US3320892A - Fuel injection system - Google Patents

Fuel injection system Download PDF

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Publication number
US3320892A
US3320892A US522007A US52200765A US3320892A US 3320892 A US3320892 A US 3320892A US 522007 A US522007 A US 522007A US 52200765 A US52200765 A US 52200765A US 3320892 A US3320892 A US 3320892A
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United States
Prior art keywords
fuel
delivery
injection
pressure
pump
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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
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US522007A
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English (en)
Inventor
George D Wolff
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.)
Allis Chalmers Corp
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Allis Chalmers Corp
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Publication date
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Priority to US522007A priority Critical patent/US3320892A/en
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Publication of US3320892A publication Critical patent/US3320892A/en
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Expired - Lifetime legal-status Critical Current

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    • 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
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • F02M41/126—Variably-timed valves controlling fuel passages valves being mechanically or electrically adjustable sleeves slidably mounted on rotary 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/122—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor with piston arranged radially to driving shaft

Definitions

  • This invention relates to a fuel injection system for diesel engines and particularly to precharging the fuel injection lines prior to injection.
  • the delivery passage is connected to the supply pressure chamber for a brief interval following injection to terminate injection. It is also known that pressure relief after injection is necessary in order to absorb the reflected pressure waves from the nozzle. If such relief is not afforded, pressure surges occurring after cutoff of fuel delivery to the injector may cause secondary injection which in turn causes a decrease in combustion efliciency. Relieving the pressure by use of a retraction delivery valve or by connecting the fuel delivery lines briefly to the supply chamber or to a low pressure portion of the system is usually effective in preventing secondary injection; however, voids often develop from this relief in the injection lines which cause erratic pump performance. Voids in the injection lines make it particularly difiicult to control the injection in the low speed range of the engine and at low fuel delivery.
  • the retraction of the delivery valve serves to relieve pressure in the delivery line at termination of injection. More specifically the retraction delivery valve reduces the reflection of the pressure wave returning from the injector after the end of the pumping stroke. To do this a small volume of fuel, the retraction volume, is displaced by the delivery valve, upon its closing, from the high pressure system back into the pumping chamber. Thus, a void is created into which the fuel carried in the returning pressure wave from the injector is dumped. Ideally, the volume of fuel carried in the returning wave is equal to the void created (the retraction volume) and in such a case the returning pressure wave is completely absorbed so that a reflection pressure wave will not be created at the pump end of the delivery line.
  • the amplitude of the returning pressure wave and consequently the volume of fuel carried by this wave is not only a function of dimensional parameters, such as delivery line ID and injector orifice area, but is also a function of the amplitude of the primary wave initiated at the pump during the pumping stroke. It is known that the amplitude of the primary wave varies with speed and load. When the engine rpm. is increased the plunger moves faster and a pressure wave with a higher amplitude is created. When the fuel delivery of the pump is increased, the pressure buildup in the pump will be greater than with a smaller delivery. Thus, the amplitude of the primary pressure wave initiated at the pump during the pumping stroke varies with engine speed and load and so also does the amplitude of the returning pressure wave.
  • a delivery valve retraction volume should also vary with speed and load.
  • a retraction volume is conventionally selected which is ideal only for one speed load combination. For all other conditions it will be a compromise i.e. either too large, resulting in a negative reflection of the returning wave and thus voids in the high pressure system, or too small, resulting in a positive reflection and thus possibly leading to secondary injections.
  • BMEP brake mean effective pressure
  • FIG. 1 is a view of a fuel injection system, including a fuel injection pump in section, in which the present invention is incorporated;
  • FIG. 2 is a section view taken along the lines II-II in FIG. 1;
  • FIG. 3 is a section view taken along the line IIIIII in FIG. 2;
  • FIG. 4 is a partial view of the pump plunger
  • FIG. 5 is a section view taken along the line VV in FIG. 1.
  • my precharged fuel injection system includes a pump 8 having a plunger 11 reciprocated in a plunger bore 112 of the head portion of pump housing 9 by a cam 13 formed on the pump drive shaft 14.
  • the plunger 11 is rotated by a gear train including gears 16, 17 of supply pump 15 and gears 1-8, 19.
  • the plunger 11 is connected to rotate with the gear 19 and reciprocate relative thereto.
  • Gears 16 and 18 are integrally formed to provide a gear cluster and gear 17 is nonrotatably secured to the drive shaft 14.
  • the pump housing 9 includes a governor compartment 21, which is at fuel tank pressure by virtue of its being connected thereto by a return line indicated schematically by dot-dash lines 22.
  • the housing 9 also includes a supply chamber 26 which is supplied fuel by the gear pump 15 by way of conduit 27 in which a fuel filter 23 is interposed.
  • the supply pump 15 draws fuel from the fuel tank 29 by way of conduit 31.
  • the fuel tank 20 and governor compartment 21 may be maintained at near atmospheric pressure and the supply chamber 26 is maintained at an intermediate pressure, such as 50 pounds per square inch, by a pressure maintaining valve 32 disposed between the supply chamber 26 and the governor chamber 21.
  • a plurality of fuel delivery passages 36 are adapted at their outer ends, by threaded openings 37, for connection to fuel injection conduits or lines leading to the injectors.
  • the inner ends of the passages 36 terminate, as illustrated in FIG. 2, at openings 38 which are equally circumferentially spaced.
  • FIG. 1 I show an out- .wardly opening injector 61 connected in fluid communication to one of the passages 36 by line 62, indicated schematically.
  • the upper end of the bore 12 is closed to form a high pressure chamber 41.
  • the high pressure chamber 41 is at injection pressures only during the upward movement (pumping stroke) of the plunger 11.
  • the plunger 11 includes a pumping portion 42, a distributing portion 43 and an effective stroke control portion 44.
  • the distributing portion 43 of the plunger which serves as rotating valve means to cyclically and individually connect in a sequential manner the high pressure chamber 41 with the delivery passages 36, includes a radially opening port 46 which is placed in free flow fluid communication with the injection pressure chamber 41 by an axial passage 47 in the plunger 11.
  • the passage 47 is open at its upper end and connects to radial passages 48 in the effective stroke control portion 44- of the plunger 11, which cyclically register with grooves 49 in control collar 51.
  • FIG. 5 illustrates the registrability of passages 48 with grooves 49.
  • a recess 55 is formed in the distributing portion of the plunger 11 in circumferentially spaced relation to port 46.
  • the recess 55 has a circumferential width several times the circumferential width of port 46 and is placed in free flow fluid communication with the supply chamber 26 by an axial groove 56.
  • the recess 55 places the fuel delivery passages 36 in free flow fluid communication with the supply chamber 26 during a substantial portion of the time that they are out of registry with the port 46.
  • the cavities of which I speak are those formed of vapor, entrained in air and dissolved air which is liberated from the liquid fuel at low pressure.
  • the use of passage means 55, 56, which serve as a rotating valve to cyclically connect the delivery passages 36 to the supply chamber 26, is effective to equalize the pressure in, and precharge the delivery passages 36, since the latter are connected to the supply chamber 26 for a relatively long time interval.
  • the individual delivery passages 36 are connected to the supply chamber 26 for a major portion of the time, that is, over one-half the time.
  • Equalization of the pressure in the delivery passages and precharging them to supply chamber pressure insures equal delivery of pressure fluid to the cylinder injectors during injection.
  • a fuel pump using my precharging concept could be provided with a delivery valve between the injection chamber 41 and the port 46, I have found the delivery valve to be unnecesary and its elimination results in further improvement in engine performance.
  • the delivery valve is a source of reflection for the returning pressure wave in the delivery lines and hence its elimination is beneficial. Also, elimination of the delivery valve decreases the volume of the high pressure system of the pump with resulting improvement in delivery performance.
  • My fuel pump also makes it possible for a given fuel system to have a shorter duration of injection and this provides fast burning of the fuel and more efficient combustion.
  • diesel injectors with outwardly opening valves may be used to great advantage over inwardly opening injectors.
  • the closing pressure for inwardly opening injectors has necessarily been increased as engine BMEP has increased, thus reducing valve seat life. Since the combustion gases tend to force the outwardly opening valve 63 closed rather than open (as occurs in an inwardly opening injector), a lower closing pressure can be used for valve 63 without permitting entrance of combustion gases into injector pressure chamber 64. Reducing closing pressure of the injector valve results in longer life of the valve seat 66. Also, as is well known, the cost of outwardly opening injectors is substantially less than inwardly opening nozzles.
  • My prechar-ged fuel injection system provides improved fuel injection through precise and equal delivery of fuel to the engine cylinders, permits higher cylinder operating pressures without attendant problems of combustion gases entering the injectors or excessive injector valve closing pressures and affords a marked reduction in cost of injection equipment through reduced pump and injector costs.
  • a pump housing including a bore, a plurality of valveless delivery passages adapted to connection to fuel delivery lines, respectively, an injection pressure chamber, and a supply chamber, means supplying fuel to said supply chamber and maintaining the latter at a pressure substantially above atmospheric pressure, means for cyclically transferring fuel from said supply chamber to said injection pressure chamber and for pressurizing it to an injection pressure including a reciprocable pump plunger in said bore, and
  • a pumping housing including a high pressure chamber, a supply chamber, a bore between said chambers, and a plurality of delivery passages terminating at their inner ends at said bore in circumferentially spaced openings and adapted at their outer ends for connection to fuel delivery lines, means suplying fuel to said supply chamber and maintaining the latter at a pressure substantially above atmospheric pressure, and
  • a pump plunger reciprocably and rotatably mounted in said bore having cyclically open and closed passage means extending between said high pressure chamber and said supply chamber, and
  • valve portion defining a passage means operable upon rotation of said plunger to cyclically and individually connect said delivery passages to said high pressure chamber during injection and another passage means independent of said cyclically open and closed pasage means operable upon rotation of said plunger to cyclically connect said delivery passages in free flow fluid communication with said supply chamber during a substantial portion of the time the delivery passages are disconnected from said high pressure chamber.
  • said another passage means is a recess registrable with said openings during rotation of said plunger and an axially extending groove in the periphery of said plunger extending between said recess and a portion of said plunger disposed in said supply chamber.
  • a fuel injection pump comprising:
  • a housing including a supply chamber
  • a plunger bore opening at one end into said supply chamber and closed at its other end to provide a high pressure chamber
  • a plunger reciprocably and rotatively disposed in said bore including a distributing portion
  • a fuel injection pump comprising:
  • a housing including a supply chamber a plunger bore opening at one end into said supply chamber and closed at its other end to provide a high pressure chamber, and
  • valveless fuel delivery passages having inner ends terminating in equally and circumferentially spaced openings respectively at said bore intermediate said high pressure chamber and said supply chamber and having outer ends adapted for connection with fuel injection conduits respectively.
  • a plunger reciprocably and rotatively disposed in said bore including a distributing portion
  • a fuel injection system comprising: an injection pump having a housing including a high pressure chamber,
  • valveless delivery passages defining openings in said bore between said chambers and at equally spaced circumferential intervals
  • a rotatable and reciprocable pump plunger in said bore having a radially opening port cyclically registrable with said passages one at a time during rotating of said plunger
  • passage means connecting said port in fluid receiving relation to said high pressure chamber, cyclically open and closed passage means extending between said high pressure chamber and said supply chamber, eans maintaining said supply chamber at an intermediate pressure, and
  • passage means independent of said cyclically open and closed passage means continuously connecting said delivery passages to said supply chamher during a substantial portion of the time they are out of registry with said port, said portion of time being at least twice the time required for said port to rotate through two of said circumferential intervals.
  • a fuel injection pump comprising: wall means defining a high pressure chamber,
  • valveless delivery passages adapted at their outer ends for connection to fuel injection conduits respectively and terminating at their inner ends in said bore at equally and circumferentially spaced openings, means maintaining said supply chamber at an intermediate pressure means for cyclically transferring fuel from said supply chamber to said high pressure chamber and for cyclically pressurizing the transferred fuel to an injection pressure including a reciprocable pump plunger, rotating valve means in said bore cyclically and individually connecting said delivery passages to said high pressure chamber to effect delivery of fuel therethrough at injection pressure, and passage means independent of said second named means connecting said delivery passages in continuous free flow fluid communication with said supply chamber during at least one quarter of the time the delivery passages are disconnected from said high pressure chamber.

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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)
US522007A 1964-10-20 1965-12-20 Fuel injection system Expired - Lifetime US3320892A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US522007A US3320892A (en) 1964-10-20 1965-12-20 Fuel injection system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US40518964A 1964-10-20 1964-10-20
US522007A US3320892A (en) 1964-10-20 1965-12-20 Fuel injection system

Publications (1)

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US3320892A true US3320892A (en) 1967-05-23

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Application Number Title Priority Date Filing Date
US522007A Expired - Lifetime US3320892A (en) 1964-10-20 1965-12-20 Fuel injection system

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US (1) US3320892A (fr)
CH (1) CH427407A (fr)
DE (1) DE1242409B (fr)
FR (1) FR1450316A (fr)
GB (1) GB1093563A (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3352245A (en) * 1965-12-09 1967-11-14 Allis Chalmers Mfg Co Fuel injection system
US3440964A (en) * 1966-12-09 1969-04-29 Ambac Ind Fuel injection pump
EP0013140A1 (fr) * 1978-12-22 1980-07-09 AMBAC Industries, Incorporated Pompe d'injection de carburant
US4233002A (en) * 1978-05-09 1980-11-11 Benjamin Birenbaum Fuel injection system
US6322336B1 (en) * 1999-02-05 2001-11-27 Memminger-Iro Gmbh Lubricating device for a plurality of lubricating stations
US20060013703A1 (en) * 2004-07-15 2006-01-19 Mitsuo Yokozawa Multi-channel pump and its control method
US20090035629A1 (en) * 2004-07-15 2009-02-05 Nidec Sankyo Corporation Multi-channel pump, fuel cell and control methods therefor

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2449332C2 (de) * 1974-10-17 1986-08-07 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffverteilereinspritzpumpe für Brennkraftmaschinen
DE3049366A1 (de) * 1980-12-29 1982-07-29 Spica S.p.A., Livorno Kraftstoffverteiler-einspritzpumpe fuer verbrennungsmotoren
US5215060A (en) * 1991-07-16 1993-06-01 Stanadyne Automotive Corp. Fuel system for rotary distributor fuel injection pump
EP2143545A1 (fr) * 2008-07-07 2010-01-13 Nestec S.A. Procédé et dispositif de conditionnement d'un liquide alimentaire

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB359603A (en) * 1930-08-02 1931-10-29 Napier & Son Ltd Improvements in or relating to fuel injection pumps
US2544561A (en) * 1945-06-11 1951-03-06 American Bosch Corp Fuel injection pump
US2804825A (en) * 1950-11-17 1957-09-03 British Internal Combust Eng Delivery valves for fuel injection pumps
US2813523A (en) * 1953-10-29 1957-11-19 Bosch Arma Corp Fuel injection pump
GB804026A (en) * 1956-05-30 1958-11-05 Cav Ltd Liquid fuel injection pumps
CH349124A (de) * 1956-05-30 1960-09-30 Cav Ltd Brennstoffeinspritzpumpe
US2965087A (en) * 1958-01-29 1960-12-20 Bosch Arma Corp Fuel injection pump
US2969784A (en) * 1958-03-13 1961-01-31 Borg Warner Fuel injection mechanism
US3023705A (en) * 1958-09-24 1962-03-06 Bosch Gmbh Robert Injection pump
US3099217A (en) * 1959-11-12 1963-07-30 Bessiere Pierre Etienne Fuel injection pumps having distributing pistons
US3146716A (en) * 1961-12-26 1964-09-01 Allis Chalmers Mfg Co Fuel supplying mechanism
GB971536A (en) * 1959-11-12 1964-09-30 Expl Des Procedes Chimiques Et Improvements in fuel injection pumps having distributing pistons

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1165346B (de) * 1959-11-12 1964-03-12 Expl Des Procedes Chimiques Et Brennstoffeinspritzpumpe mit um seine Achse verdrehbarem, als Verteiler wirkenden Pumpenkolben
FR1282101A (fr) * 1960-12-07 1962-01-19 Perfectionnements apportés à des pompes (notamment des pompes d'injection de combustible) dont le piston alternatif constitue en même temps un distributeur tournant
US3138103A (en) * 1961-12-26 1964-06-23 Allis Chalmers Mfg Co Fuel supplying mechanism

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB359603A (en) * 1930-08-02 1931-10-29 Napier & Son Ltd Improvements in or relating to fuel injection pumps
US2544561A (en) * 1945-06-11 1951-03-06 American Bosch Corp Fuel injection pump
US2804825A (en) * 1950-11-17 1957-09-03 British Internal Combust Eng Delivery valves for fuel injection pumps
US2813523A (en) * 1953-10-29 1957-11-19 Bosch Arma Corp Fuel injection pump
GB804026A (en) * 1956-05-30 1958-11-05 Cav Ltd Liquid fuel injection pumps
CH349124A (de) * 1956-05-30 1960-09-30 Cav Ltd Brennstoffeinspritzpumpe
US2965087A (en) * 1958-01-29 1960-12-20 Bosch Arma Corp Fuel injection pump
US2969784A (en) * 1958-03-13 1961-01-31 Borg Warner Fuel injection mechanism
US3023705A (en) * 1958-09-24 1962-03-06 Bosch Gmbh Robert Injection pump
US3099217A (en) * 1959-11-12 1963-07-30 Bessiere Pierre Etienne Fuel injection pumps having distributing pistons
GB971536A (en) * 1959-11-12 1964-09-30 Expl Des Procedes Chimiques Et Improvements in fuel injection pumps having distributing pistons
US3146716A (en) * 1961-12-26 1964-09-01 Allis Chalmers Mfg Co Fuel supplying mechanism

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3352245A (en) * 1965-12-09 1967-11-14 Allis Chalmers Mfg Co Fuel injection system
US3440964A (en) * 1966-12-09 1969-04-29 Ambac Ind Fuel injection pump
US4233002A (en) * 1978-05-09 1980-11-11 Benjamin Birenbaum Fuel injection system
EP0013140A1 (fr) * 1978-12-22 1980-07-09 AMBAC Industries, Incorporated Pompe d'injection de carburant
US4229148A (en) * 1978-12-22 1980-10-21 Ambac Industries, Incorporated Fuel injection pump
US6322336B1 (en) * 1999-02-05 2001-11-27 Memminger-Iro Gmbh Lubricating device for a plurality of lubricating stations
USRE40898E1 (en) * 1999-02-05 2009-09-01 Memminger-Iro Gmbh Lubricating device for a plurality of lubricating stations
US20060013703A1 (en) * 2004-07-15 2006-01-19 Mitsuo Yokozawa Multi-channel pump and its control method
US20090035629A1 (en) * 2004-07-15 2009-02-05 Nidec Sankyo Corporation Multi-channel pump, fuel cell and control methods therefor
US8163440B2 (en) 2004-07-15 2012-04-24 Nidec Sankyo Corporation Fuel cell and control method therefor

Also Published As

Publication number Publication date
DE1242409B (de) 1967-06-15
GB1093563A (en) 1967-12-06
FR1450316A (fr) 1966-05-06
CH427407A (fr) 1966-12-31

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Legal Events

Date Code Title Description
AS Assignment

Owner name: CONNECTICUT NATIONAL BANK THE, A NATIONAL BANKING

Free format text: SECURITY INTEREST;ASSIGNOR:ALLIS-CHALMERS CORPORATION A DE CORP.;REEL/FRAME:004149/0001

Effective date: 19830329

Owner name: WOODS KATHLEEN D., AS TRUSTEE

Free format text: SECURITY INTEREST;ASSIGNOR:ALLIS-CHALMERS CORPORATION A DE CORP.;REEL/FRAME:004149/0001

Effective date: 19830329