EP0178428A2 - Pompe d'injection combinée avec l'injecteur commandée par électricité pour l'injection de carburant dans moteurs Diesel - Google Patents

Pompe d'injection combinée avec l'injecteur commandée par électricité pour l'injection de carburant dans moteurs Diesel Download PDF

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Publication number
EP0178428A2
EP0178428A2 EP85110504A EP85110504A EP0178428A2 EP 0178428 A2 EP0178428 A2 EP 0178428A2 EP 85110504 A EP85110504 A EP 85110504A EP 85110504 A EP85110504 A EP 85110504A EP 0178428 A2 EP0178428 A2 EP 0178428A2
Authority
EP
European Patent Office
Prior art keywords
pump
channel
overflow
housing part
section
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
EP85110504A
Other languages
German (de)
English (en)
Other versions
EP0178428B1 (fr
EP0178428A3 (en
Inventor
Jean Leblanc
Jean Pigeroulet
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 AT85110504T priority Critical patent/ATE42612T1/de
Publication of EP0178428A2 publication Critical patent/EP0178428A2/fr
Publication of EP0178428A3 publication Critical patent/EP0178428A3/de
Application granted granted Critical
Publication of EP0178428B1 publication Critical patent/EP0178428B1/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
    • 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
    • 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
    • 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
    • F02M59/366—Valves being actuated electrically

Definitions

  • the invention relates to an electrically controlled pump nozzle according to the preamble of the main claim.
  • a pump nozzle for diesel engines known from US Pat. No. 4,392,612
  • the pump stroke during the delivery stroke Fuel injection quantity displaced from the pump work chamber to the injection nozzle is determined by the duty cycle of a normally open, electromagnetically operated overflow valve, which is inserted into an overflow channel connecting the pump work chamber with a low pressure chamber.
  • the first section of the overflow channel which is permanently connected to the pump work chamber, is then under the full injection pressure when the overflow valve for controlling the fuel injection blocks the connection between the two sections of the overflow channel and thus blocks the fuel from the low pressure chamber.
  • the overflow valve is fastened to a housing part projecting laterally on the pump housing at the level of the cylinder bore, and the first section of the overflow channel that can be placed under injection pressure cannot be carried out directly from the pump work chamber to the overflow valve in such an arrangement, but has a bent course .
  • This first section of the overflow channel therefore consists of a branch bore arranged laterally offset from the cylinder bore and a cross channel connecting this branch bore with a control channel controlled by the overflow valve.
  • this transverse channel has been made from the outside, from an inlet bore through the laterally projecting housing part, into the branch bore.
  • the transverse channel traverses the control channel forming a control pressure chamber of the overflow valve in this pump nozzle and must be closed to the outside by a sealing plug towards the inlet.
  • Such sealing plugs form a constant risk of leakage because of the very high injection pressures of around 1000 bar, or they are destroyed by the high pressures or driven out of the bore.
  • the aim of the invention is now, in pump nozzles of the type mentioned, in which a direct connection between the pump work space and the overflow valve is not possible for structural reasons, to design the first section of the overflow channel which can be placed under injection pressure in such a way that it is easy to produce even without a sealing plug and a sealed connection between the pump work chamber and the overflow valve is guaranteed.
  • the pump piston with its lateral surface which is fitted into the cylinder bore with a play in the range of a few thousandths of a millimeter, forms the necessary seal for the tap bore emanating from the pump work chamber with the transverse channel connecting the overflow valve.
  • No special sealing means are therefore required for the section of the transverse channel separated by means of the pump piston, and the transverse channel can be designed as a simple transverse bore crossing the cylinder bore.
  • a pump nozzle according to the invention which, according to claim 2, as is known from the patent mentioned at the outset, is provided with a flange surface located on the laterally projecting housing part and serving to fasten an actuator of the overflow valve, against which an end face on the overflow valve can be clamped in a pressure-tight manner Control channel to avoid inadmissibly large dead spaces as a blind hole from the flange surface in the laterally projecting housing part up to a connection point with the cross channel.
  • the overflow valve which is designed as a structural unit comprising all valve components, can thus be manufactured and tested on its own and then attached to the projecting housing part of the pump nozzle be flanged.
  • the two sections of the overflow channel which have a very high pressure difference, are perfectly sealed against one another by the surfaces which can be easily ground flat and form a sealing gap, the flange surface on the projecting housing part and the end face of the overflow valve.
  • pressure equalization grooves formed in the lateral surface of the pump piston or in can be formed in accordance with the characterizing features of claims Wall of the cylinder bore are introduced.
  • FIG. 1 shows a longitudinal section through the first embodiment
  • FIG. 2 shows a partial cross section along the line II-II in FIG. 1, but through the second embodiment having pressure compensation grooves in the cylinder bore.
  • the first exemplary embodiment of an electrically controlled pump nozzle 10 according to the invention shown in FIG. 1 consists of a piston injection pump 9, which is mechanically driven by a camshaft in a manner which is not shown, but is known, the one designated 11 Pump housing receives a pump piston 13 driven with a constant stroke and guided in a cylinder bore 12 and on the front side carries an injection nozzle 16, which is fastened by means of a screw sleeve 14 with the interposition of a pressure valve 15, and is therefore not shown in detail.
  • the pump piston 13 is known, therefore only by one Arrow A indicated drive means driven by a pump plunger 17 against the restoring force of a plunger spring 18. With its end face 19, it delimits a pump working chamber 21 located in the cylinder bore 12, which is closed on the injection nozzle side by the pressure valve 15 and can be connected to the injection nozzle 16 via a pressure channel 53.
  • the pump work chamber 21 is in the drawn outer dead center position of the pump piston 13 by a feed pump 22 under a low inlet pressure of e.g. 4 bar standing fuel supplied.
  • This fuel passes from the feed pump 22 via a feed line 23 and at least one opening 24 in the wall of the screw sleeve 14 into a low pressure chamber 25 surrounding the pressure valve 15 within the screw sleeve 14 and from there via an inlet channel 26 into the pump work chamber 21.
  • the low pressure chamber 25 and the pump working space 21 are also connected to one another via an overflow channel 28 which can be controlled by an overflow valve 27 in the drawn open position of this valve.
  • the inlet pressure of the fuel supplied to the low pressure chamber 25 from the feed pump 22 via the feed line 23 is determined by a pressure relief valve 29 which is inserted into a return line 31.
  • This return line 31 is part of one of the further pump nozzles the same internal combustion engine leading ring line drawn interrupted and ultimately leads the excess fuel back to a tank 32.
  • the overflow valve 27 which operates as a 2/2-way valve, is a solenoid valve which is shown only partially in section in FIG. 1 to show its control function and is the subject of a parallel application with regard to its special configuration.
  • the overflow valve 27 is designed as a needle valve, the valve member 33 of which is actuated by an electric actuator 34 formed by an electromagnet and is surrounded by a pressure chamber 35 in the region of its end section facing away from the actuator 34.
  • This pressure chamber 35 is on the one hand permanently connected to the pump working chamber 21 via a first section 28a of the overflow duct 28 and on the other hand can be connected to the low-pressure chamber 25 via a second section 28b of the overflow duct 28 shown in dashed lines in FIG.
  • the connection from the pressure chamber 35 to the low-pressure chamber 25 which is open in FIG. 1 carries at the transition from the pressure chamber 35 to the second section 28b of the overflow channel 28 a conical valve seat 36 which can be closed by a conical closing surface 33a on the valve member 33,
  • the overflow valve 27 is fastened to a housing part 11 a which projects laterally on the pump housing 11 at the level of the cylinder bore 12. Extending into this housing part 11a is the first section 28a of the overflow channel, which extends from the pump work chamber 21 and which, in order to achieve the compact construction important according to the invention, is made of a flow connected to the pump work chamber 21 til 27 laterally offset to the cylinder bore 12 stub bore 37, a control channel 38 controlled by the overflow valve 27 and a cross-channel 32 connecting this stub bore 37 with the control channel 38.
  • the transverse channel 39 extends in the form of an oblique branch hole from the side of the housing designated 11c, facing away from the laterally projecting housing part 11a, through the cylinder bore 12 to the control channel 38, cuts the branch hole 37 and forms an orifice 37a at this point the branch bore 37.
  • the transverse channel 39 is placed in such a way that it crosses the cylinder bore 12 in a region which is covered by the outer surface 13a of the pump piston 13 in each stroke position.
  • the first section 28a of the overflow channel 28, which consists of the tap bore 37, the control channel 38 and the transverse channel 39 and is under injection pressure when the overflow valve 27 is blocked, is sealed by means of the outer surface 13a of the pump piston 13 without additional sealing means.
  • a flange surface 11b which is arranged at right angles to the longitudinal axis of the pump piston 13 and serves to fasten the overflow valve 27, and against which an end face 27a of the overflow valve 27 is clamped in a pressure-tight manner.
  • the overflow valve 27 is one of both the actuator 35 and all valve components, for. B. valve member 33, pressure chamber 35 and valve seat 36, comprehensive unit and also has in its end face 27a opening connecting channels 41a and 41b for the two sections 28a and 28b of the overflow channel 28.
  • the control channel 38 in the first section 28a of the overflow channel 28 is perfectly sealed with respect to a section of the second section 28b of the overflow channel 28, also drilled from the flange surface 11b in the laterally projecting housing part 11a
  • the lateral surface 13a of the pump piston J3 is provided with two pressure compensation grooves 42 which are permanently connected to the pump working chamber 21 and are designed as longitudinal grooves. These pressure compensation grooves 42 are symmetrical to the longitudinal axis of the transverse channel 3Q with a lateral spacing from one another and to the housing side 11c facing away from the projecting housing part 11a, incorporated into the lateral surface 13a of the pump piston 13. This distance corresponds to the distance a shown in FIG. 2 for the second exemplary embodiment.
  • the second exemplary embodiment shown in FIG. 2 in a partial cross section along line II-II in FIG. 1, differs from the first exemplary embodiment shown in FIG. 1 only in the modified arrangement of two pressure compensation grooves made in the wall of the cylinder bore. Since only the pump housing and the pump piston are designed differently, these and their modified components are given a reference number increased by 100, the other unchanged components are designated as in FIG. 1,
  • the two pressure equalization grooves 42 in FIG. 1 correspond in FIG. 2 to the pressure equalization grooves 142 which are incorporated into the wall of the cylinder bore 112 and which are machined symmetrically to the longitudinal axis of the transverse channel 39 and at a lateral distance a from one another into the wall of the cylinder bore 112 in the form of longitudinal grooves. They are opposite the part of the transverse channel 39 that can be set under injection pressure, ie. they point to the housing side 11c facing away from the laterally projecting housing part J1a. So that these pressure compensation grooves 142 always remain connected to the pump work space 21, they have to be made down to the lowest point of the pump work space 21,
  • the power supply to the actuator 34 of the overflow valve 27 is switched off in accordance with the operating data determined in an electronic control device.
  • the overflow valve 27 is switched to its open position shown in FIG. 1, as a result of which the pressure in the pump working chamber 21 drops suddenly, and the injection nozzle 16 and the pressure valve 15 close, so that the injection is ended.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
EP85110504A 1984-09-14 1985-08-21 Pompe d'injection combinée avec l'injecteur commandée par électricité pour l'injection de carburant dans moteurs Diesel Expired EP0178428B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85110504T ATE42612T1 (de) 1984-09-14 1985-08-21 Elektrisch gesteuerte pumpeduese fuer die kraftstoffeinspritzung bei dieselbrennkraftmaschinen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3433710 1984-09-14
DE19843433710 DE3433710A1 (de) 1984-09-14 1984-09-14 Elektrisch gesteuerte pumpeduese fuer die kraftstoffeinspritzung bei dieselbrennkraftmaschinen

Publications (3)

Publication Number Publication Date
EP0178428A2 true EP0178428A2 (fr) 1986-04-23
EP0178428A3 EP0178428A3 (en) 1987-12-16
EP0178428B1 EP0178428B1 (fr) 1989-04-26

Family

ID=6245358

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85110504A Expired EP0178428B1 (fr) 1984-09-14 1985-08-21 Pompe d'injection combinée avec l'injecteur commandée par électricité pour l'injection de carburant dans moteurs Diesel

Country Status (5)

Country Link
US (1) US4669659A (fr)
EP (1) EP0178428B1 (fr)
JP (1) JPS6172869A (fr)
AT (1) ATE42612T1 (fr)
DE (2) DE3433710A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4836161A (en) * 1986-10-08 1989-06-06 Daimler-Benz Aktiengesellschaft Direct fuel injection method for a diesel engine
WO1992010666A1 (fr) * 1990-12-11 1992-06-25 Lucas Industries Public Limited Company Pompe de carburant
WO1992010669A1 (fr) * 1990-12-11 1992-06-25 Lucas Industries Public Limited Company Pompe de carburant
EP0528226A1 (fr) * 1991-08-16 1993-02-24 Robert Bosch Gmbh Gicleur commandé électriquement pour des dispositifs d'injection de combustible de moteurs à combustion interne
US5485823A (en) * 1990-12-11 1996-01-23 Lucas Industries Public Limited Company Fuel pump having a leaked fuel conveying structure
WO2019110190A1 (fr) * 2017-12-07 2019-06-13 Robert Bosch Gmbh Dispositif d'alimentation en carburant destinée à des carburants cryogéniques

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3629751C2 (de) * 1986-09-01 1998-07-02 Bosch Gmbh Robert Voreinspritzvorrichtung für Brennkraftmaschinen
DE3629754C2 (de) * 1986-09-01 1994-07-14 Bosch Gmbh Robert Vorrichtung zur Erzeugung von Voreinspritzungen bei Pumpedüsen
GB8828157D0 (en) * 1988-12-02 1989-01-05 Lucas Ind Plc Fuel injection nozzles
US5011079A (en) * 1989-02-27 1991-04-30 Cummins Engine Company, Inc. Unit injector and drive train with improved push rod-plunger connection
DE3924127A1 (de) * 1989-07-20 1991-01-31 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
JP2734132B2 (ja) * 1989-11-06 1998-03-30 トヨタ自動車株式会社 ユニットインジェクタ
US5072709A (en) * 1990-03-29 1991-12-17 Cummins Engine Co., Inc. Fuel injection for an internal combustion engine
WO1993007382A1 (fr) * 1991-10-11 1993-04-15 Caterpillar Inc. Ensemble actionneur et soupape amorti pour injecteur a commande electronique
US5385301A (en) * 1992-10-28 1995-01-31 Zexel Corporation Fuel injector with spill off for terminating injection
DE4237726C2 (de) * 1992-11-09 1993-12-23 Hermann Dr Ing Golle Pumpedüse zur Kraftstoffeinspritzung für Brennkraftmaschinen
US5651501A (en) * 1993-12-23 1997-07-29 Caterpillar Inc. Fluid damping of a valve assembly
US5862995A (en) * 1996-04-01 1999-01-26 Diesel Technology Company High pressure fluid passage sealing for internal combustion engine fuel injectors and method of making same
US5918630A (en) * 1998-01-22 1999-07-06 Cummins Engine Company, Inc. Pin-within-a-sleeve three-way solenoid valve with side load reduction
US6109536A (en) * 1998-05-14 2000-08-29 Caterpillar Inc. Fuel injection system with cyclic intermittent spray from nozzle
DE19918984A1 (de) * 1999-04-27 2000-11-02 Deutz Ag Kraftstoffversorgungssystem einer Brennkraftmaschine
DE10055271A1 (de) * 2000-11-08 2002-05-23 Bosch Gmbh Robert Druck/Hubgesteuerter Injektor mit hydraulischem Übersetzer
DE10102234A1 (de) 2001-01-19 2002-07-25 Bosch Gmbh Robert Vorrichtung zur Kraftstoff-Hochdruckversorgung einer Brennkraftmaschine
DE10305187A1 (de) * 2003-02-08 2004-08-19 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung, insbesondere für Brennkraftmaschinen mit Kraftstoff-Direkteinspritzung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4392612A (en) * 1982-02-19 1983-07-12 General Motors Corporation Electromagnetic unit fuel injector
US4463900A (en) * 1983-01-12 1984-08-07 General Motors Corporation Electromagnetic unit fuel injector
US4540122A (en) * 1983-10-26 1985-09-10 General Motors Corporation Electromagnetic unit fuel injector with pivotable armature
US4568021A (en) * 1984-04-02 1986-02-04 General Motors Corporation Electromagnetic unit fuel injector

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4836161A (en) * 1986-10-08 1989-06-06 Daimler-Benz Aktiengesellschaft Direct fuel injection method for a diesel engine
WO1992010666A1 (fr) * 1990-12-11 1992-06-25 Lucas Industries Public Limited Company Pompe de carburant
WO1992010669A1 (fr) * 1990-12-11 1992-06-25 Lucas Industries Public Limited Company Pompe de carburant
US5485823A (en) * 1990-12-11 1996-01-23 Lucas Industries Public Limited Company Fuel pump having a leaked fuel conveying structure
EP0528226A1 (fr) * 1991-08-16 1993-02-24 Robert Bosch Gmbh Gicleur commandé électriquement pour des dispositifs d'injection de combustible de moteurs à combustion interne
WO2019110190A1 (fr) * 2017-12-07 2019-06-13 Robert Bosch Gmbh Dispositif d'alimentation en carburant destinée à des carburants cryogéniques

Also Published As

Publication number Publication date
DE3433710A1 (de) 1986-03-27
JPS6172869A (ja) 1986-04-14
ATE42612T1 (de) 1989-05-15
EP0178428B1 (fr) 1989-04-26
EP0178428A3 (en) 1987-12-16
DE3569784D1 (en) 1989-06-01
JPH0551064B2 (fr) 1993-07-30
US4669659A (en) 1987-06-02

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