US3762379A - System for injecting metered quantity of fuel into engine - Google Patents

System for injecting metered quantity of fuel into engine Download PDF

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Publication number
US3762379A
US3762379A US00167299A US3762379DA US3762379A US 3762379 A US3762379 A US 3762379A US 00167299 A US00167299 A US 00167299A US 3762379D A US3762379D A US 3762379DA US 3762379 A US3762379 A US 3762379A
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United States
Prior art keywords
fuel
injection pump
fuel injection
pump
during
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Expired - Lifetime
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US00167299A
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English (en)
Inventor
N Hobo
Y Natsume
Y Suzuki
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Denso Corp
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NipponDenso Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/40—Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2700/00—Mechanical control of speed or power of a single cylinder piston engine
    • F02D2700/02—Controlling by changing the air or fuel supply
    • F02D2700/0269—Controlling by changing the air or fuel supply for air compressing engines with compression ignition
    • F02D2700/0282—Control of fuel supply
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/40—Engine management systems

Definitions

  • a fuel injection pump adapted for intermittent injection of fuel is generally so constructed that the fuel suction port in the pump cylinder communicates with the pump chamber at the end of the suction stroke of the pump plunger during the operating cycle of the fuel injection pump, and in the delivery stroke of the pump plunger, the pump plunger closes the fuel suction port in the pump cylinder so as to supply fuel under pressure to the fuel injection nozzle.
  • the inventors have experimentally ascertained the fact that, in such a system, the volume of the space in the fluid passage ranging from the fuel suction port of the fuel injection pump to the fuel outlet port of the solenoid operated valve open and closed by the needle valve member (which space will hereinafter be referred to as a stabilizing chamber) is intimately related with the duration of the timing pulse or period of time during which the metering can be carried out by the solenoid operated valve.
  • the period of time during which the fuel can be metered by the solenoid operated valve is limited to the period of time during which the fuel suction port is open and communicates with the pump chamber in the suction stroke of the pump plunger of the fuel injection pump.
  • the fuel outlet port of the solenoid operated valve is suitably spaced from the fuel suction port of the fuel injection pump and thus the stabilizing chamber of a suitably large volume is provided in the fluid passage therebetween, the fuel can be metered by the solenoid operated valve not only during the period of time in which the fuel suction port is in its open position in the suction stroke of the pump plunger but also during the delivery stroke of the pump plunger.
  • the solenoid operated valve When, in this case, the solenoid operated valve is disposed in close proximity to the fuel suction port of the fuel injection pump and a period of time during which the solenoid operated valve is held in its open position is varied to meter a suitable quantity of fuel to be drawn into the pump chamber in each operating cycle of the fuel injection pump, the solenoid operated valve can only meter the fuel during a limited period of time which ranges from the time at the end of the suction stroke of the pump plunger to the time immediately before the subsequent delivery stroke of the pump plunger takes place in the operating cycle of the fuel injection pump. This period of time is equal, at the most, to the half of the entire period of time occupied by one operating cycle of the fuel injection pump.
  • the metering period of time is of the order of 0.004 second at the most when the pump is driven by the shaft rotating at the maximum speed of 1,800 r.p.m. and it is difficult to attain the metering with high precision.
  • the stabilizing chamber has an excessively large volume
  • the variation in the quantity of fuel delivered from the fuel injection pump occurs with a certain time lag relative to the variation in the quantity of fuel metered by the solenoid operated valve in each operating cycle.
  • the use of such a fuel injection pump with such a poor response characteristics for a diesel engine is undesirable in that hunting occurs in the diesel engine.
  • the stabilizing chamber provided in the fluid passage leading from the fuel outlet port of the solenoid operated valve to the fuel suction port of the fuel injection pump is selected to have a suitable volume lying within a predetermined range so that the solenoid operated valve can meter the fuel over a period of time which is more than the period of time in which the fuel suction port is in its open position in one complete operating cycle of the fuel injection pump.
  • the solenoid operated valve can meter the fuel over a period of time which is substantially equal to the period of time occupied by one complete operating cycle of the fuel injection pump, and the metering period of time can be substantially extended to 0.0083 second when, for example, the shaft driving the pump is rotating at its maximum speed of 1,800 r.p.m.
  • FIG. 1 is a schematic front elevational view partly in section of an embodiment of the present invention.
  • FIG. 2 is a chart illustrating the operation of the fuel injection pump in the system according to the present invention.
  • a fuel feed pump 2 draws fuel from a fuel reservoir 1 to supply same to a fuel injection pump 7 through an electromagnetically or solenoid operated valve 4.
  • a pressure regulator 3 is connected between the outlet of the fuel feed pump 2 and the fuel reservoir 1.
  • the solenoid operated valve 4 comprises a needle valve member 4a of magnetic material, an energizing coil or solenoid 4b, a spring 40 normally urging the needle valve member 4a against the valve seat, a fuel outlet port 6a and a fuel inlet port 6b.
  • An electrical control means generates a timing pulse of a duration corresponding to the quantity of the fuel required by a diesel engine so as to apply this timing pulse to the solenoid 4b of the solenoid operated valve 4.
  • the fuel injection pump 7 comprises a pump cylinder 11, a pump plunger slidably received in the pump cylinder 11, a fuel suction port 9 bored in the wall of the pump cylinder 11, and a pump chamber 12 defined within the pump cylinder 11 by the pump plunger 10.
  • a stabilizing chamber 8 is formed in the fluid passage connecting the fuel outlet port 6a of the solenoid operated valve 4 to the fuel suction port 9 of the fuel injection pump 7.
  • a delivery valve 15 is connected to a fuel injection nozzle 17 by a high pressure conduit 16.
  • the pressure of fuel discharged from the fuel feed pump 2 is maintained at a constant value of about 2 kilograms per square centimeter by the pressure regulator 3.
  • the needle valve member 4a is urged away from the valve seat against the force of the spring 4c so that the solenoid operated valve 4 is urged to the open position and kept in such a position for a period of time which is determined depending on the duration of the timing pulse.
  • a metered quantity of fuel is discharged through the fuel outlet port 6a.
  • the fuel suction port 9 communicates with the pump chamber 12 for a period of time which ranges from the time at the end of the suction stroke of the pump plunger 10 to the time immediately before the subsequent delivery stroke of the pump plunger 10 takes place in the operating cycle of the fuel injection pump 7, and the fuel metered by the solenoid operated valve 4 flows into the pump chamber 12.
  • the number of operating cycles of the solenoid operated valve 4 is selected to be equal to the number of operating cycles of the fuel injection pump 7 so that the quantity of fuel supplied to the fuel injection pump 7 in each operating cycle is approximately equal to the quantity of fuel passed through the fuel outlet port 6a of the solenoid operated valve 4 each time it is energized. This fuel is forced through the delivery valve 15 and the high pressure conduit 16 to be injected by the fuel injection nozzle 17 during the delivery stroke of the pump plunger 10.
  • the fuel outlet port 6a of the solenoid operated valve 4 is disposed in close proximity to the fuel suction port 9 of the fuel injection pump 7 and thus the fluid passage connecting therebetween has a sufficiently small volume, the period of time during which the fuel is supplied into the pump chamber 12 of the fuel injection pump 7 due to the open position of the solenoid operated valve 4 is naturally limited to the period of time during which the fuel suction port 9 communicates with the pump chamber 12.
  • the stabilizing chamber 8 is provided in the fluid passage leading from the fuel outlet port 6a of the solenoid operated valve 4 to the fuel suction port 9 of the fuel injection pump 7 and the total volume of the fluid passage including the stabilizing volume chamber 8 is selected to be larger than a predetermined value as seen in FIG.
  • a space is produced in a portion of the stabilizing chamber 8 for receiving therein the quantity of fuel to be metered by the subsequent operation of the solenoid operated valve 4.
  • this quantity of fuel metered by the solenoid operated valve 4 can pass through the fuel outlet port 6a into this space irrespective of whether or not the fuel suction port 9 of the fuel injection pump 7 communicates with the pump chamber 12.
  • This quantity of fuel is delivered to the fuel injection nozzle 17 in the subsequent delivery stroke of the pump plunger 10 of the fuel injection pump 7.
  • the stabilizing volume chamber 8 may have a largest possible volume as far as the supply of the fuel metered by the solenoid operated valve 4 into the fuel injection pump 7 is concerned, but there is a minimum stabilizing which is determined by various factors including the period of time in which the solenoid operated valve 4 is kept open, the maximum discharge capacity of the fuel injection pump 7, the period of time in which the solenoid operated valve 4 is in its open position and the fuel suction port 9 of the fuel injection pump 7 communicates with the pump chamber 12, and the quantity of fuel metered by the solenoid operated valve 4.
  • FIG. 2 shows the results of measurement on the fuel injection pump 7 which is adapted for distributing fuel to four cylinders ofa diesel engine and in which the volume of the pump chamber varies by Vb mm in each operating cycle for supplying fuel to one cylinder.
  • the horizontal axis represents the number of revolutions N per minute of the shaft driving the pump
  • the vertical axis represents the quantity of delivery Q mm lstcy per cylinder in each operating cycle
  • the period of time T during which fuel is metered by the solenoid operated valve 4 is taken as a parameter.
  • FIG. 2 represent the operating characteristics when the stabilizing chamber 8 has a volume Va 150 mm, while the broken lines represent similar characteristics when the fuel outlet port 6a of the solenoid operated valve 4 is disposed in close proximity to the fuel suction port 9 of the fuel injection pump 7 so that the stabilizing chamber 8 has an extremely small volume Va mm. It will be apparent from FIG.
  • the quantity of delivery Q is independent of the number of revolutions N of the drive shaft of the fuel injection pump and is determined primarily by the duration of the timing pulse applied to the solenoid 4b of the solenoid operated valve 4, and the metering can be reliably attained up to the number of revolutions N 1,800 rpm.
  • the quantity of delivery Q is abruptly decreased with the increase in the number of revolutions N beyond N 1,000 r.p.m. in the case of the metering period of time T 7 msec and thus reliable metering of fuel cannot be attained.
  • the volume Va of the stabilizing chamber 8 should be so selected as to satisfy the relation Va 2 e Vb where e is a constant which lies in the range of 0.1 to l and Vb is the variation in the volume of the pump chamber 12 of the fuel injection pump 7 in each operating cycle.
  • the metering of fuel by the solenoid operated valve 4 can be reliably carried out when Va is selected to satisfy the above relation.
  • the provision of the stabilizing chamber 8 adversely affects the transient response of the fuel injection pump 7 and this transient response becomes worse with the increase in the volume Va of the stabilizing chamber 8.
  • the lag of the variation in the quantity of fuel delivered from the fuel injection pump 7 relative to the variation in the quantity of fuel metered by the solenoid operated valve 4 may be considered as a first order lag.
  • the rate of variation v in the volume per second is given by v N/60'M-Vb where Vb is the variation in the volume of the pump chamber 12 in one operating cycle of the fuel injection pump 7, N is the number of revolutions per minute of the shaft driving the pump, and M is the number of operating cycles of the fuel injection pump 7 during one rotation of the drive shaft.
  • the time constant Td of the first order lag is given by Td Va/v 60/N-Va/MVb.
  • the practically preferred value of the volume Va of the stabilizing chamber 8 should lie in the following range:
  • the volume Va of the fluid passage leading from the fuel outlet port of the solenoid operated valve open and closed by the needle valve member to the fuel suction port of the fuel injection pump is selected to lie within the range satisfying the relation 0.1 Vb 2 Va 5 MVB, where Vb is the variation the volume of the pump chamber during one operating cycle of the fuel injection pump and M is the numberof operating cycles of the fuel injection pump during one rotation of the drive shaft of the diesel engine.
  • Vb is the variation the volume of the pump chamber during one operating cycle of the fuel injection pump
  • M is the numberof operating cycles of the fuel injection pump during one rotation of the drive shaft of the diesel engine.
  • the solenoid operated valve can meter the fuel even in the period in which the fuel suction port of the fuel injection pump is closed due to the delivery stroke of the pump plunger, and thus the metering period of time can be substantially extended to the period of time occupied by one complete operating cycle of the fuel injection pump.
  • the present invention is therefore advantageous in that fuel can be metered with high precision and no hunting occurs in the diesel engine equipped with the fuel injection pump.
  • a system for injecting a metered quantity of fuel into an engine having a crankshaft comprising:
  • a fuel injection pump including a cylinder, a piston reciprocated in said cylinder to deliver fuel and defining within said cylinder a pump chamber, said cylinder having a fuel suction port for receiving fuel which is opened by said piston during a fuel receiving cycle portion and closed by said piston during a fuel delivery cycle portion,
  • electromagnctically operated metering means having a fuel inlet port and a fuel outlet port
  • volume Va of said fluid passage is so selected as to lie within the range satisfying the relation 0.1 Vb Va MVb, where Vb is the variation in the volume of the pump chamber during one operating cycle of said fuel injection pump and M is the number of operating cycles of said fuel injection pump during one rotation of the drive shaft, 5

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  • 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)
US00167299A 1970-08-10 1971-07-29 System for injecting metered quantity of fuel into engine Expired - Lifetime US3762379A (en)

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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4059369A (en) * 1975-01-28 1977-11-22 Robert Bosch G.M.B.H. Fuel injection pump
US4180037A (en) * 1976-12-26 1979-12-25 Nippondenso Co., Ltd. Injection pump control system
US4406267A (en) * 1981-09-02 1983-09-27 Ford Motor Company Electromagnetically controlled fuel injection pump spill port valve assembly
DE4115103A1 (de) * 1990-07-16 1992-04-02 Diesel Tech Corp Kraftstoff-einspritzanlage mit gemeinsamer druckleitung
US5207203A (en) * 1992-03-23 1993-05-04 General Motors Corporation Fuel system
US5230613A (en) * 1990-07-16 1993-07-27 Diesel Technology Company Common rail fuel injection system
WO1994007015A1 (en) * 1992-09-18 1994-03-31 General Electric Company Electronic fuel injection system for large compression ignition engine
US5373829A (en) * 1991-11-08 1994-12-20 Bayerische Motoren Werke Ag Fuel supply system of an internal-combustion engine
DE4413156C1 (de) * 1994-04-15 1995-08-10 Daimler Benz Ag Für eine Brennkraftmaschine vorgesehene Kraftstoffeinspritzanlage
US6325050B1 (en) * 2000-03-24 2001-12-04 General Electric Company Method and system for controlling fuel injection timing in an engine for powering a locomotive
US6394072B1 (en) * 1990-08-31 2002-05-28 Yamaha Hatsudoki Kabushiki Kaisha Fuel injection device for engine
GB2385386A (en) * 2002-02-15 2003-08-20 Delphi Tech Inc Pump assembly
US20060162696A1 (en) * 2003-01-30 2006-07-27 Spoolstra Gregg R Fuel injector pump with trapped volume
US20080116300A1 (en) * 2006-11-16 2008-05-22 Mario Ricco Fuel adjustment and filtering device for a high-pressure pump

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4276000A (en) * 1978-01-31 1981-06-30 Lucas Industries Limited Liquid fuel pumping apparatus
DE3140933A1 (de) * 1981-10-15 1983-05-05 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffzumesseinrichtung fuer kraftstoffeinspritzpumpen

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1664610A (en) * 1925-01-08 1928-04-03 Louis O French Fuel-feeding system
US3516395A (en) * 1967-02-22 1970-06-23 Sopromi Soc Proc Modern Inject Fuel injection system for internal combustion engines
US3568646A (en) * 1968-04-08 1971-03-09 Teldix Gmbh Fuel injection apparatus for internal combustion engines
US3592177A (en) * 1968-10-04 1971-07-13 Teldix Gmbh Fuel-injection apparatus for internal-combustion engines
US3661130A (en) * 1969-03-19 1972-05-09 Bosch Gmbh Robert Safety device for limiting the rotational speed of internal combustion engines

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1664610A (en) * 1925-01-08 1928-04-03 Louis O French Fuel-feeding system
US3516395A (en) * 1967-02-22 1970-06-23 Sopromi Soc Proc Modern Inject Fuel injection system for internal combustion engines
US3568646A (en) * 1968-04-08 1971-03-09 Teldix Gmbh Fuel injection apparatus for internal combustion engines
US3592177A (en) * 1968-10-04 1971-07-13 Teldix Gmbh Fuel-injection apparatus for internal-combustion engines
US3661130A (en) * 1969-03-19 1972-05-09 Bosch Gmbh Robert Safety device for limiting the rotational speed of internal combustion engines

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4059369A (en) * 1975-01-28 1977-11-22 Robert Bosch G.M.B.H. Fuel injection pump
US4180037A (en) * 1976-12-26 1979-12-25 Nippondenso Co., Ltd. Injection pump control system
US4406267A (en) * 1981-09-02 1983-09-27 Ford Motor Company Electromagnetically controlled fuel injection pump spill port valve assembly
DE4115103A1 (de) * 1990-07-16 1992-04-02 Diesel Tech Corp Kraftstoff-einspritzanlage mit gemeinsamer druckleitung
US5230613A (en) * 1990-07-16 1993-07-27 Diesel Technology Company Common rail fuel injection system
US6394072B1 (en) * 1990-08-31 2002-05-28 Yamaha Hatsudoki Kabushiki Kaisha Fuel injection device for engine
US5373829A (en) * 1991-11-08 1994-12-20 Bayerische Motoren Werke Ag Fuel supply system of an internal-combustion engine
US5207203A (en) * 1992-03-23 1993-05-04 General Motors Corporation Fuel system
EP0724074A3 (de) * 1992-09-18 1998-10-07 General Electric Company Elektronisches Einspritzsystem für einen grossen verdichtunggezündeten Motor
WO1994007015A1 (en) * 1992-09-18 1994-03-31 General Electric Company Electronic fuel injection system for large compression ignition engine
US5394851A (en) * 1992-09-18 1995-03-07 General Electric Company Electronic fuel injection system for large compression ignition engine
EP0724074A2 (de) * 1992-09-18 1996-07-31 General Electric Company Elektronisches Einspritzsystem für einen grossen verdichtunggezündeten Motor
US5526790A (en) * 1994-04-15 1996-06-18 Mercedes-Benz Ag Fuel injection system for an internal combustion engine
DE4413156C1 (de) * 1994-04-15 1995-08-10 Daimler Benz Ag Für eine Brennkraftmaschine vorgesehene Kraftstoffeinspritzanlage
US6325050B1 (en) * 2000-03-24 2001-12-04 General Electric Company Method and system for controlling fuel injection timing in an engine for powering a locomotive
GB2385386A (en) * 2002-02-15 2003-08-20 Delphi Tech Inc Pump assembly
US20060162696A1 (en) * 2003-01-30 2006-07-27 Spoolstra Gregg R Fuel injector pump with trapped volume
US7353805B2 (en) * 2003-01-30 2008-04-08 Robert Bosch Gmbh Fuel injector pump with trapped volume
US20080116300A1 (en) * 2006-11-16 2008-05-22 Mario Ricco Fuel adjustment and filtering device for a high-pressure pump
US7603986B2 (en) * 2006-11-16 2009-10-20 C.R.f Societa Consortio per Azioni Fuel adjustment and filtering device for a high-pressure pump

Also Published As

Publication number Publication date
DE2137832C2 (de) 1986-04-17
DE2137832A1 (de) 1972-02-17

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