US3861833A - Fuel injection pump - Google Patents

Fuel injection pump Download PDF

Info

Publication number
US3861833A
US3861833A US336538A US33653873A US3861833A US 3861833 A US3861833 A US 3861833A US 336538 A US336538 A US 336538A US 33653873 A US33653873 A US 33653873A US 3861833 A US3861833 A US 3861833A
Authority
US
United States
Prior art keywords
fuel
shuttle
pump
stop
chamber
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
US336538A
Other languages
English (en)
Inventor
Daniel Salzgeber
Robert Raufeisen
Charles W Davis
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.)
Stanadyne Automotive Corp
Original Assignee
Stanadyne LLC
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 Stanadyne LLC filed Critical Stanadyne LLC
Priority to US336538A priority Critical patent/US3861833A/en
Priority to DE19742405452 priority patent/DE2405452A1/de
Priority to FR7405851A priority patent/FR2219316B1/fr
Priority to GB4599374*A priority patent/GB1416120A/en
Priority to GB659674A priority patent/GB1416119A/en
Priority to IN320/CAL/74A priority patent/IN140149B/en
Priority to SE7402276A priority patent/SE396117B/xx
Priority to BR1293/74A priority patent/BR7401293D0/pt
Priority to IT48752/74A priority patent/IT1008948B/it
Priority to CA193,580A priority patent/CA1000142A/en
Priority to ES423702A priority patent/ES423702A1/es
Priority to JP49024102A priority patent/JPS49117827A/ja
Priority to US05/493,242 priority patent/US3938911A/en
Application granted granted Critical
Publication of US3861833A publication Critical patent/US3861833A/en
Assigned to MANUFACTURERS HANOVER TRUST COMPANY, AS AGENT reassignment MANUFACTURERS HANOVER TRUST COMPANY, AS AGENT SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: STANADYNE AUTOMOTIVE CORP.
Assigned to STANADYNE AUTOMOTIVE CORP., A CORP. OF DE reassignment STANADYNE AUTOMOTIVE CORP., A CORP. OF DE ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: STANADYNE, INC.
Anticipated expiration legal-status Critical
Assigned to STANADYNE INC. reassignment STANADYNE INC. RELEASE OF SECURITY INTEREST Assignors: CHEMICAL BANK, AS SUCCESSOR IN INTEREST TO MANUFACTURERS HANOVER TRUST COMPANY
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • F02M41/14—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 rotary distributor supporting pump pistons
    • F02M41/1405—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 rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis

Definitions

  • a liquid fuel injection pump for supplying precisely measured charges of fuel under high prssure has a housing in which a fuel distributing rotor is journaled.
  • the rotor carries a high pressure charge pump for pressurizing the charges of fuel and a pair of through bores in the housing mount a pair of shuttles which alternate in pumping measured charges of fuel into the charge pump chamber.
  • Fuel regulated by a metering valve is delivered to a chamber at one end of each shuttle and the fuel charge so produced is then pumped into the charge pump chamber by applying hydraulic pressure to the other end of the shuttle.
  • a ball check valve carried by the rotor isolates the shut tles from the charge pump.
  • An axially adjustable stop at each end of each through bore limits the movement of each shuttle in each direction and the stops for each shuttle are accessible through the end of its through bore for changing the limit of movement of the shuttle in each direction independently of the other stop for the shuttle.
  • a passage supplies fuel to a closer plunger which hydraulically seats the ball check valve and the fuel trapped between the plunger and its stop cushions the impact therebetween as the charge pump pressurizes the pressure, in the rotor.
  • Fuel injection pumps of the type involved in this invention deliver metered charges of liquid fuel under high pressure to the cylinders of an associated engine in timed relationship to their operation. It is desirable that such fuel injection pumps be effective over a wide speed range, effectively govern the engine to provide substantially constant speed operation under widely varying loads, and operate efficiently over relative long periods of time with little or no maintenance. Accordingly, it is a principal object of this invention to provide a new and improved fuel injection pump which meets these requirements.
  • Another object of this invention is to provide such a fuel pump having a new and improved positive displacement low pressure shuttle for feeding discrete charges of fuel to the high pressure pump chamber wherein charge-to-charge variation in the fuel delivered by the pump is minimized. Included in this object is the provision of such a pump in which the stops at both ends of a pair of alternately operating shuttles are accessible for control and/or easy adjustment in response to desired parameters selected for the operation of operating the pump with precision in the uniformity of charges delivered by the two shuttles.
  • Another object of this invention is the provision of an improved fuel injection pump in which an improved low inertia shuttle feeding system is utilized.
  • Still another object of this invention is to provide such a pump wherein the maximum fuel which can be injected at a given engine speed is accurately and automatically controlled at varying levels correlated with engine speed.
  • a further object of this invention is to provide such a pump having new and improved means for relieving excess pressure in the fuel conduits to plugged nozzles supplied by the pump. Included in this object is the provision of means for fixing the maximum unbalance in the radial forces acting on the distributor rotor of the pump.
  • a still further object of this invention is to provide such a pump having a rotor mounted check valve with an improved positive acting closer for the valve to minimize the stresses imposed thereon.
  • FIG. 1 is a cross-sectional view of an exemplary fuel injection pump embodying the present invention
  • FIG. 1A is a fragmentary cross-sectional view of the drive shaft assembly of the pump of FIG. 1;
  • FIG. 2 is a schematic view of the pump of FIG. 1 showing the hydraulic circuits thereof;
  • FIG. 3 is a partial schematic view similar to FIG. 2 showing a sequence during the charging of the pump chamber
  • FIG. 4 is a cross-sectional view taken along the line 44 of FIG. 1;
  • FIG. 5 is an enlarged fragmentary cross-sectional view of the rotor mounted ball check mechanism of FIG. 1;
  • FIG. 6 is a cross-sectional view taken along line 66 of FIG. 1
  • the pump has a hydraulic head 10 with a cylindrical bore 12 in which a sleeve I4 is tightly mounted.
  • the sleeve 14 in turn provides a cylindrical bore 16 in which a distributor rotor 18 is rotatably. mounted.
  • Hydraulic head 10 is secured to a drive housing II by removable means (not shown).
  • the drive housing includes a mounting flange for attaching the pump to the engine and contains a drive shaft 13 and shaft seals 15.
  • fuel from a supply tank (not shown) is delivered to the pump inlet 20 to a vane-type low pressure inlet or supply pump 22, the output of which is pressurized to a pressure correlated with engine speed.
  • the output is delivered to a large annular groove 24, through passage 26, and past an electric shutoff valve 28 which serves to shut off fuel delivery by the pump independent of governor operation.
  • the fuel flows through a passage 30 and a metering port 32 to an annulus 34 formed on the periphery of the distributor rotor 18 with the metered fuel pressure in the annulus 34 having a pressure regulated by the metering valve 134.
  • the fuel flows past a one-way ball check valve 36 in a manner hereinafter more fully described and through axial passage to pump chamber 38.
  • the pump chamber 38 is shown as being formed by a pair of intersecting transverse bores in an enlarged part of the rotor.
  • a pair of opposed plungers 50 are mounted for reciprocating movement in each bore.
  • Surrounding the distributor rotor 18 is a generally annular cam ring 60 which is journaled in a cylindrical recess 62 for a limited arcuate movement and is disposed in the plane of revolution of the plungers 50.
  • the cam ring 60 is restrained from rotating by an adjustable timing advance piston 64 and a connecting pin 66 which interconnects the advance piston 64 and the cam ring 60.
  • Cam rollers 68 and cam roller shoes 70 are carried by the rotor between the plungers 50 and the cam ring.
  • the plungers 50 move radially outwardly as required to receive the charge of fuel delivered to the pump chamber.
  • the cam rollers 68 are positioned between adjacent cam lobes of the cam ring 60. Rotation of the rotor 18 then causes the rollers 68 to pass over the cam lobes of cam ring 60 to translate the profile of the cam into reciprocal motion of the plungers to pressurize the charge of fuel in the pump chamber 38 on the inward stroke of the plungers 50.
  • the fuel is pressurized to a high pressure, say, up to 12,000 psi, in chamber 38, and is delivered through passage 40, past delivery valve 41, and into delivery chamber 42. From the delivery chamber 42, the pressurized fuel flows through diagonal distributing passage 44 which registers sequentially with a plurality of passages 46 to the outlets 48 for sequential delivery to the injector for each of the several cylinders of the associated engine.
  • a high pressure say, up to 12,000 psi
  • End cap 82 provides an annular recess which houses the lower pressure or supply inlet pump 22 and is removably secured to the end of the pump housing 10 by suitable means (not shown).
  • O-ring 84 seals the end cap 82 to the housing type
  • the vane tupe inlet pump 22 is a positive displacement pump having a plurality of segmented vanes 88 which are encircled by a linear 90 disposed eccentrically with respect to the axis of rotation of distributor rotor 18.
  • An annular ring 92 having one end received in a circular groove 94 locates the eccentric linear 92.
  • the pump 22 is provided with an end plate 96 which is resiliently biased against the end of the ring 90 by an annular washer 98 and a wave spring washer 100 which bottoms against the end of the annular recess 102 formed in the end cap 82.
  • a coaxial inlet strainer 104 mounted within the inlet fittng 80 through which new fuel entering the pump passes before entering the inlet passage 106 of end plate 96.
  • a kidney shaped arcuate groove 108 formed in the end plate 96 serves as an outlet for the pump 22 from which the fuel flows through a radial slot 110 in end plate 96 to a central cavity 112. From the central cavity 112, the output fuel flows axially through a central passage provided between the segmented vanes 88 and in the radial slots 113 of the rotor 18 which slideably mounts the vanes 88 to hydraulically bias the segmented vanes outwardly into close contact with the inner periphery of the eccentric liner 90.
  • the fuel then flows to the large annulus 114 provided at the end of the distributor rotor 18 immediately adjacent the supply pump 22.
  • the end plate 96 further mounts an axially projecting coaxial pressure regulator generally indicated by the numeral 116.
  • the regulator 116 is pro-- vided with a cylindrical housing 118 mounting a valve 120 which is adjustably biased to a closed position against an annular stop 112 such that valve 120 closes spill port 126 in cylindrical housing 118.
  • Stop 122 is fixedly secured in the end plate 96 by a split ring 124 mounted in an annular groove 125 in end plate 96.
  • Regulated output fuel from pump 22 flows from annulus 24 through passage 26, past shutoff valve 28, through passage 30 to port in governor tube 132.
  • the metering valve 134 rotatably and slideably mounted in governor tube 132, has a necked-down portion 136 aligned with inlet port 130 to provide an annulus 137 within the governor tube.
  • a triangular shaped metering port 32 is provided in the governor tube 132 at an axial position aligned with the shoulder of the metering valve at the left end of annulus 137 so that its degree of opening is determined by the axial position of the metering valve 134 which is connected to rotate with governor flyweight assembly 139 which in turn is driven by the rotor through gears 138, 140.
  • the governor flyweight assembly 139 exerts an axial force on the metering valve 134 to urge it toward a closed position against the bias of springs 142 and 144 until an equilibrium condition is reached.
  • the spring force of spring 144 is set by a movable seat 146 c'ontrolled by the throttle 148 to establish the speed at which equilibrium takes place.
  • the free end of the metering valve 134 is provided with a drilled axial passage 162.
  • a movable closure 166 is biased against the end of the metering valve 134 by the spring 142 and/or spring 144 to close the drilled passage.
  • Spring 142 has a low spring rate and is effective only at low speed where it provides improved governor operation.
  • the passage 162 is provided with a port 164 in the side wall of metering valve 134 which communicates with an annulus 172.
  • Output fuel from inlet pump 22 is bled into the annulus 172 through the bleed orifice 182, and the pressure thereof, which is substantially higher at all operating speeds than the pressure in passage 162, causes a slight separation between the end of the metering valve 134 and the closure 166 to spill fuel from passage 162. Since the spring force of spring 144 opposes flyweight force and this force is transmitted hydraulically between closure 166 and metering valve 134, the spill of fuel from passage 162 is in an amount to result in a pressure in passage 162 correlated with flyweight force.
  • flyweight force is directly proportional to the square of the speed
  • an equivalently proportioned N control pressure is established in passage 162, as well an in annulus 172, passage 174, and annulus 176 to deliver a speed related N control pressure to advance piston 64 and fuel limiting plunger 178 through passage 180.
  • conduit 180 is connected to a passage 184 in advance piston 64 to deliver N 35 control pressure to operate a servo piston 186 which acts against the bias of a spring 188 to control the flow of fuel from inlet pump 22 through conduit 190 from the transfer pump to chamber 192 at one end of the advance piston 64 through annulus 194 and passage 195 with reed valve 196 preventing reverse flow through passage 195 and preventing sharp pressure impulses imposed in the trapped fuel in chamber 192 from being present in annulus 194.
  • Passage 197 is provided for dumping fuel from chamber 192 upon a reduction in operating speed.
  • a steel insert 198 is press fit in the crossbore of the advance piston for receiving the connecting pin 66 to prevent the enlargement and deformation of the crossbore under the high stresses imposed between the pin 66 and the crossbore due to the repeated impact loads imparted thereon by the operation of the pump.
  • a reed valve 196 is attached to the end of the advanced piston 64 covering passage 195 to prevent reverse flow of trapped fuel in the chamber 192 through the passage 195.
  • the reaction pressure generated in chamber 192 is much larger than that provided by the supply pump and advancing motion of the piston therefore occurs only between pumping strokes.
  • N control pressure from conduit 180 controls the axial position of fuel limiting plunger 178 by controlling the addition to, and the dumping from, the chamber 202 of fuel by the position of the servo valve 204 relative to plunger 178.
  • the cavity 201 communicates with conduit 190 and is connected to annulus 211 on valve 204 by passage 205.
  • Fuel at N control pressure enters chamber 203 at one end of'valve 204 via conduit 180.
  • a bias spring 208 At the opposite end of servo valve 204 is a bias spring 208 which is adjustable by means of screw 207.
  • Servo valve 204 reaches a position of equilibrium when the pressure in chamber 203 equals the spring force of spring 208.
  • the torque limiting plunger 178 is provided with a passage 209 having a radial port into the servo valve chamber controlled by land 204A. Since conduit delivers pressure from supply pump 22 to the annulus 211, additional fuel may enter the chamber 202 when the land 204A is to the left relative to the port of conduit 209, and trapped fuel in chamber 202 is dumped from chamber 202 when the port is to the left of the land 204A to control the axial position of torque limiting plunger 178 according to engine speed.
  • metering valve 134 controls the amount of restriction offered to the flow of fuel through the triangular metering port 32 to maintain the speed of the associated engine despite varying loads. Fuel that passes through the metering port 32, flows to a groove 34 on the rotor 18.
  • pressurized fuel from inlet pump 22 is delivered by passage 26 to shuttle space 224 to force the shuttle downward against stop 238 and serve as a positive displacement pump to deliver the charge of fuel previously delivered to shuttle space 214 into the pump chamber 38 (FIG. 1) past ball valve 36.
  • the charge of fuel so delivered to the pump chamber 38 is equal to shuttle displacement. This charge is pumped into the pump chamber 38 by a pressure dependent only on the output pressure of inlet pump 22.
  • the pressure in rotor passage 40 decreases to the same level as housing pressure, and the pressure in passage 242, which is in continuous communication with the pressurized output of inlet pump 22 through passage 26 moves inlet ball check closer piston 244 upwardly to seat the ball 36 prior to the rotation of a roller 68 up a cam lobe of cam ring 60 and the resulting pressurization of the fuel in chamber 38.
  • the diameter of closer piston 244 is smaller than the seating diameter of ball 36 so that, despite the fact that supply pump pressure acts on each in opposition to the other during the delivery of a metered charge of fuel to pump chamber 38, the closer piston 244 does not prevent opening motion of ball 36 and charging flow is permitted.
  • the highly pressurized fuel from pump chamber 38 is discharged through the axial passage 40, past delivery valve 41 into delivery chamber 42, and by diagonal passage 44 to a passage 46, with which the passage 44 registers during the pumping stroke, for injection into a cylinder of the associated engine.
  • the delivery valve 41 is of the volume retraction type so that as the rollers 68 reach the tops of the cam lobes to terminate the forward flow of fuel in passage 40, the spring 43 moves the delivery valve 41 to the left, as viewed in FIG. 1. to a position where cuff 45 overlies shoulder 47 to prevent reverse flow past delivery valve 41 by way of external flutes 52. Further movement of the delivery valve adds a prescribed increase of space to be occupied by the fuel trapped downstream of valve 41.
  • a feature of the invention is that the unique delivery valve disclosed provides a flat seat seal wherein the pressure of the trapped fuel in chamber 42 and spring 43 provide the biasing force for the seal. As shown, the delivery valve is provided with a flat end which seats against a transverse end wall 49 to form the seal.
  • the end of delivery valve 41 is provided with a recess 51 aligned with passage 40.
  • This recess is displaced or offset from the seal surface so that any cavitation erosion due to the sudden reduction in pressure in passage 40 and the inertia of the fuel therein does not damage the seal surfaces between delivery valve 41 and the annular shoulder 49 which are perpendicular to the axis of passage 40.
  • a short axial slot 244 on rotor 18 momentarily registers with the passage 46, to relieve any high residual pressure which may be present in the passage 46 in the event of a plugged nozzle.
  • slot 244 is connected to annulus 256, passage 258, and a pressure relief valve 260 which limits the maximum residual pressure in the passage 46 between injections to a safe level, say, 1500 psi, and prevents the maximum pressure generated during injection from progressively building-up to a destructive level despite the presence of a plugged nozzle and repeated injections of a charge of fuel thereto. This limits the side loading imposed on the rotor by the pressure in a passage 46.
  • the pumping plungers 50 are moved rapidly outwardly during the charging of pump chamber 38. This displaces the fuel which occupied the space radially outwardly of the plungers 50 immediately preceeding the charging of the pump chamber and results in a sudden pressure impulse up to, say, 80 psi.
  • Such pressure pulses are repetitious and would normally have a deleterious effect on resilient seals such as shaft seals exposed thereto.
  • This invention provides a novel means for protecting shaft seals 15 from the harmful effect of these pressure pulses.
  • a pressure shield in the form of an annular dam 17 is disposed between the shaft seals 15 and fuel within the housing 11 which is subjected to the pressure spikes.
  • the dam 17 is preferably formed of aluminium and is spaced from shaft 13 by a narrow annular gap 19 which offers a restricted passage to the flow of fuel therethrough and dampens the pressure spikes imposed on seals 15.
  • the dam 17 abuts a shoulder 21 and is secured against rotation by a pin 33.
  • shuttle 216 The functioning of the shuttle 216 and the feeding of metered charges of fuel to the pump chamber 38 has been described in connection with a single shuttle 216.
  • a pair of identical shuttles as shown in FIG. 4, are used. These identical shuttles function alternatively for delivering acharge of fuel to the pump chamber 38 with the distributor rotor 18 being provided with a plurality of each of the slots 222, 230, 210, and 232 around its periphery for sequential registration with the passages associated with the two shuttles.
  • the use of two shuttles, halves the number of slots 230 and 210 which are required.
  • a feature of this invention is that the pair of shuttles 216, while alternating in the delivering of fuel to the pump chamber 38 and involving a design subject to charge-to-charge variation due to manufacturing differences such as the length of the stems 238, and the shuttles 216, are constructed to prevent such variations.
  • the stops at both ends of the shuttles 216 are accessible for adjustment or control. Where fixed stops 218 are used, they threadably engage their respective bores and may be precisely adjusted by bottoming the stops and then backed off a precise number of turns to provide precise vernier calibration of the maximum travel of the shuttles and hence the maximum charge of fuel delivered by the two shuttles.
  • the shuttle mechanism includes a light-weight low inertia shuttle 216, and an elongated massive stop 238. Not only does this design produce a faster response time of the shuttle, but it also results in shuttle chamber 214 for the metered fuel which is effectively sealed against leakage by the long path between stem 238 and its bore. Further since the mass of stem 238 is substantially greater than the mass of shuttle 215, the stem serves as an energy absorber for the shuttle 216, and reduces impact loading between stops 238 and cam surfaces 240.
  • one end of the ball check valve closer piston 244 is subjected to the high pressure impulsed generated in the pump chamber 38. As a result, these forces drive the closer piston 244 against its stop 245 at high velocity when pumping starts.
  • This invention provides means for cushioning the shock that would normally occur as the closer piston strikes the stop.
  • the stop 245 is formed by a hardened button which is held against the bottom of the recess 247 for the closer piston 244.
  • a spring washer 249 tightly biases the stop 245 against the bottom wall of recess 247.
  • the end of the closer piston 244 and the mating surface of the stop 246 are flat so that, as the closer piston reaches the stop 246 at high speed, the fuel therebetween must be squeezed out and serves to cushion the termination of movement of piston 244.
  • the button 246 is provided with a central passage 251 which being filled with fuel, serves as a surge chamber with the fuel therein pressurized to assist in cushioning the impact the inhibiting cavitation.
  • closer piston is elongated and its cross'section is small to provide a high length-todiameter ratio.
  • an effective seal is provided between the high pressure passage 40 and the laterally directed passage 242 along the full length of closer piston 244 to substantially eliminate the possibility of leakage of high pressure metered charges of fuel.
  • a liquid fuel injection pump suited for the delivery of measured charges of liquid fuel under high pressure to an associated engine comprising a pump chamber wherein the charges are pressurized to high pressure, means for metering the fuel delivered to the pump chamber to provide measured charges of fuel in amounts correlated with engine operating conditions, a pair of through bores in the housing of said pump respectively mounting a pair of shuttles, first chambers respectively disposed at one end of each of said pair of shuttles alternatively receiving the measured charges of fuel prior to their delivery to the pump chamber, a second chambers respectively disposed at the other end of each of said shuttles, a source of hydraulic pressure connected to said second chambers to actuate said shuttles alternatively to deliver the previously metered charges of fuel to the pump chamber, means for isolating said shuttle mechanism from said pump chamber during the pressurizing of the charges in said pump chamber and an axially adjustable stop at each end of each through bore limiting the movement of each shuttle in each direction, the stops for each shuttle being accessible through the ends of its through bore and independent of each other for charging the limit of the movement
  • each shuttle is bottomed against one of its stops at the beginning of the delivery of each measured charge to the first chamber associated therewith, and the one stop is axially movable during operation in response in an operating condition of the engine.
  • each of said movable stops have substantially greater mass than said shuttles whereby the stops serves as energy absorbers for the shuttles.
  • said isolating means comprises a check valve positioned between the inlet passage and said pump chamber to isolate the inlet passage from said pump chamber during the pressurizing of the fuel therein, a closer plunger for seating said check valve, a passage for continuously supplying fuel under pressure to the end of said closer plunger opposite said check valve to seat said check valve after the delivery of a charge of fuel to said pump chamber and before the pressurization thereof, a stop engageable with said end of said closer plunger for limiting the movement of said closer plunger away from said check valve under the infleunce of the high pressure generated in said pump chamber, said passage for supplying fuel under pressure communicating with said end of said closer plunger through a port substantially in the plane of said end of said closer plunger, said end of said closer plunger and the mating surface of said stop being flat to form a pump to radially squeeze out the fuel trapped therebetween through an increasingly restricted passage as the closer plunger approaches the stop thereby to cushion the impact of the plunger against the stop.
  • stop comprises a removable button which is spring biased toward the bottom of a closed recess in UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION PATENT NO. 13,861,833

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
US336538A 1973-02-28 1973-02-28 Fuel injection pump Expired - Lifetime US3861833A (en)

Priority Applications (13)

Application Number Priority Date Filing Date Title
US336538A US3861833A (en) 1973-02-28 1973-02-28 Fuel injection pump
DE19742405452 DE2405452A1 (de) 1973-02-28 1974-02-05 Kraftstoffeinspritzpumpe
FR7405851A FR2219316B1 (enrdf_load_stackoverflow) 1973-02-28 1974-02-13
GB4599374*A GB1416120A (en) 1973-02-28 1974-02-13 Fuel injection pump
GB659674A GB1416119A (en) 1973-02-28 1974-02-13 Fuel injection pump
IN320/CAL/74A IN140149B (enrdf_load_stackoverflow) 1973-02-28 1974-02-14
BR1293/74A BR7401293D0 (pt) 1973-02-28 1974-02-21 Aperfeicoamentos em uma bomba para injecao de combustivel
SE7402276A SE396117B (sv) 1973-02-28 1974-02-21 Brensleinsprutningspump
IT48752/74A IT1008948B (it) 1973-02-28 1974-02-26 Pompa di iniezione del carburante per motore a combustione interna
CA193,580A CA1000142A (en) 1973-02-28 1974-02-27 Fuel injection pump
ES423702A ES423702A1 (es) 1973-02-28 1974-02-27 Perfeccionamientos en bombas de inyeccion de combustible para motores de encendido por compresion.
JP49024102A JPS49117827A (enrdf_load_stackoverflow) 1973-02-28 1974-02-28
US05/493,242 US3938911A (en) 1973-02-28 1974-07-31 Fuel injection pump with metering valve controlled cooling

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US336538A US3861833A (en) 1973-02-28 1973-02-28 Fuel injection pump

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US05/493,242 Division US3938911A (en) 1973-02-28 1974-07-31 Fuel injection pump with metering valve controlled cooling

Publications (1)

Publication Number Publication Date
US3861833A true US3861833A (en) 1975-01-21

Family

ID=23316553

Family Applications (1)

Application Number Title Priority Date Filing Date
US336538A Expired - Lifetime US3861833A (en) 1973-02-28 1973-02-28 Fuel injection pump

Country Status (11)

Country Link
US (1) US3861833A (enrdf_load_stackoverflow)
JP (1) JPS49117827A (enrdf_load_stackoverflow)
BR (1) BR7401293D0 (enrdf_load_stackoverflow)
CA (1) CA1000142A (enrdf_load_stackoverflow)
DE (1) DE2405452A1 (enrdf_load_stackoverflow)
ES (1) ES423702A1 (enrdf_load_stackoverflow)
FR (1) FR2219316B1 (enrdf_load_stackoverflow)
GB (2) GB1416120A (enrdf_load_stackoverflow)
IN (1) IN140149B (enrdf_load_stackoverflow)
IT (1) IT1008948B (enrdf_load_stackoverflow)
SE (1) SE396117B (enrdf_load_stackoverflow)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4002415A (en) * 1974-08-13 1977-01-11 C.A.V. Limited Distributor type fuel injection pumps
US4019835A (en) * 1974-07-19 1977-04-26 C.A.V. Limited Liquid fuel injection pumping apparatus
US4046494A (en) * 1975-08-20 1977-09-06 Stanadyne, Inc. Fuel injection pump and replaceable check valve therefor
US4067304A (en) * 1975-12-06 1978-01-10 Lucas Industries Limited Fuel pumping apparatus
US4073277A (en) * 1975-01-28 1978-02-14 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US4200067A (en) * 1978-05-01 1980-04-29 General Motors Corporation Hydraulic valve actuator and fuel injection system
US4201170A (en) * 1978-07-31 1980-05-06 Stanadyne, Inc. Fuel injection pump with positive displacement delivery valve having two port areas opened according to fuel flow rate
US4206728A (en) * 1978-05-01 1980-06-10 General Motors Corporation Hydraulic valve actuator system
US4329961A (en) * 1980-09-29 1982-05-18 General Motors Corporation Diesel injection pump timing control with electronic adjustment
US4329962A (en) * 1980-09-29 1982-05-18 General Motors Corporation Diesel injection pump timing control with eccentric cam pin
US4351283A (en) * 1981-05-01 1982-09-28 General Motors Corporation Diesel fuel injection pump secondary fuel metering control system
US4397615A (en) * 1980-07-26 1983-08-09 Lucas Industries Limited Fuel injection pumping apparatus
US4438747A (en) * 1981-05-28 1984-03-27 Lucas Industries Limited Fuel injection pumping apparatus
US4453522A (en) * 1980-04-28 1984-06-12 Stanadyne, Inc. Apparatus for adjusting the timing of a fuel injection pump
US4457277A (en) * 1981-04-23 1984-07-03 Lucas Industries Plc Fuel injection pumping apparatus
EP0113510B1 (en) * 1982-12-09 1988-01-07 General Motors Corporation Diesel fuel injection pump with adaptive torque balance control
US5178524A (en) * 1990-06-08 1993-01-12 Lucas Industries Fuel injection pump

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3968779A (en) * 1975-02-11 1976-07-13 Stanadyne, Inc. Fuel injection pump and injection control system therefor
US4100903A (en) * 1976-12-13 1978-07-18 Stanadyne, Inc. Rotary distributor fuel injection pump
GB8619991D0 (en) * 1986-08-16 1986-09-24 Lucas Ind Plc Fuel pumping apparatus
GB9315342D0 (en) * 1993-07-23 1993-09-08 Lucas Ind Plc Fuel pumping apparatus
DE4407617B4 (de) * 1994-03-08 2010-08-12 Robert Bosch Gmbh Kraftstoffeinspritzpumpe für Brennkraftmaschinen

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2975941A (en) * 1958-11-10 1961-03-21 Holley Carburetor Co Fuel metering and pumping device
US3058425A (en) * 1960-02-19 1962-10-16 Cav Ltd Liquid fuel pumps for internal combustion engines
US3319616A (en) * 1964-02-25 1967-05-16 Cav Ltd Liquid fuel pumps for use with internal combustion engines
US3509823A (en) * 1967-07-04 1970-05-05 Cav Ltd Liquid fuel pumping apparatus
US3536421A (en) * 1967-08-16 1970-10-27 Cav Ltd Liquid fuel pumping apparatus
US3603705A (en) * 1968-10-15 1971-09-07 Cav Ltd Check valves
US3664773A (en) * 1969-10-01 1972-05-23 Cav Ltd Liquid fuel injection pumping apparatus

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2975941A (en) * 1958-11-10 1961-03-21 Holley Carburetor Co Fuel metering and pumping device
US3058425A (en) * 1960-02-19 1962-10-16 Cav Ltd Liquid fuel pumps for internal combustion engines
US3319616A (en) * 1964-02-25 1967-05-16 Cav Ltd Liquid fuel pumps for use with internal combustion engines
US3509823A (en) * 1967-07-04 1970-05-05 Cav Ltd Liquid fuel pumping apparatus
US3536421A (en) * 1967-08-16 1970-10-27 Cav Ltd Liquid fuel pumping apparatus
US3603705A (en) * 1968-10-15 1971-09-07 Cav Ltd Check valves
US3664773A (en) * 1969-10-01 1972-05-23 Cav Ltd Liquid fuel injection pumping apparatus

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4019835A (en) * 1974-07-19 1977-04-26 C.A.V. Limited Liquid fuel injection pumping apparatus
US4002415A (en) * 1974-08-13 1977-01-11 C.A.V. Limited Distributor type fuel injection pumps
US4073277A (en) * 1975-01-28 1978-02-14 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
US4046494A (en) * 1975-08-20 1977-09-06 Stanadyne, Inc. Fuel injection pump and replaceable check valve therefor
US4067304A (en) * 1975-12-06 1978-01-10 Lucas Industries Limited Fuel pumping apparatus
US4200067A (en) * 1978-05-01 1980-04-29 General Motors Corporation Hydraulic valve actuator and fuel injection system
US4206728A (en) * 1978-05-01 1980-06-10 General Motors Corporation Hydraulic valve actuator system
US4201170A (en) * 1978-07-31 1980-05-06 Stanadyne, Inc. Fuel injection pump with positive displacement delivery valve having two port areas opened according to fuel flow rate
US4453522A (en) * 1980-04-28 1984-06-12 Stanadyne, Inc. Apparatus for adjusting the timing of a fuel injection pump
US4397615A (en) * 1980-07-26 1983-08-09 Lucas Industries Limited Fuel injection pumping apparatus
US4329961A (en) * 1980-09-29 1982-05-18 General Motors Corporation Diesel injection pump timing control with electronic adjustment
US4329962A (en) * 1980-09-29 1982-05-18 General Motors Corporation Diesel injection pump timing control with eccentric cam pin
US4457277A (en) * 1981-04-23 1984-07-03 Lucas Industries Plc Fuel injection pumping apparatus
US4351283A (en) * 1981-05-01 1982-09-28 General Motors Corporation Diesel fuel injection pump secondary fuel metering control system
US4438747A (en) * 1981-05-28 1984-03-27 Lucas Industries Limited Fuel injection pumping apparatus
EP0113510B1 (en) * 1982-12-09 1988-01-07 General Motors Corporation Diesel fuel injection pump with adaptive torque balance control
US5178524A (en) * 1990-06-08 1993-01-12 Lucas Industries Fuel injection pump

Also Published As

Publication number Publication date
JPS49117827A (enrdf_load_stackoverflow) 1974-11-11
ES423702A1 (es) 1977-01-16
DE2405452A1 (de) 1974-09-05
IT1008948B (it) 1976-11-30
FR2219316A1 (enrdf_load_stackoverflow) 1974-09-20
GB1416119A (en) 1975-12-03
BR7401293D0 (pt) 1974-12-03
FR2219316B1 (enrdf_load_stackoverflow) 1980-07-18
CA1000142A (en) 1976-11-23
SE396117B (sv) 1977-09-05
GB1416120A (en) 1975-12-03
IN140149B (enrdf_load_stackoverflow) 1976-09-18

Similar Documents

Publication Publication Date Title
US3861833A (en) Fuel injection pump
US4083345A (en) Fuel injection pump
US4449507A (en) Dual pressure metering for distributor pumps
US4662825A (en) Hydraulic pump
US3771506A (en) Fuel injection pump and automatic timing means therefor
US4079719A (en) Timing control for fuel pump
US4100903A (en) Rotary distributor fuel injection pump
US3938911A (en) Fuel injection pump with metering valve controlled cooling
US3848576A (en) Fuel injection pump for internal combustion engines
US2572118A (en) Fuel injector
US4537352A (en) Fuel injection apparatus
JPS59119056A (ja) 燃料噴射量制御装置
GB2275307A (en) I.c.engine high pressure distributor fuel injection system
US4667641A (en) Injection pump with radially mounted spill control valve
US4301777A (en) Fuel injection pump
US3204561A (en) Fuel pump
US3936232A (en) Fuel injection pumping apparatus with timing adjustment
US3494288A (en) Rotary distributor pump
US3494289A (en) Rotary distributor pump
US3433160A (en) Liquid fuel pumping apparatus
US4347818A (en) Externally controlled fuel delivery curve adjustment mechanism for a fuel injection pump
US3204622A (en) Fuel injection pump timing device
US3099219A (en) Self-regulating reciprocating piston pumps, in particular for the injection of fuel into internal combustion engines
US4046494A (en) Fuel injection pump and replaceable check valve therefor
US3489091A (en) Rotary distributor pump

Legal Events

Date Code Title Description
AS Assignment

Owner name: MANUFACTURERS HANOVER TRUST COMPANY, AS AGENT

Free format text: SECURITY INTEREST;ASSIGNOR:STANADYNE AUTOMOTIVE CORP.;REEL/FRAME:005046/0096

Effective date: 19890210

AS Assignment

Owner name: STANADYNE AUTOMOTIVE CORP., A CORP. OF DE, CONNECT

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:STANADYNE, INC.;REEL/FRAME:005130/0582

Effective date: 19890210

AS Assignment

Owner name: STANADYNE INC., CONNECTICUT

Free format text: RELEASE OF SECURITY INTEREST;ASSIGNOR:CHEMICAL BANK, AS SUCCESSOR IN INTEREST TO MANUFACTURERS HANOVER TRUST COMPANY;REEL/FRAME:007308/0169

Effective date: 19950201