EP0078983B1 - Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen - Google Patents

Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen Download PDF

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Publication number
EP0078983B1
EP0078983B1 EP82109914A EP82109914A EP0078983B1 EP 0078983 B1 EP0078983 B1 EP 0078983B1 EP 82109914 A EP82109914 A EP 82109914A EP 82109914 A EP82109914 A EP 82109914A EP 0078983 B1 EP0078983 B1 EP 0078983B1
Authority
EP
European Patent Office
Prior art keywords
valve
pump
fuel
working space
pump working
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.)
Expired
Application number
EP82109914A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0078983A1 (de
Inventor
Franz Eheim
Wilfried Böhringer
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 EP0078983A1 publication Critical patent/EP0078983A1/de
Application granted granted Critical
Publication of EP0078983B1 publication Critical patent/EP0078983B1/de
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
    • F02M59/20—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
    • 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
    • F02M59/205—Quantity of fuel admitted to pumping elements being metered by an auxiliary metering device
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87917—Flow path with serial valves and/or closures
    • Y10T137/88062—Coaxial oppositely directed seats

Definitions

  • the invention is based on a fuel injection device according to the preamble of the main claim.
  • a fuel injector of this type is known from SU-A-174468.
  • There is a check valve is provided, which is arranged coaxially adjacent to the pump work space, but whose return spring is supported on the pump housing on the side of the pump work space and whose movable valve member is designed as a ball that controls the opening of a connecting channel formed on the pump work space as a valve seat its other end is controlled by a plate-shaped movable valve member of the electromagnetically operated metering valve.
  • This configuration has the disadvantage that between the valve seat of the check valve and the pump work space there is a harmful dead space required for the check valve, which has a disadvantageous effect on the accuracy of the injection quantity control in the various operating points of the injection device.
  • This device has the disadvantage that the spring, which brings the movable valve member into the closed position, has to be made relatively strong, so that at the end of the metering stroke of fuel in the pump work chamber, a refueling of fuel is reliably prevented during the continuing suction stroke of the pump piston or that a suction of fuel with the electromagnet of the metering valve switched off is avoided at all.
  • the fuel injection device according to the invention with the characterizing features of the main claim has the advantage that it can be realized with a very small harmful dead space with little assembly effort, since the spring-side part of the check valve is located on the side of the valve seat facing away from the pump working space. Furthermore, the metering valve and the check valve can be used as a structural unit directly adjacent to the pump work space in the housing.
  • a cylinder bore 2 is provided in a pump housing 1, in which a pump piston 3 encloses a pump working chamber 4.
  • the pump piston 3 is driven by means of a cam disk 5, which runs on a roller ring 6, by means not shown, and performs a reciprocating pump movement with a successive suction stroke and delivery stroke during its rotary movement.
  • the fuel supply to the pump working chamber 4 takes place via a fuel inlet channel 8, which leads to a pump suction chamber 9 shown in dash-dot lines.
  • This pump suction chamber 9 is supplied with fuel by means of a fuel feed pump 11 from a fuel tank 12, the pressure in the pump suction chamber 9 being adjusted with the aid of a pressure control valve 14 which is connected in parallel to the fuel feed pump 11.
  • An electromagnetically operable metering valve 16 is inserted into the fuel inlet channel 8 as a fuel quantity metering device. Downstream of this metering valve 16 is also in the direction of the pump work chamber 4 opening check valve 17 is provided.
  • a blind bore 18 arranged in the pump piston 3 leads from the pump work chamber 4, from which a radial bore 19 leads to the outside.
  • Another radial bore 20 connects the blind bore 18 with a distributor groove 21, through which delivery lines 22 are connected to the pump work chamber 4 in succession when the pump piston 3 rotates and its delivery stroke.
  • the delivery lines 22 are distributed according to the number of cylinders to be supplied to the internal combustion engine, not shown, on the circumference of the cylinder bore 2 and each contain a relief valve 23, via which they are connected to an injection valve 24.
  • annular groove 26 is also provided, which is connected to the pump suction chamber 9 via at least one bore 27.
  • the annular groove 26 is arranged in such a way that the radial bore 19 in the pump piston 3 is opened from a maximum delivery stroke, so that the fuel delivered from this point in the further stroke movement of the pump piston 3 via the blind bore 18 serving as a relief channel 18, the radial bore 19 and the Bore 27 can flow into the pump suction chamber 9 and thus the pressure delivery in the delivery line 22 is interrupted.
  • an injection adjustment piston 29 is also provided, which is coupled to the roller ring 6 and is adjustable against the force of a spring 30.
  • the injection adjusting piston 29 includes a pressure chamber 31, which is connected to the pump suction chamber 9 via a throttle 32 and is therefore acted upon by a speed-dependent pressure in the pump suction chamber 9.
  • the injection timing piston 29 adjusts the injection timing to early by rotating the roller ring 6 with increasing speed.
  • the pressure chamber 31 is also connected via a solenoid valve 34 to the suction side of the fuel delivery pump 11 and can be relieved with the aid of this solenoid valve 34.
  • the solenoid valve 34 is controlled by an electronic control unit 36, which also serves to control the electromagnetically actuated metering valve 16 in the fuel inlet channel 8.
  • the control unit 36 operates as a function of parameters that are to be taken into account for the dimensioning and the timing of the fuel injection quantity.
  • the control unit 36 can, for. B. contain at least one map in which target values for the amount of fuel to be injected are contained in indirect or direct form. In a manner known per se, the speed n, the temperature T, the air pressure P L and the load can be taken into account as parameters.
  • signals of a needle stroke transmitter in the injection valve 24 can be detected as further parameters for determining the actual start of injection and the actual fuel injection duration.
  • control signals can also be used to determine the start of delivery or the delivery time via a pressure transmitter 38, which is suitably arranged on the high-pressure side of the fuel injection pump.
  • a pressure transmitter 38 which is suitably arranged on the high-pressure side of the fuel injection pump.
  • an encoder 39 z. B. in the form of an inductive sensor on the cam disc 5 are provided.
  • FIGS. 2a and 2b shows the course of the stroke h of the pump piston 3 over the angle of rotation ⁇ .
  • This curve part B of the elevation curve runs very flat and is linear except for the border area at the reversal points of the pump piston 3.
  • the pressure stroke part A of the elevation curve in Fig. 2b is divided into three sections.
  • the fuel present in the pump work chamber 4 is compressed until the delivery pressure which causes the injection valve 24 to be reached is reached.
  • the second part of the survey curve extends between the points FB and EO. In this area, fuel is delivered into the delivery line 22.
  • the check valve 17 is closed by the delivery pressure, possibly supported by the spring installed there. Thus, the electromagnetically actuated metering valve 16 is relieved of pressure.
  • the radial bore 19 When the point EO of the elevation curve is reached, the radial bore 19 is brought into connection with the annular groove 26, so that the pump working chamber 4 is relieved of pressure in the pump suction chamber 9. The remaining amount of fuel to be displaced by the pump piston 3 flows out there. This takes place in the area between the opening EO of the radial bore 19 and the top dead center OT of the pump piston 3.
  • the metering valve 16 is opened at the latest when top dead center OT is reached. The opening can take place earlier since the fuel inlet channel 8 is closed by the check valve 17 during the pressure stroke. In the area between TDC and the closing point ES of the radial bore 19, fuel is drawn in via the large opening cross section of the metering valve 16.
  • the effective suction stroke of the pump piston 3 begins from ES, during which fuel is drawn in at MS until the metering valve 16 closes.
  • the effective suction stroke length h s is thus determined on the one hand by the geometric design of the fuel injection pump or by determines the position of the control edge delimiting the annular groove 26 and, on the other hand, by the switching time of the metering valve 16.
  • the switching times of the metering valve 16 are recorded by actuation with a current intensity 1, where at is the total opening time of the metering valve 16 and ⁇ z is for that Measuring effective time.
  • the metering valve 16 can be opened significantly before the start of the actually effective suction stroke h s and there is a rinsing phase between the effective delivery stroke and the effective suction stroke of the pump piston 3 (EO-ES), when the metering valve 16 is opened, the injection time within the possible injection timing adjustment range is required not be considered further.
  • the effective suction stroke length for the metering can be controlled directly without the need to report back the amount of fuel actually injected.
  • Very good control results are obtained if the actual fuel injection quantity is recorded in a manner known per se by means of the control unit 36 and compared in a comparison device of the control unit with a target fuel quantity signal formed there.
  • the actual fuel quantity can be determined by a needle stroke transmitter or by a correspondingly evaluated pressure signal from the pressure transmitter 38.
  • the target fuel quantity is formed from the parameters mentioned at the beginning with the load as a reference variable.
  • the actual opening time of the metering valve 16 is then corrected in accordance with the comparison result when the actual fuel quantity deviates from the target value.
  • the basic opening duration signal of the metering valve 16 is formed in accordance with the target fuel quantity signal.
  • a pressure-sensing transmitter 40 is provided on the bore 27, the signal of which is input to the control unit 36.
  • An integrating device in the control unit 36 is set with the signal of the transmitter 40, which characterizes the point ES, and as soon as the output value of the integrating device has reached the setpoint value for the fuel quantity given by the control unit 36, a switching signal from the two values is sent to the metering valve 16 for closing of the fuel inlet channel 8 issued.
  • the integration runtime must be corrected by an integration time constant adapted to the speed during integration. This can be done with known methods, on the one hand the design of the integrator itself is speed-dependent in an analog manner or the integrator integrates in constant integration steps with speed-dependent frequency.
  • a correction signal can also be generated from an TDC signal that is achieved with the aid of the transmitter 39 and the signal that is output by the transmitter 40, which corrects the opening phase of the metering valve 16, which is switched in synchronism with the speed.
  • FIG. 1 shows a partial view of a fuel injection pump designed according to the schematic illustration in FIG. 1, the same reference numerals being chosen for the parts having the same effect.
  • a cylinder liner 44 is fitted, in which the cylinder bore 2 is formed and the pump piston 3 is slidably mounted.
  • the electromagnetically actuated metering valve 16 is inserted, for example screwed, into the pump housing 1, the valve housing 45 of which at least partially surrounds an end plate 46 with tabs 47.
  • the end plate 46 lies sealingly against the cylinder liner 44 and, on the one hand, delimits the pump work chamber 4 in the axial direction.
  • the valve housing 45 is pot-shaped and supports a collar 50 of an outer core 51 in an inner bore 48 on an inner shoulder 49.
  • the outer core 51 is connected in a manner not shown via a yoke to an annular inner core 56.
  • a magnetic coil 57 is at least partially enclosed by an insulating support body 58 which is inserted with the magnetic coil 57 into the annular space formed between the outer core 51 and the inner core 56.
  • the current supply to the solenoid coil takes place, for example, via contact pins 59, only one of which is shown.
  • a flat anchor 61 is arranged between the end faces of the outer core 51 and the inner core 56 and the guide membrane 54.
  • a movable valve part 62 is connected to the flat armature, e.g. B. soldered or welded.
  • the valve part 62 penetrates a central guide opening 63 in the guide membrane 54 and works together with a fixed valve seat 64 formed on the valve seat body 55.
  • the valve part 62 and the flat armature 61 are guided through the central guide opening 63 of the guide membrane 54 in the radial direction on the one hand to the valve seat 64 and on the other hand to the end face of the outer core 51 and the inner core 56.
  • the guide membrane 54 is not rigidly connected to the valve part 62 or to the flat anchor 61.
  • the flat anchor 61 has an annular guide collar 65 facing the guide membrane 54, on which a guide edge 66 is formed which bears against the guide membrane 54, which means that Flat anchor 61 is guided parallel to the end face of the outer core 51 and inner core 56.
  • the valve part 62 has, for example, a spherical interaction with the valve seat 64 Migen section, for example flattened as a spherical zone.
  • the guide diaphragm 54 rests bent and under tension against the guide edge 66 of the flat armature 61.
  • the valve part 62 is acted upon in the closing direction of the metering valve by a compression spring 67 which, on the other hand, projects into an inner bore 68 of the inner core 56 and is supported on a slide member 69.
  • the force of the compression spring 67 on the flat armature 61 and the valve part 62 can be influenced by axially displacing the slide member 69.
  • a chamber 71 formed upstream of the valve seat 64 and through which the movable valve part 62 extends is in communication with the fuel inlet channel 8.
  • the solenoid 57 When the solenoid 57 is excited, the flat armature 61 is attracted and the valve part 62 lifts off the valve seat 64, so that fuel can flow from the chamber 71 into a receiving bore 72 formed in the valve seat body 55, in which a return spring 73 is arranged, which is supported by a spring plate 74 on a valve needle 75 of the check valve 17.
  • the valve needle 75 extends through a bore 76 adjoining the receiving bore 72 and bears against a valve seat 78 with a conical sealing part 77.
  • the bore 76 and the valve seat 78 are formed in a valve seat plate 79 which is clamped between the valve seat body 55 and the end plate 46.
  • the opening movement of the valve needle 75 of the check valve 17 towards the pump work chamber 4 is limited by a stop 81 in the end plate 46.
  • the integration of the check valve 17 into the metering valve 16 not only results in a reduction in the installation space required, but also allows the two valves to be mounted together in the pump housing with the smallest possible dead space volume.

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)
  • High-Pressure Fuel Injection Pump Control (AREA)
EP82109914A 1981-11-07 1982-10-27 Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen Expired EP0078983B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19813144361 DE3144361A1 (de) 1981-11-07 1981-11-07 Kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen
DE3144361 1981-11-07

Publications (2)

Publication Number Publication Date
EP0078983A1 EP0078983A1 (de) 1983-05-18
EP0078983B1 true EP0078983B1 (de) 1985-05-29

Family

ID=6145922

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82109914A Expired EP0078983B1 (de) 1981-11-07 1982-10-27 Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen

Country Status (4)

Country Link
US (1) US4491111A (ja)
EP (1) EP0078983B1 (ja)
JP (1) JPS5885327A (ja)
DE (2) DE3144361A1 (ja)

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3309971A1 (de) * 1983-03-19 1984-09-20 Robert Bosch Gmbh, 7000 Stuttgart Einrichtung zum foerdern von kraftstoff
JPS59221432A (ja) * 1983-05-31 1984-12-13 Toyota Motor Corp 分配型燃料噴射ポンプ
DE3322929A1 (de) * 1983-06-25 1985-01-10 Robert Bosch Gmbh, 7000 Stuttgart Drehzahlregler fuer kraftstoffeinspritzpumpen von brennkraftmaschinen
US4482094A (en) * 1983-09-06 1984-11-13 General Motors Corporation Electromagnetic unit fuel injector
DE3336871A1 (de) * 1983-10-11 1985-04-25 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer mehrzylindrige brennkraftmaschinen
JPS6098146A (ja) * 1983-11-02 1985-06-01 Nippon Soken Inc 内燃機関の燃料制御方法
DE3581160D1 (de) * 1984-09-14 1991-02-07 Bosch Gmbh Robert Elektrisch gesteuerte kraftstoffeinspritzpumpe fuer brennkraftmaschinen.
GB8430259D0 (en) * 1984-11-30 1985-01-09 Lucas Ind Plc Electromagnetically operable valve
EP0307947B1 (en) * 1987-09-16 1993-11-18 Nippondenso Co., Ltd. Variable discharge high pressure pump
US4977882A (en) * 1988-08-26 1990-12-18 Diesel Kiki Co., Ltd. Distributor type fuel injection pump
US5058553A (en) * 1988-11-24 1991-10-22 Nippondenso Co., Ltd. Variable-discharge high pressure pump
DE3934953A1 (de) * 1989-10-20 1991-04-25 Bosch Gmbh Robert Magnetventil, insbesondere fuer kraftstoffeinspritzpumpen
DE4016309A1 (de) * 1990-05-21 1991-11-28 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5133645A (en) * 1990-07-16 1992-07-28 Diesel Technology Corporation Common rail fuel injection system
US5211205A (en) * 1992-07-22 1993-05-18 Bg 300, Inc. Fuel pressure regulator
EP1221552B1 (en) * 1996-07-05 2004-10-13 Nippon Soken, Inc. High-pressure pump for use in fuel injection system for diesel engine
US6019126A (en) * 1998-09-04 2000-02-01 Kelada; Maher I. Remote function verification of low pressure and vacuum relief devices
JP2000186649A (ja) * 1998-12-24 2000-07-04 Isuzu Motors Ltd 吐出量可変制御型高圧燃料ポンプ
DE19860672A1 (de) * 1998-12-29 2000-07-13 Bosch Gmbh Robert Kolbenpumpe zur Kraftstoffhochdruckerzeugung
DE10124238A1 (de) * 2001-05-18 2002-11-28 Bosch Gmbh Robert Hochdruck-Kraftstoffpumpe, insbesondere für direkteinspritzende Brennkraftmaschinen, sowie Kraftstoffsystem und Brennkraftmaschine
US6832748B2 (en) * 2001-12-05 2004-12-21 Cummins Inc. Outwardly opening, seat-sealed, force balanced, hydraulic valve and actuator assembly
US8517760B2 (en) 2007-08-20 2013-08-27 Ford Global Technologies, Llc Cord wrap and power plug receptacle arrangement for inflator
US8981921B2 (en) 2007-09-08 2015-03-17 Ford Global Technologies, Llc Status indicator and reminder system for vehicle temporary mobility kit
IT1394070B1 (it) * 2009-05-13 2012-05-25 Bosch Gmbh Robert Gruppo valvola per controllare l'alimentazione e la mandata di combustibile di una camera di compressione di una pompa a pistoni di alta pressione e pompa a pistoni di alta pressione comprendente tale gruppo valvola

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3724436A (en) * 1970-04-02 1973-04-03 Nippon Denso Co Fuel feed control device for internal combustion engines

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB106631A (ja) *
US2969088A (en) * 1956-03-16 1961-01-24 Controls Co Of America Pilot valve
US3183932A (en) * 1961-07-13 1965-05-18 Pneumo Dynamics Corp Regulator valve
GB1166502A (en) * 1967-03-30 1969-10-08 Ether Ltd Improvements in or relating to Adjustable Valves
DE2460404B2 (de) * 1974-12-20 1977-12-15 Eisenwerk Weserhütte AG, 4970 Bad Oeynhausen Elektromagnetisch betaetigtes dreiwege-druckregelventil
DE2503324C2 (de) * 1975-01-28 1985-10-31 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe für Brennkraftmaschinen
JPS55112858A (en) * 1979-02-23 1980-09-01 Daihatsu Motor Co Ltd Fuel injection pump device
JPS5933900Y2 (ja) * 1979-03-29 1984-09-20 株式会社小松製作所 インジエクタ装置
US4385614A (en) * 1979-04-06 1983-05-31 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
DE2942010A1 (de) * 1979-10-17 1981-05-07 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3724436A (en) * 1970-04-02 1973-04-03 Nippon Denso Co Fuel feed control device for internal combustion engines

Also Published As

Publication number Publication date
EP0078983A1 (de) 1983-05-18
JPS5885327A (ja) 1983-05-21
DE3263924D1 (en) 1985-07-04
US4491111A (en) 1985-01-01
JPH0364691B2 (ja) 1991-10-08
DE3144361A1 (de) 1983-05-19

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