of 1,000 to 2,000 bar desired for air-compressing, self-igniting internal combustion engines.
  • the task according to claim 5 provides that on the piston slide and / or within the K olbenschiebers a relatively movable about this damping mass, a damping piston element is provided in particular.
  • This damping mass advantageously counteracts any rebound movements of the piston slide after it hits the valve seat, so that rebound movements are largely avoided.
  • this solution according to the invention also ensures that such a control valve according to the invention can be used in a fuel injection device for multi-cylinder internal combustion engines with the desired advantages.
  • the damping mass can of course also by other shapes such.
  • the damping mass is preferably designed as a damping piston with a tubular cross-sectional structure that is axially movable in a receiving space provided in the piston, the damping piston being stable within the receiving space by means of a stop element that can be attached to the piston slide.
  • the stop element can be designed or attached to the spool in such a way that the receiving space is larger Longitudinal extension than the damping piston, that is, in the axial direction of the spool when the damping piston is inserted, there is a distance between the end face region of the damping piston and the stop surface of the stop element.
  • the stop element can preferably be screwed into the high-pressure side end face of the piston valve.
  • the stop element is preferably hollow-cylindrical.
  • control valves 1 are intended to be used in a fuel injection device of a multi-cylinder, self-igniting, air-compressing internal combustion engine.
  • the control valves 1 according to the invention are assigned to a fuel injection pump which, as is generally customary, consists of a pump housing, a pump element designed as a pump piston, which can be moved in a known manner via a cam and a spring-loaded plunger in a pump chamber .
  • the control valves 1 are connected to the fuel injection pump, not shown, via the high-pressure connection channel 2.
  • the high pressure channel 3 leads to a fuel injector, not shown.
  • the high-pressure connection channel 2 and the high-pressure channel 3 leading to the fuel injection nozzle are controlled by a valve body 4 designed as a piston slide, the high-pressure side piston slide area 5 of which is delimited by a seat edge 6.
  • the seat edge 6 interacts with a valve seat 8 incorporated in the valve housing space 7 and provides the high-pressure connection between the high-pressure connection channel 2 and the high-pressure channel 3 leading to the fuel injector in the closed position of the spool 4.
  • a high-pressure chamber 9 and a low-pressure chamber 10 are formed on the high-pressure side in the valve housing space 7, an outflow channel 11 leading from the latter to a fuel tank (not shown).
  • the high-pressure connection channel 2 in the open position of the control valve 1 can be connected to the outflow channel 11 leading into the fuel tank, so that the valve body 4 can be opened or closed in the high-pressure phase of the fuel injection pump the start of injection or the end of injection is adjustable.
  • the actuating elements of the control valve have not been shown.
  • the piston slide ß preferably druckfederbeetzt and is actuated by an electromagnetic actuator, which is controlled by an electrically operated measurement processing.
  • the electromagnetic actuating device acts on the end face of the low-pressure piston valve region 12 and a compression spring on the end surface of the high-pressure piston valve region 5.
  • These actuating elements of the piston slide are preferably designed analogously to the actuating elements as described in the unpublished patent application P 33 02 294.1, to which express reference is also made in this regard.
  • valve housing space 7 of the control valve according to the invention according to FIG. 1 has a section 13 between its valve seat 8 and the high-pressure connection channel 2 or the high-pressure channel 3, which section is designed with the same diameter as the entire high-pressure side spool area 5.
  • the diameter of the section on the valve housing side 13 is of course formed with such a fit allowance that the axial movement of the spool 4 is not affected.
  • the low-pressure piston valve 12 is designed with a smaller diameter overall than the high-pressure piston valve region 5.
  • the valve housing space 7 has a housing space chamber 15 on the high-pressure side and a housing space chamber 16 on the low-pressure side, which are respectively assigned to the end faces 14 (high-pressure side) and 17 (low-pressure side).
  • the high-pressure side housing chamber 15 and the low-pressure side housing chamber 16 are connected to each other via a bore 18 extending within the piston slide 4.
  • a damping mass which is movable relative to this is provided within the piston slide 4.
  • This damping mass is provided as a D ämpfungskolbenelement 22 formed with a tubular cross-sectional structure and arranged to be movable in the axial direction of the spool 4 in a receiving space 23rd
  • the receiving space 23 has a greater axial longitudinal extent than the damping piston element 22.
  • This receiving space 23 or the axial movability of the damping piston element 22 is limited towards the high-pressure side end face 14 by a stop element 24 which can be screwed into this end face 14. Due to the greater longitudinal extent of the receiving space 23, a distance x is thus given.
  • the damping piston bears against the stop element 24 due to the difference in inertia.
  • the damping piston 22 moves with a time delay, which is predetermined by the distance x and thus the size of the damping piston 22 or receiving space 23, toward the end face 25 of the receiving space 23 facing the seat edge 6.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
EP85109245A 1984-07-25 1985-07-24 Soupape de commande pour dispositif d'injection de combustible Expired EP0171667B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85109245T ATE41042T1 (de) 1984-07-25 1985-07-24 Steuerventil fuer eine kraftstoffeinspritzvorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843427421 DE3427421A1 (de) 1984-07-25 1984-07-25 Steuerventil fuer eine kraftstoffeinspritzvorrichtung
DE3427421 1984-07-25

Publications (2)

Publication Number Publication Date
EP0171667A1 true EP0171667A1 (fr) 1986-02-19
EP0171667B1 EP0171667B1 (fr) 1989-03-01

Family

ID=6241541

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85109245A Expired EP0171667B1 (fr) 1984-07-25 1985-07-24 Soupape de commande pour dispositif d'injection de combustible

Country Status (5)

Country Link
US (2) US4653723A (fr)
EP (1) EP0171667B1 (fr)
JP (1) JPS6138158A (fr)
AT (1) ATE41042T1 (fr)
DE (2) DE3427421A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0309797A2 (fr) * 1987-09-26 1989-04-05 Robert Bosch Gmbh Soupape magnétique
WO1991003641A1 (fr) * 1989-08-30 1991-03-21 Robert Bosch Gmbh Soupape de commande electromagnetique

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4238727C2 (de) * 1992-11-17 2001-09-20 Bosch Gmbh Robert Magnetventil
DE4243665C2 (de) * 1992-12-23 2003-11-13 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung, insbesondere Pumpedüse für Brennkraftmaschinen
DE4322546A1 (de) * 1993-07-07 1995-01-12 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
US5636615A (en) * 1995-02-21 1997-06-10 Diesel Technology Company Fuel pumping and injection systems
DE19510588B4 (de) * 1995-03-23 2006-08-17 Bosch Rexroth Aktiengesellschaft Ventilsitzkonstruktion
US5865371A (en) * 1996-07-26 1999-02-02 Siemens Automotive Corporation Armature motion control method and apparatus for a fuel injector
US6045120A (en) * 1998-01-13 2000-04-04 Cummins Engine Company, Inc. Flow balanced spill control valve
US6116209A (en) * 1998-05-27 2000-09-12 Diesel Technology Company Method of utilization of valve bounce in a solenoid valve controlled fuel injection system
DE19837333A1 (de) * 1998-08-18 2000-02-24 Bosch Gmbh Robert Steuereinheit zur Steuerung des Druckaufbaus in einer Pumpeneinheit
GB2361645A (en) 2000-04-26 2001-10-31 Blatchford & Sons Ltd Prosthetic foot
DE10032923A1 (de) 2000-07-06 2002-01-24 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
US6655653B2 (en) 2001-04-20 2003-12-02 Woodward Governor Company Method and mechanism to reduce flow forces in hydraulic valves
DE10119271A1 (de) * 2001-04-20 2002-10-24 Zahnradfabrik Friedrichshafen Regelventil
US6792975B2 (en) 2001-05-24 2004-09-21 Borgwarner Inc. Pulse-width modulated solenoid valve including axial stop spool valve
EP1321663A3 (fr) * 2001-12-19 2003-07-02 Robert Bosch Gmbh Dispositif d'injection de combustible pour moteur à combustion interne
US20060096643A1 (en) * 2004-11-10 2006-05-11 Mccarty Michael W Seal assembly for a fluid pressure control device
US9500171B2 (en) * 2012-12-12 2016-11-22 Hamilton Sundstrand Corporation Pressure regulating valve
US11192679B2 (en) * 2018-02-20 2021-12-07 Universidad Continental S.A.C. Food container with multiple compartments and incorporated drinks holder

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH318004A (de) * 1953-04-27 1956-12-15 Knoll Andre Steuerorgan für flüssige und gasförmige Medien.
GB2036867A (en) * 1978-12-08 1980-07-02 Ford Motor Co Fuel flow control valve assembly
GB2041577A (en) * 1979-01-31 1980-09-10 Lucas Industries Ltd Fuel System for internal combustion engines
DE3201432A1 (de) * 1982-01-19 1983-09-08 Uwe 2000 Hamburg Heine Daempfungseinrichtung fuer steuerkolben
EP0114375A2 (fr) * 1983-01-25 1984-08-01 Klöckner-Humboldt-Deutz Aktiengesellschaft Dispositif d'injection du combustible pour moteurs à combustion interne à auto-allumage par compression d'air

Family Cites Families (14)

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Publication number Priority date Publication date Assignee Title
US1781224A (en) * 1929-02-02 1930-11-11 Henry F Gilg Valve
US1743758A (en) * 1929-07-25 1930-01-14 Cobb Robert Raymond Air-valve safety device
US2213999A (en) * 1936-09-12 1940-09-10 George Valve Company Packless valve assembly
US2836198A (en) * 1952-11-07 1958-05-27 Robert M Mcneill Control valve
US3122154A (en) * 1961-01-09 1964-02-25 Siebel Explosive actuated valve
US3356333A (en) * 1965-04-05 1967-12-05 Scaramucci Domer Valve seat with lip-like seal
US3680832A (en) * 1969-03-20 1972-08-01 Nikex Nehezipari Kulkere Closure device for streaming media, in particular high pressure liquids
GB1433034A (en) * 1972-05-26 1976-04-22 Kernforschung Gmbh Ges Fuer Glandless electromagnetic valve
US3779225A (en) * 1972-06-08 1973-12-18 Bendix Corp Reciprocating plunger type fuel injection pump having electromagnetically operated control port
US4276000A (en) * 1978-01-31 1981-06-30 Lucas Industries Limited Liquid fuel pumping apparatus
DE2842155A1 (de) * 1978-09-28 1980-04-10 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3002361A1 (de) * 1979-01-25 1980-07-31 Lucas Industries Ltd Steuerventil
DE2935912A1 (de) * 1979-09-06 1981-03-26 MAN B & W Diesel GmbH, 86153 Augsburg Brennstoffeinspritzvorrichtung fuer brennkraftmaschinen
FR2481752A1 (fr) * 1980-04-30 1981-11-06 Renault Vehicules Ind Amelioration des dispositifs mecaniques d'injection de combustible, notamment pour des moteurs diesel

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH318004A (de) * 1953-04-27 1956-12-15 Knoll Andre Steuerorgan für flüssige und gasförmige Medien.
GB2036867A (en) * 1978-12-08 1980-07-02 Ford Motor Co Fuel flow control valve assembly
GB2041577A (en) * 1979-01-31 1980-09-10 Lucas Industries Ltd Fuel System for internal combustion engines
DE3201432A1 (de) * 1982-01-19 1983-09-08 Uwe 2000 Hamburg Heine Daempfungseinrichtung fuer steuerkolben
EP0114375A2 (fr) * 1983-01-25 1984-08-01 Klöckner-Humboldt-Deutz Aktiengesellschaft Dispositif d'injection du combustible pour moteurs à combustion interne à auto-allumage par compression d'air

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0309797A2 (fr) * 1987-09-26 1989-04-05 Robert Bosch Gmbh Soupape magnétique
EP0309797A3 (en) * 1987-09-26 1990-05-09 Robert Bosch Gmbh Magnetic valve
WO1991003641A1 (fr) * 1989-08-30 1991-03-21 Robert Bosch Gmbh Soupape de commande electromagnetique

Also Published As

Publication number Publication date
DE3427421A1 (de) 1986-01-30
US4653723A (en) 1987-03-31
JPS6138158A (ja) 1986-02-24
US4757973A (en) 1988-07-19
EP0171667B1 (fr) 1989-03-01
ATE41042T1 (de) 1989-03-15
DE3568468D1 (en) 1989-04-06

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