EP0596054B1 - Kraftstoffeinspritzeinrichtung für brennkraftmaschinen - Google Patents

Kraftstoffeinspritzeinrichtung für brennkraftmaschinen Download PDF

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Publication number
EP0596054B1
EP0596054B1 EP93907795A EP93907795A EP0596054B1 EP 0596054 B1 EP0596054 B1 EP 0596054B1 EP 93907795 A EP93907795 A EP 93907795A EP 93907795 A EP93907795 A EP 93907795A EP 0596054 B1 EP0596054 B1 EP 0596054B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
fuel
electrically controlled
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.)
Expired - Lifetime
Application number
EP93907795A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0596054A1 (de
Inventor
Bernhard Bonse
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 EP0596054A1 publication Critical patent/EP0596054A1/de
Application granted granted Critical
Publication of EP0596054B1 publication Critical patent/EP0596054B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/16—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor characterised by the distributor being fed from a constant pressure source, e.g. accumulator or constant pressure positive displacement 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator

Definitions

  • the invention is based on a fuel injection device for internal combustion engines according to the preamble of claim 1.
  • a fuel injection device for internal combustion engines according to the preamble of claim 1.
  • Such a fuel injection device is already known from US Pat. No. 4,964,389 or the corresponding DE-A-38 43 467.
  • a predetermined fuel injection quantity is metered into an intermediate store via the electrically controlled valve in the fuel line discharging from the store, the output of which can be connected to the distributor opening via a second electrically controlled valve.
  • the amount of fuel supplied to the intermediate store via the first electrically controlled valve which is below the injection pressure provided by the high-pressure store, is measured by the stroke of a storage piston delimiting the intermediate store and the opening duration of the first electrically controlled valve is correspondingly determined by a control device.
  • the first electrically controlled valve thus controls the amount of fuel to be injected.
  • the second electrically controlled valve is opened at the desired injection point in time and the fuel stored by the intermediate store is conveyed to the respective injection
  • the second electrically controlled valve determines the injection timing.
  • This device is quite complex in that, in addition to two electrically controlled valves, a high-pressure intermediate store is also required.
  • a fuel injection pump of the generic type is also known from EP-A1-0 381 954.
  • the electrically controlled valve provided there is arranged in a connecting line leading from the high-pressure accumulator to the distributor, upstream of the latter and, through its open position, controls the point in time at which injection begins and the duration of its open state, the fuel injection quantity.
  • the electrically controlled valve operates as a 2/2 valve with regard to its intended function and, on the other hand, because of its design as a 3/2 valve, it relieves the pressure on the fuel-carrying area between the electrically controlled valve, distributor and a respective injection line up to the pressure valve upstream of the injection valve.
  • the electrically controlled valve according to this prior art must be a very fast-acting valve in order to be able to control the required injection times and short injection durations even with small fuel injection quantities. If an increased accuracy with regard to the injection point is to be achieved, this requires a high technical outlay for such a valve.
  • the fuel injection device according to the invention with the characterizing features of claim 1 has the advantage that it is constructed very simply with as few components as possible and exact, fast control times of the injection process can be achieved by means of the two electrically controlled valves.
  • FIG. 1 shows a first exemplary embodiment with a radial piston distributor pump as a pressure generator and as a device for controlling a plurality of fuel injection valves which are supplied with fuel from a high-pressure accumulator
  • FIG. 2 shows a second exemplary embodiment with a modified embodiment of a pressure control device, the high-pressure accumulator of the first exemplary embodiment.
  • FIG. 1 shows a partial section through parts of a high-pressure pump of the radial piston distributor injection pump type.
  • a distributor piston 2 is driven in rotation in a bore 3 by a drive (not shown further).
  • pump cylinders 6 lying radially to its axis of rotation 5, in which pump pistons 7 can be moved back and forth enclose a pump work space 8 between them.
  • the pump pistons On its outer end face, the pump pistons rest on roller shoes 10 with rollers 11, which run on a cam track 12 of a cam ring 13 when the distributor piston rotates.
  • the cam ring is mounted in the housing 14 of the high-pressure fuel pump.
  • the distributor 2 has a first annular groove 15 and a second annular groove 16 at an axial distance therefrom.
  • a fuel supply line 17 opens via a filling valve 18 in the form of a check valve, the fuel supply line being supplied with fuel by a fuel feed pump 19 driven synchronously with the distributor 2, which fuel is kept at a specific delivery pressure by means of a pressure control valve 20, which Relieved fuel supply line 17 to the suction side of the feed pump 19.
  • a pressure line 22 also leads from the second annular groove 16, in which a delivery valve 23 is arranged, which is designed as a check valve opening away from the annular groove 16.
  • the pressure line 22 opens into a high-pressure accumulator 24 via this delivery valve 23.
  • the second annular groove is finally in constant communication with the pump work chamber 8 through a pressure line 26.
  • the high-pressure accumulator is connected to the first annular groove 15 via a fuel line 28, in which a first electrically controlled valve 29, here a solenoid valve, is arranged.
  • This annular groove is permanently connected to a distributor opening of the distributor 2 in the form of a distributor groove 31, which is incorporated into the lateral surface of the distributor and extends parallel to the axis of rotation of the distributor and which is connected in succession to injection lines 23 leading away from the bore 3 when the distributor rotates .
  • These injection lines 33 lead via a pressure valve 34, which as a conventional pressure valve or as Constant pressure or constant space valve can be connected to a fuel injector on the internal combustion engine.
  • a relief line 35 branches off from the first annular groove 15, in which a second electrically controlled valve 36, here again a solenoid valve, is arranged. Both solenoid valves 29 and 36 are controlled by an electrical control device 37.
  • the high-pressure accumulator 24 also has a relief line 38, in which either a pressure-maintaining valve 39 which controls a specific pressure in the high-pressure accumulator 24 and which operates mechanically is arranged, or an electrically controlled valve 40, here again a solenoid valve which is controlled by the electrical control device 37 in accordance with signals from a pressure transmitter 41, which detects the pressure in the high-pressure accumulator 24 and emits corresponding signals to the electrical control device.
  • a pressure-maintaining valve 39 which controls a specific pressure in the high-pressure accumulator 24 and which operates mechanically is arranged
  • an electrically controlled valve 40 here again a solenoid valve which is controlled by the electrical control device 37 in accordance with signals from a pressure transmitter 41, which detects the pressure in the high-pressure accumulator 24 and emits corresponding signals to the electrical control device.
  • the fuel injection device described works as follows: If the distributor piston is driven in rotation, which is usually done via the crankshaft of the associated internal combustion engine in synchronism with its speed, the pump pistons are moved back and forth following the cams of the cam track 12 via the roller shoes 10. In the case of an outward movement corresponding to a suction stroke, the pump pistons 7 then suck in fuel via the filling valve 18. During the pressure stroke then caused by the cams of the cam track, the pump pistons 7 displace fuel under high pressure via the delivery valve 23 into the high-pressure accumulator until a certain predetermined pressure is achieved there. This pressure can either be set by the pressure holding valve 39 or via the pressure transmitter 41 in connection with the electrical one Control device 37 and the solenoid valve 40. As long as the predetermined pressure in the accumulator 24 has not been reached, there is no outflow via the relief line 38. When the set pressure is exceeded, the pressure-maintaining valve or the solenoid valve opens in an analog or clocked manner.
  • fuel can be drawn from the internal combustion engine for high-pressure injection. This takes place via the first electrically controlled valve 29, which is opened under the control of the electrical control device at a desired start of injection, the second electrically controlled valve 36 being closed.
  • the fuel then flowing out of the high-pressure accumulator 24 reaches the corresponding fuel injection nozzle via the distributor groove 31 and one of the injection lines 33 and there for injection.
  • the amount of fuel to be injected there is controlled by the second electrically controlled valve 36, in that it is opened when the fuel injection quantity is reached, so that the first annular groove 15 is relieved and the pressure in the injection line 33 or on the fuel injection valve drops below the injection pressure.
  • the first electrically controlled valve 29 is preferably closed. This closing of the first electrically controlled valve can also take place briefly after the opening of the second electrically controlled valve 36. In the former case, there is a minimum loss of fuel brought to high pressure from the accumulator 24. With the help of the pressure valve 34, a constant pressure in the injection line between the injection valve and pressure valve is usually maintained in the breaks between the high pressure injection processes, if this is designed as a constant pressure valve is. But there is also the possibility of an arrangement of Control grooves on the distributor piston to relieve the individual injection lines after the injection to a predetermined pressure level.
  • the proposed system also has advantages in that the design of the cams of the cam track no longer has to be matched to the special conditions during the time of the injection.
  • the cam drives only serve to provide the high injection pressure.
  • the conveying strokes can Pump pistons are in the periods in which the fuel injection valves from the high-pressure accumulator 24 are also supplied with high-pressure fuel for injection. The memory is thus kept free of any pressure pulsations that may occur during the injection processes.
  • the storage pressure can be controlled via an outflow control or else via the control of a delivery rate of the high-pressure pump, which would have meant the advantage of a lower drive power but a somewhat greater effort.
  • the design of the delivery capacity of the high-pressure pump advantageously offers the possibility of generating a high injection pressure in the accumulator 24 even at a low speed, in which case the accumulator is relieved accordingly at a higher speed, with the possible adjustment of the accumulator pressure to the speed.
  • the fuel injection device described is characterized above all by simple components with universal control options for the start of injection and the amount of injection.
  • a pump of the axial piston pump type can also be used according to FIG.
  • One of these has a rotatingly driven front cam disk 44, which runs on fixedly mounted rollers, only one of which is shown.
  • a pump and distributor piston 46 Connected to the end cam disk is a pump and distributor piston 46, which is rotatably carried along by the end cam disk 44 and is axially moved back and forth on the rollers 45 by the cam track 47 of the end cam disk in a pump cylinder 48 into which the pump - And distributor piston 46 includes a pump work chamber 49 at the end.
  • the end cam disk is held in contact with the rollers 45 by a strong return spring 50 so that the pump piston 46 safely performs its suction stroke.
  • the pump piston is moved during a complete revolution into a plurality of reciprocating suction and delivery strokes connected to the pump working chamber 49. During its suction strokes, it sucks in fuel via a suction groove 51 connected to the pump working space 49 in its outer surface and a fuel supply or suction line 52 opening into the pump cylinder 48.
  • the control edges delimiting the suction groove close the mouth of the suction line 52 and the fuel located in the pump work chamber 49 is compressed and via an axial blind bore 54, which starts from the end face of the pump piston 46 and a transverse bore 55 in an annular groove 56 in the surface of the guided in the pump cylinder 48 area of the pump piston.
  • This annular groove 56 is in constant communication with a pressure line 57, which corresponds to the pressure line 22 and opens into the high-pressure accumulator 24 and contains a delivery valve 23.
  • the annular groove 56 is in constant communication with a relief line 58, in which a pressure-maintaining valve 59, which opens to the relief side, is arranged.
  • a first annular groove 60 is provided in the lateral surface of the pump piston 46, corresponding to the first annular groove 15 or the second annular groove 16 from the exemplary embodiment in FIG. 1.
  • This first annular groove 16 is in turn via a fuel line 28 connected to the high-pressure accumulator 24 and contains the first electrically controlled valve 29.
  • the relief line 35 also branches off from the first annular groove 60 with the second electrically controlled valve 36.
  • the distributor groove 31 is also connected to the first annular groove 60, via which in the Course of the rotation of the pump and distributor pistons 46 each during the delivery stroke, one of the injection lines 31 is actuated, which likewise contains a pressure valve 34 and leads to the respective injection valve on the fuel injection pump.
  • this exemplary embodiment with respect to the first annular groove 60 has the same structure as the exemplary embodiment according to FIG. 1, the width of the annular groove in the axial direction of the pump piston 46 and the length of the distributor groove having to take into account the pumping stroke movements of the pump piston 46.
  • the solenoid valves 29 and 36 are actuated in the same way as in the exemplary embodiment according to FIG. 1, and the intended pump strokes of the pump piston can be designed analogously to the instructions for FIG.
  • suction control with the aid of the suction groove 15 is provided for this.
  • suction grooves corresponding to the number of suction strokes of the pump piston per revolution can be provided with a single suction line 52 or more, or only one suction groove is provided and the suction lines are corresponding to the number of suction strokes of the pump piston on the circumference of the pump cylinder 48 distributed.
  • control of the suction stroke with the aid of a control edge offers advantages over a filling valve designed as a check valve. It can of course also be used analogously in the exemplary embodiment according to FIG. 1.
  • the pressure-maintaining valve 59 designed here as a check valve can of course also be a solenoid valve controlled by a pressure sensor, analogous to the exemplary embodiment according to FIG.
  • the pressure generation was carried out with the aid of pumps corresponding to the design of conventional distributor pump types, these pumps also taking on the distributor function in addition to the pressure generation for the high-pressure accumulator, it is also possible to provide a high-pressure pump and a separate distributor in a known manner.
  • the high pressure generation is in principle independent of the distributor function.
  • a very compact structural unit results if a pump of the distributor pump type is used as a pressure generator.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP93907795A 1992-04-25 1993-04-10 Kraftstoffeinspritzeinrichtung für brennkraftmaschinen Expired - Lifetime EP0596054B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4213720 1992-04-25
DE4213720 1992-04-25
PCT/DE1993/000330 WO1993022554A1 (de) 1992-04-25 1993-04-10 Kraftstoffeinspritzeinrichtung für brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0596054A1 EP0596054A1 (de) 1994-05-11
EP0596054B1 true EP0596054B1 (de) 1996-03-13

Family

ID=6457521

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93907795A Expired - Lifetime EP0596054B1 (de) 1992-04-25 1993-04-10 Kraftstoffeinspritzeinrichtung für brennkraftmaschinen

Country Status (6)

Country Link
US (1) US5363824A (ko)
EP (1) EP0596054B1 (ko)
JP (1) JPH07500400A (ko)
KR (1) KR940701500A (ko)
DE (1) DE59301885D1 (ko)
WO (1) WO1993022554A1 (ko)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19904075A1 (de) * 1999-02-02 2000-08-03 Bosch Gmbh Robert Zuführeinrichtung für ein flüssiges Medium
DE19904074A1 (de) * 1999-02-02 2000-08-03 Bosch Gmbh Robert Zuführeinrichtung für ein flüssiges Medium

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2275307B (en) * 1993-02-18 1996-06-05 Bosch Gmbh Robert A fuel-injection system for internal combustion engines
US5678521A (en) * 1993-05-06 1997-10-21 Cummins Engine Company, Inc. System and methods for electronic control of an accumulator fuel system
GB2283533B (en) * 1993-05-06 1996-07-10 Cummins Engine Co Inc Distributor for a high pressure fuel system
ES2146952T3 (es) * 1993-09-14 2000-08-16 Lucas Industries Ltd Sistema de alimentacion de combustible.
GB9322850D0 (en) * 1993-11-05 1993-12-22 Lucas Ind Plc Control valve
US5499614A (en) * 1994-11-03 1996-03-19 Siemens Electric Limited Means and method for operating evaporative emission system leak detection pump
GB9422864D0 (en) 1994-11-12 1995-01-04 Lucas Ind Plc Fuel system
GB9509733D0 (en) * 1995-05-13 1995-07-05 Lucas Ind Plc Fuel pumping apparatus
DE19640826B4 (de) * 1995-10-03 2004-11-25 Nippon Soken, Inc., Nishio Speicherkraftstoffeinspritzvorrichtung und Druckregelvorrichtung hierfür
FR2741672A1 (fr) * 1995-11-29 1997-05-30 Lucas Ind Plc Systeme d'alimentation de carburant
DE19954206A1 (de) * 1999-11-11 2001-05-23 Bosch Gmbh Robert Kraftstoffeinspritzsystem
WO2004070190A1 (en) * 2003-01-30 2004-08-19 Robert Bosch Gmbh Fuel injector pump with trapped volume
EP2608686B1 (en) 2010-08-24 2015-06-17 Eli Alelov Inhalation device including substance usage controls

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE103691C (ko) *
US2391221A (en) * 1944-07-04 1945-12-18 Beeh Louis Multiple pump
DD103691A1 (ko) * 1973-04-06 1974-02-05
US4324409A (en) * 1980-08-15 1982-04-13 Schmid Tool & Engineering Corp. Sled body and adjustable attachment means for snow skis
JPS5835260A (ja) * 1981-08-28 1983-03-01 Hitachi Ltd 分配型燃料噴射ポンプ
DE3248713A1 (de) * 1982-12-31 1984-07-05 Robert Bosch Gmbh, 7000 Stuttgart Verfahren zur einspritzung von kraftstoff und kraftstoffeinspritzvorrichtung zur durchfuehrung des verfahrens
EP0118038A3 (en) * 1983-02-04 1986-03-12 Hitachi, Ltd. Fuel injection pump
GB8432310D0 (en) * 1984-12-20 1985-01-30 Lucas Ind Plc Liquid fuel pumping apparatus
DE3601191A1 (de) * 1986-01-17 1987-07-23 Aeg Elotherm Gmbh Phasenregeleinrichtung fuer parallelschwingkreisumrichter
US4884549A (en) * 1986-04-21 1989-12-05 Stanadyne Automotive Corp. Method and apparatus for regulating fuel injection timing and quantity
DE3719807A1 (de) * 1987-06-13 1988-12-22 Bosch Gmbh Robert Verteilerkraftstoffeinspritzpumpe der radialkolbenbauart
DE3722264A1 (de) * 1987-07-06 1989-01-19 Bosch Gmbh Robert Kraftstoffeinspritzanlage fuer brennkraftmaschinen
DE3843467A1 (de) * 1988-12-23 1990-06-28 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen
DE3903313A1 (de) * 1989-02-04 1990-08-09 Bosch Gmbh Robert Speicherkraftstoffeinspritzvorrichtung
GB8918429D0 (en) * 1989-08-12 1989-09-20 Lucas Ind Plc Fuel pumping apparatus
DE4019586A1 (de) * 1990-06-20 1992-01-02 Bosch Gmbh Robert Kraftstoffeinspritzsystem fuer brennkraftmaschinen
US5265576A (en) * 1993-01-08 1993-11-30 Stanadyne Automotive Corp. Calibration system for electrically controlled fuel injection pump

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19904075A1 (de) * 1999-02-02 2000-08-03 Bosch Gmbh Robert Zuführeinrichtung für ein flüssiges Medium
DE19904074A1 (de) * 1999-02-02 2000-08-03 Bosch Gmbh Robert Zuführeinrichtung für ein flüssiges Medium

Also Published As

Publication number Publication date
KR940701500A (ko) 1994-05-28
US5363824A (en) 1994-11-15
DE59301885D1 (de) 1996-04-18
JPH07500400A (ja) 1995-01-12
WO1993022554A1 (de) 1993-11-11
EP0596054A1 (de) 1994-05-11

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